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WO2006125998A1 - Transporteur vibrant - Google Patents

Transporteur vibrant Download PDF

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Publication number
WO2006125998A1
WO2006125998A1 PCT/GB2006/001929 GB2006001929W WO2006125998A1 WO 2006125998 A1 WO2006125998 A1 WO 2006125998A1 GB 2006001929 W GB2006001929 W GB 2006001929W WO 2006125998 A1 WO2006125998 A1 WO 2006125998A1
Authority
WO
WIPO (PCT)
Prior art keywords
conveying member
base
vibratory
absorbing mass
conveying
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.)
Ceased
Application number
PCT/GB2006/001929
Other languages
English (en)
Inventor
Timothy John Blackwall Moulsdale
Ran Mendelewicz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wright Machinery Ltd
Original Assignee
Wright Machinery Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Wright Machinery Ltd filed Critical Wright Machinery Ltd
Publication of WO2006125998A1 publication Critical patent/WO2006125998A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • B65G27/28—Applications of devices for generating or transmitting jigging movements with provision for dynamic balancing
    • 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
    • B65G27/28—Applications of devices for generating or transmitting jigging movements with provision for dynamic balancing
    • B65G27/30—Applications of devices for generating or transmitting jigging movements with provision for dynamic balancing by means of an oppositely-moving mass, e.g. a second conveyor

