US3659465A - Vibrating apparatus utilizing a plurality of vibrating sources - Google Patents

Vibrating apparatus utilizing a plurality of vibrating sources Download PDF

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US3659465A
US3659465A US3659465DA US3659465A US 3659465 A US3659465 A US 3659465A US 3659465D A US3659465D A US 3659465DA US 3659465 A US3659465 A US 3659465A
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vibrating
vibration
plurality
confronting
machines
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Goro Oshima
Shigeki Nishitake
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Yaskawa Electric Corp
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Yaskawa Electric Corp
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    • BPERFORMING OPERATIONS; TRANSPORTING
    • B65CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65GTRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G27/00Jigging conveyors
    • B65G27/34Jigging conveyors comprising a series of co-operating units
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B06GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06BMETHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00Machine element or mechanism
    • Y10T74/18Mechanical movements
    • Y10T74/18056Rotary to or from reciprocating or oscillating
    • Y10T74/18344Unbalanced weights

Abstract

A vibrating apparatus utilizing a plurality of vibrating sources, in which confronting massive bodies each including a rotary-type vibration-applying machine are distributed, through respective resonant resilient members such as springs, onto such a vibrating body to be vibrated as a conveyer, and said machines are operated in synchronous and in phased relation, whereby an extremely long vibrating-type conveyer which has not been possible has become practical, power output capacity of the apparatus is increased, and manufacture of a vibrating-type conveyer having a desired length can be made possible by connecting a plurality of unit conveyers.

Description

United States Patent Oshima et al.

451 May 2, 1972 [54] VIBRATING APPARATUS UTILIZING A PLURALITY OF VIBRATING SOURCES [72] Inventors: Goro' Oshima; Shigeld Nlshitake, both of Kitakyushu-shi, Japan [73] Assignee:

2,972,895 2/1961 Wilson ..74/61 3,053,379 9/1962 Rbder et al.. ..74/61 3,342,075 9/1967 Lowe ..74/6l 3,505,885 4/ 1970 Waschulewski et al ..74/6l Primary Examiner-Milton Kaufman Assistant Examiner-Wesley S. Ratliff, Jr. Attorney-Ward, Fitzpatrick et al.

[5 7] ABSTRACT A vibrating apparatus utilizing a plurality of vibrating sources, in which confronting massive bodies each including a rotarytype vibration-applying machine are distributed, through respective resonant resilient members such as springs, onto such a vibrating body to be vibrated as a conveyer, and said machines are operated in synchronous and in phased relation, whereby an extremely long vibrating-type conveyer which has not been possible has become practical, power output capacity of the apparatus is increased, and manufacture of a vibrating-type conveyer having a desired length can be made possible by connecting a plurality of unit conveyers.

3 Claims, 13 Drawing Figures 6 5 2 I l l u n 111-11L1 Mn A, XE,

i i 5 7 V 7 4 PATENTEDMM 2 I972 SHEET 1 OF 3 FIG.3

PATENTEUMM 2 I972 SHEET 2 OF 3 FIG.?

E S E M m m P OT E NS M O .0 A m i w m OL Y O 2 s n E O0 SAME PHASE E s A H P m E R E F m D DIRECTION IBRATING DIRECTION DIFFERENT PHASE FIG.8

SAME

PHASE PHASE V|BRAT|ON OFEFUH'ING POSITION SAME PHASE DIFFERENT PATENTEDMAY 21972 SHEET 3 OF 3 FIG;

FIG

FIG.

FIG. I3

VIBRATING APPARATUS UTILIZING A PLURALITY OF VIBRATING SOURCES BACKGROUND OF THE INVENTION The present invention relates to a vibrating apparatus in utilizing a plurality of vibrating sources.

A long conveyer to be vibrated and to which a plurality of magnetic vibrators are attached has been conventionally well known. In the conveyer mentioned above, since the magnetic vibrators are usually excited by the same electric source, vibration-applying forces generated by the respective magnetic vibrators are necessarily in synchronism and in phase.

