GB1566917A - Creación de Inventos y Patentes con Inteligencia Artificial

GB1566917A – Single face corrugating machine
– Google Patents

GB1566917A – Single face corrugating machine
– Google Patents
Single face corrugating machine

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Publication number
GB1566917A

GB1566917A
GB11084/77A
GB1108477A
GB1566917A
GB 1566917 A
GB1566917 A
GB 1566917A
GB 11084/77 A
GB11084/77 A
GB 11084/77A
GB 1108477 A
GB1108477 A
GB 1108477A
GB 1566917 A
GB1566917 A
GB 1566917A
Authority
GB
United Kingdom
Prior art keywords
roller
serrated
machine
tooth
rollers
Prior art date
1976-03-17
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

Application number
GB11084/77A
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

BHS Bayerische Berg Hutten und Salzwerke AG

Original Assignee
BHS Bayerische Berg Hutten und Salzwerke AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
1976-03-17
Filing date
1977-03-16
Publication date
1980-05-08

1977-03-16
Application filed by BHS Bayerische Berg Hutten und Salzwerke AG
filed
Critical
BHS Bayerische Berg Hutten und Salzwerke AG

1980-05-08
Publication of GB1566917A
publication
Critical
patent/GB1566917A/en

Status
Expired
legal-status
Critical
Current

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Classifications

B—PERFORMING OPERATIONS; TRANSPORTING

B32—LAYERED PRODUCTS

B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM

B32B3/00—Layered products comprising a layer with external or internal discontinuities or unevennesses, or a layer of non-planar form; Layered products having particular features of form

B32B3/26—Layered products comprising a layer with external or internal discontinuities or unevennesses, or a layer of non-planar form; Layered products having particular features of form characterised by a particular shape of the outline of the cross-section of a continuous layer; characterised by a layer with cavities or internal voids ; characterised by an apertured layer

B32B3/28—Layered products comprising a layer with external or internal discontinuities or unevennesses, or a layer of non-planar form; Layered products having particular features of form characterised by a particular shape of the outline of the cross-section of a continuous layer; characterised by a layer with cavities or internal voids ; characterised by an apertured layer characterised by a layer comprising a deformed thin sheet, i.e. the layer having its entire thickness deformed out of the plane, e.g. corrugated, crumpled

B—PERFORMING OPERATIONS; TRANSPORTING

B31—MAKING ARTICLES OF PAPER, CARDBOARD OR MATERIAL WORKED IN A MANNER ANALOGOUS TO PAPER; WORKING PAPER, CARDBOARD OR MATERIAL WORKED IN A MANNER ANALOGOUS TO PAPER

B31F—MECHANICAL WORKING OR DEFORMATION OF PAPER, CARDBOARD OR MATERIAL WORKED IN A MANNER ANALOGOUS TO PAPER

B31F1/00—Mechanical deformation without removing material, e.g. in combination with laminating

B31F1/20—Corrugating; Corrugating combined with laminating to other layers

B31F1/24—Making webs in which the channel of each corrugation is transverse to the web feed

B31F1/26—Making webs in which the channel of each corrugation is transverse to the web feed by interengaging toothed cylinders cylinder constructions

B31F1/28—Making webs in which the channel of each corrugation is transverse to the web feed by interengaging toothed cylinders cylinder constructions combined with uniting the corrugated webs to flat webs ; Making double-faced corrugated cardboard

B31F1/2845—Details, e.g. provisions for drying, moistening, pressing

B31F1/2863—Corrugating cylinders; Supporting or positioning means therefor; Drives therefor

B—PERFORMING OPERATIONS; TRANSPORTING

B32—LAYERED PRODUCTS

B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM

B32B29/00—Layered products comprising a layer of paper or cardboard

B32B29/002—Layered products comprising a layer of paper or cardboard as the main or only constituent of a layer, which is next to another layer of the same or of a different material

B32B29/005—Layered products comprising a layer of paper or cardboard as the main or only constituent of a layer, which is next to another layer of the same or of a different material next to another layer of paper or cardboard layer

B—PERFORMING OPERATIONS; TRANSPORTING

B32—LAYERED PRODUCTS

B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM

B32B29/00—Layered products comprising a layer of paper or cardboard

B32B29/08—Corrugated paper or cardboard

B—PERFORMING OPERATIONS; TRANSPORTING

B32—LAYERED PRODUCTS

B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM

B32B7/00—Layered products characterised by the relation between layers; Layered products characterised by the relative orientation of features between layers, or by the relative values of a measurable parameter between layers, i.e. products comprising layers having different physical, chemical or physicochemical properties; Layered products characterised by the interconnection of layers