Definitions

  • the present invention relates to a conveying apparatus, and particularly to an excited-conveyor vibratory conveying apparatus.
  • Vibratory conveying systems are often used to transport objects or particulate material and are in widespread use in view of their versatile material-handling capabilities.
  • Such devices typically include a generally elongate conveying member that is vibrated by an associated drive system so that material is conveyed along the length of the conveying member.
  • a vibratory device is connected to a support frame to excite or vibrate the support frame, with the vibrations being transferred to the conveying member through springs.
  • Such systems are known as two-mass vibratory conveyor systems or excited frame vibratory systems.
  • a two-mass, vibratory conveyor of the base-excited conveyor design includes a trough supported by springs from a base support structure that is vibrated by an eccentric rotating mass. The vibration is transmitted to the trough through the springs.
  • a known approach to reducing vibratory movement of the base structure has been to make the base structure very substantially heavier than the conveying member.
  • US 2001/0019009 Al also discloses a base-excited conveyor arranged such that centres of gravity of the conveyor-bed mass, the conveyor mass, and the base mass are co-linear with the force drive line, as taught by Carmichael.
  • US 2001/0019009 discloses the use of an electromagnetic drive that eliminates the transients occurring during start-up and shutdown of the conveyor.
  • a conveyer system with a conveying tray and a counter mass is disclosed in United States Patent No. 5,462,155.
  • the conveying tray and the mass are driven in opposing directions and are physically constrained to vibrate reciprocally by a coupler which is provided between the tray and the mass.
  • US 3,668,939 proposes a vibratory conveyor comprising a set of counter- masses mounted from the base, the counter-masses being designed to resonate at the frequency of a force driving the conveying system.
  • the invention provides a vibratory conveying apparatus for moving materials, comprising: a base; a conveying member supported from the base by at least one resilient support; a drive arranged to excite said conveying member into vibration; and an absorbing mass supported from the base by at least one resilient support such that movement of the absorbing mass is substantially parallel to that of the conveying member, and that a line passing through the absorbing mass' centre of gravity and the conveying member's centre of gravity is substantially perpendicular to the at least one resilient conveying member support, wherein the natural frequency of the absorbing mass is arranged to be substantially equal to the natural frequency of the conveying member, or a multiple thereof, whereby when the conveying member is excited into vibration by the drive, the absorbing mass vibrates substantially in phase opposition to the conveying member, resulting in the absorption of energy from the base.
  • a significant advantage of the invention is that vibration of the base can be substantially reduced without needed a massive base, whereby the mass of the conveyor base can be reduced so as to reduce costs.
  • the vibratory conveying apparatus can transfer less vibration into the floor or ceiling supports.
  • the absorber mass may be arranged to vibrate with a natural frequency that is substantially equal to a multiple of the conveying member's natural frequency, the multiple being 10 or less, preferably 5 or less, and most preferably 3 or less.
  • the absorber mass can be arranged such that a line passing through the absorbing mass' centre of gravity and the conveying member's centre of gravity is substantially perpendicular to the at least one resilient conveying member support.
  • the resilient supports may be of any such suitable form for supporting the conveying member or the absorbing mass.
  • a suitable resilient support is a spring that restricts movement of the conveying member to a generally single plane.
  • the resilience or stiffness of the spring may be adjustable so that the natural frequency of the conveying member or the absorbing mass can be altered as required.
  • the base of the vibratory conveying apparatus may be supported from a mounting frame via vibration isolators. This helps to further reduce any vibratory forces that may act on the floor or ceiling that supports the vibratory conveying apparatus.
  • the drive may be an electromagnetic drive. Unlike mechanical drives such as counter rotating mass drives, an electromagnetic drive does not have a transient stage and can be operated at a required frequency immediately. Use of an electromagnetic drive also enables the operation of the conveying apparatus to be more easily controlled.
  • the resilient absorbing mass supports may be made from the same non-elastometric material as the resilient conveying member supports.
  • the base will generally be arranged such that it has a natural frequency that is different from the natural frequency of the conveying member and its supporting springs. Such an arrangement further avoids unwanted vibrations and movement of the base by reducing the possibility that vibratory forces exerted upon the base by the vibration of the conveying member may excite it.
  • Figure 1 is a perspective view of an exemplary embodiment of a vibratory conveyor according to the invention.
  • FIG. 2 is a schematic diagram of the vibratory conveying apparatus shown in Figure 1 ;
  • Figure 3 is an illustration of the relationship between the centres of gravity and the resilient supports for conveying apparatus shown in Figure 1 ;
  • FIG. 4 is a diagram of a vibratory conveyor according to an alternative embodiment of the invention. While the present invention is susceptible of embodiment in various forms, there is described and shown in the drawings presently preferred embodiments. These embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. Like reference numerals refer to like elements throughout.
