CA1289981C - Process and device for feeding a thin binder impregnated uncured primary webof mineral wool onto a receiving conveyor - Google Patents
Process and device for feeding a thin binder impregnated uncured primary webof mineral wool onto a receiving conveyorInfo
- Publication number
- CA1289981C CA1289981C CA000550646A CA550646A CA1289981C CA 1289981 C CA1289981 C CA 1289981C CA 000550646 A CA000550646 A CA 000550646A CA 550646 A CA550646 A CA 550646A CA 1289981 C CA1289981 C CA 1289981C
- Authority
- CA
- Canada
- Prior art keywords
- pendulum
- conveyor
- movement
- output end
- speed
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H45/00—Folding thin material
- B65H45/02—Folding limp material without application of pressure to define or form crease lines
- B65H45/06—Folding webs
- B65H45/10—Folding webs transversely
-
- D—TEXTILES; PAPER
- D04—BRAIDING; LACE-MAKING; KNITTING; TRIMMINGS; NON-WOVEN FABRICS
- D04H—MAKING TEXTILE FABRICS, e.g. FROM FIBRES OR FILAMENTARY MATERIAL; FABRICS MADE BY SUCH PROCESSES OR APPARATUS, e.g. FELTS, NON-WOVEN FABRICS; COTTON-WOOL; WADDING ; NON-WOVEN FABRICS FROM STAPLE FIBRES, FILAMENTS OR YARNS, BONDED WITH AT LEAST ONE WEB-LIKE MATERIAL DURING THEIR CONSOLIDATION
- D04H1/00—Non-woven fabrics formed wholly or mainly of staple fibres or like relatively short fibres
- D04H1/40—Non-woven fabrics formed wholly or mainly of staple fibres or like relatively short fibres from fleeces or layers composed of fibres without existing or potential cohesive properties
- D04H1/42—Non-woven fabrics formed wholly or mainly of staple fibres or like relatively short fibres from fleeces or layers composed of fibres without existing or potential cohesive properties characterised by the use of certain kinds of fibres insofar as this use has no preponderant influence on the consolidation of the fleece
- D04H1/4209—Inorganic fibres
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H45/00—Folding thin material
- B65H45/02—Folding limp material without application of pressure to define or form crease lines
- B65H45/06—Folding webs
- B65H45/10—Folding webs transversely
- B65H45/101—Folding webs transversely in combination with laying, i.e. forming a zig-zag pile
- B65H45/107—Folding webs transversely in combination with laying, i.e. forming a zig-zag pile by means of swinging or reciprocating guide bars
-
- D—TEXTILES; PAPER
- D04—BRAIDING; LACE-MAKING; KNITTING; TRIMMINGS; NON-WOVEN FABRICS
- D04H—MAKING TEXTILE FABRICS, e.g. FROM FIBRES OR FILAMENTARY MATERIAL; FABRICS MADE BY SUCH PROCESSES OR APPARATUS, e.g. FELTS, NON-WOVEN FABRICS; COTTON-WOOL; WADDING ; NON-WOVEN FABRICS FROM STAPLE FIBRES, FILAMENTS OR YARNS, BONDED WITH AT LEAST ONE WEB-LIKE MATERIAL DURING THEIR CONSOLIDATION
- D04H1/00—Non-woven fabrics formed wholly or mainly of staple fibres or like relatively short fibres
- D04H1/70—Non-woven fabrics formed wholly or mainly of staple fibres or like relatively short fibres characterised by the method of forming fleeces or layers, e.g. reorientation of fibres
- D04H1/74—Non-woven fabrics formed wholly or mainly of staple fibres or like relatively short fibres characterised by the method of forming fleeces or layers, e.g. reorientation of fibres the fibres being orientated, e.g. in parallel (anisotropic fleeces)
Landscapes
- Engineering & Computer Science (AREA)
- Textile Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Inorganic Chemistry (AREA)
- Treatment Of Fiber Materials (AREA)
- Advancing Webs (AREA)
- Preliminary Treatment Of Fibers (AREA)
- Paper (AREA)
- Jigging Conveyors (AREA)
- Structure Of Belt Conveyors (AREA)
- Reinforced Plastic Materials (AREA)
Abstract
Abstract The invention relates to a process for feeding out a primary web of mineral wool onto a receiving conveyor. For this purpose, a pendulum conveyor has been used. In order to achieve good quality and the desired capacity the primary web must be thin and output rate high, which causes problems in fixing the primary web into the already fed out web and in looping the edges of the fed out web. According to the invention, these problems have been solved by making the trajectory and rate of motion of the output end (10) of the receiving conveyor (2) to comprise a central portion (B1) with a constant speed, which equals or is close to the output rate of the primary web, and an outmost portion (B2) having a retarding or accelerating speed, respectively. By this means the output end may move close to the receiving conveyor and be rapidly fixed into the bed while the pendulum allows appropriate space in the extreme positions for the edge loop, which also is rapidly fixed into the bed and forms an even edge. The invention relates also to a device for carrying out the process.
Description
lZ~39~81 A process and de~ice for feeding a thin binder impregnated un-cured primary web of mineral wool onto a recei~ing conveyor The present in~ention re1ates to a process for feeding a thin binder impregnated uncured mineral wool web on a receiving con-~eyor and to a de~ice for carrying out the process according to the preamble of claims 1 and 9.
When manufacturing mineral wool sheets, it is crucial to achie~e a product that is as uniform and homogenous as possible, yielding a higher insulation capacity. Moreo~er, it should be as elastic as possible at a low density, requiring the fibres to be extended mainly in the sheet plane. Due to the elasticity, the sheet may be compressed for the packing and transport step.
in order to achie~e this, a thin primary web, of which the basis weight ~aries in the range of 110 to 450 g/m , preferably 100 to 200 g/m is collected on a collecting con~eyor immediately after the defibration. The thinner the primary web, the better the quality of the finished product. In order to keep the capacity on the desired level while producing a thin primary web, the speed of the primary web as well as that of its con~eying de~ices has to be high. Normally, the speed of the primary web is o~er 100 m/min, howe~er, the basis weight of the primary web being only in the range of 100 to 200 g/m , an e~en higher speed is required in order to keep the capacity on the desired le~el.
Various methods of folding mineral wool webs are described in the US patent specification 2 450 916 from 1948 and the somewhat younger GB patent specification 772 628, among others. These ha~e subsequently been completed with methods of folding the primary web by means of pendulum con~eyors.
~289381 When pendulum con~eyors are being used for the feeding out of pri-mary web, it is critical that the speed of the output end is about the same as that of the primary web, in order to a~oid folding or stretching of the web at the output moment.