The above-mentioned conveyer, however, has a disadvantage in that the vibration-applying force is relatively low and its capacity is limited in comparison with proposed system in which a vibration-applying force may be generated by means of a machine consisting of an eccentric weight and an induction motor for rotating said weight, said machine being referred to as a rotary type vibration-applying machine hereinafter.

Vibrating apparatus comprising a plurality of the rotary type vibration-applying machines have not yet been manufactured. The reason therefor resides in the fact that induction motors have a certain amount of slip with respect to their synchronous speed so that it is impossible to maintain a predetermined vibration-imparting direction; that is, the rotary positions of the eccentric weights cannot be maintained in synchronism or in phase. Accordingly, for the purpose of embodying practically a system in which a conventional long conveyer is vibrated by means of rotary-type vibration-applying machines, it has been usual to adapt a system of the type, in which large capacity type vibration-applying machines of a pair are provided and these machines are combined with a plurality of resonant springs or one of said machines is made to have a greater rigidity than the other machine, and these machines are coupled with a plurality of resonant springs, whereby two mass-vibrating systems are formed. However, the

vibrating apparatuses as mentioned above have various disadvantages. For example, their constructions are very complex, they are not suitable for standardization because of the necessity of designing individually the apparatus in accordance with the length of the conveyer, and it is impossible to intentionally adjust the length of the apparatus so as to be matched with a modification of a process in a fractory in which said vibrating apparatus is to be provided.

SUMMARY OF THE INVENTION Therefore, it is an essential object of the invention to provide a vibrating apparatus adapted for a particularly long conveyer and having no disadvantages of the conventional vibrating apparatuses.

The above and other objects of the invention have been attained by vibrating apparatus comprising a vibrating body like a conveyer, a plurality of confronting mass bodies which are distributively attached to said vibrating body through respective resonent resilient members, vibration-protecting device for supporting the apparatus on a stationary member, and rotary-type vibration-applying machines each comprising an induction motor and an eccentric weight, said machines being respectively possessed by said confronting mass bodies.

The foregoing objects as well as the characteristic features and functions of the invention will become apparent and more readily understandable by the following description when read in conjunction with the accompanying drawings, in which the same or equivalent members are designated by the same numerals and characters.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. I, 2 and 3 are schematic views showing vibrating apparatus according to the invention;

FIG. 4 is a side view of an example of the invention;

FIG. 5 is an enlarged view of a part of the example shown in FIG. 4;

FIG. 6 is a lateral view, in section along VI-VI in FIG. 5;

FIG. 7 (I), (II), (III) and (IV) are schematic views showing various resonant conditions of the vibrating apparatus according to the invention;

FIG. 8 is a characteristic curve of the vibrating apparatus according to the invention; and

FIGS. 9, 10, ll, 12 and 13 are schematic views for showing, respectively, other different examples of the invention.

DETAILED DESCRIPTION OF THE INVENTION In general, when several rotary-type vibrating machines are directly attached to a vibrating body, stable states of various modes are produced in accordance with various conditions such as rigidity, weight and natural vibrating frequency of the vibrating body, property of supporting spring, vibrating force applied to the vibrating body, and the like. For the sake of convenience, FIGS. 1 to 3 will be described in respect of a case in which two vibration-applying machines A and B are provided.

1. When, as shown in FIG. I, the weight of a vibrating body C is very large in comparison with the vibration-applying force applied to said the body C and rigidity of said body C is very large, two vibration-applying machines A and B are asynchrous to each other irrespective of their rotating directions and each of said machines rotates without relation to the other machine.

2. When, as shown in FIG. 2 the vibrating body C is small in its vibrating weight and large in its rigidity and the vibrating frequency of the vibration-applying force is larger than the natural vibrating frequency of the whole system, a synchronizing power due to the vibration is imparted upward and downward in the case when rotating directions of the vibration-applying machines A and B are mutually opposite thereby to cause synchronous rotations of said machines, but rotary phases of the machines are same in only the vertical direction and difi'erent by 180 in the horizontal direction, that is, in the direction so as to cancel mutually the forces applied from the machines in said direction, whereby only vertical vibration of the body C is generated.

