DE7613723U1 - VIBRATING DRIVE - Google Patents

Description

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DR. HANS W. HOFMANN

Patent attorney 62 Wiesbaden 1 Hauberisserstraßo 36

601 Π FRCS

VIBRATING DRIVE.

The invention relates to egg non vibratory drive for the treatment of solid materials, which has an elastically suspended oscillating frame, which is generated by a vibration generator from two parallel, is driven transversely to the longitudinal axis of the oscillating frame, synchronously and oppositely rotating eccentric shafts, wherein the imbalances of the two eccentric shafts are equal and the vibrations take place linearly in a plane which the plane connecting the eccentric shafts is essentially in the middle cuts between the two eccentric shafts.

Vibratory drives of this type are used to separate material grain sizes suitable or are used to convey material, e.g. in building construction and civil engineering, in mines and in chemical Industry.

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Vibration generators are already included in all of these applications two eccentric shafts that rotate synchronously and in opposite directions, known.

They differ from arrangements with an eccentric shaft in that they generate linear vibrations, while the arrangements with only one eccentric shaft are circular or perform elliptical oscillations. In doing so, for example when separating grain sizes, 'only' one of the two components the circular or elliptical motion used.

In contrast to this, linear vibrating vibratory drives are used the movement, guided in a direction that can be chosen so that all of the energy can be used usefully.

V. '~: tcrh: r. ^m '" ^icc °" irhwinaant.trieb partly horizontally, partly inclined. In the case of inclination, the material is driven in part by gravity. Although this also allows the use of elliptical or circular vibrations, there is the disadvantage that the processed material, if it consists of pieces of different sizes, is difficult to control in terms of transport speed, since the large pieces tend to be under the influence of gravity to fall faster than the smaller pieces.

In contrast to this, the speed of the material can be set very precisely in the case of horizontally oscillating arrangements. In fact, this speed depends on the inclination of the plane of oscillation to vertical by the vibrations simultaneously advancing and size separation of the material bew i r ken.

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In the case of horizontal vibratory drives, vibration generators are mostly used used with two eccentric shafts whose imbalances are of the same size and fixed at symmetrical points of the two shafts and which are driven synchronously and in opposite directions.

Such vibratory drives generate linear vibrations in one Level, which is the level connecting the two core worlds cuts. It is possible to arrange the two shafts on the swing frame in such a way that the one connecting the axles Plane is inclined in the direction of the Materia 1 transport and thereby the plane of vibration is inclined to the vertical once and for all is fixed.

With some horizontal vibratory drives, especially with screen feeders directly attached to crushing mills, the problem often arises of changing the speed of the material to be transported, the state of which fluctuates greatly over time, without changing the vibrating effect. So contain many materials, in particular _; if they come from the ground and are moist, small grains "that adhere firmly to the large blocks. In order to separate these blocks from the adhering particles, it is desirable to shake the large and dry blocks for a longer time or more intensely.

In the known arrangements with linear vibration for the mater ia 1, transport the work at an angle., A change in the material 1vorschubgeswindigkeit only by changing the rotational speed of the eccentric shafts can be achieved. This results in a reduction in speed

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Reducing the Rüttelamp! Itude because at the same time the Horizontal and the vertical component become smaller. This means that the materials are shaken longer on a device of a given length, but the shaking movement is involved weaker, so that the desired result is not achieved with this type of setting. - -

It is still the case with horizontally operated vibratory drives known, the vibration generator having the two eccentric shafts to be arranged on a rotatable support so that the plane intersecting the two eccentric shafts can be inclined. However, this support must then be combined with the adjustment mechanism be mounted on the swing frame, which leads to difficult to solve strength problems.

The object of the present invention is to provide an oscillating drive in which the screening capacity of the horizontal or inclined oscillating frame can be changed without the oscillating drive must be stopped that the change in performance is infinitely variable occurs and that the reduction in the feed rate no reduction in the jolting effect. Farther is intended to set the feed rate for materials in a large Area can be changed and also negative, i.e. reverse speeds enable. Reverse speeds are particular This is important if a vault of material forms in the feed hopper, which is also due to the increase in the feed speed cannot be brought to collapse. When reversing the

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However, the large blocks g, egen will push speed the soffit of the Materia 1 vault thrown and bring thereby this obstacle to collapse.

These tasks are achieved in that the angle adjustment of the imbalances to change the vibration level without change the vibration amplitude relative to each other during operation is infinitely variable.

The change in the angle setting is a further development of the invention of the unbalances 360 against each other, i.e. 180 on both sides, so that the change in the vibrational plane 180, i.e. 90 on both sides.