Up till now, the pendulum mechanism usually has comprised an ope-ration, in which the extreme positions ha~e been highest abo~e the recei~ing con~eyor, and the lower dead point of the pendulum has been closest to the recei~ing con~eyor. In order to achie~e the desired capacity with the thin primary webs, the out-put rate of the pendulum con~eyors should increase, howe~er this is not feasible with known de~ices. In fact, a high speed pendu-lum conveyor that feeds out a light web and has a high pendulum frequency yields an inexact laying of the primary web. A pendulum con~eyor dri~en in a known manner by a connecting rod and oscil-lating along a circular arc imparts a speed to the output end of the con~eyor that is maximal when the pendulum is in the central position and decreases sinusoidally to zero in the extreme posi-tion, from where a sinusoidal acceleration reoccurs. The output end of such a pendulum con~eyor must, in its lowest position, be disposed c. 0,2 times the output width, which normally is 2 m, abo~e the fed out wool web, in order to allow the primary web to be deposited in an uniform layer on the recei~ing con~eyor without being stretched. The distance between the pendulum and the recei~-ing con~eyor being that long up to 40 cm and more, the fed out web will get une~en edges. The output rate being c. 130 m/min, the irregularities of the secondary web formed will be c. +/_ ~a of the output width. This signifies that the secondary web must be imparted a correspondingly larger width in order to achie~e a faultless web of the desired width, since the undesired material has to be cut off. This means a great loss of material.
Pendulum output mechanisms, in which the folding process is car-ried out by continuously feeding out the primary web at a constant height abo~e the support, at a constant height, are also known. An 128998~
articulation system for maintaining the output end of the pendulum mechanism at a constant height abo~e the receiving con~eyor is pro~ided, and the to and fro motion is obtained by a chain/con-necting rod-mechanism. The speed profile of the oscillating motion has a constant speed period in the middle and a sinoidal retarda-tion and acceleration phase in each end position. The pendulum must be rapidly retarded and accelerated in the end positions for the pendulum motion to correspond to the output amount of the primary web per unit of time, causing great strains in the mechan-ical constructions. Consequently, the mechanism is appropriate only at output rates below c. 100 m/min.
Another drawback of pendulum mechanisms ha~ing a high pendulum frèquency is constituted of the strong flows of air generated by the rapid back and fro motion of a pendulum mechanism ha~ing a large surface. The air flows hamper the depositing of the thin primary web onto the bed.
Prior known are thus pendulum mechanisms for feeding thin pri-mary webs in o~er-lapping layers on a recei~ing con~eyor.
However, they all present considerable drawbacks; the edges are uneven, causing great loss of material, the speeds are too low to fullfil the capacity requirement, the retardation and acceleration forces are strong, causing great mechanical stress in the con-structions: the problem of air flow jeopardizes the depositing of the primary web.
The purpose of the present in~ention is to reduce or totally eliminate these drawbacks, and especially to obtain an exact out-laying with e~en edges and a web with high homogeneity, and this has been achie~ed by pro~iding a method and a de~ice, of which the main characteristics are presented in claims 1 and 6 In a preferred embodiment of the in~ention a prior known dri~e system is used, imparting to the oscillating pendulum con~eyor, called pendulum from now on, a constant rate of motion in the ~ ~r middle of the pendulum motion and a sinusoidally decreasing respecti~ely increasing speed in the extreme positions of the pendulum motion. The period ha~ing constant speed may be in the range of 30 to 60% of the entire pendulum swing. The constant speed of the pendulum in the central area equals totally or nearly totally the output rate of the primary web. This enab-les the pendulum to be disposed closer to the recei~ing surface, at about half of the distance allowed by con~entional crank dri~e, thus ensuring considerably better the deposit and the fixation of the primary web on the recei~ing con~eyor.
In areas outside the phase ha~ing a constant speed the pendulum is dri~en at a sinusoidally decreasing respecti~ely increasing ra-te, while the pendulum pursues its pendulum motion. At least during part of the motion at a decreasing respecti~ely increa-sing rate in the extreme positions of the pendulum swing, the output end of the pendulum is arranged to rise in the final phase of the pendulum motion and to sink in the initial phase. Due to the changing of the height of the pendulum in the retardation re-spectively the acceleration phase, potential energy is stocked respectively discharged, resulting in less stress forces on the mechanism than those generated when the output end of the pendulum describes a horizontal path o~er the entire pendulum swing.
The pendulum motion, consisting of a central portion ha~ing a constant speed and two extreme portions having retarding and ac-celerating speeds, is appropriately produced by means of an end-less dri~e chain running over two coplanar interspaced chain wheels, whereby a connecting rod connects the pendulum with a carrier on the dri~e chain. The centre distance of the chain wheels corresponds to the portion of the pendulum motion ha~ing a constant speed and half the circumference of each wheel corres-ponds to the pendulum motion ha~ing retarding and accelerating speed.
~28998~
The pendulum motion consisting of a central portion ha~ing constant speed and two extreme portions ha~ing retarding and accelerating speed may also be produced by means of a so-called Ferguson gear, in which the rotary motion is transmitted by elliptical gear wheels.
The output end of the pondulum may be guided to mo~e along diffe-rently shaped paths in the course of the pendulum motion. The most simple embodiment is an arched trajectory, whereby the pendulum swings around a stationary point of bearing. In such an embodi-ment, the pendulum operates with great accuracy at output rates of c. 200 m/min. This is allowed by the fact that the output end of the pendulum may strike ~ery close to the recei~ing con~eyor, and closest thereto at the midpoint of the total swing, whereby the fed out primary web may be immediately fixed into the underlying fed out wool web and thus remains undisturbed by the air flows caused by the pendulum motion. In the extreme positions of the pendulum motion the lower end of the pendulum rises c. 0.1 times the output width i.e. appr. 20 cm with an output width of 200 cm, resulting in a more exact position for the edge folding, due to the smaller folding loop of the wool web. Another ad~antage of this embodiment is that the pendulum may be relati~ely short, c.
0.7 to 1.0 times the output width, i.e. c. 140 to 200 cm, which results in lower mass-moments of inertia and smaller stresses in the dri~ing de~ice. The air flow disturbances are also reduced by a shorter pendulum.
In this embodiment, the pendulum may be adjusted to strike at its closest point only 5 to 10 cm above the recei~ing con~eyor and thus to fix almost immediately the fed out web into the central area of the trajectory. This results in a wool web ha~ing ~ery e~en edges. At a constant speed of abo~e c. 50% of the out-put width, which is 200 cm, and a maximum pendulum swing of 80%
and a pendulum length of c. 75% of the output width, i.e. 150 cm, the pendulum rises c. 12%, i.e. 24 cm, in the extreme positions.
~289981 Another preferred embodiment of the in~ention is the one in which the pendulum and its output end are made to mo~e horizontally at a constant height abo~e the recei~ing con~eyor in the central zo-ne of the pendulum swing and to rise abo~e this in the outmost positions.