B32B7/04—Interconnection of layers

B32B7/12—Interconnection of layers using interposed adhesives or interposed materials with bonding properties

B—PERFORMING OPERATIONS; TRANSPORTING

B32—LAYERED PRODUCTS

B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM

B32B2250/00—Layers arrangement

B32B2250/26—All layers being made of paper or paperboard

B—PERFORMING OPERATIONS; TRANSPORTING

B32—LAYERED PRODUCTS

B32B—LAYERED PRODUCTS, i.e. PRODUCTS BUILT-UP OF STRATA OF FLAT OR NON-FLAT, e.g. CELLULAR OR HONEYCOMB, FORM

B32B2317/00—Animal or vegetable based

B32B2317/12—Paper, e.g. cardboard

B32B2317/127—Corrugated cardboard

Description

PATENT SPECIFICATION
( 11) 1 566 917 ( 21) Application No 11084/77 ( 22) Filed 16 Mar 1977 ( 31) Convention Application No 2611325 ( 32) Filed 17 Mar 1976 in ( 33) Fed Rep of Germany (DE)
Complete Specification Published 8 May 1980
INT CL 3 B 32 B 3/30 29/00 Index B 5 N D 15 at Acceptance 0330 2900 ( 54) A SINGLE FACE CORRUGATING MACHINE ( 71) We, BHS-BAYERISCHE BERG-, HUTTEN UND SALZWERKE AKTIENGESELLSCHAFT, a Body Corporate organised and existing under the Laws of the Federal Republic of Germany, of Nymphenburger Strasse 120, 8000 Munchen 19, Federal Republic of Germany, do hereby declare the invention, for which we pray that a patent may be granted to us and the method by which it is to be performed, to be described in and by the following statement:
This invention relates to a single face corrugating machine comprising two cooperating serrated rollers and a pressure roller co-operating with one serrated roller, each serrated roller having serration-type teeth with tooth tips and tooth roots, a paper web to be corrugated being fed between the two said serrated rollers under mutual pressure exerted thereon and a cover paper web being supplied to the web of the corrugated paper between the one serrated roller and said pressure roller.
In a single face corrugation machine, the corrugations are formed between two heated serrated rollers which rotate in opposite directions and which are pressed against one another along the pitch line These serrated rollers are cylindrical rollers with serrations which are formed in the roller shell, which correspond to the desired shape of the corrugation of the paper to be corrugated, which are parellel to the axes of said rollers and which are of equal depth on both said rollers The serration tips, i e the tips of the said serration-like teeth of each roller, press the paper against the serration trough, i e the serration roots of the respective mating roller, thereby imparting a permanent corrugation to it The profile tortn of the serrated rollers corresponds to their task and the teeth of a serrated roller are thus fundamentally different from gear teeth In the case of gears, whose task is to transmit or convert a speed and torque, this transmission is accomplished in principle by the gears engaging on the contacting gear flanks A considerable amount of clearance is provided in principle between the tooth tip and tooth root in order to prevent the gears from seizing Circumferential forces are transmitted between adjacent tooth flanks by positive engagement.
In the case of serration-type teeth, however, whose task is to corrugate a web of paper or other material passing therethrough, there must not be any tooth flank/paper web/tooth flank contact In order to obtain a stable paper corrugation, the serration-type teeth are pressed against the serration troughs under high linear pressures exerted on the interposed paper and, in addition, a considerable temperature is also used The one serrated roller, which is not driven by an external means, is carried along, i e it is rotated by the serrated roller which is provided with a drive means This occurs substantially by positive engagement across the paper which is pinched between the tooth tip and tooth root A substantial torque transmission would not be possible with serration-type teeth and is not even required, since the only counter-torque which exists is the torque caused by the friction of the serrated roller mounting.
A comparison with normal gears shows that the laws for gear toothing which were developed for gears cannot be applied to serration-type teeth Down to the present day, serration-type teeth are composed of circles and straight lines in accordance with the desired shape of the corrugated paper.
The periodic variations in axial spacing between the centers of the two serrated rollers which occur in the rhythm of twice the tooth frequency are put up with because the rollers do not roll off each other perfectly and the variations are of a magni0UE 4 ( 44) ( 51) ( 52) ( 19) 1 566 917 tude of a few hundredths of a millimeter.
The serrated roller, which is lever-mounted and pressed against the other by hydraulic cylinders, yields by this amount and thus reduces and increases periodically the amount of sag accordingly.
The conditions in the glueing zone between the one serrated roller and the pressure roller are not any different and may even be more unfavourable Since the latter has a circular shape, every serration will exert a jolt onto the pressure roller each time it passes over the two paper webs which are interposed between the two rollers in this zone This will cause a change in the spacing from the center of the adjacent serrated roller in the rhythm of the tooth frequency The magnitude of the variation in axial spacing corresponds to the arc height between the chord disposed above two adjacent teeth and the external diameter of the serrated roller It is approximately twice as large as that between the two afore-mentioned serrated rollers and can approach almost 1/10 of a millimeter in the case of coarse toothing.