In a simplified arrangement suitable for numerous fields of application is sufficient, the change in the angle setting is of the unbalances 180 against each other, i.e. 90 on both sides, see above that the change: the vibration level 90 so 45 naci. both Pages is.

With a horizontal swing frame, the highest feed speed is generally achieved in a plane inclined to the horizontal, whereby the inclination, depending on the type of materials and frame load, i.e. depending on the thickness of the material a 1 layer on the frame, is variable and between 30 and 45 is for the usual materials that are fed into a primary crusher via a pre-screening device, for example. It is therefore advantageous if the vibration generator is connected to the vibrator frame in a plane that is preferably between 15 and 30 relative to the horizontal plane and that the vibration plane is approximately 30 to 15 relative to the horizontal for the feed and

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from about 30. to 15 against the vertical for the return of the material to be treated is inclined.

The advantage of this arrangement is that through the Change in angle adjustment by +; 90 and through

0 one. Angle adjustment of the plane of oscillation by * + 5 is made possible, the vibration level between about 30 to 15 to the horizontal for the Vor 1 erection and approximately between 30 and 15 to incline to the vertical for the return direction. In order to both a maximum forward and reverse speed can be set i t reach.

In a further embodiment of the invention, the plane of oscillation runs around essentially in the middle between the two eccentric shafts and intersects the center of gravity of the oscillating frame regardless of the set direction of oscillation. This ensures the linearity of the frame's oscillation. Furthermore, it is advantageous if one of the two eccentric shafts by a motor is immediately driven when the other shaft is connected in a known manner Mitteis a chain, a toothed belt or a ahn ¹ cozy endless connection center 1 with the first eccentric shaft and when the length of approaching part of the Vsrbindungsmitte1s can be changed at the expense of the length of the downstream part.

It is also possible to have each of the two eccentric shafts through one drive your own engine. The eccentric shafts are advantageous for this driven by two asynchronous motors, their rotors are electrically coupled and their power is fed from the same network

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Field windings are electrically adjustable in angle, so that a Phase difference between the rotors is adjustable.

Further details of the invention emerge from the drawing shown schematically. Show it:

1a, 1b, 2a, 2b, 3a, 3b, 4a, 4b with the two eccentric shafts

different Ste 1 1 ungender imbalance, ff

Fig. 5 shows the structure of a vibratory drive on a horizontal ψ

Swing frame,

6 shows a side view of a loading device with a vibratory drive according to the invention, 7 shows the side view of an arrangement according to FIG 8 shows an enlarged section of an arrangement according to FIG. 6 with a control mechanism,

9 shows an embodiment with electrical adjustment of the Phases 1 age.

In Fig. La and Ib are two eccentric shafts Al and A2 with one Equipped with the same unbalance Bl and B2 and driven synchronously in the opposite direction. The joint support of Waves is not shown. The unbalances B1, B2 are in this Example permanently symmetrical. Each of the imbalances generates a centrifugal force f when the shaft rotates, which is in the vertical Add the middle plane of the shafts up to the maximum force R = 2f when the eccentric shafts are in position Ib. In Fig. 2a the two shafts are rotated against each other, wherein the shaft Al is set shifted counterclockwise by- ^ 5 arvfc is. The maximum resulting force R = 2f has in this

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Make an angle of -22.5 ° to the vertical, as shown in Fig. 2b.

In Fig. 3a, the shaft Al is adjusted by + 90 ° and the Resultant R = 2f forms an angle of -45, as shown in Fig. 3b.

In Fig. 4a, the shaft A1 is adjusted by 90 ° clockwise, resulting in an inclination of the maximum force by 45 against the vertical, as shown in Fig. 4b. The result R thus represents an oscillation vector of constant maximum intensity. It has its starting point in the middle of the plane that connects the two eccentric shafts and has the direction that corresponds to half the adjustment angle of the eccentric levels. The angle adjustment can be up to η 8 θ "if the adjustment of the ueiu'cn 'J ₁ ,», achter, ur,. Against each other is possible.

However, it is also possible to change the range on 90 °, which makes it easier to control the adjustment. To do this, the vibratory drive must be inclined on the frame in such a way that that the feed and return of the material are enabled. Such an arrangement is shown in FIG. Here are the Imbalances in the eccentric shafts are symmetrical, so that the plane of oscillation is perpendicular to the plane connecting the shafts. It is assumed that the oscillating frame is horizontal and that the nature of the materials and the load on the frame are such that the feed of the materials with maximum Speed is achieved by an oscillation plane inclined by 40 ° to the horizontal.