  • a vibratory conveying apparatus 10 is supported by a base 12.
  • the base 12 is an elongate frame generally extending in an intended direction of movement of material from a rear end 14 to a front end 16.
  • the vibratory conveying apparatus 10 includes an elongate conveying member or tray 18 that extends between a rear end 20 and a front end 22.
  • the conveying member 18 includes a conveying bed 24 for receiving material to be moved.
  • the conveying bed 24 includes side-walls 26 that extend between the rear end 20 and the front end 22.
  • the conveying bed 24 supports the material as it is being conveyed from the rear end 20 to the front end 22.
  • the conveying member 18 is mounted via a resilient support (not visible) to the base 12.
  • the resilient support may comprise beam springs or leaf springs to enable the conveying member 18 to move in a generally forward and rearward reciprocating motion with respect to the base 12.
  • the vibratory conveying apparatus 10 includes a vibratory drive means (not shown) for vibrating the conveying member 18 in the intended direction of conveying.
  • An absorbing mass (not visible) is mounted via at least one resilient support (not visible) to the base 12 such that the movement of the absorbing mass is parallel to the movement of the conveying member 18.
  • the conveying member 18 is vibrated by the vibratory drive means with the material progressively moving from the rear end 20 to the front end 22.
  • the absorbing mass also vibrates to counteract the vibration of the conveying member 18, resulting in the absorption of energy from the base.
  • the absorbing mass and its resilient support can have the same natural frequency as the conveying member 18 (and its resilient members), the absorbing mass can vibrate out of phase with the conveying member 18 in order to minimise the forces transmitted to the base 12.
  • FIG. 2 a schematic diagram of the vibratory conveying apparatus 10 of Figure 1 is shown.
  • the base 12 of the vibratory conveying apparatus 10 is supported via vibration isolators 28 from stationary supports 30 and has a known centre of gravity 32.
  • the stationary supports 30 are attached to the floor, although alternatively the conveying apparatus 10 may be mounted to an upper support, such as a ceiling.
  • the vibration isolators 28 are resilient support means for absorbing vertical vibratory forces and may be of any such suitable form, such as rubber mounts or hydraulic dampers for example.
  • the resilient supports 34 are spaced apart along the length of the conveying member 18, at each side, and across the width if required.
  • the supports 34 are arranged to enable the conveying member 18 to undergo vibrational movement in a generally forward and rearward reciprocating motion with respect to the base 12.
  • the resilient supports 34 are attached with suitable fasteners between the supports 34 and the base 12.
  • the length, thickness and number of the resilient supports 34, leaf springs for example, may be varied to adjust the total equivalent resilience or stiffness K with which the conveying member 18 is supported.
  • the resilient supports 34 are at a slight incline angle with respect to the longitudinal direction of the base 12 such that support angle between the resilient supports 34 and the longitudinal direction of the base 12 is less than ninety degrees.
  • the angle between the resilient supports 34 and the longitudinal direction of the base 12 may be seventy degrees (70°).
  • the conveying member 18 has a known mass M and a centre of gravity 36.
  • the mass of the resilient supports 34 is usually negligible compared to the conveying member 18.
  • the conveying member's centre of gravity 36 may also include a fraction of the weight of the resilient supports 34.
  • a vibratory drive 38 is connected to the base 12 and the conveying member 18 for causing vibratory motion of the conveying member 18 in the intended plane.
  • the vibratory drive 38 preferably comprises an electromagnetic drive 38a and an armature 38b, as opposed to a mechanical drive.
  • the electromagnetic drive 38a connected to the base 12 applies an electromagnetic force to the armature 38b connected to the conveying member 18 to excite the conveying member 18 into motion.
  • the electromagnetic drive 38a is adapted such that it applies the electromagnetic force at a frequency substantially equal to the natural frequency of the conveying member 18 and its resilient supports 32.
  • An absorbing mass 40 which may be simply a block of material such as steel, for example, is mounted via a plurality of resilient supports 42 to the base 12.
  • the resilient supports 42 are spaced apart longitudinally along both sides of the absorbing mass 40 and parallel to the conveying member's resilient supports 34 such that the absorbing mass 40 to undergoes vibrational movement parallel to the vibrational movement of the conveying member 18.
  • the length, thickness or number of the resilient supports 42 can be varied to adjust the total equivalent resilience or stiffness k a with which the absorbing mass 40 is supported.
  • the absorbing mass 40 has a known mass m a and a centre of gravity 44. Again, for practical purposes, the mass of the resilient supports 42 is usually negligible compared to absorbing mass 40. If the mass of the resilient supports 42 is not negligible, the absorbing mass' centre of gravity 44 may also include a fraction of the weight of the resilient supports 42.
  • the absorbing mass 40 is also arranged such that a line passing through the absorbing mass' centre of gravity 44 and the conveying member's centre of gravity 36 is substantially perpendicular to the conveying member's resilient supports 34. This preferred arrangement can reduce the moments acting at on the base.