Even if the magnitude of the change in axial spacing between the pressure roller and serrated roller and between two serrated rollers is small, the dynamic forces which occur are very considerable due to the high frequency which can approach a magnitude of 800 Hz and due to the large masses of the rollers (about 1000 kg per roller).
High pressures must be used for this reason alone in order to maintain permanent contact on both sides on the paper passing therethrough and in order to ensure clean impressions and glueing When the pressures can no longer compensate sufficiently for the dynamic jolts which increase greatly at higher machine speeds, the result is a temporary raising of the rollers, poor impressions and glueing, as well as the feared «high-low» phenomenon in which only every other corrugation has a good impression and is correctly glued Moreover, the periodical variations in axial spacing are a principal cause of the loud machine noise in the case of single face corrugating machines.
The object of the present invention is to avoid the periodic changes in axial spacing without impairing in any way the impression or glueing operation There should be no contact between the flanks of the serrationlike teeth, but rather the required, adequate flank clearance should be maintained.
Moreover, the geometrical dimensions of the corrugated paper web and the single face corrugated cardboard formed from said corrugated paper web and the smooth cover web should not be varied at all or only insignificantly.
According to the present invention a machine for corrugating a single face of a paper web comprises a first and a second cooperating serrated roller rotatable in opposite directions with a constant axial spacing and able to receive therebetween a paper web to be corrugated, and a pressure roller cooperating with said second serrated roller such that they may receive therebetween the corrugated paper web and a cover paper web, each of said serrated rollers having serration teeth with tooth tips and tooth roots, the tooth roots of one at least of said rollers being made as a concave curve corresponding to rolling the tooth tip of the mating roller enlarged by a dimension equal to the thickness of the paper web to be corrugated, and the pressure roller having surface depressions parallel to its axis, each of said depressions being a rolling curve of the tooth tip of the cooperating second serrated roller enlarged by a dimension equal to the sum of the thicknesses of the corrugated paper web and the cover paper web.
The machine of the invention has the following advantages:
a) clean, uniform impressions without»high-low» phenomena; b) reliable glueing of the cover web to each corrugation; c) a higher production speed of the corrugating machine; d) lower impression pressures and thus more favourable roller dimensions; e) longer service life of the serrated rollers and the pressure roller; f) a considerable reduction in the operating noise.
An embodiment of the invention will now be described in detail in the following with reference to the accompanying drawings, in which:Figure 1 is a schematic side elevation of a single face corrugating machine; Figure 2 is a section of a corrugated paper web; Figure 3 is the serration-like tooth tip and root on a serrated roller; Figure 4 is the geometric relationships between the tooth tip and the tooth root of two co-operating serrated rollers with a corrugated paper web interposed therebetween; Figure 5 is the design in accordance with the invention of the tooth tips and tooth roots of two serrated rollers with a paper web interposed therebetween; Figure 6 is the design in accordance with the invention of the serrated roller and the pressure roller with the corrugated paper web and cover web interposed therebetween.
Figure 1 illustrates in schematic form a single face corrugating machine A paper web 1 is corrugated between two counterrotating, heated serrated rollers 4 and 5 1 566 917 which are pressed together Before being fed into the corrugating machine, the web 1 to be corrugated is normally rendered pliant for the impression by pre-heating and spraying it with low-pressure steam, whereas the smooth paper web 2 to be glued onto said paper web is heated as it passes over a pre-heating cylinder.
The serrated rollers 4 and 5 have serrations 6 and 7 parallel to the roller axis corresponding to the desired corrugation shape of the paper 1 to be corrugated Lugs of sickel-shaped stationary guide plates 9 engage annular serrations 8 ‘ of the first serrated roller 4 The guide plates 9 extend in a semi-circular shape around the second serrated roller 5, which is not provided with annular serrations, at a distance from the roller somewhat larger than the thickness of the paper The lugs of the guide plates are designed to lift the corrugated paper 1 out of the serrations of the first serrated roller 4 after impression and then hold the paper 1 in the serrations of the roller 5 by the inner contour of the guide plates facing the second serrated roller 5.
Approximately 900 after the impression zone, i e in the area of mutual co-operation of rollers 4 and 5, glue is applied by means of a rotating glue application roller 11 to the tops of the corrugations in the corrugated paper 1 which is held in position in the serrations of the second serrated roller 5 by the guide plates At the sites where the guide plates are located, this roller 11 is provided with annular serrations 12, thereby permitting the roller bearing the glue film located between the guide plates to be brought close enough to the second serrated roller 5 so that the glue is transferred to the outer tips of the corrugations of the corrugated paper 1 The circumferential speed of the glue application roller 11 is approximately equal to the circumferential speed of the second serrated roller 5 and directed in the same direction The glue film on the glue application roller has a constant thickness due to the fact that any excess glue from a glue pan 13 is squeezed off in an adjustable gap 14 relative to a squeegee 15 co-operating with the glue application roller or relative to a wiper blade (not shown).