The rising motion may be started at any point after the mid point of the pendulum motion, but at the latest during the retardation phase of the pendulum motion, thus allowing for the primary web, which is fed out from the output end of the pendulum at a constant rate, enough space below the output end which then mo~es at a low-er rate than the output rate of the primary web. The rising mo-tion thus starts at the earliest immediately after the mid point of the pendulum motion, the pendulum and its output end then describing a continuous arched line, or at the latest at such a point before the extreme position of the pendulum swing, that enough space is allowed to be formed below the rising pendulum for the accumulating loop to settle under control and to form an e~en edge during the re~erse motion.
The path described by the output end may be a linearly rising, circular, progressi~ely arched line or ~arious combinations of these.
By means of various guide de~ices the pendulum or its output end is forced to de~iate from the natura1 pendulum motion ha~ing a circular output path. From the moment there is a de~iation from the natural pendulum motion, the oscillating point of the pendulum must be ~ertically mo~able or the swinging radius of the output end be ~ariable.
An output traiectory consisting of a mainly horizontal central portion and an arched end portion being desired, an arm mounted on bearings in the pendulum may for instance comprise a lower end that is pi~otally mounted on bearings outside the pendulum, thus 1~89g81 forcing the pendulum to describe an essentially horizontal path.
During this part of the motion the oscillating point of the pen-dulum sinks/rises. The oscillating point has been disposed so as to reach a stop or else stop in the position in which the pen dulum is to pass into a rising motion in the outmost zone of the pendulum swing respecti~ely sinking motion in the same zone during the re~erse motion. The mounting of the arm on bearings in the pendulum is disposed so as to enable the pendulum to oscillate with regard to the arm at this stage, e.g. be means of fork bear-ings. A spring may appropriately be disposed between the connec-ting rod top of the pendulum and the arm guiding the height posi-tion of the pendulum, whereby the acceleration and retardation forces are partly equilibrated in the extreme positions of the pendulum.
The motion of the pendulum may also be guided by for instance a fixed guide disposed symmetrically with regard to the central axis along which a wheel mounted on bearings in the pendulum or a sliding body are disposed to mo~e. The trajectory of the output end will then correspond to the shape of the guide. The height of the guide abo~e the ouptut end is determined by the optimization of geometry and mass forces.
The oscillating point of the pendulum may alternati~ely be sta-tionary while the output end is radially mo~able in relation to the oscillating point.
The in~ention will be described more in detail belGw as a number of preferred embodiments of the in~ention and referring to the enclosed figures, in which:
figure 1 presents a schematical representation of the pendulum motion of two preferred embodiments; the motion of the pendulum at a constant speed and subsequently at a retarded and an accele-rated speed, while the output end of the pendulum describes a cir-~ Z89~
cular path (case A) respectively the motion of the pendu1um at a-constant speed and subsequently at a retarded and an accelerated speed while the output end during the constant speed phase moves at a constant height above the receiving conveyor and during the retardation respectively acceleration phase moves along an arched path (case 8), figure 2 shows a preferred embodiment of the pendulum including the associated driving device and the pendulum shown in three different positions, and figure 3 shows another preferred embodiment of the pendulum in-cluding the associated driving device and showing the pendulum in three different positions.
In figure 1, the right side of the figure shows the case (A), in which the pendulum both during the period at a constant speed and the period at a retarded and an accelerated speed oscillates around the point P, which is stationary in this case, and the output end describes a circular arc. The pendulum is driven by the guide device D by means of a chain having constant speed.
A connecting rod V is mounted on bearings on a carrier to the drive chain at the point T and to the pendulum mechanism at the point K . In the drive chain the points 1 to 12 have been mark-ed, whereby the points 1 and 7 indicate the central position of the pendulum, the points 4 and 10 the extreme positions of the pendulum and the points 12 and 2 respectively 6 and 8 the limits of the area having a constant speed. When the point T of the connecting rod is in the position 1, the pendulum is suspended from the oscillating point P and the position of the output end is indicated by the number 1 (A). From 1 to 2 the connecting rod mo-ves at a constant speed and the output end describes a circular arc since the oscillating point P is stationary. From 2 to 4 the pendulum moves with retardation, changes the direction o~ motion at the point 4 and from 4 to 6 with acceleration, while the out-, ~2sssal put end describes a rising respecti~ely sinking circular arc fromthe connecting rod 6 to 7 mo~es at a constant speed, while the ouput end describes a rising respecti~ely a sinking circular arc.
Depending on the position of the fastening point KA on the pen-dulum with regard to the dri~e de~ice D, more or less geometrical assymmetry is achie~ed, i.e. the points 3 and 5 respecti~ely 2 and 6 deviate somewhat from each other, which appears from the rough drawing. The pendulum rises in the extreme position 4 c. 24 cm, which also appears from the figure drawn in the scale 1:10, and forms a controlled loop of the primary web at the turning point.
Owing to the smaller distance of the output end to the recei~ing con~eyor S and the synchronization between the output rate and the oscillating rate of the output end, the fed out primary web is rapidly fixed to the bed, which also appears from the rough draw-ing. The motion of the pendulum from the point 7 to 1 is the re-verse image of the motion between the points 1 and 7, howe~er not represented.
The left side of figure 1 shows the case (B) in which the output end of the pendulum during the period of constant speed mo~es at a constant height abo~e the recei~ing con~eyor SB and during the period of retarded and accelerated motion mo~es along a circular path. In the central position of the pendulum, point 7, the oscil-lating point of the pendulum is at P but sinks to the point P
during the dri~e motion up to point 8, whereby the output end mo-~es along a horizontal line. During the retardation phase from point 8 to 10 and the acceleration phase from point 10 to 12, the oscillating point P is kept stationary and the output end descri-bes a circular arc. As it appears from the figure, the recei~ing con~eyor SB is situated higher than in case A, because the oscillating point of the pendulum is higher placed in the central position in case B.
, -:
, `
~289~8~
The pendulum rises in its extreme position c. 16 cm, which appears from the figure. The looping is well controlled also in this case due to the short distance of the primary web to the bed particu-larly o~er the distances 7-8 and 12-1 and to the synchronization between the output rate and the oscillating rate of the output end o~er these distances.
In order to make the output end of the pendulum mo~e horizontally during a major part, in the shown cases 50% of the pendulum swing, whereby the oscillating point must mo~e from P to P, special measures are required. Two preferred embodiments of such arrange-ments are shown in f;gures 2 and 3.
Figures 2 and 3 show the pendulum part of a machine for producing mineral wool web and the associated dri~e mechanism. The recei-~ing con~eyor of the primary web is marked with 1, the associated pendulum con~eyor with 2, the two opposite con~eyors with 2a and 2b and the conducting rollers in the output end with 3a and 3b.
