FI83674C - Method and Device for Laying Thin Binder Impregnated Primary Cure of Mineral Wool on a Receiving Conveyor - Google Patents

Description

Method and apparatus for laying out thin binder-impregnated mineral wool primary web on a receiving conveyor

This invention relates to a method for laying out a thin binder impregnated uncured mineral wool web on a receiving conveyor and to a device for carrying out the method according to the preamble of claims 1 and 7.

In the manufacture of mineral wool sheets, it is of great importance that the product be as uniform and homogeneous as possible, which gives increased insulation capacity. Furthermore, at low density it should be as elastic as possible, which assumes that the fibers are stretched in the plane of the disc. Thanks to its elasticity, the disc can be compressed for the packaging and transport stage.

To achieve this, a thin conveyor belt is collected immediately after the fiber on a collection conveyor, the surface weight of which varies between 100 and 450 g / m 2, preferably 100-200 g / m 2. The thinner the primary web, the better the quality of the finished product. In order to maintain the capacity at the desired level while making the primary path thin, the primary path speed and the speed of its transport devices should be high. Normally, the primary web speed is over 100 m / min, but for surface weights of the primary web only 100-200 g / m 2, even higher speeds are required to keep the capacity at the desired level.

Various methods for folding mineral wool webs are described, inter alia, in US patent 2 450 916 from 1948 and in the somewhat younger GB patent 772 628. These have later been supplemented with methods for folding the primary web by means of commuting conveyors.

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When using pendulum conveyors for dispensing the primary web, it is important that the speed of the pendulum output end is approximately equal to the primary web output speed, so that the web is neither folded nor stretched at the instant of output.

The pendulum mechanism has so far most often functioned so that the end positions lie at most above the receiver conveyor and the lower dead position of the pendulum closest to the receiver conveyor. In order to achieve the desired capacity with the thin primary paths, the output speed of the shuttle conveyor should be increased, but it is not possible to do this with known devices. Namely, a fast-moving commuter conveyor that exits a light path and has a high commuting frequency gives inaccurate laying of the primary path.

The rate of movement of the output end of a pendulum conveyor, which in a known manner is driven by a crank and which pivots about a fixed pivot axis, is highest in the center position of the pendulum and decreases sinusoidally to zero in the outer position, from which again a sinusoidal acceleration occurs. The output end of such a pendulum conveyor must in its lower position lie about 0.2 times the commutation width, which is normally 2 m, above the pendulum wool web in order for the primary web to lie in an even layer on the recipient conveyor and not be stretched. With such a long distance between the pendulum and the receiver conveyor, 40 cm and more, the edges of the suspended path become uneven. With an output speed of about 130 m / min, the irregularities in the formed secondary path rise to about +/- 5% of the output width. This means that the secondary web must be given a correspondingly higher width in order to achieve a flawless web of the desired width, since the unwanted material must be cut away. This is a big waste of material.

It is also known in the pivot delivery mechanisms where the folding process is carried out so that the primary web is always delivered directly above the ground, at constant height. A joint system is arranged to pitch the output end of the pendulum mechanism at a constant height above the receiver conveyor, and the reciprocating movement

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3,83674 is poured through a chain / crank mechanism. The velocity profile of the pendulum movement has a constant center of velocity in the middle and a sinusoidal deceleration and acceleration phase in each end position. The pendulum must be decelerated and accelerated rapidly in the end positions in order for the pendulum's movement to correspond to the output amount of the primary path per unit of time, which entails large point stresses in the mechanical structures. Therefore, the mechanism can conveniently be used only at discharge rates below about 100 m / min.

A disadvantage of high pendulum frequency pendulum mechanisms is, moreover, the strong air currents which arise when the large surface pendulum mechanism moves rapidly on and off. The air currents interfere with the closure of the thin primary web on the substrate.

From earlier, commuting mechanisms for laying thin primary paths in overlapping layers on a receiver conveyor are thus known. However, they all suffered from significant disadvantages; the edges are uneven and cause a great deal of material waste; the speeds are too low to meet the capacity requirement; the deceleration and acceleration forces are high and cause Large mechanical stresses in the structures; the air flow problem aggravates a safe layout of the primary path.

The purpose of this invention is to reduce or completely eliminate these drawbacks and in particular to achieve an accurate layout with even edges and high homogeneity in the web. This has been achieved by establishing a method and a device whose essential features are set forth in claims 1 and 7.