  • the arrangement is also such that the natural frequency of the absorbing mass 40 is substantially equal to the natural frequency of the conveying member 18.
  • the requirement for this arrangement can be expressed as:
  • Matching of the natural frequencies can be achieved by changing the relevant masses, M and m a> or stiffness, K and k a , of the resilient supports.
  • the resilient supports 42 that support the absorbing mass 40 are made from the same non-elastometric material as the resilient supports 34 which support the conveying member 18. This minimises any difference between the natural frequency of the absorbing mass 40 and the natural frequency of the conveying member 18 that may be caused by temperature changes
  • the base 12 is arranged to have a natural frequency that is different from the natural frequency of the conveying member 18, the absorbing mass 40 and the drive 38.
  • the conveying member 18 is excited in to vibratory motion by the vibratory drive 38, preferably at a frequency substantially equal to the natural frequency of the conveying member 18.
  • the absorbing mass also vibrates to counteract the vibration of the conveying member 18, that is in phase opposition, resulting in the absorption of energy from the base.
  • the arrangement such that the natural frequency of the absorbing mass 40 is substantially equal to the natural frequency of the conveying member 18 results in the absorbing mass 40 vibrating out of phase (preferably 180° out of phase) with the conveying member 18, thus absorbing energy and reducing the forces transmitted to the base 12.
  • the absorbing mass 40 is not directly driven, but reacts to the tendency of the base 12 to move due to the forces applied by the vibrating conveying member 18.
  • the centres of gravity 36,44 of the conveying member 18 and the absorbing mass 40 respectively, are arranged such that a line through them is perpendicular to the line 46 which illustrates the angle of the resilient supports 34,42.
  • the force 48 applied by the drive 38 is located at a distance from the line through the centres of gravity 36,44 of the conveying member 18 and the absorbing mass 40. This force 48 can be in along line of varying direction, as indicate by the various arrows extend from the point of force 48.
  • the centre of gravity 32 of the base 12 is a distance 50, measured longitudinally of the conveyor, from the line through the centres of gravity 36,44 of the conveying member 18 and the absorbing mass 40.
  • the absorber mass 40 is connected via a resilient support 52 to the base 12 and supported on a slide 54.
  • the surface of the slide 54 upon which the absorber mass 40 rests is arranged so that it is inclined at an angle substantially perpendicular to the conveying member's resilient supports 34.
  • the resilient support 52 is attached to the base 12 using a suitable fastener and arranged such that the absorbing mass 40 can undergo vibrational movement parallel to the vibrational movement of the conveying member 18.
  • the arrangement is also such that a line passing through the absorbing mass' centre of gravity 44 and the conveying member's centre of gravity 36 is substantially perpendicular to the conveying member's resilient supports 34. This arrangement minimises the moments acting at on the base.
  • the arrangement is also such that the natural frequency of the absorbing mass 40 is substantially equal to the natural frequency of the conveying member 18.
  • the operation of the vibratory conveying apparatus 10 is largely the same as in the embodiment of Figure 2.
  • the vibratory motion of the absorbing mass 40 to counteract the vibration of the conveying member 18 is realised by the absorber mass 40 sliding over the surface of the slide 54.
  • the arrangement such that the natural frequency of the absorbing mass 40 is substantially equal to the natural frequency of the conveying member 18 results in the absorbing mass 40 vibrating out of phase with the conveying member 18, thus absorbing energy and reducing the forces transmitted to the base 12 and to the supporting structure through the base 12.
  • the overall movement of the base 12 is in the range of 1-4 mm when there is no absorbing mass 40 attached to the base 12 and the overall stroke of the conveying member is approximately 6mm.
  • Inclusion of the absorbing mass 40 can reduce the overall movement of the base to 0.1-1 mm.
  • Such a reduction in vibration of the base means that bases with lighter bases can be used, which in turn means that less expensive and more manageable conveying apparatus can be manufactured.
  • the absorber mass may be arranged to vibrate with a natural frequency that is substantially equal to a multiple of the conveying member's natural frequency.
  • the requirement for this arrangement can be expressed as:
  • the resilient supports 34 may be in any suitable arrangement for supporting the conveying member 18.
  • the vibratory drive 38 may not be connected to or supported by the base 12 or the conveying member 18 but simply arranged such that the vibratory drive 38 applies a force to the conveying member 18 directly, thus exciting the conveying member 18 into vibratory motion. It also within the scope of the present invention that the vibratory drive may be controllable so that its characteristics, such as drive frequency or magnitude for example, may be altered.
  • more than one absorbing mass may be used to counteract the vibration of the conveying member 18. It will be appreciated that such a plurality of masses may all be of equal or differing mass, or any combination thereof. However, to minimise the moments acting at on the base, the masses should be arranged such that a line passing through each absorbing mass' centre of gravity and the conveying member's centre of gravity is substantially perpendicular to the conveying member's resilient supports.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jigging Conveyors (AREA)