3. In the case described in the above item (2), if the vibrating frequency of the vibration-applying force is extremely smaller than the natural vibrating frequency of the whole system, the synchronizing force due to the vibration is imparted to right and left directions thereby to cause synchronous rotations of the machines A and B, but rotary phases of the machines A and B are same in only the horizontal directions as shown in FIG. 3 and different by 180 in the vertical direction, whereby only horizontal vibration of the body C is generated.

4. In the case described in the above item (2), if the vibration-applying machines A and B are rotated in the same direction, a pendulum vibration center of which corresponds to the center of gravity of each machine is generally established, so that the machines A and B are synchronously rotated with a difference of 180 in their phases.

5. In the case described in the above item (2), the vibrationapplying machines A and B cannot be operated in synchronous and same-phased states. (According to the present invention, the vibration-applying machines A and B can be synchronously rotated with same phase as will be machines A and B, F represents the vibration-applying force of the vibration-applying machine, andI represents the inertia moment of the vibration mass. On the contrary, in the case of the item (5), the vibration becomes a circular vibration and the intensity thereof corresponds to ZF/W, where F represents the same force as described above and W represents weight of the vibration mass. Accordingly, if it be assumed that in both cases of the above items (4) and the weight of the vibration mass and vibration-applying forces caused by the vibration-applying machines A and B are the same, the following relation is established 2RF/I 2F/W. Accordingly, in the case of the item (5) the vibration intensity is larger and a larger vibration energy is required than the case in item (4).

As will be understoodfrom the cases of items (2) and (3), it is clear that the vibration state is stable where the vibration energy is minimum, so that vibration is not stable in the case of the item (5), but is stable in the case of the item (4).

In the present invention, the vibrating apparatus is constructed so that energy of pendulum vibration may be larger than the energy of circular vibration. That is, as shown in FIG. 3, the vibratiomapplying machines A and B are, respectively, mounted on the vibrating body C through respective resonant springs D and E. Now, let it be assumed that the vibration-applying machines A and B are rotated in the same direction at a speed corresponding to'a rotation near the natural vibrating frequency of the vibration system consisting of the machines A, B, the vibrating body C, and the resonant springs D, E. In this case, the machine A and B are brought into synchronous and stable states when their rotational phases are different by 180 from each other, compression, tension and bending moment are exerted onto vibrating body C, so that the generated energy should be relatively large. However, when the machines A and B are made to be synchronous and stable and in the same rotational phase, the immoderate stresses as mentioned above cannot generate, so that the energy required for the vibration of the system becomes minimum. That is, according to the construction as shown in FIG. 3, continuation of the stable operation of the system will be secured only when the vibration machines A and B are synchronously operated in the same rotational phase.

Referring to FIGS. 4, 5 and 6, the vibration system comprises a vibrating body 1 such as, for example, a vibrating trough consisting of a plurality of unit troughs each having a predetermined length, said unit troughs being fixedly connected to one another; a plurality of confronting massive bodies 3 each of which is connected with a respective unit trough through a resonant rubber spring 4; vibration-applying machines 5 each of which is attached to a respective massive body 3; plate-shaped springs 6 for regulating the vibration direction of the vibrating body, said springs acting to regulate the system so that the trough 1 and massive bodies 3 vibrate in the direction perpendicular to that of the plate-shaped springs; and vibration-protecting springs 7 which support the parts of the apparatus on a stationery member such as the ground. The vibration-applying machine 5 consists of an induction motor and an eccentric weight attached to an end of the shaft of said motor, so that a circular vibration-applying force is generated by driving said motor by application of an electric source thereto.