The receiving con~eyor has been marked with 4, the dri~e mechanism with 5, the two wheels of the dri~e mechanism with 5a and 5b and the connecting rod with 6. The parts 1 to 6 correspond mutually in the figures 2 and 3 and ha~e thus been marked with the same numbers.
In figure 2, the wheel that conducts the pendulum motion in a guide de~ice has been marked with 7 and the axis of the wheel fi-xed on the pendulum con~eyor with 7a. The guide along which the wheel 7 has been arranged to run and which determines the tra-jectory of the output end has been marked with 9. The output end of the pendulum con~eyor has been marked with 10.
When producing a mineral wool web, the primary web is fed out on its recei~ing con~eyor 1 and runs further between the con~eyors 2a and 2b into the pendulum mechanism 2, and is fed out at the output end 10. The pendulum swings to and fro while the primary web is being fed out between the conducting rollers 3a and 3b. As i289~
the connecting rod mo~es between the dri~e wheels 5a and 5b, the distance b , the wheel 7 gains a constant rate of motion and simultaneously mo~es o~er the plane portion of the guide 9, whe-reby the conducting rolls 3a and 3b co~er the distance Bl at a constant height abo~e the recei~ing conveyor. As the connecting rod mo~es along the circumference of the dri~e wheels, equalling the distances b2, the wheel 7 mo~es o~er the upwards bended end of the guide 9, whereby the output end of the pendulum describes a corresponding arched path o~er the distance B2. The position of the guide 9 is determined by the desired kinetic geometry. The oscillating point 22 of the pendulum is displacable along the line of the central pendulum motion and the recei~ing con~eyor 1 of the primary web is mounted on bearings by articulation in order to be able to ~ertically follow the motion of the input end of the pendulum.
Figure 3 shows another preferred embodiment of the pendulum of the in~ention. The lower end of an arm 20 is fixed on bearings outsi-de the pendulum on the central line of the oscillating motion, and its upper end is mounted on fork-bearings to the bearing point 8 of the connecting rod 6 on the pendulum. The bearing point 8 is disposed to run in the fork 21 at the upper end of the arm. The oscillating point 22 of the pendulum is ~ertically displacable along the central line of the motion and the recei~ing con~eyor 1 of the primary web is mounted on bearings by articulation in or-der to be able to follow the mo~ements of the pendulum ~ertically, likewise as in the preceding case. As the connecting rod mo~es o~er the horizontal area between the dri~e wheels the pendulum is drawn into an angular position while the oscillating point mo~es downwards until its reaches a stop 23 at the end of the constant speed period. The stop pre~ents the oscillating point from being further dispaced downwards and the pendulum is forced to swing around the oscillating point P fixed by now. During this retarding part of the motion the fastening point 8 is displaced upwards in the fork 21 and thus does not pre~ent the pendulum from rising along an arched line. During the subsequent accelera-tion phase the pendulum swings down and the output end 10 descri-bes the same arched line, while the fastening point 8 simulta-neously is displaced towards the bottom of the fork 21. The same motion is repeated in the opposite direction.
It is ad~antageous to dispose a spring between the central axis and the arm 20 to pick up part oF the retardation and acceleration forces generated by the oscillation of the pendulum.
The embodiments of figures 2 and 3 each show a pendulum motion composed so that the horizontal or essentially horizontal output motion coincides with the phase ha~ing a constant speed and the rising respecti~ely sinking motion coincides with the phase ha~ing retarded respecti~ely accelerated speed. The controlled trajectory of the output end, de~iating from the arched trajectory, may of course be adjusted to start at any point during the periGd of constant speed b or the period of retarding or accelerating motion b2.
As stated abo~e, the retardation and acceleration forces are less than in prior used methods, partly due to the rising motion at the sides of the output and partly due to a smaller pendulum ha-~ing less mass.
It is ob~ious that a person skilled in the art is able to accomp-lish the in~enti~e idea of a pendulum motion rising in the extreme positions, ha~ing a constant rate of motion in the central phase of the pendulum swing, in several different manners in addition to the embodiments described abo~e.
When manufacturing mineral wool sheets, it is crucial to achie~e a product that is as uniform and homogenous as possible, yielding a higher insulation capacity. Moreo~er, it should be as elastic as possible at a low density, requiring the fibres to be extended mainly in the sheet plane. Due to the elasticity, the sheet may be compressed for the packing and transport step.
in order to achie~e this, a thin primary web, of which the basis weight ~aries in the range of 110 to 450 g/m , preferably 100 to 200 g/m is collected on a collecting con~eyor immediately after the defibration. The thinner the primary web, the better the quality of the finished product. In order to keep the capacity on the desired level while producing a thin primary web, the speed of the primary web as well as that of its con~eying de~ices has to be high. Normally, the speed of the primary web is o~er 100 m/min, howe~er, the basis weight of the primary web being only in the range of 100 to 200 g/m , an e~en higher speed is required in order to keep the capacity on the desired le~el.
Various methods of folding mineral wool webs are described in the US patent specification 2 450 916 from 1948 and the somewhat younger GB patent specification 772 628, among others. These ha~e subsequently been completed with methods of folding the primary web by means of pendulum con~eyors.
~289381 When pendulum con~eyors are being used for the feeding out of pri-mary web, it is critical that the speed of the output end is about the same as that of the primary web, in order to a~oid folding or stretching of the web at the output moment.
Up till now, the pendulum mechanism usually has comprised an ope-ration, in which the extreme positions ha~e been highest abo~e the recei~ing con~eyor, and the lower dead point of the pendulum has been closest to the recei~ing con~eyor. In order to achie~e the desired capacity with the thin primary webs, the out-put rate of the pendulum con~eyors should increase, howe~er this is not feasible with known de~ices. In fact, a high speed pendu-lum conveyor that feeds out a light web and has a high pendulum frequency yields an inexact laying of the primary web. A pendulum con~eyor dri~en in a known manner by a connecting rod and oscil-lating along a circular arc imparts a speed to the output end of the con~eyor that is maximal when the pendulum is in the central position and decreases sinusoidally to zero in the extreme posi-tion, from where a sinusoidal acceleration reoccurs. The output end of such a pendulum con~eyor must, in its lowest position, be disposed c. 0,2 times the output width, which normally is 2 m, abo~e the fed out wool web, in order to allow the primary web to be deposited in an uniform layer on the recei~ing con~eyor without being stretched. The distance between the pendulum and the recei~-ing con~eyor being that long up to 40 cm and more, the fed out web will get une~en edges. The output rate being c. 130 m/min, the irregularities of the secondary web formed will be c. +/_ ~a of the output width. This signifies that the secondary web must be imparted a correspondingly larger width in order to achie~e a faultless web of the desired width, since the undesired material has to be cut off. This means a great loss of material.