Abstract

L’invention concerne un transporteur vibrant (10) servant à acheminer des matières et comprenant : un socle (12) ; un élément transporteur (18) maintenu sur le socle par au moins un support élastique (34) ; un dispositif d’entraînement (38) conçu pour faire vibrer l’élément transporteur ; et une masse absorbante (40) maintenue sur le socle par au moins un support élastique (42) de façon à ce que le mouvement de la masse absorbante soit sensiblement parallèle à celui de l’élément transporteur, et à ce qu’une droite passant par le centre de gravité (44) de la masse absorbante et le centre de gravité (36) de l’élément transporteur soit sensiblement perpendiculaire audit au moins un support élastique de l’élément transporteur. L’invention est caractérisée en ce que la fréquence propre de la masse absorbante est choisie de façon à être sensiblement égale à la fréquence propre de l’élément transporteur, ou à un multiple de celle-ci, de telle sorte que la masse absorbante vibre sensiblement en opposition de phase par rapport à l’élément transporteur lorsque le dispositif d’entraînement fait vibrer l’élément transporteur, et absorbe ainsi l’énergie provenant du socle.
PCT/GB2006/001929 2005-05-27 2006-05-26 Transporteur vibrant Ceased WO2006125998A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0510897.2 2005-05-27
GB0510897A GB2426562B (en) 2005-05-27 2005-05-27 Vibratory conveyor

Publications (1)

Publication Number Publication Date
WO2006125998A1 true WO2006125998A1 (fr) 2006-11-30

Family

ID=34834782

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2006/001929 Ceased WO2006125998A1 (fr) 2005-05-27 2006-05-26 Transporteur vibrant

Country Status (2)

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GB (1) GB2426562B (fr)
WO (1) WO2006125998A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112218809A (zh) * 2018-04-05 2021-01-12 克特朗技术公司 震荡输送器

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT360907B (de) * 1978-12-18 1980-02-10 Tyrolia Freizeitgeraete Schwingfoerderer
GB2086003A (en) * 1980-10-24 1982-05-06 Fry Controls Alan Ltd Vibratory Feeder
DE4138957A1 (de) * 1990-12-01 1992-07-02 Kumeth Siegmund Vibrationslaengsfoerderer

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3668939A (en) * 1969-11-13 1972-06-13 Rex Chainbelt Inc Plane omnidirectional absorber
DE4326146A1 (de) * 1993-08-04 1995-02-09 Koeberlein Josef Masch Vibrations-Linear-Förderer
US6415913B2 (en) * 1997-03-17 2002-07-09 Fmc Technologies, Inc. Excited base conveyor system

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT360907B (de) * 1978-12-18 1980-02-10 Tyrolia Freizeitgeraete Schwingfoerderer
GB2086003A (en) * 1980-10-24 1982-05-06 Fry Controls Alan Ltd Vibratory Feeder
DE4138957A1 (de) * 1990-12-01 1992-07-02 Kumeth Siegmund Vibrationslaengsfoerderer

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112218809A (zh) * 2018-04-05 2021-01-12 克特朗技术公司 震荡输送器
CN112218809B (zh) * 2018-04-05 2022-05-13 克特朗技术公司 震荡输送器

Also Published As

Publication number Publication date
GB2426562A (en) 2006-11-29
GB2426562B (en) 2010-04-14
GB0510897D0 (en) 2005-07-06

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