The example as illustrated in FIGS. 4, 5 and 6 constitutesa vibration system having four freedoms, in which the trough l and the confronting bodies each including the vibration-applying machine 5 are connected by means of the resonant springs 4. Since the members constituting said system have, respectively, their natural vibration frequencies, the vibration system is restricted by said frequencies, whereby the vibration-applying machines are operated in their synchronous and in-phased states or in their synchronous and out of-phased (about 120) states. Now, let it be assumed that the spring constant of each resonant spring 4, weights of each unit trough and the con-v fronting mass body 3, and vibration-applying force are constant. In this condition, if sequence and synchronous state of generation of the resonances are considered from that having the lowest vibration frequency, they become as shown in FIG. 7. That is, in the state of FIG. 7 (I), the whole parts of the trough l are subjected to upward and downward vibration owing to actions of the vibration-protecting springs, and in the state of FIG. 7 (II), the trough 1 is subjected to a vibration as shown in FIG. 7 (II) owing to the primary lateral natural frequency of the trough 1 itself. Further more, in the state of FIG. 7 (III), owing to the natural vibration frequency of the each confronting mass body 3 (including the vibration-applying machine 5), said mass body 3 vibrates in the arrow direction a and the trough 1 takes an almost stationary state; and in the state of FIG. 7 (IV), the trough 1 and the confronting mass bodies 3 are subjected respectively to their vibrations having their natural vibration frequencies in respective arrowdirections b and 0 having a certain angle (about 20 30) with respect to feeding direction of one material.

In FIG. 8, there are shown respective resonant states of the above-mentioned cases (I), (II), (III), and (IV). In embodying the examples according to the invention, it is preferable to separate the positions of the state (II) and (III) from that of the state (IV) as much as possible so as to avoid disturbance to be applied to operation of the apparatus. If the state (III) is near the state (IV), even when the electric source is switched on, the operation of the apparatus at the state (III) and a normal operation cannot be established. Furthermore, sometimes there is an operational need to vary the amplitude of the trough by varying rotational speed of the induction motor thereby to control feed quantity of the material. In this case also, if the operation stays at the state of (III), normal opera tion cannot be established, so that from thedesign point of view the positions of the cases (II), (III) should be selected toward the lower vibration frequency as much as possible.

The example shown in FIG. 9 relates to an apparatus, in which the unit troughs 2 are fixedly connected to one another and the confronting mass bodies 3 are fixedly connected to respective unit troughs, and mass bodies being attached to one another by means of respective resonant springs 4. Operation and effects of the example of FIG. 9 is the same as those of the example of FIG. 4 except that the confronting mass bodies 3 also are subjected to vibration together with the trough l. The confronting mass body 3 may be constructed so as to be of trough-shape, thereby to form a two-step conveyer. In this case, the direction of the feeding material is the same at the upper and lower positions.

The example of FIG. 10 relates to the case, in which the trough 1 and the confronting mass'bodies 3 are continuously unified so as to have no joint portions. Operation and effects of the example of FIG. 10 are the same as those of the example of FIG. 9, but the former example has an inconvenient disadvantage such that it is necessary to design anew the mass body 3 and the trough 1, depending upon required lengths of each of the mass bodies 3 and the trough l.

The example of FIG. 1] relates to the case, in which upper and lower troughs l and 11 are arranged so as to clamp the confronting mass bodies 3, said troughs and mass bodies are connected by means of resonant springs 4 and 14 respectively, the trough I and the confronting mass bodies 3are connected by means of plate-shaped springs 6 slanted leftward at an angle, and the trough I1 and the mass bodies 3 are connected by mass of plate-shaped springs 16 slanted rightward at an angle. According to the example of FIG. 11, when the vibration-applying machines are driven, the troughs l and 11 are subjected to different and inclined vibration, respectively, (the confrouting mass bodies 3 are made to vibrate in the horizontal direction), whereby the material is conveyed toward one side, for example, rightward by means of the trough 1 and the material can be conveyed toward the other side, for example, leftward by means of the trough 11. Accordingly, a simple and efiecient both-directional feeding conveyer can be obtained.