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To get a position under these conditions by changing the direction of the plane of oscillation by + 45 reach / which allows the maximum feed rate as well as a position of sufficient return speed is guaranteed, the common plane of the two eccentric shafts A1, A2 is inclined at an angle of 15 to the horizontal.

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As a result, the resulting vibration level can be increased by 60 in the Feed direction (Ra) can be set, this is a larger one Inclination as that of the maximum feed rate (ram). The level can also be inclined by / 50 in the upright direction (.i-V) will.

6 and 7 show an embodiment of a pre-screen hsqrhickunasei nr icht that with an inventive Oscillating drive is equipped and in which the angle adjustment the imbalances by means of a control mechanism according to Fig succeeded.

It consists of an oscillating frame 1 in the form of a box welded from sheet steel. The screen surface of the frame 1 comprises several successive horizontal planes that form three floors. These are the frame 1, a loading level 2, which is extended by a first pre-screening level 3, and a second and third pre-screening level 4 and 5, which consist of horizontal plates that run over the entire width of the frame 1. The plates of the three Vorsiebebenen 3,4,5 are on the whole length with longitudinal ski ■ tzen 6 'is provided, to the end of the dsm t frame 1 side, which is opposite to the loading plane 2, always

become wider and open in that direction.

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The teeth 7 that have remained between the said gaps 6 are reinforced with longitudinal plates 8, which are set up on edge below the Εοβηβη ₃ , ι », 5 under each tooth 7. The loading and sieving surface of the frame is held by cross supports. The loading level 2 is held directly by two carriers 9 and the pre-sieves 3, 4 and 5 by means of plates 8 and by a carrier 10. The levels 2, 3, 4 and 5, the plates 8 and the carriers 9 and 10 are welded to one another and to the side walls 11, 12 of the frame 1. The frame 1 has four feet 13 which are attached to the outside of the side walls 11 and 12 at some distance from the longitudinal ends of the aforementioned side walls. The four feet rest on rubber blocks 14, which are fastened with Igur.gsmi ttel η 15 on a frame 16, which is, for example, welded together from beams,

attached.

Furthermore, the loading level 2 is outside in the longitudinal direction? the side opposite the pre-sieves 3, 4, 5 through a limited inclined plane 17, which is intended to prevent the Materia 1ien arriving from above on the loading level 2 on this side falling off. In addition, two Querplattenl8,19 are the zuein other inclined, attached below the ends of the screen surface, which is formed from three pre-screens 3,4,5 to Parts of the material that form the slots 6 of the pre-screening levels 3,4,5 have happened to lead into a funnel, which is located below the loading device.

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The vibratory drive of this loading arrangement has two y

_{paral1elverlaufende}} horizontal eccentric shafts 20,21 which are arranged transversely to the length of the frame 1, as Figure 7 shows.

The Exienterwel1 en 20,21 are rotatable in the side walls 11, 12 of the frame 1 are arranged and on the protruding ends the imbalances 23,24,25,26 placed on disks 22, with the imbalances 23,24 and 25,26 assume the same angular position on the eccentric shafts.

The two eccentric shafts 20,21 are with a through the Diameter of the discs 22 certain minimum distance on the

j frame 1 arranged. The one connecting the waves goes Level through the center of gravity of the frame 1 and is inclined downwards by 15 relative to the horizontal.

The two shafts 20,21 are on one side of the frame 1 with couplings 27,28 with the drive shafts 29,30 one Control mechanism 31 connected, which is stationary next to the frame is arranged on a base plate 32. This baseplate is connected to the frame 16 and carries an electric drive motor 33 and an electric control motor 34, which in Fig.8 is shown in more detail.

In Figure 8, the control mechanism is arranged in a housing 35, of which only the side wall 36 is shown. It consists of the two shafts 29, 30, which are aligned with the eccentric shafts 20, 21 are connected. The shaft 30 is in front of the wall 36 with a washer 37 provided, which is connected to the motor 33 via a belt ^ R or a similar connecting means is connected. Within the

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Housing 35, the shaft 30 is provided with a chain wheel 39. . The shaft 29 in turn carries a sprocket 40 with the Wheel 39 is connected via a chain 41, which runs over the two wheels 39, 40 in such a way that the two wheels

circulate synchronously and in opposite directions. The two chain lengths 42, 43 of the chain 41 run between the two wheels 3'9, 40 over d'e Sprockets 44 and 46, the sprocket 44 having a fixed position, but the sprocket 46 movable on the free end of one Lever 47 is arranged, which is pivotable about an axis 48. The spring 49 ensures sufficient tension of the Ke ", te 41.