Approximately 1800 after the impression zone, the smooth paper web 2 is pressed against the glued corrugation tops of the corrugated web located in the serrations of the second serrated roller 5 by means of a pressure roller 8, thereby gluing the two paper webs together.
The spacing T of the single face corrugated cardboard 3 is thus determined in the glueing zone It corresponds to the spacing of the serrations 7 on the second serrated roller 5 measured on the external diameter thereof.
As has already been stated, the serrated roller 4 has a number of annular serrations 8 ‘ which are normally spaced equidistantly from one another, which are distributed over the entire length of the roller and which co-operate with the stationary guide plates 9, thereby lifting the corrugated paper out of the serrations of the first serrated roller 4 after impression.
The second serrated roller 7 co-operates with the pressure roller 8 This pressure roller 8, which has approximately the same diameter as the two serrated rollers 4 and 5, is heated just like these rollers, normally by steam This steam is conducted into the cavities of the hollow rollers 4, 5 and 8 through rotary ducts (not shown in detail).
The condensate is removed from the rollers again through siphon pipes and rotary ducts.
At least one of the three rollers, i e the serrated roller 4 provided with annular serrations 8 ‘, usually together with the pressure roller 8 as well, is designed with convex or concave-vaulted shell surface which is calculated according to the impression pressures exerted such that constant line pressures are ensured over the entire width of the paper web.
The axes of the two serrated rollers 4 and and of the pressure roller 8 are disposed advantageously in a plane inclined at approx 450 The glue application unit is located obliquely below the second serrated roller 5 which is termed the lower serrated roller.
The first serrated roller 4 is designated the upper serrated roller The serrated roller 5 co-operating with the pressure roller 8 as well as the pressure roller 8 itself are driven at a speed corresponding to the desired production speed The pressure roller 8 has a slightly lower circumferential speed as compared to the serrated roller 5 so that the paper web 2 is always taut.
The upper serrated roller, serrated roller 4, has no drive means, but is carried along during the impression process while meshing with the serrated roller 5 The rollers are pressed against each other in the direction of the arrows 16 and 17 (Figure 1) usually by means of hydraulic cylinders which engage on bearing levers on both sides in which the bearings of these rollers are accommodated and which themselves are pivotally mounted in the stationary machine frameworks Driven rollers also include the glue application rollers 11 and the squeegee roller 15.
According to Figure 2, the spacing T of the serrations 7 of the lower serrated roller 5 measured on the external diameter thereof, corresponds to the spacing of the corrugated web and thus to the spacing of the single face corrugated cardboard 3 The corrugated web contour illustrated in Figure 2 1 566 917 shows that for given spacing T and profile height h, the flanks 20 are steeper and the flank angles a smaller, the broader the curved corrugation segments 18 and 19 are chosen to be In practice, the limits for a are defined by the fact that a «latticework» with the best possible stability is to be formed using the smallest possible amount of stretched paper length.
It has been found that good, stable corrugated cardboards can be produced using flank angles a between approx 20 and 400 with a favourable paper consumption at the same time.
The serration profile of conventional serrated rollers is composed of circles and straight lines according to Figure 3 which shows a greatly enlarged cross section through a serration-type tooth of the lower serrated roller 5 The serration tips 21 are designed with a radius Rl which is somewhat smaller than the trough radius R 2 of the tooth roots 22 The tooth flanks 23 follow the tip and root radius in a straight line and tangentially.
The serration 6 of the upper serrated roller 4 is exactly identical to the conventional design of the serration 7 of the lower serrated roller S with respect to the profile dimensions they are normally produced using the same tool The profile dimensions have the same construction even if the rollers do not have the same dimensions which sometimes occurs They are then manufactured with a different number of serrations according to their diameter Most of the time, however, roller diameters and serration numbers are selected to be equal in the case of both rollers so that if one tooth is damaged by a foreign body, complete damage is not sustained by both rollers.
When impressing the paper in accordance with Figure 4, the tip 21 ‘ of the serration tooth 24 of the one serrated roller presses the paper web 1 into the gap between two adjacent serration teeth 25 and 26 against the root 22 of the other serrated roller or the tip 21 of the second serrated roller against the root 22 ‘ of the first serrated roller, and the paper is respectively pressed only between the serration tips 21, 21 ‘ of the one roller and the serration troughs 22, 22 ‘ of the mating roller.
There is no pressure along the flanks due to the difference in radii between the root radius R 2 and the tip radius Rl (Figure 3).
A certain amount of flank clearance exists.