In an advantageous embodiment according to the invention, a prior art drive system is used which gives the oscillating pendulum conveyor, hereinafter called the pendulum, a constant rate of movement in the center of the pendulum movement and sinusoidal decreasing and increasing velocity in the end positions of the pendulum movement. The period of constant speed can vary between 30 and 60% of the entire pendulum stroke. The constant velocity of the pendulum in the center region corresponds wholly or almost completely with the output velocity of the primary path 4,83674 '. This allows the pendulum to be closer to the receiving surface, at about half the distance compared to what was possible in conventional cranking, with a significantly safer layout and fixing of the primary path on the receiving conveyor so that it follows.

In the areas outside the constant speed phase, the pendulum is driven at a sinusoidal decreasing and increasing speed, while the pendulum continues its pendulum movement. During at least part of the movement with decreasing and increasing velocity in the outer positions of the pendulum stroke, the output end of the pendulum is arranged to rise in the final phase of the pendulum movement and to sink in the initial phase. Thanks to the height change of the pendulum during the deceleration and acceleration phases, respectively. potential energy is released which makes the actuation forces on the mechanism less than when the output end of the pendulum describes a horizontal path over the entire pendulum stroke.

The pendulum movement consisting of a center part at a constant speed and: two end parts at a decelerating and accelerating speed are conveniently accomplished by means of an endless drive chain running across two in the same pane and at a certain distance from each other sprockets, whereby a crank connecting the pendulum to a co-driver on the drive chain. The center distance between the sprockets corresponds to the portion of the pendulum movement which has a constant velocity and each • half the circumference of the wheel corresponds to the pendulum movement at a decelerating and accelerating speed.

The pendulum movement consisting of a center part at a constant speed and. two end portions with decelerating and accelerating speeds can also be achieved by, for example, a so-called "Ferguson" gear, where the rotational motion is transmitted with elliptical gears.

! The pendulum and its output end can, during the course of the pendulum movement: be controlled to move in webs of different shapes. The simplest embodiment is an octagonal movement path, the pendulum pivoting about a stationary storage point. According to one such embodiment, the pendulum operates

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5 83674 with great accuracy at application speeds of about 200 m / min.

This is possible thanks to the fact that the output end of the pendulum can extend very close to the receiving conveyor and closest to it in the center of the pendulum stroke, whereby the laid out primary web can immediately be fixed in the underlying laid out wool web and thereby not disturbed by the air currents of the pendulum movement. In the outermost positions of the pendulum movement, the lower end of the pendulum increases about 0.1 times the laying width or about 20 cm at a laying width of 200 cm, which results in a more precise position for the folding at the edges as a result of the smaller winding path of the wool web. Another advantage of this embodiment is that the pendulum can be made relatively short, about 0.7-1.0 times the layout width, about 140-200 cm, and this results in lower mass moment of torque and less force sensing in the drive. The air flow disturbances also become smaller with a shorter pendulum.

In this embodiment, the pendulum can be set to extend at its nearest point only 5-10 cm above the receiver conveyor and thus, almost immediately, fix the suspended path in the center region of the path. This leads to a wool web with very even edges. With a constant velocity above about 50% of the paving width, which is 200 cm, and a maximum pendulum swing of 80% and a pendulum length of about 75% of the paving width, i.e. 150 cm, the pendulum rises in the outer positions about 12%, i.e.

24 cm.

Another advantageous embodiment of the invention is that in which the pendulum and its output end are caused to move horizontally in the center zone of the pendulum stroke at a constant height above the receiving conveyor and in the outer zones rise from it. The raising motion can be started where, as heist after the center position of the pendulum movement, but most recently during the deceleration phase of the pendulum movement, so that for the primary path, which is output at constant speed from the output end of the pendulum, sufficient space is formed for an accumulating alternating path with the output end end. output rate. Thus, the rising motion begins at the earliest immediately after the pendulum 6 83674 'roro Lson' middle position, whereby the pendulum and Ge> 's discharge end describe a continuous bag-shaped line, or at the latest so much pending insertion. the outer position of the aa, that during the rising pendulum, there is sufficient space in Ida's space for the accumulating coil, said that at the return movement one lies restrained and forms an even chariot. The rising path described by the discharge end may be linearly ascending, circular, progressively baking or various combinations thereof.