As an extension of the plane that connects the two shafts 29, 30 , a shaft 50 is rotatably arranged in the side walls of the housing 35 beyond the shaft 29. On this wave. 50, on the side opposite the frame 1, a toothed segment 51 is arranged, in which a worm driven by a motor 34 meshes. Within the housing 35, the shaft 50 carries a lever 53 with two arms of equal length, on the free ends of which two chain wheels 54, 55 are arranged. The chain length 42 of the chain 41 runs from the wheel 40 over the wheel 54, then over the wheel 44 before it meets the sprocket 39 again. while the chain length 43 runs from the wheel 39 over the wheel 55 before it hits the wheel 40 again.

BeJ the assembly wisrädj, the pivot lever 53 perpendicular to the line attached, which connects the three shafts 30,29,50. The chain 41 is placed over the individual wheels in such a way that the

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Imbalance weights 25.26 and 23.24 when the shafts 29,30 rotate are symmetrical to each other by the motor 33. This creates then the linear oscillation in the plane perpendicular to the plane connecting the two eccentric shafts. If you then pull the lever 53 moved in one or the opposite direction, causes a change in the chain lengths 42 and 43 of the chain 41 and thereby an angular displacement of the two shafts 29.30 and thus a change in the angle that the unbalances 23.24 and 25.26 have against each other without the synchronous and opposite rotation of the shafts 29,30 changes. In Fig.8 is one of the possible end positions of the lever shown. With this lever position there is an angular shift by 90 according to Fig. 3a. A corresponding Displacement according to Figure 4a occurs in the other end position of the Lever 53. This angular shift is caused by the opposite

| set change in length of the chain lengths 42,43 when the lever

j is pivoted from the perpendicular to the line passing through the shafts 30,29,51.

The chain 41 can, of course, be matched by any other! 'Like transmission means, for example. A double toothed belt, be replaced. Likewise, the pivot lever 53 and its screw control can be replaced by equivalent means which allow an opposite change in length of the chain lengths 42, 43 of the chain 41 and thereby a change in the position of the two wheels 54, 55 relative to one another.
In the embodiments described so far, the

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two eccentric shafts 2 O> 21 driven by a motor 33 namely the shaft 21 directly, the shaft 20 via a Lanyard 41. However, this lanyard must partially transmitted the entire moment. In the case of very large vibratory drives, this can lead to stability problems.

The two eccentric shafts 20, 21 are therefore advantageous driven separately by two identical independent motors.

They are mechanically linked by the control mechanism 31.

The advantage is that the drive torque is no longer needs to be transmitted., but that the K2tte 41 only establishes the synchronism of the two shafts, with only very little forces that have to be transmitted.

Finally, the control mechanism can be omitted completely, if two synchronous motors are used and the phase position electrically adjustable by one or both motors.

An arrangement of this type is shown in FIG. The two Motors 56,57 are synchronized asynchronous motors. the stator windings 58,59 connected in star are connected in such a way that that the direction of rotation of the fields is opposite when they are connected to a supply network by means of a three-phase switch 60 are. The windings of the rotors 61 and 62 are directly coupled to one another. To do this, three resistors 63,64,6S same value in the star with the three phases of the rotor windings connected, namely the resistors 63 and 65 directly and the resistor 64 by means of an interrupter switch 66. It is furthermore a switch 67 to C delta connection of the resistors

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63,64,65 and a two-pole switch 68 to supply the Rotor windings provided with direct current.

This circuit corresponds to the familiar display for synchronized asynchronous motors through an I resistors. The start-up of the arrangement takes place in that the switch is closed and the switch 66 is opened, as well as the start-up resistors 63,64,6S are connected in delta by the switch 67 After the start-up phase, the rotors 61, 62 of the motors 57 run synchronously in the opposite direction and drive over the Couplings 27, 28 to the two eccentric shafts 20, 21. To change the phase position of the two eccentric shafts is rotated one of the stators, for example the stator 53 about its axis, in order to bring it into the position shown in broken lines in FIG this does not affect synchronous operation. In order to achieve this angular displacement, the stator can open be flanged to a corresponding support, which by means of a control mechanism, such as a worm gear, as in Fig. 8 shown, can be movable.

Another possibility for the infinitely variable comprehensibility of the Eccentric waves is the electrical phase shift of the Supply voltage of the stators against each other.