Pendulum output mechanisms, in which the folding process is car-ried out by continuously feeding out the primary web at a constant height abo~e the support, at a constant height, are also known. An 128998~
articulation system for maintaining the output end of the pendulum mechanism at a constant height abo~e the receiving con~eyor is pro~ided, and the to and fro motion is obtained by a chain/con-necting rod-mechanism. The speed profile of the oscillating motion has a constant speed period in the middle and a sinoidal retarda-tion and acceleration phase in each end position. The pendulum must be rapidly retarded and accelerated in the end positions for the pendulum motion to correspond to the output amount of the primary web per unit of time, causing great strains in the mechan-ical constructions. Consequently, the mechanism is appropriate only at output rates below c. 100 m/min.
Another drawback of pendulum mechanisms ha~ing a high pendulum frèquency is constituted of the strong flows of air generated by the rapid back and fro motion of a pendulum mechanism ha~ing a large surface. The air flows hamper the depositing of the thin primary web onto the bed.
Prior known are thus pendulum mechanisms for feeding thin pri-mary webs in o~er-lapping layers on a recei~ing con~eyor.
However, they all present considerable drawbacks; the edges are uneven, causing great loss of material, the speeds are too low to fullfil the capacity requirement, the retardation and acceleration forces are strong, causing great mechanical stress in the con-structions: the problem of air flow jeopardizes the depositing of the primary web.
The purpose of the present in~ention is to reduce or totally eliminate these drawbacks, and especially to obtain an exact out-laying with e~en edges and a web with high homogeneity, and this has been achie~ed by pro~iding a method and a de~ice, of which the main characteristics are presented in claims 1 and 6 In a preferred embodiment of the in~ention a prior known dri~e system is used, imparting to the oscillating pendulum con~eyor, called pendulum from now on, a constant rate of motion in the ~ ~r middle of the pendulum motion and a sinusoidally decreasing respecti~ely increasing speed in the extreme positions of the pendulum motion. The period ha~ing constant speed may be in the range of 30 to 60% of the entire pendulum swing. The constant speed of the pendulum in the central area equals totally or nearly totally the output rate of the primary web. This enab-les the pendulum to be disposed closer to the recei~ing surface, at about half of the distance allowed by con~entional crank dri~e, thus ensuring considerably better the deposit and the fixation of the primary web on the recei~ing con~eyor.
In areas outside the phase ha~ing a constant speed the pendulum is dri~en at a sinusoidally decreasing respecti~ely increasing ra-te, while the pendulum pursues its pendulum motion. At least during part of the motion at a decreasing respecti~ely increa-sing rate in the extreme positions of the pendulum swing, the output end of the pendulum is arranged to rise in the final phase of the pendulum motion and to sink in the initial phase. Due to the changing of the height of the pendulum in the retardation re-spectively the acceleration phase, potential energy is stocked respectively discharged, resulting in less stress forces on the mechanism than those generated when the output end of the pendulum describes a horizontal path o~er the entire pendulum swing.
The pendulum motion, consisting of a central portion ha~ing a constant speed and two extreme portions having retarding and ac-celerating speeds, is appropriately produced by means of an end-less dri~e chain running over two coplanar interspaced chain wheels, whereby a connecting rod connects the pendulum with a carrier on the dri~e chain. The centre distance of the chain wheels corresponds to the portion of the pendulum motion ha~ing a constant speed and half the circumference of each wheel corres-ponds to the pendulum motion ha~ing retarding and accelerating speed.
~28998~
The pendulum motion consisting of a central portion ha~ing constant speed and two extreme portions ha~ing retarding and accelerating speed may also be produced by means of a so-called Ferguson gear, in which the rotary motion is transmitted by elliptical gear wheels.
The output end of the pondulum may be guided to mo~e along diffe-rently shaped paths in the course of the pendulum motion. The most simple embodiment is an arched trajectory, whereby the pendulum swings around a stationary point of bearing. In such an embodi-ment, the pendulum operates with great accuracy at output rates of c. 200 m/min. This is allowed by the fact that the output end of the pendulum may strike ~ery close to the recei~ing con~eyor, and closest thereto at the midpoint of the total swing, whereby the fed out primary web may be immediately fixed into the underlying fed out wool web and thus remains undisturbed by the air flows caused by the pendulum motion. In the extreme positions of the pendulum motion the lower end of the pendulum rises c. 0.1 times the output width i.e. appr. 20 cm with an output width of 200 cm, resulting in a more exact position for the edge folding, due to the smaller folding loop of the wool web. Another ad~antage of this embodiment is that the pendulum may be relati~ely short, c.
0.7 to 1.0 times the output width, i.e. c. 140 to 200 cm, which results in lower mass-moments of inertia and smaller stresses in the dri~ing de~ice. The air flow disturbances are also reduced by a shorter pendulum.
In this embodiment, the pendulum may be adjusted to strike at its closest point only 5 to 10 cm above the recei~ing con~eyor and thus to fix almost immediately the fed out web into the central area of the trajectory. This results in a wool web ha~ing ~ery e~en edges. At a constant speed of abo~e c. 50% of the out-put width, which is 200 cm, and a maximum pendulum swing of 80%
and a pendulum length of c. 75% of the output width, i.e. 150 cm, the pendulum rises c. 12%, i.e. 24 cm, in the extreme positions.
~289981 Another preferred embodiment of the in~ention is the one in which the pendulum and its output end are made to mo~e horizontally at a constant height abo~e the recei~ing con~eyor in the central zo-ne of the pendulum swing and to rise abo~e this in the outmost positions.
The rising motion may be started at any point after the mid point of the pendulum motion, but at the latest during the retardation phase of the pendulum motion, thus allowing for the primary web, which is fed out from the output end of the pendulum at a constant rate, enough space below the output end which then mo~es at a low-er rate than the output rate of the primary web. The rising mo-tion thus starts at the earliest immediately after the mid point of the pendulum motion, the pendulum and its output end then describing a continuous arched line, or at the latest at such a point before the extreme position of the pendulum swing, that enough space is allowed to be formed below the rising pendulum for the accumulating loop to settle under control and to form an e~en edge during the re~erse motion.
The path described by the output end may be a linearly rising, circular, progressi~ely arched line or ~arious combinations of these.
By means of various guide de~ices the pendulum or its output end is forced to de~iate from the natura1 pendulum motion ha~ing a circular output path. From the moment there is a de~iation from the natural pendulum motion, the oscillating point of the pendulum must be ~ertically mo~able or the swinging radius of the output end be ~ariable.
An output traiectory consisting of a mainly horizontal central portion and an arched end portion being desired, an arm mounted on bearings in the pendulum may for instance comprise a lower end that is pi~otally mounted on bearings outside the pendulum, thus 1~89g81 forcing the pendulum to describe an essentially horizontal path.