This flank clearance is necessary to corrugate a paper web in the single face corrugating machine A squeeze in the flanks would inevitably lead to the destruction of the paper flanks It would not be possible to achieve even fairly adequate production speeds and the manufactured cardboard would not have any resistance to crushing.
The flank clearance gradually disappears with the natural wear of the serrated rollers which occurs substantially only at the tips and troughs subject to pressure The set of rollers thus has to be replaced.
According to Figure 5 and 6, and in accordance with the invention, perfect rolling occurs in the restricted area between the tips and roots of the serrations of the two serrated rollers 4 and 5 and between the serration tips of the lower serrated roller 5 and the pressure roller 8 while including the inter-posed paper webs This rolling is such that it in no way impairs the impression or glueing operations.
No contact or rolling is permitted between the flanks of the serration teeth and the required adequate flank clearance is maintained there In addition, the geometric dimensions of the corrugated paper web according to Figure 2 and the single face corrugated cardboard 3 formed from this paper web and the smooth cover web 2 is not changed at all or only insignificantly.
The shape of the tooth tip 21 and/or 21 ‘, for example, can be changed such that, instead of one radius RI, another convex curve is selected with a radius of curvature which continuously varies by small amounts to the right and left of the peak This radius of curvature, however, may not fall below a minimum value determined by the strength of the paper at any point.
In all cases, the trough radius R 2 is, in at least one serrated roller 4 or 5 a concave curve corresponding to rolling the tooth tip of the mating roller enlarged by a dimension equal to the thickness of the paper web to be corrugated if both rollers were allowed to rotate against one another while maintaining a constant axial spacing In the case of the pressure roller 8 the axial spacing constancy by rolling is achieved in that flat, longitudinal surface depressions parallel to the roller axis are formed in the circular surface thereof The contour of these depressions corresponds to rolling the tooth tip of the cooperating second serrated roller enlarged by a dimension equal to the sum of the thicknesses of the corrugated paper and the cover paper to be glued thereto.
The pitch circles on which the rollers theoretically roll on one another, as well as their external diameters and their circumferential speeds are selected accordingly so that practical, useful rolling curves are formed both in the serrated rollers 4 and 5 as well as in the pressure roller 8.
The next section is intended to explain the limits within which the contours of the teeth tips may be varied and the view-points under which the corresponding rolling curves can be regarded as useful As has already been mentioned, good, stable corrugated cardboards are obtained with a simullie 11 l 12 ( 12 ‘ 131 1 566 917 taneous, favourable consumption of paper, according to Figure 2, with flank angles between 20 and 400 Hence, the limits for the selectable tip shapes are thus determined Furthermore, the radius of curvature of the tip curve R 1 may at no point be smaller than a minimum radius determined by the strength of the corrugated webs.
Root curves in the serrated rollers 4 and 5 which are formed as rolling curves of the respective tooth heads must comply with the following conditions if they are to be useful:
The impression force must be able to be conveyed in every phase of the rollers rotation from a tooth tip across the paper in a favourable transfer angle into the rolling curve of the mating roller.
The transfer angles P 3 and 13 ‘ are defined as being the angle between the straight connecting lines from the respective center of the roller to the momentary point of contact and the perpendicular at this point of contact (cf Figure 5 and 6) The transfer angle 13 is zero when a tooth tip points exactly toward the center of the mating roller The momentary point of contact is then located on the line connecting the two centers of said rollers This phase position zero is repeated with each tooth.
After a rotation by one-half the serration spacing, the transfer angle is at its maximum respectively Transfer angles up to a magnitude of 450 can be considered favourable.
Engagement overlap must exist through at least one-half the serration spacing to the right and left of phase position zero i e.
through a total of at least one complete serration spacing since the desired axial spacing constancy is thus guaranteed.
In the case of the two serrated rollers 4 and 5, in which a serration tip of one roller engages the serration trough of the mating roller, the entire profile overlap can be subdivided into the engagement tip I root II and tip II root I i e in a borderline case an engagement overlap would suffice covering 1/4 the serration spacing to the right and left of the peak point respectively, i e.
absolutely covering one-half the serration spacing The rolling should not be permitted to extend up onto the flanks If this should occur in certain combinations, the flanks of the serration teeth are intentionally machined until they are so hollow that the required flank clearance exists everywhere.
In the case of the rolling curves on the shell of the pressure roller 8 according to Figure 6, only those curves are considered to be useful which produce the required engagement overlap with a surface depression depth of only a few l Oths of a millimeter so that the cover web 2 to be glued is not deformed inadmissibly and the glueing process is not impaired.