The mutual displacement of the imbalances of the eccentric shafts allows the oscillation plane of the oscillating drive to be rotated without affecting the amplitude. If one assumes the neutral position, which in the example shown corresponds to an inclination of 15 to the vertical, then it is possible to shift the resultant more strongly into the feed

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direction up to the maximum material speed or to straighten them up or even to achieve the return of the material. When straightening up, the vertical increases Component at the expense of the horizontal. This will make the Feed speed lower and the shaking effect increases. Both changes improve screening, which is of great interest when dealing with dirty, unsorted materials should be treated because the effectiveness of the screening of the vertical amplitude and depends on the number of shocks, which in turn is inversely poportional of the feed rate. With the arrangement according to the invention, the sieving efficiency is thus easily and continuously pin adjustable.

The embodiments shown in an understanding and especially flat can be varied and modified without departing from the scope of the invention. An arrangement according to the Invention not only as a pre-screen loading device horizontal vibrating frame but can be applied to any other vibrating device. The sieve surface can consist of one single or multiple floors and is selected according to the given operating data.

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Claims (1)

J Ji) TI 9 «i> (* ti η« PROTECTION CLAIMS 1. Vibratory drive for the treatment of solids, d has a resiliently suspended swing frame through ] a vibration generator from two parallel, transverse to Shift the longitudinal axis of the oscillating frame, synchronously and in opposite directions rotating eccentric shaft is driven, the imbalances of the two eccentric shafts are of the same size and the vibrations take place linearly in a plane, which is the eccentric shaft connecting plane essentially in the middle between the two Eccentric shafts cut geke η n_ζ e i c h - i * ¹ dft, ² » -tsJo net that the angular position of the unbalances' to change the vibration plane without changing the vibration amplitude infinitely variable relative to one another during operation. 2. Vibratory drive according to claim 1, characterized in that the change in the angular position of the unbalances · 36 0 against each other, that is 180 on both sides, so that the change in the oscillation plane is 180, i.e. 90 on both sides. 3. Vibratory drive according to claim 1, characterized in that the 7613723 12/16/76 '«/ lit · · · 11 »·· ·« rf · -18- ( f22>, 2V ^ ZsJ ) Change of the angular position of the unbalances 180 against each other so 90 is on both sides, so that the change in Oscillation plane 90, that is 45 on both sides. 4. Vibratory drive according to claim 3, characterized in that the vibratory drive in a preferably between IS and 30 against it horizontal inclined plane with the swing frame ': nT is connected and that the vibration level is about 30 to 0 " ^T * 0 15 against the'horizontale for the advance and about 30 to 15 against the vertical for the return of the to be treated Material is inclined. 5. oscillating drive according to any one of claims 1-4, characterized in that the vibration level in the Wese nt1 i chen runs in the middle between the two Exzenterwe11enlver1 and the center of gravity of the oscillating frame * independently of the set Schw-i ngungsr i rect cuts. 6. Oscillating drive according to one of claims 1 to 5, characterized in that means for changing the angular position are provided in a manner known per se, which are composed of two drives connected by a chain or belt or a similar endless connecting means where dm is the length of the on the part of a roll approaching lanyard costs the length of the running part can be changed. 1 9 / 7613723 12/16/76 7. Oscillating drive according to claim 6, characterized in that a motor is provided for driving, which has an eccentric shaft 1 e directly, the other eccentric shaft via a connecting ®
with motivation. 8 .Swing drive according to claim 6, characterized in that two (S ^ 5J) (2 ^ 30) same engines! the eccentric drives we 1 1 en I UiTa b häng i g. 9. Oscillating drive according to claim 6, characterized in that dip Length of the part ending at 1 "and the part going down (kl) p Connection means aurcn ^ we i ümi c. ikro ® Locations relative to the means of connection T are mutually changeable 10 oscillating drive according to claim 9, characterized in that the (15 "VTcT)
two umI en kr oil 1 en I aujL the free ends of a rotatable Equal arm lever are arranged, whose axis of rotation is in the Level lies which the axes of the drive center elT for the eccentric shafts connects and who is misunderstood in the middle. ^. Oscillating drive according to claim 10, characterized in that the control mechanism consists of an electrically powered Schneckentrieb and a Zohnschoibe'bostnht, which with the 7613723 1B.12.76 20 / tea - 20 - equal-armed lever 'is connected. 1 2, oscillating drive according ei nem of claims 1-5, characterized in that ffi, 3rd Q) that the Exzent chsen era "by having two start windings asynchronous 'are driven at the same supply network, the rotors of electric' are coupled and whose field windings are angular adjustable, so that a phase difference is adjustable between the rotors. 7813723 UMU