EP1897627B1 - Crible, en particulier un crible à résonance spécifique pour des mélanges difficilement séparables, comme les mélanges de sable et d'huile lourde - Google Patents

Crible, en particulier un crible à résonance spécifique pour des mélanges difficilement séparables, comme les mélanges de sable et d'huile lourde Download PDF

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Publication number
EP1897627B1
EP1897627B1 EP07016980A EP07016980A EP1897627B1 EP 1897627 B1 EP1897627 B1 EP 1897627B1 EP 07016980 A EP07016980 A EP 07016980A EP 07016980 A EP07016980 A EP 07016980A EP 1897627 B1 EP1897627 B1 EP 1897627B1
Authority
EP
European Patent Office
Prior art keywords
screening apparatus
support frame
energy storage
sieve
base support
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.)
Not-in-force
Application number
EP07016980A
Other languages
German (de)
English (en)
Other versions
EP1897627A3 (fr
EP1897627A2 (fr
Inventor
Ralph Naberg
Udo Artur Zöllner
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.)
Paul GmbH and Co KG
Pohl GmbH and Co KG
Original Assignee
Paul GmbH and Co KG
Pohl GmbH and Co KG
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 Paul GmbH and Co KG, Pohl GmbH and Co KG filed Critical Paul GmbH and Co KG
Publication of EP1897627A2 publication Critical patent/EP1897627A2/fr
Publication of EP1897627A3 publication Critical patent/EP1897627A3/fr
Application granted granted Critical
Publication of EP1897627B1 publication Critical patent/EP1897627B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B07—SEPARATING SOLIDS FROM SOLIDS; SORTING
    • B07B—SEPARATING SOLIDS FROM SOLIDS BY SIEVING, SCREENING, SIFTING OR BY USING GAS CURRENTS; SEPARATING BY OTHER DRY METHODS APPLICABLE TO BULK MATERIAL, e.g. LOOSE ARTICLES FIT TO BE HANDLED LIKE BULK MATERIAL
    • B07B1/00—Sieving, screening, sifting, or sorting solid materials using networks, gratings, grids, or the like
    • B07B1/42—Drive mechanisms, regulating or controlling devices, or balancing devices, specially adapted for screens