The example of FIG. 12 relates to the case, in which the vibration applying machine 5 is divided to an induction motor 5 and an eccentric weight 15a and the members are coupled by means of a belt. This example is particularly advantageous from the view point of securing maintenance of the bearings in the case of using vibrations-applying machines each having large capacity. The example of FIG. 13 relates to the case, in which the induction motor 15 is provided at a stationary position such as the ground, whereby more advantageous maintenance of the motor can be secured.

In all examples, if each of the vibration-applying machines has a mass required for the necessary vibration, the confronting mass bodies may be omitted.

According to the present invention, since as described above in detail, confronting mass bodies each including the rotary-type vibration-appling machine are distributed, through respective resonant resilient members such as springs, onto such a vibrating body to be vibrated as a conveyer and said machine are made to be operated in synchronous and samephased states, an extremely long vibrating-type conveyer is practically embodied. Furthermore, there is no limit in power capacity of the apparatus, and a vibrating-type conveyer having a desired length can be easily constructed by connecting a plurality of unit conveyers.

We claim:

1. A vibrating apparatus having a plurality of vibrating sources, comprising, in combination, an elongated body of indefinite length to be vibrated, a plurality of confronting massive bodies equidistantly spaced at a substantial distance apart one from the next adjacent one and attached to said body to be vibrated through respectively independent resonant springs and each comprising an induction motor and an eccentric weight driven by said induction motor; and a vibration protecting device for supporting the apparatus of a stationary member.

2. The vibrating apparatus according to claim 1, wherein a plurality of confronting massive bodies are firmly fixed to one another.

3. The vibrating apparatus according to claim 1, wherein a common confronting massive body is disposed on the center line of a pair of parallelly arranged vibrating bodies.

l i I i i

Claims (3)

1. A vibrating apparatus having a plurality of vibrating sources, comprising, in combination, an elongated body of indefinite length to be vibrated, a plurality of confronting massive bodies equidistantly spaced at a substantial distance apart one from the next adjacent one and attached to said body to be vibrated through respectively independent resonant springs and each comprising an induction motor and an eccentric weight driven by said induction motor; and a vibration protecting device for supporting the apparatus of a stationary member.
2. The vibrating apparatus according to claim 1, wherein a plurality of confronting massive bodies are firmly fixed to one another.
3. The vibrating apparatus according to claim 1, wherein a common confronting massive body is disposed on the center line of a pair of parallelly arranged vibrating bodies.
US3659465D 1968-11-09 1969-11-07 Vibrating apparatus utilizing a plurality of vibrating sources Expired - Lifetime US3659465A (en)