By means of various control devices the pendulum is forced to deviate from the natural pendulum movement with a circular discharge path. As soon as one deviates from the natural pendulum movement, the pendulum's oscillation point must be movable vertically.

For example, when desiring a dispensing web consisting of a substantially horizontal portion of a center portion and a bag-shaped end portion, the arm stored at the pendulum at its lower end may be pivotally stored outside the pendulum, thereby forcing the pendulum to describe a substantially horizontal path. During this part of the movement, the pen's pivot point drops / rises. The pivot point is arranged to meet a stop or otherwise stop in the pelvis where the pendulum must switch to movement up in the outer zone of the pendulum rake and down into the sarana zone during the return movement. The arm's bearing in the pendulum is arranged so that at this stage, for example, by means of a fork bearing, the pendulum swing in relation to the arm is made possible.

The movement of the pendulum can also be controlled, for example, by a fixed and symmetrically arranged guide along the center axis along which a wheel or slide body stored on the pendulum is arranged to move. The path of movement of the output end will then correspond to the shape of the guide. The height of the guide from the output end is determined by the optimization of the geometry and the mass forces.

A spring can conveniently be arranged between the pendulum crank stop and the arm which controls the height of the pendulum, whereby the acceleration and deceleration forces are partially offset in the outermost position of the pendulum.

In the following, the invention will be described in more detail in the form of some advantageous embodiments of the invention and with reference to the accompanying figures, in which: Figure 1 shows a schematic representation of the pendulum movement according to two advantageous embodiments; the movement of the pendulum at a constant speed and then at a decelerated and accelerated speed, all below the output end of the pendulum, describes a circular path (case A) and the movement of the pendulum at a constant speed and then at a decelerated and accelerated speed while the output end during the constant speed phase moves at a constant height above the receiver conveyor and during the deceleration and acceleration phases, L moves a two-lane path (fa 1 l 'f. n), figure 2 shows an advantageous embodiment of the pendant with accessory drive device and the pendant shown in three different positions, and figure 3 shows another advantageous embodiment of the pendulum with the associated drive device and with the pendulum shown in three different positions.

In Figure 1, the right side of the figure shows the case (A), where the pendulum • jabbed during the period of constant speed and the period of accelerated and accelerated speed pivots around the point P, which in this case is stationary , and the output end describes a circular pitch. The pendulum is driven by the drive device D at a constant speed chain. A tie rod V is stored on a carrier to the drive chain at point T and to the pendulum mechanism at point K. Points 1-12 are noted on the drive chain, where

* »*. A

points 1 and 7 indicate the center position of the pendulum, points 4 and 10 of the pendulum: * V extreme positions and points 12 and 2 and 6 and 8, respectively, the boundaries of the area at constant speed. Since the point T of the loom is; in position 1, the pendulum hangs down from the pivot point P and the position of the output end is shown by the number 1 (A). From 1 to 2, the crankshaft moves at a constant speed and the discharge end describes a circular lug because the pivot point P is stationary. From 2 to 4, the pendulum moves during deceleration, changes the direction of movement at point 4 and from 4 to 6 during acceleration and from 6 to 7 at a constant speed, all while the output end describes a rising and a decreasing circular lug. Dependent father

the position of the attachment point K on the pendulum relative to the drive device eA

greater or less geometric asymmetry, i.e. points 3 and 5 and 2 and 6 respectively differ slightly from each other, as shown in the sketch. In the outermost position 4, the pendulum rises approximately 24 cm, which can also be read from the figure drawn in scale 1:10, and forms a controlled loop of the primary path at the turning point. Thanks to the relative proximity of the output end to the receiver conveyor S and the correspondence between the output end

A

the feed rate and the output speed of the output end, the laid out primary web is quickly fixed to the substrate, which is also shown in the sketch. The movement of the pendulum from points 7 to 1 is the mirror image of the movement between points 1 and 7, but has not been shown.

The left side of Figure 1 shows the case (B) where the output end of the pendulum during the constant speed period moves on the console; tant height above the receiving conveyor S and during the period.

B

the for retarded and accelerated motion moves along a circular path. In the center position of the pendulum, point 7, the pendulum turns; but drops to the point P during the driving motion up to point 8, the output end moving along a horizontal line. During the deceleration stage from point 8 to 10 and the acceleration stage from point 10 to 12, the pivot point P is poured stationary and the output end describes a circular pitch. As shown in the figure, the reception "in" the gSport transports is higher up in case A because the pendulum in the middle position in case B has its pivot point higher up.