It has been found that in particular the right choice of the pitch circles 27, 28 in Figures 5, and 31, 32 in Figures 6 on which the rollers 4, 5 and 8 theoretically roll on one another, have a decisive influence on the usefulness of the resultant rolling curves 70 with respect to the external diameters of said rollers and thus with respect to their circumferential speeds, in particlar if the circular arc shape is retained for the contour of the serration tip The result in this case, 75 for example, is useful rolling curves for the two serrated rollers 4 and 5 when the pitch circle of the one roller is positioned in the area of its tooth tips and the pitch circle of the other roller in the area of the tooth 80 roots.
An example for such a serration toothing in accordance with the invention is illustrated is Figure 5 The pitch circle 27 of the upper serrated roller 4 in this example 85 coincides exactly with the external diameter thereof enlarged by a dimension equal to the paper thickness, and the pitch circle 28 of the lower serrated roller 5 coincides with the root diameter In Figure 5 in which two 90 phase positions of the rolling motion which are offset by one-half the serration spacing are shown in the form of solid and dotted lines, and in which the same reference numerals are used for the individual seg 95 ments of the serrated toothing as were used in Figures 3 and 4, it is evident that the tooth tips 21 and 21 ‘ shaped as circular arcs with the corrugated web 1 in the central part of the drawing, roll on one another in a clean 100 manner in the serration troughs 22 and 22 ‘ formed as rolling curves with sufficient overlap without pinching the paper between the tooth flanks 23 and 23 ‘.
The contour 22 of the tooth root of the 105 lower serrated roller 5 is an equidistant to an elongated epicycloid in this case.
The contour 22 ‘ of the tooth root of the upper serrated roller 4 is an equidistant to a shortened epicycloid The serration spacing 110 measured on the external diameter of the upper serrated roller is somewhat smaller in this example than the serration spacing of the lower serrated roller 5 which is also measured on the external diameter Accord 115 ingly, the circumferential speeds also differ somewhat, thereby favourably influencing the engagement overlap Figure 5 also reveals how the lugs 10 (indicated by the dotted line) of the guide plates 9 (Figure 1) 120 cause the corrugated web 1 to remain in the serration of the lower serrated roller 5.
Referring to Figure 6, it is necessary for producing useful surface depressions in the shell of the pressure roller 8 which are 125 rolling curves of the tooth tips of the lower serrated roller 5 in particular those with a tip in a circular arc shape, to move the pitch circles of the theoretical rolling process out of the rolling zone This shift can be effected 130 1 566 917 either toward the axis of rotation of the lower serrated roller 5 or toward the axis of rotation of the pressure roller 8 In the first case, the result is a lower and in the latter case a greater circumferential speed of the pressure roller periphery as compared to the circumferential speed of the external diameter of the lower serrated roller 5 This has a favourable effect on the engagement overlap, in particular producing depressions of shallow depth.
A corresponding relative movement occurs between the cover web 2 and the pressure roller periphery which does not affect the glueing process due to the corresponding braking effect of the cover web 2.
The number of depressions 29 in the pressure roller 8 must be chosen to be smaller than, equal to or greater than the number of serrations on the lower serrated roller 5, depending on the diameter ratio of the theoretical pitch circle 32 of the pressure roller 8 as compared to the theoretical pitch circle 31 of the lower serrated roller 5 The reverse is true for the speeds at which these rollers are to be driven.
Figure 6, which illustrates an example of the design of the depressions 29 in the pressure roller 8 as being rolling curves of the tooth tips of the lower serrated roller 5 enlarged by a dimension equal to the sum of the thicknesses of the corrugated and cover webs 1 and 2, again reveals the clean rolling conditions The depression contour can also be determined for this example as an equidistant to an elongated epicycloid.
Transitions with sharp edges between the depression contour 29 and the cylindrical part 30 of the pressure roller periphery are avoided by the use of transition radii 33.
If the tooth tip contour of the serrated rollers is designed not as a circle, but as another constantly convex curve, other diameter ratios of the pitch circles can be selected which are favourable for the design of the resultant rolling curves Elliptical, parabolic or hyperbolic shapes as well as elongated or shortened hypocycloids or equidistants to the afore-stated types of curves are mentioned as examples of useful tip curves.
The hypocycloid-type tip shapes produced extended or shortened epicycloids as rolling curves for the mating rollers.
In any case, the present invention will thus advantageously accomplish the object of avoiding the periodic changes in spacing by effecting perfect rolling in the defined region between the serration tips and serration roots of the two serrated rollers 4 and 5 as well as between the serration tips of the lower serrated roller 5 and the pressure roller 8 while including the interposed paper webs 1 or 1 and 2, such rolling however being effected in such a manner that it in no way impairs the impression and glueingoperations No contact or rolling occurs between the flanks of the serration-type teeth On the contrary, the required, adequate flank clearance is maintained there 70 Furthermore, the geometrical dimensions of the corrugated paper web 1 and the single face corrugated cardboard 3 formed of said corrugated paper web and the smooth cover web 2 are not changed at all or only 75 insignificantly.

