US3892308A - Control of reversible vibratory equipment - Google Patents
Control of reversible vibratory equipment Download PDFInfo
- Publication number
- US3892308A US3892308A US375786A US37578673A US3892308A US 3892308 A US3892308 A US 3892308A US 375786 A US375786 A US 375786A US 37578673 A US37578673 A US 37578673A US 3892308 A US3892308 A US 3892308A
- Authority
- US
- United States
- Prior art keywords
- absorbers
- pressure
- vibration
- work member
- vibratory
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G27/00—Jigging conveyors
- B65G27/10—Applications of devices for generating or transmitting jigging movements
- B65G27/32—Applications of devices for generating or transmitting jigging movements with means for controlling direction, frequency or amplitude of vibration or shaking movement
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G27/00—Jigging conveyors
- B65G27/10—Applications of devices for generating or transmitting jigging movements
- B65G27/16—Applications of devices for generating or transmitting jigging movements of vibrators, i.e. devices for producing movements of high frequency and small amplitude
- B65G27/18—Mechanical devices
- B65G27/20—Mechanical devices rotating unbalanced masses
Definitions
- ABSTRACT A resiliently supported vibratory conveyor or processing unit is equipped with a plurality of tunable dynamic vibration absorbers and controls so that the vibratory response of the unit to the centrifugal force of rotating eccentric weights joumalled in the unit may be varied from a minimum to a maximum amplitude along either of a pair of oppositely inclined paths of movement.
- a resiliently mounted conveyor or processing unit driven by rotating eccentric weights is provided with at least two sets of tunable dynamic vibration absorbers that may be selectively tuned to either oppose or aid the eccentric weights in producing vibration of the conveyor or unit along either of a pair of axes.
- a processing unit operating according to the invention is illustrated in the drawings.
- FIG. 1 is a schematic side elevation of a processing unit and the controls for tuning the absorbers.
- FIG. 2 is a graph showing the relationship between the inflation pressure and the amplitudes of vibration of the work member and absorber members.
- a vibratory conveyor or processing unit that may be vibrated to convey material in either direction to either discharge material or level the material in the unit may comprise a container or trough constituting a work member 1 that is elastically supported for vibration on a plurality of vibration isolators in the form of air springs 2.
- the work member is vibrated by eccentric weights 3 mounted on a shaft 4 journalled in the work member 1.
- the shaft 4 may be the rotor shaft of a motor for direct drive or it may be belt driven from a motor 5 mounted on the work member.
- the shaft 4 is located near the center of gravity of the work member. Without absorbers, to be described, the work member would vibrate in a generally circular orbit in response to the centrifugal force of the eccentric weights 3.
- the direction and amplitude of vibration of the work member I in response to the centrifugal force of the eccentric weights 3 is controlled by a plurality of tunable dynamic vibration absorbers 6, 7, 8 and 9.
- Each of the absorbers comprise a mass of vibrating weight 10 that is guided with respect to the work member by rocker arms 11 connected between the weight and work memher I.
- the motion of the weight 10 is controlled by a pair of air springs 12, the spring rate of which may be adjusted by adjustment of the inflation pressure of the air springs.
- the air springs 12 are arranged on opposite sides of the weight 10 so that the springs oppose each other insofar as static pressures and forces are concerned.
- the effective spring rate of the pair urging the weight I0 to the center of its path of movement is the sum of the individual spring rates.
- the absorbers are arranged in pairs, the members of each pair being generally equidistant from the center of gravity of the work member 1.
- the absorbers 6 and 9 form one pair adapted to vibrate along a path inclined upwardly toward the left.
- the absorbers 7 and 8 form a second pair adapted to vibrate along a path inclined upwardly toward the right.
- one pair of absorbers such as the pair 6 and 9 are tuned so that the weights 10 in combination with the springs 12 are resonant at the operating speed of the eccentric weights, the weights vibrate at such amplitude and phase as to practically counterbalance the force of the eccentric weights in the direction of vibration of the weights. Thus, there is little or no vibration of the work member in that direction.
- the other pair of absorbers 7 and 8 are tuned so that work member 1 as one member and the weights 10 of the absorbers 7 and 8 as the other member and the cooperating air springs form a two mass vibratory system that is resonant near the operating speed, preferably just below the operating speed.
- the weights 10 of the absorbers 7 and 8 vibrate in phase with the eccentric weights 3 to reinforce or augment the force of the eccentric weights to increase the vibration of the work member along the path of vibration of the weights 10 of the absorbers 7 and 8.
- the amount of reinforcement of the force may be varied to vary the amplitude of vibration of the work member.
- the relation between the amplitude and phase of vibration of the work member and absorber weights with relation to the eccentric weights is shown in the graph, FIG. 2.