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Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4149627A (en) * 1977-07-01 1979-04-17 Vibranetics, Inc. Vibratory conveyor improvement
US4212731A (en) * 1977-07-13 1980-07-15 Morgardshammar Aktiebolag Drive device without transmission for producing an elliptical shaking movement
US4611709A (en) * 1979-07-02 1986-09-16 General Kinematics Vibratory conveyor
US5056652A (en) * 1979-07-02 1991-10-15 General Kinematics Corporation Vibratory conveyor
US5094342A (en) * 1979-07-02 1992-03-10 General Kinematics Corporation Vibratory conveyor
US6024210A (en) * 1997-12-04 2000-02-15 Rosenstrom; Bo Richard Electrically coupled multiple shaft drive system for vibrating equipment
US6253908B1 (en) * 1998-01-08 2001-07-03 Allen Machinery, Inc. Vibratory conveyor
US6325202B1 (en) 1999-11-22 2001-12-04 Fmc Corporation Interconnection for a conveyor system
US20050023111A1 (en) * 1999-07-30 2005-02-03 Dumbaugh George D. Vibratory conveying apparatus adapted to be driven by accumulatively phased rotating eccentric weights
US6851548B1 (en) 1999-07-30 2005-02-08 Kinergy Corporation Vibratory conveying apparatus adapted to be driven by a plurality of accumulatively phased pairs of rotating eccentric weights
US20050242003A1 (en) * 2004-04-29 2005-11-03 Eric Scott Automatic vibratory separator
US20050242009A1 (en) * 2004-04-29 2005-11-03 Norman Padalino Vibratory separator with automatically adjustable beach
US20050242002A1 (en) * 2004-04-29 2005-11-03 Lyndon Stone Adjustable basket vibratory separator
US20060243643A1 (en) * 2002-11-06 2006-11-02 Eric Scott Automatic separator or shaker with electromagnetic vibrator apparatus
US20100235002A1 (en) * 2002-11-06 2010-09-16 National Oilwell Varco, L.P. Magnetic Vibratory Screen Clamping
US20110067633A1 (en) * 2008-01-23 2011-03-24 Correa Rafael S Vibration mechanism for vertical egg alignment prior to in-ovo injection
US8316557B2 (en) 2006-10-04 2012-11-27 Varco I/P, Inc. Reclamation of components of wellbore cuttings material
US8556083B2 (en) 2008-10-10 2013-10-15 National Oilwell Varco L.P. Shale shakers with selective series/parallel flow path conversion
US8622220B2 (en) 2007-08-31 2014-01-07 Varco I/P Vibratory separators and screens
US8733540B2 (en) * 2012-10-10 2014-05-27 Key Technology, Inc. Excited frame vibratory conveyor
US9073104B2 (en) 2008-08-14 2015-07-07 National Oilwell Varco, L.P. Drill cuttings treatment systems
US9079222B2 (en) 2008-10-10 2015-07-14 National Oilwell Varco, L.P. Shale shaker
US9643111B2 (en) 2013-03-08 2017-05-09 National Oilwell Varco, L.P. Vector maximizing screen
CN107161540A (en) * 2017-06-01 2017-09-15 大唐东北电力试验研究所有限公司 A kind of plastid motor synchronizing resonance pendulum vibrating system of twin-engined drives three

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3837686A1 (en) * 1988-11-05 1990-05-10 Willi Bayer Three-dimensional oscillation system

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2200724A (en) * 1937-01-18 1940-05-14 Samuel D Robins Means for producing gyratory motion
US2972895A (en) * 1958-08-07 1961-02-28 Hewitt Robins Inc Vibrating means for screens and the like
US3053379A (en) * 1956-06-21 1962-09-11 Schenck Gmbh Carl Material handling vibrating machine
US3342075A (en) * 1965-02-23 1967-09-19 Missouri Rogers Corp Vibrating mechanism
US3505885A (en) * 1968-03-12 1970-04-14 Losenhausen Maschinenbau Ag Vibration generators

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2200724A (en) * 1937-01-18 1940-05-14 Samuel D Robins Means for producing gyratory motion
US3053379A (en) * 1956-06-21 1962-09-11 Schenck Gmbh Carl Material handling vibrating machine
US2972895A (en) * 1958-08-07 1961-02-28 Hewitt Robins Inc Vibrating means for screens and the like
US3342075A (en) * 1965-02-23 1967-09-19 Missouri Rogers Corp Vibrating mechanism
US3505885A (en) * 1968-03-12 1970-04-14 Losenhausen Maschinenbau Ag Vibration generators