During this part of the motion the oscillating point of the pen-dulum sinks/rises. The oscillating point has been disposed so as to reach a stop or else stop in the position in which the pen dulum is to pass into a rising motion in the outmost zone of the pendulum swing respecti~ely sinking motion in the same zone during the re~erse motion. The mounting of the arm on bearings in the pendulum is disposed so as to enable the pendulum to oscillate with regard to the arm at this stage, e.g. be means of fork bear-ings. A spring may appropriately be disposed between the connec-ting rod top of the pendulum and the arm guiding the height posi-tion of the pendulum, whereby the acceleration and retardation forces are partly equilibrated in the extreme positions of the pendulum.
The motion of the pendulum may also be guided by for instance a fixed guide disposed symmetrically with regard to the central axis along which a wheel mounted on bearings in the pendulum or a sliding body are disposed to mo~e. The trajectory of the output end will then correspond to the shape of the guide. The height of the guide abo~e the ouptut end is determined by the optimization of geometry and mass forces.
The oscillating point of the pendulum may alternati~ely be sta-tionary while the output end is radially mo~able in relation to the oscillating point.
The in~ention will be described more in detail belGw as a number of preferred embodiments of the in~ention and referring to the enclosed figures, in which:
figure 1 presents a schematical representation of the pendulum motion of two preferred embodiments; the motion of the pendulum at a constant speed and subsequently at a retarded and an accele-rated speed, while the output end of the pendulum describes a cir-~ Z89~
cular path (case A) respectively the motion of the pendu1um at a-constant speed and subsequently at a retarded and an accelerated speed while the output end during the constant speed phase moves at a constant height above the receiving conveyor and during the retardation respectively acceleration phase moves along an arched path (case 8), figure 2 shows a preferred embodiment of the pendulum including the associated driving device and the pendulum shown in three different positions, and figure 3 shows another preferred embodiment of the pendulum in-cluding the associated driving device and showing the pendulum in three different positions.
In figure 1, the right side of the figure shows the case (A), in which the pendulum both during the period at a constant speed and the period at a retarded and an accelerated speed oscillates around the point P, which is stationary in this case, and the output end describes a circular arc. The pendulum is driven by the guide device D by means of a chain having constant speed.
A connecting rod V is mounted on bearings on a carrier to the drive chain at the point T and to the pendulum mechanism at the point K . In the drive chain the points 1 to 12 have been mark-ed, whereby the points 1 and 7 indicate the central position of the pendulum, the points 4 and 10 the extreme positions of the pendulum and the points 12 and 2 respectively 6 and 8 the limits of the area having a constant speed. When the point T of the connecting rod is in the position 1, the pendulum is suspended from the oscillating point P and the position of the output end is indicated by the number 1 (A). From 1 to 2 the connecting rod mo-ves at a constant speed and the output end describes a circular arc since the oscillating point P is stationary. From 2 to 4 the pendulum moves with retardation, changes the direction o~ motion at the point 4 and from 4 to 6 with acceleration, while the out-, ~2sssal put end describes a rising respecti~ely sinking circular arc fromthe connecting rod 6 to 7 mo~es at a constant speed, while the ouput end describes a rising respecti~ely a sinking circular arc.
Depending on the position of the fastening point KA on the pen-dulum with regard to the dri~e de~ice D, more or less geometrical assymmetry is achie~ed, i.e. the points 3 and 5 respecti~ely 2 and 6 deviate somewhat from each other, which appears from the rough drawing. The pendulum rises in the extreme position 4 c. 24 cm, which also appears from the figure drawn in the scale 1:10, and forms a controlled loop of the primary web at the turning point.
Owing to the smaller distance of the output end to the recei~ing con~eyor S and the synchronization between the output rate and the oscillating rate of the output end, the fed out primary web is rapidly fixed to the bed, which also appears from the rough draw-ing. The motion of the pendulum from the point 7 to 1 is the re-verse image of the motion between the points 1 and 7, howe~er not represented.
The left side of figure 1 shows the case (B) in which the output end of the pendulum during the period of constant speed mo~es at a constant height abo~e the recei~ing con~eyor SB and during the period of retarded and accelerated motion mo~es along a circular path. In the central position of the pendulum, point 7, the oscil-lating point of the pendulum is at P but sinks to the point P
during the dri~e motion up to point 8, whereby the output end mo-~es along a horizontal line. During the retardation phase from point 8 to 10 and the acceleration phase from point 10 to 12, the oscillating point P is kept stationary and the output end descri-bes a circular arc. As it appears from the figure, the recei~ing con~eyor SB is situated higher than in case A, because the oscillating point of the pendulum is higher placed in the central position in case B.
, -:
, `
~289~8~
The pendulum rises in its extreme position c. 16 cm, which appears from the figure. The looping is well controlled also in this case due to the short distance of the primary web to the bed particu-larly o~er the distances 7-8 and 12-1 and to the synchronization between the output rate and the oscillating rate of the output end o~er these distances.
In order to make the output end of the pendulum mo~e horizontally during a major part, in the shown cases 50% of the pendulum swing, whereby the oscillating point must mo~e from P to P, special measures are required. Two preferred embodiments of such arrange-ments are shown in f;gures 2 and 3.
Figures 2 and 3 show the pendulum part of a machine for producing mineral wool web and the associated dri~e mechanism. The recei-~ing con~eyor of the primary web is marked with 1, the associated pendulum con~eyor with 2, the two opposite con~eyors with 2a and 2b and the conducting rollers in the output end with 3a and 3b.
The receiving con~eyor has been marked with 4, the dri~e mechanism with 5, the two wheels of the dri~e mechanism with 5a and 5b and the connecting rod with 6. The parts 1 to 6 correspond mutually in the figures 2 and 3 and ha~e thus been marked with the same numbers.
In figure 2, the wheel that conducts the pendulum motion in a guide de~ice has been marked with 7 and the axis of the wheel fi-xed on the pendulum con~eyor with 7a. The guide along which the wheel 7 has been arranged to run and which determines the tra-jectory of the output end has been marked with 9. The output end of the pendulum con~eyor has been marked with 10.
When producing a mineral wool web, the primary web is fed out on its recei~ing con~eyor 1 and runs further between the con~eyors 2a and 2b into the pendulum mechanism 2, and is fed out at the output end 10. The pendulum swings to and fro while the primary web is being fed out between the conducting rollers 3a and 3b. As i289~
the connecting rod mo~es between the dri~e wheels 5a and 5b, the distance b , the wheel 7 gains a constant rate of motion and simultaneously mo~es o~er the plane portion of the guide 9, whe-reby the conducting rolls 3a and 3b co~er the distance Bl at a constant height abo~e the recei~ing conveyor. As the connecting rod mo~es along the circumference of the dri~e wheels, equalling the distances b2, the wheel 7 mo~es o~er the upwards bended end of the guide 9, whereby the output end of the pendulum describes a corresponding arched path o~er the distance B2. The position of the guide 9 is determined by the desired kinetic geometry. The oscillating point 22 of the pendulum is displacable along the line of the central pendulum motion and the recei~ing con~eyor 1 of the primary web is mounted on bearings by articulation in order to be able to ~ertically follow the motion of the input end of the pendulum.