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The pendulum rises in its outermost position about 16 cm which can be read from the figure. In this case, the loop formation is also extremely restrained thanks to the proximity of the primary path to the substrate especially during the stretch 7 - R and 12-1 and the correspondence in the output speed and the output speed of the output end during said distances.

To ascertain that the output end of the pendulum moves horizontally during a large part of, in the cases shown, 50% of the pendulum stroke, where the pivot point must move from P 'to P, special measures are required. A couple of advantageous embodiments with such arrangements are shown in Figures 2 and 3.

Figures 2 and 3 show the pendulum portion of a machine for manufacturing a mineral wool web and associated drive mechanism. The take-away conveyor has been designated 1, the associated conveyor in the pendulum conveyor with 2, its two resistant conveyors ined 2a and 2b and the break rollers at the discharge end with 3a and 3b. The receiving conveyor has been denoted by 4, the drive mechanism by 5, the two wheels by the drive mechanism by 5a and 5b, and the crankcase by 6. Parts 1-6 correspond to each other in Figures 2 and 3 and: · · are therefore denoted by the same numbers.

• »· · ·: · In figure 2 it has wheels which in a guide device control the pendulum movement. denoted by 7 and the wheel pl. the shuttle conveyor fixed shaft with 7a. The guide which the wheel 7 is arranged to run along and which determines the path of movement of the output end has been denoted by 9. The output end of the pen conveyor has been denoted by 10.

In the production of the mineral wool web, the primary web is measured down on its receiver conveyor 1 and further runs between the conveyors 2a and 2b in the pendulum mechanism 2, and is discharged at the output end 10.. The pendulum turns off and on while the primary path is measured '**. between the break rollers 3a and 3b. As the connecting rod moves between the drive. the wheels 5a and 5b, the distance b ^, the wheel 7 obtains a constant speed of movement and at the same time moves over the flat part of the gear 8 3 6 7 4 on the 9, while the break rollers 3a and 3b travel the distance on? constant height above the receiver conveyor. As the crankcase moves along the periphery of the drive wheel, corresponding to the distances b, the wheel 7 moves over the bent ends of the guide 9, the pendulum? m. wet end discloses a corresponding octagonal path over stream B can. The position of the guide 9 is determined by the desired geometry of motion. The pivot point of pivot 22 is arranged to be displaceable along the line of the center pendulum movement and the receiving path conveyor 1 of the primary path is articulated in order to be able to follow the movement in the vertical direction of the pendulum input end.

Figure 3 shows another advantageous embodiment of the pendant according to the invention. An arm 20 is fixedly fixed at its lower end outside the pendulum on the center line of the pivotal movement, and at its upper end forked to the storage point 8 of the crank 6 on the pendulum. The storage point 8 is arranged to run in the fork 21 at the upper end of the scythe. The pivot point 22 is vertically displaceable along the motion:? line center and the primary path receiving conveyor 1 are articulated stored so as to be able to follow the pendulum movements in vertical direction, in the same way as in the preceding case. As the crankcase moves over it: the horizontal area between the drive wheels pulls out the pendulum in angular position while the pivot point moves downward until at the end of the constant speed period it bumps against a stop 23. The stop prevents the further swing of the pivot point. and the pendulum is forced to pivot around the now fixed pivot point P. During this retarding portion of the movement, the attachment point 8 is moved upward in the fork 21, thereby not preventing the pendulum's elevation along an ovoid line. During the following acceleration stage, the pendulum swings down and the discharge end 10 describes the same bag-shaped line at the same time as the attachment point 8 is displaced against the bottom of the fork 21. The same movement is repeated at opposite hali.

It is advantageous to arrange a spring between the center shaft and the arm 20 to absorb some of the deceleration and acceleration forces that arise during the pendulum swing.

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The embodiments of Figures 2 and 3 each show a similarly composed pendulum movement, that the horizontal or substantially horizontal output movement coincides with the phase of constant velocity and the rising or decreasing movement, respectively, coincides with the phase of retarded and accelerated velocity, respectively. Of course, the forced-end of the output end, which varies from the oblique path of movement, can be controlled to begin where as heist during the period of constant velocity b 2 or the period of decelerating and accelerating movement b 2

It will be apparent that one skilled in the art can implement the inventive idea with a pendulum movement rising in the end positions, which has a constant rate of movement in the center phase of the pendulum stroke, in a variety of ways in addition to the embodiments described herein.