- the inflation pressure is low, at the left in the figure, the resonant frequency is low, the work member I vibrates at an amplitude X1 while the weights l0 vibrate at an amplitude X2.
- the amplitude of vibration XI of the work member is about twice that obtained without any absorbers.
- a further increase in pressure raises the natural frequency until at a pressure P2 the amplitude of vibration of the work member I becomes practically zero.
- the absorbers 6, 7, 8, and 9 are arranged in pairs acting along different paths, it is possible to select both the direction of vibration (direction of vibratory conveying) and the amplitude of vibration by inflating the several air springs to the proper pressures. Although a working amplitude of vibration may be obtained with inflation pressures above or below the pressure Pr for resonance, one must tune much closer to resonance when operating on the high pressure side of resonance. Thus, for stability it is desirable to operate at the lower pressures when vibrating the work member 1.
- the pressure P2 for vibration suppression and the preferred pressure PI for increased or working amplitude of vibration are separated by the pressure Pr at resonance, and since the system may be self destructive at resonance one cannot reverse the direction of vibration while the eccentric weights are rotating at full speed. Furthermore, since at the desired operating pressure Pl, the operating frequency is just above the resonant frequency of the system, it is practically impossible to accelerate the eccentric weights through the resonant frequency. Therefore, in a practical system it is necessary to inflate the air springs of those absorbers that are to suppress vibration of the work member 1 to the pressure P2 while reducing the pressure in the other air springs to a pressure much lower than the working pressure P1 before starting the motor 5. Once the motor 5 is running and the eccentric weights 3 are rotating at the operating frequency the low pressure air springs may be inflated to the working pressure P1.
- the control equipment to properly inflate the air springs for vibratory conveying in either direction is illustrated in the lower part of FIG. 1. As shown this equipment comprises a connecting 20 to a source of compressed air, a primary pressure regulator 21 pressure gage 22 and filter 23 to supply clean air under pressure to an air supply manifold 24.
- air is supplied through pressure regulators, needle valves and three way valves to the air springs of the several absorbers 6, 7, 8 and 9.
- the air pressure in the air springs of absorbers 6 and 9 is set at pressure P2 while the pressure in absorbers 7 and 8 is set near pressure Pl.
- the supply line 24 is connected through pressure regulator 25 (set to pressure P2) and needle valve 26 to pressure line 27 and through three way reversing valves 28 and 29 and lines 30 and 31 to the springs of absorbers 6 and 9.
- absorbers 7 and 8 are pressurized through lines 32 and 33 respectively connected through reversing valves 34 and 35, and start up valves 36, 37 to lines 38, 39 controlled by pressure regulators 40, 41 and needle valves 42, 43. All of the needle valves are supplied to control the rate at which the pressures may be changed.
- the pressure regulators 40 and 41 set the pressures in the absorbers 7 and 8 at pressure Pl (FIG. 2) to control the amplitudes of vibration. Individual regulators are used to permit fine adjustment of the tuning to compensate for variations in the air springs and other components of the system.
- solenoid valve 44 is energized so that line pressure from line 24 is applied through valve 44 to the actuators of start up valves 36, 37, 45 and 46 and these valves connect lines 38 and 39 to the reversing valves.
- the valves 36, 37, 45, and 46 are in the positions shown so that a low pressure controlled by pressure regulator 47 is applied to the air springs of absorbers 7 and 8.
- Pressure switches 48, 49, 50 are connected to each of the controlled pressure lines and included in the electrical start and run controls of the motor to prevent starting and to stop the motor in the event improper pressures exist in the related lines.
- solenoid operated valve 51 is energized to supply pressure to the operators of the reverse valves 28, 29, 34, and 35. This has the effect of applying pressure P2 from line 27 to the air springs of absorbers 7 and 8 while connecting lines 30 and 31 of absorbers 6 and 9 through start up valves 45 and 46 to lines 52, 53 controlled by pressure regulators 54, 55.
- the operation for the reverse direction of conveying is then as previously described for operation in the forward direction of conveying.
- these isolators are inflated through a line 56 controlled by a pressure regulator 57 and monitored by a pressure switch 58 arranged to stop the motor 5 in the event of loss of inflation pressure,
- the arrangement of the various sets of absorbers on a work member subjected to centrifugal force of rotating eccentric weights allows the direction and amplitude of vibration to be readily selected and controlled by variation in air pressure in the springs of the absrohers.
- a method of controlling the vibration of an elastically supported work member in response to vibratory force of rotating eccentric weights journalled in the member and equipped with tunable dynamic absorbers arranged in sets each operative along a particular path comprises, tuning a first set of said absorbers to oppose motion of said work member along a first path and simultaneously tuning a second set of said absorbers to form a two mass vibratory system to control the amplitude of the vibratory motion of said work member along a second path.