Figure 3 shows another preferred embodiment of the pendulum of the in~ention. The lower end of an arm 20 is fixed on bearings outsi-de the pendulum on the central line of the oscillating motion, and its upper end is mounted on fork-bearings to the bearing point 8 of the connecting rod 6 on the pendulum. The bearing point 8 is disposed to run in the fork 21 at the upper end of the arm. The oscillating point 22 of the pendulum is ~ertically displacable along the central line of the motion and the recei~ing con~eyor 1 of the primary web is mounted on bearings by articulation in or-der to be able to follow the mo~ements of the pendulum ~ertically, likewise as in the preceding case. As the connecting rod mo~es o~er the horizontal area between the dri~e wheels the pendulum is drawn into an angular position while the oscillating point mo~es downwards until its reaches a stop 23 at the end of the constant speed period. The stop pre~ents the oscillating point from being further dispaced downwards and the pendulum is forced to swing around the oscillating point P fixed by now. During this retarding part of the motion the fastening point 8 is displaced upwards in the fork 21 and thus does not pre~ent the pendulum from rising along an arched line. During the subsequent accelera-tion phase the pendulum swings down and the output end 10 descri-bes the same arched line, while the fastening point 8 simulta-neously is displaced towards the bottom of the fork 21. The same motion is repeated in the opposite direction.
It is ad~antageous to dispose a spring between the central axis and the arm 20 to pick up part oF the retardation and acceleration forces generated by the oscillation of the pendulum.
The embodiments of figures 2 and 3 each show a pendulum motion composed so that the horizontal or essentially horizontal output motion coincides with the phase ha~ing a constant speed and the rising respecti~ely sinking motion coincides with the phase ha~ing retarded respecti~ely accelerated speed. The controlled trajectory of the output end, de~iating from the arched trajectory, may of course be adjusted to start at any point during the periGd of constant speed b or the period of retarding or accelerating motion b2.
As stated abo~e, the retardation and acceleration forces are less than in prior used methods, partly due to the rising motion at the sides of the output and partly due to a smaller pendulum ha-~ing less mass.
It is ob~ious that a person skilled in the art is able to accomp-lish the in~enti~e idea of a pendulum motion rising in the extreme positions, ha~ing a constant rate of motion in the central phase of the pendulum swing, in several different manners in addition to the embodiments described abo~e.
Claims (9)
1. A method of feeding a thin binder impregnated uncured primary web of mineral wool in zigzag formation on a receiving conveyor by means of a pendulum conveyor arranged above the receiving conveyor, said pendulum conveyor swinging in a plane perpendicular to the direction of motion of said receiving conveyor, wherein the speed of the receiving conveyor is lower than the speed at which the primary web is fed, the swinging movement of the pendulum conveyor is given a constant speed in the middle of the swinging movement and a retarding and an accelerating speed, respectively, in the end parts of the swinging movement, and the output end of the pendulum conveyor, before turning of the pendulum conveyor, is raised in relation to the receiving conveyor and is lowered after turning, during mainly the same part of the returning movement, characterized in that the output end of the pendulum conveyor covers at least 30% and maximum 60%, preferably 50%, of the pendulum stroke during the movement with a constant speed, and that the constant speed is mainly the same as the feeding speed of the primary web.
2. Method as in claim 1, characterized in that the output end of the pendulum conveyor moves at a constant distance above the receiving conveyor during at least part of, preferably during the whole, movement of said conveyor with constant speed.
3. Method as in claim 1, characterized in that the output end of the pendulum conveyor moves parallel to the receiving conveyor during the whole movement having a constant speed and during part of the following movement having a retarding speed, as well as during the return movement of the pendulum stroke during a corresponding part of the movement having an accelerating speed and again, during the whole movement having a constant speed.
4. Method as in any one of claims 1 - 3, characterized-in that raising and lowering of the output end of the pendulum conveyor occurs along an arcuate, preferably an arcuate circular path.
5. Method as in any one of claims 1 - 3, characterized in that the moving path of the output end of the pendulum conveyor is determined by a guide.
6. An apparatus for feeding a thin binder impregnated uncured primary web of mineral wool in zigzag formation onto a receiving conveyor, comprising a pendulum conveyor arranged above the receiving conveyor, said pendulum conveyor swinging in a vertical plane perpendicular to the movement direction of said receiving conveyor, said primary web being fed from the lower end of the pendulum conveyor onto said receiving conveyor, the movement speed of which is lower than the feeding speed of the primary web, whereby said primary web is deposited in overlapping pleats, thus forming a secondary web of desired thickness, a connecting rod, the one of which is associated to the pendulum conveyor and the other end of which is associated to a driving chain running over two wheels situated at a distance from each other, characterized in that the distance between the centres of said wheels corresponds in the movement of the pendulum to at least 30% and maximum 60%, preferably 50%, of a single pendulum stroke, which is formed by the projection of said distance plus two fourths of the periphery, which gives the output end of the pendulum conveyor a constant speed over at least 30% and maximum 60%, preferably 50%, of the pendulum stroke, and in that the output end, before the turning point of the pendulum, is arranged to raise in relation to the receiving conveyor and to sink after the turning point, during an essentially corresponding part of the return stroke, either as a result of the free pendulum movement or by means of a device which gives the output end a desired moving path and a device which enables vertical movement of the swinging axis.
7. An apparatus as in claim 6, characterized in that the pendulum conveyor is furnished with a swinging arm which at its lower end is fixed on bearings outside the pendulum, on the center line of the pendulum, and at its upper end mounted on fork-bearings or the like on the pendulum conveyor.
8. An apparatus as in claim 7, characterized in that a stop is arranged to stop the vertical movement of the swinging axis when the pendulum conveyor is passing into a free pendulum movement.