Claims (10)

A method for folding a thin, mineral wool, binder-treated uncured primary web on a receiving conveyor (4) to provide rapid adhesion of the web to a primary web already fed to the receiving conveyor, the method folding the web into a receiving conveyor , and when the speed of the receiving conveyor is lower than the output speed of the primary web so that the primary web descends into limit folds forming a secondary web of the desired thickness, characterized in that the outlet end (10) of the pendulum conveyor (2) is at least 30% and at most 60%, preferably 50%, of the total oscillation and is equal to or close to the output speed of the primary web, and that the remaining portion oscillates the deceleration conveyor outlet end (10) rises at least by a certain portion of the decelerating motion, which includes the remainder of the decelerating motion, and immediately thereafter descends by a corresponding portion of the accelerating motion of the return motion. A method according to claim 1, characterized in that the outlet end (10) of the pendulum conveyor (2) starts to rise during the constant speed phase, continuing to rise during the whole deceleration phase, and descends during the corresponding acceleration phase and constant speed phase. i6 8 3 6 74 A method according to claim 1, characterized in that the outlet end (10) of the pendulum conveyor (2) follows an arcuate path, most preferably a circular arc, during the entire pendulum movement. A method according to claim 1, characterized in that the outlet end (10) of the pendulum conveyor (2) follows a substantially horizontal path to the point where it starts to rise and from the point to which it has descended. Method according to claim 4, characterized in that the outlet end (10) of the pendulum conveyor (2) follows a substantially horizontal path during the constant speed phase and rises, most preferably arcuately, during the decelerating phase phase, and that it descends, most preferably arcuately, during the accelerating speed during the phase and moves to a substantially horizontal motion during the constant speed phase of the return movement. Method according to one of the preceding claims, characterized in that the pendulum conveyor (2) is moved by means of a chain drive (5) and a palm (6) known per se. 1 2 Apparatus for folding a thin, mineral wool, binder-treated uncured primary web on a receiving conveyor (4) to provide rapid adhesion of the web to a primary web already fed to the receiving conveyor, the apparatus comprising a predominantly horizontal first receiving conveyor (2) ), from the lower end (10) of which the primary web is fed to said receiving conveyor (4) below, the pendulum conveyor oscillating in a plane perpendicular to the direction of movement of the latter receiving conveyor (4) and the speed of movement of this receiving conveyor forming a secondary web of the desired thickness i7 83674, the pendulum conveyor being adapted to receive its pendulum movement from a crank (6) its end is connected to a pendulum conveyor and at one end to an endless drive chain running around two sprockets (5a, 5b) in the same plane and at a certain distance from each other, characterized in that the distance between the sprockets (5a, 5b) and the wheel diameters are adjusted so that the movement of the palm with the drive chain over the horizontal portion is at least 30% and at most 60%, most preferably 50% of the pendulum oscillation, that the crank or close to this, and the remainder of the oscillation shall have a decelerating speed before the extreme position of the oscillation and an accelerating velocity after the extreme position, essentially equal parts of the oscillation, and that h the output end (10) of the rotary conveyor (2) is adapted to follow an upward movement of at least a certain portion of the oscillation before the extreme position and a descending movement of an equal length after the extreme position, either as a result of its free pendulum motion or by means of free pendulum motion devices. Device according to claim 7, wherein the pendulum shaft (22) of the pendulum conveyor (2) is adapted to be vertically displaceable to allow horizontal movement of the output head (10), characterized in that the pivot arm (20) is fixedly mounted or similarly mounted on a pendulum conveyor (2) with a degree of freedom such that the pendulum conveyor is capable of performing a complete oscillation regardless of the length of the arm. Device according to Claim 8, characterized in that the vertical movement of the pendulum axis (22) of the pendulum conveyor (2) is adapted to stop and move to free pendulum movement in the horizontal part of the trajectory of the pendulum conveyor outlet end (10). Device according to Claim 9, characterized in that the stop (23) is adapted to stop the vertical movement of the pendulum shaft (22) as the pendulum conveyor (2) moves into free pendulum movement. Device according to Claim 7 or 8, characterized in that at least one wheel (7) or a corresponding roller or sliding element is arranged on the pendulum conveyor (2) so that, in contact with the control device (9) during pendulum movement, it transmits the desired pendulum conveyor (2) range of motion.