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4149627A (en) * 1977-07-01 1979-04-17 Vibranetics, Inc. Vibratory conveyor improvement
US4212731A (en) * 1977-07-13 1980-07-15 Morgardshammar Aktiebolag Drive device without transmission for producing an elliptical shaking movement
US4611709A (en) * 1979-07-02 1986-09-16 General Kinematics Vibratory conveyor
US5056652A (en) * 1979-07-02 1991-10-15 General Kinematics Corporation Vibratory conveyor
US5094342A (en) * 1979-07-02 1992-03-10 General Kinematics Corporation Vibratory conveyor
US6024210A (en) * 1997-12-04 2000-02-15 Rosenstrom; Bo Richard Electrically coupled multiple shaft drive system for vibrating equipment
US6253908B1 (en) * 1998-01-08 2001-07-03 Allen Machinery, Inc. Vibratory conveyor
US6948611B2 (en) 1999-07-30 2005-09-27 Kinergy Corporation Vibratory conveying apparatus adapted to be driven by accumulatively phased rotating eccentric weights
US20050023111A1 (en) * 1999-07-30 2005-02-03 Dumbaugh George D. Vibratory conveying apparatus adapted to be driven by accumulatively phased rotating eccentric weights
US6851548B1 (en) 1999-07-30 2005-02-08 Kinergy Corporation Vibratory conveying apparatus adapted to be driven by a plurality of accumulatively phased pairs of rotating eccentric weights
US6325202B1 (en) 1999-11-22 2001-12-04 Fmc Corporation Interconnection for a conveyor system
US8746459B2 (en) 2002-10-17 2014-06-10 National Oilwell Varco, L.P. Automatic vibratory separator
US20090242466A1 (en) * 2002-10-17 2009-10-01 George Alexander Burnett Automatic Vibratory Separator
US8561805B2 (en) 2002-11-06 2013-10-22 National Oilwell Varco, L.P. Automatic vibratory separator
US20060243643A1 (en) * 2002-11-06 2006-11-02 Eric Scott Automatic separator or shaker with electromagnetic vibrator apparatus
US8312995B2 (en) 2002-11-06 2012-11-20 National Oilwell Varco, L.P. Magnetic vibratory screen clamping
US20100235002A1 (en) * 2002-11-06 2010-09-16 National Oilwell Varco, L.P. Magnetic Vibratory Screen Clamping
US20080128334A1 (en) * 2002-11-06 2008-06-05 Eric Landon Scott Automatic vibratory separator
US8695805B2 (en) 2002-11-06 2014-04-15 National Oilwell Varco, L.P. Magnetic vibratory screen clamping
US7571817B2 (en) 2002-11-06 2009-08-11 Varco I/P, Inc. Automatic separator or shaker with electromagnetic vibrator apparatus
US20050242002A1 (en) * 2004-04-29 2005-11-03 Lyndon Stone Adjustable basket vibratory separator
US20050242003A1 (en) * 2004-04-29 2005-11-03 Eric Scott Automatic vibratory separator
US7278540B2 (en) 2004-04-29 2007-10-09 Varco I/P, Inc. Adjustable basket vibratory separator
US20050242009A1 (en) * 2004-04-29 2005-11-03 Norman Padalino Vibratory separator with automatically adjustable beach
US7331469B2 (en) 2004-04-29 2008-02-19 Varco I/P, Inc. Vibratory separator with automatically adjustable beach
US8533974B2 (en) 2006-10-04 2013-09-17 Varco I/P, Inc. Reclamation of components of wellbore cuttings material
US8316557B2 (en) 2006-10-04 2012-11-27 Varco I/P, Inc. Reclamation of components of wellbore cuttings material
US8622220B2 (en) 2007-08-31 2014-01-07 Varco I/P Vibratory separators and screens
US20110067633A1 (en) * 2008-01-23 2011-03-24 Correa Rafael S Vibration mechanism for vertical egg alignment prior to in-ovo injection
US9073104B2 (en) 2008-08-14 2015-07-07 National Oilwell Varco, L.P. Drill cuttings treatment systems
US8556083B2 (en) 2008-10-10 2013-10-15 National Oilwell Varco L.P. Shale shakers with selective series/parallel flow path conversion
US9079222B2 (en) 2008-10-10 2015-07-14 National Oilwell Varco, L.P. Shale shaker
US9677353B2 (en) 2008-10-10 2017-06-13 National Oilwell Varco, L.P. Shale shakers with selective series/parallel flow path conversion
US8733540B2 (en) * 2012-10-10 2014-05-27 Key Technology, Inc. Excited frame vibratory conveyor
US9643111B2 (en) 2013-03-08 2017-05-09 National Oilwell Varco, L.P. Vector maximizing screen
CN107161540A (en) * 2017-06-01 2017-09-15 大唐东北电力试验研究所有限公司 A kind of plastid motor synchronizing resonance pendulum vibrating system of twin-engined drives three

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