9. An apparatus as in claim 7 or 8, characterized in that a wheel or similar rolling or sliding element is arranged on the pendulum conveyor so, that when in contact with a guide device and during the pendulum movement, it transmits to the output end of the pendulum conveyor the desired moving path.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FI864452A FI83674C (en) | 1986-10-31 | 1986-10-31 | Method and Device for Laying Thin Binder Impregnated Primary Cure of Mineral Wool on a Receiving Conveyor |
| FI864452 | 1986-10-31 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1289981C true CA1289981C (en) | 1991-10-01 |
Family
ID=8523427
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000550646A Expired - Fee Related CA1289981C (en) | 1986-10-31 | 1987-10-30 | Process and device for feeding a thin binder impregnated uncured primary webof mineral wool onto a receiving conveyor |
Country Status (13)
| Country | Link |
|---|---|
| EP (1) | EP0329686B1 (en) |
| JP (1) | JPH02500737A (en) |
| KR (1) | KR890700106A (en) |
| CN (1) | CN1009911B (en) |
| AU (1) | AU607169B2 (en) |
| BG (1) | BG50603A3 (en) |
| CA (1) | CA1289981C (en) |
| FI (1) | FI83674C (en) |
| HU (1) | HUT49826A (en) |
| PL (1) | PL158611B1 (en) |
| RO (1) | RO104627B1 (en) |
| RU (1) | RU1831533C (en) |
| WO (1) | WO1988003121A1 (en) |
Families Citing this family (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FI76597C (en) * | 1986-11-12 | 1988-11-10 | Partek Ab | FOERFARANDE VID UTLAEGGNING AV MINERALULLBANAS PRIMAERBANA MED HJAELP AV PENDELTRANSPORTOER PAO EN MOTTAGARTRANSPORTOER OCH ARRANGEMANG VID SAODAN PENDELTRANSPORTOER. |
| US5065992A (en) * | 1990-06-07 | 1991-11-19 | Roll Systems, Inc. | Method for processing web material |
| US5087023A (en) * | 1990-08-23 | 1992-02-11 | The Standard Register Company | Apparatus and method for folding separated forms in a stack |
| US5558318A (en) * | 1991-01-15 | 1996-09-24 | Roll Systems, Inc. | Separator for forming discrete stacks of folded web |
| DE4127172C2 (en) * | 1991-08-16 | 1995-02-02 | Heraklith Baustoffe Ag | Device for applying fleece, in particular mineral wool fleece, to a support belt |
| JP2643778B2 (en) * | 1993-06-21 | 1997-08-20 | 産栄機設株式会社 | Method and apparatus for producing cotton collection mat |
| DE102005044772A1 (en) * | 2004-10-07 | 2006-04-13 | Deutsche Rockwool Mineralwoll Gmbh & Co. Ohg | Method and device for producing an insulating element made of fibers |
| CN100414017C (en) * | 2005-04-04 | 2008-08-27 | 北新集团建材股份有限公司 | Pendulum conveyer |
| CN102923519A (en) * | 2012-11-13 | 2013-02-13 | 江苏海大印染机械有限公司 | Modified cloth swing mechanism |
| CN105217365B (en) * | 2015-10-10 | 2017-12-12 | 中材科技股份有限公司 | A kind of cloth cotton pendulum bob machine and its uniformity compensation method |
| RU2618331C1 (en) * | 2015-12-11 | 2017-05-03 | федеральное государственное автономное образовательное учреждение высшего образования "Южно-Уральский государственный университет" (национальный исследовательский университет) (ФГАОУ ВО "ЮУрГУ" (НИУ)) | Pendulum spreader |
| FR3064938A1 (en) * | 2017-04-07 | 2018-10-12 | Compagnie Generale Des Etablissements Michelin | THE STACKING OF RUBBER MIXTURE PATCHES |
| CN107500016B (en) * | 2017-07-13 | 2024-03-08 | 南通天福机械有限公司 | Horizontal working rock wool pendulum type cotton distribution machine |
| CN108584524A (en) * | 2018-04-28 | 2018-09-28 | 王传祥 | A kind of curtain auto-folder equipment |
| CN109969853B (en) * | 2019-04-03 | 2021-01-26 | 广州市兴世机械制造有限公司 | On-line cutting waste removing method for strip |
| WO2021141546A1 (en) | 2020-01-10 | 2021-07-15 | Izoteh D.O.O. | Pendulum folder for foldable material folding |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| NL285404A (en) * | 1961-11-13 | 1900-01-01 | ||
| SE452041B (en) * | 1984-07-03 | 1987-11-09 | Rockwool Ab | Mineral wool prodn. |
| FI76597C (en) * | 1986-11-12 | 1988-11-10 | Partek Ab | FOERFARANDE VID UTLAEGGNING AV MINERALULLBANAS PRIMAERBANA MED HJAELP AV PENDELTRANSPORTOER PAO EN MOTTAGARTRANSPORTOER OCH ARRANGEMANG VID SAODAN PENDELTRANSPORTOER. |
-
1986
- 1986-10-31 FI FI864452A patent/FI83674C/en not_active IP Right Cessation
-
1987
- 1987-10-28 CN CN87107553A patent/CN1009911B/en not_active Expired
- 1987-10-29 EP EP87907241A patent/EP0329686B1/en not_active Expired - Lifetime
- 1987-10-29 WO PCT/FI1987/000143 patent/WO1988003121A1/en active IP Right Grant
- 1987-10-29 JP JP62506643A patent/JPH02500737A/en active Pending
- 1987-10-29 KR KR1019880700767A patent/KR890700106A/en not_active Application Discontinuation
- 1987-10-29 AU AU81745/87A patent/AU607169B2/en not_active Ceased
- 1987-10-29 RO RO139506A patent/RO104627B1/en unknown
- 1987-10-29 PL PL1987268494A patent/PL158611B1/en unknown
- 1987-10-29 HU HU875772A patent/HUT49826A/en unknown
- 1987-10-30 CA CA000550646A patent/CA1289981C/en not_active Expired - Fee Related
-
1989
- 1989-04-26 BG BG88260A patent/BG50603A3/en unknown
- 1989-04-28 RU SU894614045A patent/RU1831533C/en active
Also Published As
| Publication number | Publication date |
|---|---|
| PL158611B1 (en) | 1992-09-30 |
| FI83674C (en) | 1991-08-12 |
| PL268494A1 (en) | 1988-07-21 |
| RO104627B1 (en) | 1995-03-01 |
| FI864452A (en) | 1988-05-01 |
| BG50603A3 (en) | 1992-09-15 |
| HUT49826A (en) | 1989-11-28 |
| FI864452A0 (en) | 1986-10-31 |
| AU8174587A (en) | 1988-05-25 |
| CN87107553A (en) | 1988-05-11 |
| RU1831533C (en) | 1993-07-30 |
| JPH02500737A (en) | 1990-03-15 |
| AU607169B2 (en) | 1991-02-28 |
| FI83674B (en) | 1991-04-30 |
| EP0329686A1 (en) | 1989-08-30 |
| EP0329686B1 (en) | 1992-05-13 |
| CN1009911B (en) | 1990-10-10 |
| KR890700106A (en) | 1989-03-02 |
| WO1988003121A1 (en) | 1988-05-05 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKLA | Lapsed |