Claims (18)

WHAT WE CLAIM IS:-

1 A machine for corrugating a single face of a paper web comprising a first and a second cooperating serrated roller rotatable 80 in opposite directions with a constant axial spacing and able to receive therebetween a paper web to be corrugated, and a pressure roller cooperating with said second serrated roller such that they may receive therebe 85 tween the corrugated paper web and a cover paper web, each of said serrated rollers having serration teeth with tooth tips and tooth roots, the tooth roots of at least one of said rollers being made as a concave curve 90 corresponding to rolling the tooth tip of the mating roller enlarged by a dimension equal to the thickness of the paper web to be corrugated, and the pressure roller having surface depressions parallel to its axis, each 95 of said depressions being a rolling curve of the tooth tip of the corresponding second serrated roller enlarged by a dimension equal to the sum of the thicknesses of the corrugated paper web and the cover paper 100 web.

2 A machine as claimed in claim 1 in which each tooth tip of said serrated rollers is formed as a convex curve with a constant radius of curvature 105

3 A machine as claimed in claim 1 in which each tooth tip of said serrated rollers is formed as a convex curve with a radius of curvature which varies continuously to the right and left of the peak line of the curve, 110 the radius of curvature being greater than a minimum value determined by the strength of said paper web to be corrugated and flank angles of between approximately 20 and 40 for the corrugated paper web resulting from 115 the convex tip shape with a predetermined spacing and profile height.

4 A machine as claimed in claim 3 in which said convex curve is an elliptical arc.

A machine as claimed in claim 3 in 120 which said convex curve is a parabolic arc.

6 A machine as claimed in claim 3 in which said convex curve is a hyperbolic arc.

7 A machine as claimed in claim 3 in which said convex curve is an elongated 125 hypocycloid.

8 A machine as claimed in claim 3 in which said convex curve is a shortened hypocycloid.

9 A machine as claimed in any one of 130 7 1 566 917 7 the preceding claims in which each said serrated roller moves with respect to the other according to respective pitch circles, said pitch circles being such that engagement overlaps of said rollers are present in the area of the respective tooth tip and tooth root zone whose sum is equal to at least one whole tooth spacing, and that at the same time impression forces are transferred from the serration-type tooth tips across the paper web into the rolling curve of the mating roller.

A machine as claimed in claim 9 wherein the pitch circle of said first serrated roller is located in the area of its tooth tips and the pitch circle of said second serrated roller is located in the area of its tooth roots.

11 A machine as claimed in claim 1 in which said tooth tip contour is of generally arc-shaped configuration, the tooth root contour of said first serrated roller is an equidistant of an elongated epicycloid and the tooth root contour of said second serrated roller is an equidistant of a shortened epicycloid.

12 A machine as claimed in claim 1, wherein said second serrated roller and said pressure roller move with respect to each other according to respective pitch circles, the pitch circles of the pressure roller and the second serrated roller cooperating therewith being displaced out of the rolling zone of said rollers.

13 A machine as claimed in claim 12, wherein said pitch circles are displaced toward the axis of rotation of said second serrated roller.

14 A machine as claimed in claim 12, wherein said pitch circles are displaced toward the axis of rotation of said pressure roller.

A machine as claimed in claim 14, wherein the pitch circles relative to the external diameters of said second serrated roller and said pressure roller are such that there is an engagement overlap over at least one whole tooth spacing in the area of the pressure roller depressions.

16 A machine as claimed in any one of claims 12 to 15, in which the tip profile of said second serrated roller is of generally arc-shaped configuration, the serration contour of the pressure roller being an equidistant of an elongated epicycloid with the arc-shaped tip profile of said second serrated roller cooperating with said pressure roller.