Definitions

  • the invention relates to a specific Resonanzsiebmaschine for difficult to separate mixtures, such as heavy oil-sand mixtures.
  • screening machines whose sieve acceleration reaches a maximum of 6.35 g.
  • screening machines usually have a screen box as an oscillating mass, which is mounted on damping springs swinging against the floor. The screen vibration is achieved by flanged on the screen box unbalance motors.
  • a high, also referred to as Siebkennziffer K V screening acceleration is particularly necessary for the fine squeezing, are pressed in the low-mass particles that are thrown upwards due to the Siebschwingung, upon relapse in the direction of their counter-sieve through the separating openings.
  • the maximum sieving index which is known to be reached, is a maximum of 6.35 g, which is too low for the mentioned heavy oil-sand mixtures.
  • the sieve acceleration or sieving index of a screening machine should be designed so that the average sieve rotation angle range is approximately 360 ° or integer multiples thereof. This is necessary so that the falling Goodteilchen hits the screen bottom at the moment when it has reached its maximum counter-speed upwards.
  • the maximum relative impact velocity between particles and sieve plate is a high degree of separation of very fine solid particles, for example, from very high viscosity media.
  • the DE 628 949 Z shows a vibrating sieve, in which a sieve box and a vibratory bearing frame are each mounted swinging about leaf spring-like constructions on a foundation.
  • Sieve box and bearing frame are loosely connected via a helical spring-like coupling and can be offset by an eccentric on the bearing frame in vibration.
  • the US 3,032,175 A finally reveals a vibration.
  • Trough conveyor wherein a vibrating trough is coupled via double spring arrangements of head-to-head coil springs swinging on a base support frame.
  • the latter is provided with unbalance motors and also mounted swinging spring legs on a foundation.
  • the invention leaves the hitherto practiced direct acceleration of the screen box by its oscillating storage relative to the floor and the directly mounted on it unbalance motors. Furthermore, energy storage springs are used for energy transmission between the vibration partners, which no longer have the mechanical limitations of Antschpuffem, guide elements and link arms between the vibration partners, as for example in the DE 11 87 897 A or DE 68 11 940 U the case is. This was the reason that screening machines according to the prior art to a K V - were limited value of about 5 g to 6 g.
  • the approach according to the invention provides for the combination of two oscillating masses, namely the actual oscillating mass in the form of the sieve box and a counterbalancing mass in the form of the base bearing frame which oscillates via damping springs in relation to the erection floor is stored.
  • the basic idea behind this design is to accelerate the base frame as an excitation mass to approx. 3 g and, in conjunction with the energy storage spring assemblies, increase the acceleration of the sieve box due to its directional vibration in the absolute range of 10 g. This acceleration breaks down into a K V value of about 9.5 g due to the inclination of the angle of oscillation on the sieve bottom.
  • energy storage springs while double helical spring assemblies are used, which can work very energy efficient because low-damping and with greatly increased forces. This effect is dramatically enhanced by the bias of the coil springs.
  • Fig. 1 is dash-dotted lines the sieve of a screening machine indicated that a symbolized by the solid line sinusoidal oscillation performs.
  • the maximum speed of the sieve bottom in the vertical direction is at the zero crossing of the Siebschwingung.
  • Siebtechnisch makes sense only the upward zero crossing.
  • Dashed is in Fig. 1 the parabola of particles x for increasing sieve codes with the values 3.2 g; 6.35 g and 9.5 g applied.
  • the throw depends on the actual machine acceleration K as well as the throw angle ⁇ and the screen inclination ⁇ .
  • the in the Fig. 2 to 5 shown screening machine has the fundamental constructive ability to achieve such a high Siebkennziffer.
  • As a basic design element it has a base frame 1, damping springs 2, a base bearing frame 3, a sieve box 4, unbalance motors 6, and energy storage spring assemblies 5 arranged between the base frame 3 and the sieve box 4.
  • Fig. 2 The related to Fig. 2 Rear damping springs 2 are supported by a foot 7 on the rear cross member 8 of the base frame 1.
  • a vertically above support bridge 9 is erected on the horizontal traverse 10 a vertically acting piston-cylinder drive 11 is arranged.
  • a height-adjustable lifting frame 13 is suspended, at the lower cross-beam 14, the two front damping springs 2 of the base bearing frame 3 are supported.
  • the coupling of the four damping springs 2 to the base support frame 3 is in each case via a pivot bearing 15, the pivot axis extends horizontally in the transverse direction.
  • the base support frame 3 itself is essentially composed of two cheeks which form the longitudinal sides 16, 17 and two cheeks which join them transversely at the ends and which form the transverse sides 18, 19. Due to the thus delimited frame opening of the base storage frame 3, passing through the sieve plate 20 of the sieve box 4 fine screenings fall down and be transported by a transport mechanism not shown here.
  • the screen box 4 which corresponds essentially to the base support frame 3 in its layout, is based on two longitudinal sides 21, 22 and the rear transverse side 23 Fig. 2 bounded by vertical cheeks. At the front transverse side 24 of the sieve box 4 is open, so that there is not passed through the sieve tray 20 through coarse screenings can be led away from the sieve plate 20.
  • the sieve bottom 20 itself is formed by staggered, lined sieve inserts 25, whose nets, not shown, have a mesh width of, for example, 5 ⁇ m, as required for the separation of fine sand from oil silt.
  • the screen box 4 is about eight energy storage spring assemblies 5, which are distributed over its longitudinal sides 21, 22, with a sieve vibration permitting vertical distance above the base support frame 3 attached thereto.
  • These energy storage spring assemblies 5 are each formed by a double spring assembly consisting of coaxial pairs, head 29 at head 30 juxtaposed coil springs 26, 27, wherein the screen box 4 respectively with a box-fixed bearing 28 between the pairs associated heads 29, 30 of the coil springs 26, 27 is clamped.
  • Each bearing 28 is formed by a bearing bracket 31 with a laterally projecting from the sieve box clamping bearing flange 32.
  • the coil springs 26, 27 are under a bias, which allows an increase in the vibration amplitude of the sieve box 4 by three times that of the base bearing frame 3. This achieves the desired high K v value of 9.5 g.
  • the latter has on its longitudinal sides 16, 17, laterally projecting support brackets 33, on each of which the lower coil springs 26 rest.
  • support brackets 33 projects in Fig. 3 dashed lines indicated, rigidly coupled thereto support rod 34 upwards, on the free end of a lid-like counter-holder 35 is placed.
  • the support rod 34 passes through the clamping bearing flange 32 of the bearing bracket 31 of the screen box 4 under lateral clearance.
  • each energy storage spring assembly 5 is clamped between this chuck bearing flange 32 and the anvil 35.
  • Fig. 3 how out Fig. 3 becomes clear, are the energy storage spring assemblies 5 with its spring direction 36 at a small acute angle ⁇ of an optimal manner about 20 ° to the vertical, which defines the throw angle of the sieve box 4.
  • the joint line of the unbalance motors 6 is aligned in the same direction as the spring assemblies 5. Due to the height-adjustable lifting frame 13 of the screen tilt angle can be set as such.