- each of said absorbers includes air springs the inflation pressure of which is varied to tune the absorber.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
- Vibration Prevention Devices (AREA)
Abstract
Description
Claims (4)
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US375786A US3892308A (en) | 1971-11-22 | 1973-07-02 | Control of reversible vibratory equipment |
GB2400574A GB1465327A (en) | 1973-07-02 | 1974-05-30 | Control fo reversible vibratory equipment |
AU69813/74A AU493852B2 (en) | 1974-06-05 | Reversible vibratory equipment | |
DE2427907A DE2427907C2 (en) | 1973-07-02 | 1974-06-10 | Device for adjusting the vibrations of a component that is driven to vibrate |
CA202,254A CA1017971A (en) | 1973-07-02 | 1974-06-12 | Control of reversible vibratory equipment |
ZA00743775A ZA743775B (en) | 1973-07-02 | 1974-06-13 | Control of reversible vibratory equipment |
JP49076228A JPS5760243B2 (en) | 1973-07-02 | 1974-07-02 | |
BE146152A BE817175A (en) | 1973-07-02 | 1974-07-02 | PROCEDURE FOR ORDERING A REVERSIBLE VIBRATING EQUIPMENT |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US20089271A | 1971-11-22 | 1971-11-22 | |
US375786A US3892308A (en) | 1971-11-22 | 1973-07-02 | Control of reversible vibratory equipment |
Publications (1)
Publication Number | Publication Date |
---|---|
US3892308A true US3892308A (en) | 1975-07-01 |
Family
ID=26896201
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US375786A Expired - Lifetime US3892308A (en) | 1971-11-22 | 1973-07-02 | Control of reversible vibratory equipment |
Country Status (1)
Country | Link |
---|---|
US (1) | US3892308A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5713457A (en) * | 1995-12-06 | 1998-02-03 | General Kinematics Corporation | Two-way vibratory feeder or conveyor |
GB2347131A (en) * | 1999-02-26 | 2000-08-30 | Leslie Neville Reeves | Bi-directional vibratory conveyor |
US20160089697A1 (en) * | 2012-03-30 | 2016-03-31 | Burkhard SCHMITT | Screening machine for screening or refining gravel, sand or the like |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3068996A (en) * | 1961-06-27 | 1962-12-18 | Chain Belt Co | Reversible vibratory feeder |
US3253701A (en) * | 1964-03-11 | 1966-05-31 | Rex Chainbelt Inc | Bidirectional variable rate feeder |
-
1973
- 1973-07-02 US US375786A patent/US3892308A/en not_active Expired - Lifetime
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3068996A (en) * | 1961-06-27 | 1962-12-18 | Chain Belt Co | Reversible vibratory feeder |
US3253701A (en) * | 1964-03-11 | 1966-05-31 | Rex Chainbelt Inc | Bidirectional variable rate feeder |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5713457A (en) * | 1995-12-06 | 1998-02-03 | General Kinematics Corporation | Two-way vibratory feeder or conveyor |
GB2347131A (en) * | 1999-02-26 | 2000-08-30 | Leslie Neville Reeves | Bi-directional vibratory conveyor |
GB2347131B (en) * | 1999-02-26 | 2002-07-31 | Leslie Neville Reeves | Bi-directional vibratory conveyor |
US20160089697A1 (en) * | 2012-03-30 | 2016-03-31 | Burkhard SCHMITT | Screening machine for screening or refining gravel, sand or the like |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: REXNORD INC., 3500 FIRST WISCONSIN CENTER, MILWAUK Free format text: SECURITY INTEREST;ASSIGNOR:CARRIER VIBRATING EQUIPMENT, INC.;REEL/FRAME:004176/0589 Effective date: 19830831 Owner name: COUNTY OF JEFFERSON, KENTUCKY, THE POLITICAL SUB Free format text: SECURITY INTEREST;ASSIGNOR:CARRIER VIBRATING EQUIPMENT, INC.;REEL/FRAME:004176/0589 Effective date: 19830831 Owner name: FIRST NATIONAL BANK OF LOUISVILLE, 101 SOUTH FIFTH Free format text: SECURITY INTEREST;ASSIGNOR:CARRIER VIBRATING EQUIPMENT, INC.;REEL/FRAME:004176/0589 Effective date: 19830831 Owner name: CARRIER VIBRATING EQUIPMENT INC 3400 FERN VALLEY R Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:REXNORD INC;REEL/FRAME:004167/0676 Effective date: 19830831 |