17 A machine as claimed in any one of claims 12 to 15, in which the tip profile of said second serrated roller is of generally arc-shaped configuration, the serration contour of the pressure roller being an equidistant of a shortened epicycloid with the arc-shaped tip profile of said second serrated roller cooparating with said pressure roller.

18 A machine for corrugating a single face of a paper web substantially as described herein with reference to the accompanying drawings.
For the Applicants, MATITHEWS, HADDAN & CO, (Incorporating CHATWIN & COMPANY), Chartered Patent Agents, 33 Elmfield Road, Bromley, Kent, BR 1 15 U.
Printed for Her Majesty’s Stationery Office, by Croydon Printing Company Limited, Croydon, Surrey, 1980.
Published by The Patent Office 25 Southampton Buildings, London, WC 2 A l AY, from which copies may be obtained.
1 566 917

GB11084/77A
1976-03-17
1977-03-16
Single face corrugating machine

Expired

GB1566917A
(en)

Applications Claiming Priority (1)

Application Number
Priority Date
Filing Date
Title

DE2611325A

DE2611325C3
(en)

1976-03-17
1976-03-17

Single sided corrugator

Publications (1)

Publication Number
Publication Date

GB1566917A
true

GB1566917A
(en)

1980-05-08

Family
ID=5972728
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

GB11084/77A
Expired

GB1566917A
(en)

1976-03-17
1977-03-16
Single face corrugating machine

Country Status (8)

Country
Link

US
(1)

US4101367A
(en)

JP
(1)

JPS52138296A
(en)

BR
(1)

BR7701646A
(en)

DE
(1)

DE2611325C3
(en)

ES
(1)

ES456904A1
(en)

FR
(1)

FR2344401A1
(en)

GB
(1)

GB1566917A
(en)

IT
(1)

IT1086861B
(en)

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GB2284433A
(en)

1993-11-20
1995-06-07
Langston Corp
Manufacture of corrugated board

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SINGLE-SIDED CARDBOARD MACHINE

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1986-07-01
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Walter Alfred James Joyce
Improvements in and relating to sheet material

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1986-12-10
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Peters W Maschf

Single sided corrugated cardboard machine

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Kaysersberg Sa

Method of embossing a sheet with one or more plies, sheet of embossed paper.

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Mcneil Ppc Inc
Absorbent pad comprising an adhesive layer which contacts and follows the contour of recess(s) in the garment side surface of the pad

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三菱重工業株式会社

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Scm Corrugator Rolls Limited
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Roller arrangement, in particular corrugated roller arrangement

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Daio Paper Corporation
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Paper diaper and method for manufacturing extensible sheet used in the diaper

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2002-10-30
2004-05-13
Mitsubishi Heavy Industries, Ltd.
Core for corrugated paper material and corrugated paper sheet, and stepped roll for producing core for corrugated paper material, device for producing core for corrugated paper material, device for producing corrugated paper sheet and method of producing core for corrugated paper material

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2013-12-31
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Molins Machine Co Inc
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1976

1976-03-17
DE
DE2611325A
patent/DE2611325C3/en
not_active
Expired

1977

1977-03-16
ES
ES456904A
patent/ES456904A1/en
not_active
Expired

1977-03-16
US
US05/778,106
patent/US4101367A/en
not_active
Expired – Lifetime

1977-03-16
GB
GB11084/77A
patent/GB1566917A/en
not_active
Expired

1977-03-17
JP
JP2871377A
patent/JPS52138296A/en
active
Pending

1977-03-17
IT
IT48525/77A
patent/IT1086861B/en
active

1977-03-17
FR
FR7708011A
patent/FR2344401A1/en
active
Granted

1977-03-17
BR
BR7701646A
patent/BR7701646A/en
unknown

Cited By (2)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

GB2284433A
(en)

1993-11-20
1995-06-07
Langston Corp
Manufacture of corrugated board

GB2284433B
(en)

1993-11-20
1998-01-28
Langston Corp
Manufacture of corrugated board

Also Published As

Publication number
Publication date

DE2611325A1
(en)

1977-09-29

ES456904A1
(en)

1978-02-01

JPS52138296A
(en)

1977-11-18

US4101367A
(en)

1978-07-18

FR2344401B1
(en)

1985-04-26

FR2344401A1
(en)

1977-10-14

DE2611325B2
(en)

1978-01-05

BR7701646A
(en)

1978-01-03

DE2611325C3
(en)

1978-09-07

IT1086861B
(en)

1985-05-31

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