Landscapes

  • Combined Means For Separation Of Solids (AREA)
  • Vibration Prevention Devices (AREA)

Claims (10)

  1. Crible à résonance spécifique pour des mélanges difficilement séparables, comme des mélanges d'huile lourde et de sable, comprenant
    - un châssis de palier de base (3) disposé essentiellement à l'horizontale par rapport au socle support, vibrant sur des ressorts d'amortissement (2), servant de compensation à la masse oscillante,
    - plusieurs blocs-ressorts à stockage d'énergie (5), inclinés, s'appuyant sur le châssis de palier de base (3), chacun sous la forme d'un ensemble double de ressorts hélicoïdaux qui supportent un caisson de tamisage (4) en tant que masse oscillante et
    - plusieurs moteurs à balourd (6) bridés sur le châssis de palier de base (3) qui déplacent le châssis de palier de base (3) et le caisson de tamisage (4) par l'intermédiaire des blocs-ressorts à stockage d'énergie (5) dans une oscillation de tamisage orientée
    où les blocs-ressorts à stockage d'énergie (5) sont chacun constitué d'un ensemble double de ressorts à base de ressorts hélicoïdaux (26, 27) s'appuyant solidement sur le châssis de palier de base (3) avec leurs extrémités opposées l'une à l'autre, alignés par paires de manière coaxiale, tête contre tête, et où le caisson de tamisage (4) est inséré respectivement avec un palier résistant au caisson (28) entre des têtes (29, 30) des ressorts hélicoïdaux (26, 27) disposées par paires, ainsi mis sous précontrainte, de sorte qu'une oscillation de tamisage orientée avec une valeur de Kv effectif d'environ 9,5 g peut être atteinte.
  2. Crible selon la revendication 1 caractérisé en ce que les ressorts d'amortissement (2) sont disposés chacun aux extrémités des faces longitudinales (16, 17) du châssis de palier de base (3).
  3. Crible selon la revendication 2 caractérisé en ce que les ressorts d'amortissement (2) disposés aux extrémités longitudinales situées à l'opposé de deux faces longitudinales (16, 17) sont implantés réglables en hauteur.
  4. Crible selon la revendication 3 caractérisé en ce que le réglage en hauteur est réalisé par un cadre de levage (13) s'appuyant sur les ressorts d'amortissement.
  5. Crible selon l'une des revendications précitées caractérisé en ce qu'un grand nombre de blocs-ressorts à stockage d'énergie (5) est aligné le long des faces longitudinales (16, 17, 21 22) des deux côtés du châssis de palier de base (3) et du caisson de tamisage (4).
  6. Crible selon l'une des revendications précitées caractérisé en ce que les blocs-ressorts à stockage d'énergie (5) sont disposés chacun avec l'orientation du ressort inclinée à un petit angle aigu (α) d'environ 20 ° par rapport à la verticale.
  7. Crible selon l'une des revendications précitées caractérisé en ce que les paliers (28) insérés entre les ressorts hélicoïdaux (26, 27) pour le caisson de tamisage (4) sont formés chacun par une console de palier (31) avec une bride de palier d'arrimage (32) dépassant du caisson de tamisage (4).
  8. Crible selon l'une des revendications précitées caractérisé en ce que l'appui des deux ressorts hélicoïdaux (26, 27) d'un bloc-ressorts à stockage d'énergie (5) sur le châssis de palier de base (3) est formé, d'une part, par une console d'appui (33) sur le châssis de palier de base (3), et d'autre part, par une contre-poignée (35) qui est couplée fixement avec la console d'appui (33) par l'intermédiaire d'une barre de maintien (34) s'étendant dans l'espace intérieur des ressorts hélicoïdaux (26, 27).
  9. Crible selon l'une des revendications précitées caractérisé en ce que chaque fois une paire de moteurs à balourd (6) est disposée sur chaque face longitudinale (16, 17) du châssis de palier de base dans la direction de l'oscillation.
  10. Crible selon l'une des revendications précitées caractérisé en ce que les moteurs à balourd (6) sont disposés chacun avec sa ligne de poussée parallèle par rapport à l'orientation des blocs-ressorts à stockage d'énergie (5).
EP07016980A 2006-09-07 2007-08-30 Crible, en particulier un crible à résonance spécifique pour des mélanges difficilement séparables, comme les mélanges de sable et d'huile lourde Not-in-force EP1897627B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006041989A DE102006041989B4 (de) 2006-09-07 2006-09-07 Siebmaschine insbesondere für schwer trennbare Gemische, wie Schweröl-Sand-Gemische

Publications (3)

Publication Number Publication Date
EP1897627A2 EP1897627A2 (fr) 2008-03-12
EP1897627A3 EP1897627A3 (fr) 2010-01-06
EP1897627B1 true EP1897627B1 (fr) 2012-08-15

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07016980A Not-in-force EP1897627B1 (fr) 2006-09-07 2007-08-30 Crible, en particulier un crible à résonance spécifique pour des mélanges difficilement séparables, comme les mélanges de sable et d'huile lourde

Country Status (4)

Country Link
US (1) US20080217219A1 (fr)
EP (1) EP1897627B1 (fr)
DE (1) DE102006041989B4 (fr)
ES (1) ES2391787T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106925513A (zh) * 2015-12-30 2017-07-07 奥瑞（天津）工业技术有限公司 新型振动筛激振器

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009009092A1 (de) 2009-02-14 2010-08-26 Zöllner, Thorsten Siebboden zum Einbau in Siebmaschinen
CN101690929B (zh) * 2009-09-29 2012-07-18 东北大学 一种四机驱动自同步振动筛及结构参数确定方法
CA2756965C (fr) * 2010-11-08 2019-01-15 Terex Usa, Llc Systeme de suspension pour tamis vibrants
CN102671856A (zh) * 2011-02-21 2012-09-19 李卓 一种强振筛
CN102671857A (zh) * 2011-03-13 2012-09-19 李卓 一种双质体共振筛
CN102225392A (zh) * 2011-04-08 2011-10-26 鞍山重型矿山机器股份有限公司 智能防堵孔振动筛
CN103302022A (zh) * 2013-05-31 2013-09-18 吉铨精密机械(苏州)有限公司 一种多层分选直线式振动筛
CN103769363B (zh) * 2014-02-20 2015-11-25 唐山陆凯科技有限公司 一种改进的共振式振动筛
CN103990598B (zh) * 2014-06-16 2015-12-30 鞍山市万瑞矿山设备制造有限公司 双电机启动连杆式共振筛
CN107150104A (zh) * 2016-03-02 2017-09-12 科华控股股份有限公司 一种3d打印机加砂过滤顺畅和减少振动噪声的过滤网架
AU2017269489B2 (en) * 2016-05-25 2022-04-21 Finbawn Ltd A screening machine for screening material according to size
CN105855165A (zh) * 2016-06-21 2016-08-17 江苏金宝重工有限公司 一种石料振动筛
US10456809B1 (en) * 2017-03-28 2019-10-29 Conrad Leon Nagel Vibrating screen for an inlet hopper of a conveyor
CN114013914A (zh) * 2021-11-30 2022-02-08 徐州宏武纳米科技有限公司 一种高效的碳化硅冶炼出料设备

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Publication number Priority date Publication date Assignee Title
CN106925513A (zh) * 2015-12-30 2017-07-07 奥瑞（天津）工业技术有限公司 新型振动筛激振器

Also Published As

Publication number Publication date
DE102006041989B4 (de) 2009-06-04
US20080217219A1 (en) 2008-09-11
DE102006041989A1 (de) 2008-03-27
ES2391787T3 (es) 2012-11-29
EP1897627A3 (fr) 2010-01-06
EP1897627A2 (fr) 2008-03-12

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