JPH0418971B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION BACKGROUND OF THE INVENTION This invention relates generally to the manufacture of needle fin members for heat exchangers, and more particularly to new and improved apparatus for manufacturing such products. . This application is a continuation-in-part of US Patent Application No. 392,575 by the applicant.

Prior Art Applicant's US Pat.
No. 3688375 (dated September 5, 1972) and No. 3820217
No. (dated June 20, 1974), the applicant:
Disclosed is a heat exchanger tube structure in which a needle-like fin member is spirally wound around a base tube to constitute a lightweight and highly efficient heat exchanger structure, and a mechanical device for forming the structure.

As described in these patents, forming transverse cuts in the metal strip from at least one longitudinal end at equidistant locations along its length;
A fin member having a surface width corresponding to the score interval can be produced continuously. The metal strip scoring device includes a pair of cutting rollers with interdigitating or overlapping cutting teeth, each roller being spaced around its periphery equal to the longitudinal spacing of the scores. Opposing ends of the cutting teeth score the strip as it passes through the occlusion of the cutting roller. In the applicant's mentioned patent, one cutting roller is rotated by a power drive and the other is rotated in the manner of an idler wheel by contact with the strip to be scored or by tooth contact with said power-driven cutting roller. do.

Cutting devices that use one drive roller and one driven roller wear quickly when operated without cutting material. Under these conditions, it is
This is because the cutting edges of the interlocking teeth interlock with the associated teeth of the other roller. As a result, in the past, it was necessary to make the teeth in a shape with a relatively wide end face width and to position the cutting roller in a state where the amount of overlap, that is, the amount of occlusion was large. This combination of wide end face and large amount of overlap allows the cutting roller to be used even after the teeth have been heavily worn. Cutting roller devices using only one driven roller do not wear out as much during strip cutting. This is because the band is adapted to maintain a spacing between the opposing teeth of the cutting roller. However, this spacing will vary depending on the physical characteristics of the strip to be cut, so that the score in the strip will not necessarily be uniform. If the band is extremely soft, the band may not be cut and may only become wavy. Further, the above-described cutting roller device is not commercially practical for making cuts in a fin member whose end face width is very narrow in the longitudinal direction of the band.

In practice, the minimum size of a needle fin member end face that can be commercially scored with one driven cutting roller is about 0.030 inch (0.76 mm). Needle fin members made with a single-drive scoring device usually have a large amount of deformation at the end, and therefore air cannot flow over the heat exchanger mounting time fin member, and the heat of the tube made of the fin member is reduced. Exchange ability will be reduced. Furthermore, such fins are subject to such stress on their proximal ends that they may tear, thus inhibiting heat transfer between the tube and the fin.

No. 3,820,217 of the present applicant discloses that a pair of cooperating cutting rollers can be reliably driven with a zero-gap device to maintain a fixed and reliable angular relationship between the rollers and as a result of the cooperating cutting teeth. An improved band scorer is disclosed that maintains the required circumferential spacing between opposing cutting edges. The use of the zero clearance device ensures that the cutting edges do not interlock even when the cutting rollers are operated without a strip to be cut. This eliminates the rapid wear that would otherwise occur due to the cutting edges of the teeth interlocking with the cutting edges of the opposing rollers. As described in that patent, the zero-gap device is configured to maintain a predetermined small circumferential spacing between the cutting edges involved during band cutting. A more uniform scoring operation is thus possible, in which the scoring condition is less influenced by the physical characteristics of the strip to be cut. The cutting tooth can also be configured with a narrow end surface,
It is also possible to adjust the overlap amount of related teeth to a minimum. As a result, narrower needle fin members can be cut uniformly with little or no edge deformation. Furthermore, by minimizing the deformation that occurs at the base of each needle-like fin member,
Excellent heat transfer can now be achieved between the tube and each needle fin member.

U.S. Pat. No. 3,985,054 also discloses a gear driven cutting device. In this patent, a device is provided for applying a torsional load to the drive gear to eliminate backlash.

SUMMARY OF THE INVENTION The present invention provides a positive drive for a pair of interlocking toothed cutting rollers with members that adjustably determine the angular relationship and amount of overlap independent of similar positioning operations applied to each drive member. Provide equipment. As a result, peripheral clearances between the tooth profiles can be easily achieved, including negative clearances or preloads.

In the device of the present invention, the aforementioned U.S. Pat. No. 3,820,217
All the advantages of reliable cutting roller drive recognized in the above issue can be obtained. As previously mentioned, these benefits also include increased cutting roller life and improved product uniformity. Furthermore, it is possible to reduce the practical dimensions of the material that can be cut satisfactorily with the apparatus described below. This is because the position settings for both the cutting roller and the gear drive member have been optimized.
This is because it is possible to cut a small-sized bar or thin piece into the shape of a fin member with good thermal efficiency and a relatively small end face width.

Since the position of the cutting rollers is independent of the position of the drive member, both sets of cutting rollers can be adjusted to their respective ideal settings. The cutting rollers are adjusted to have overlapping teeth and a gap to match the material to be cut, and the drive set gears are adjusted to avoid backlash. The manufacturing tolerances of the cutting roller and the drive member are no longer directly correlated, resulting in lower manufacturing costs. Re-sharpening the cutting roller costs one-tenth of the original manufacturing cost. In the device of the present invention,
Replacement with a new roller or resharpening of the roller can be accomplished without disrupting the mechanism of the drive. If the cutting roller resharpening process includes grinding the outside diameter of the rollers, adjusting the center-to-center distance between the cutting rollers to maintain the desired amount of overlap or interlocking is dependent on the mechanism of the drive member. This can be easily achieved without any impact.

Another important feature of the present invention is that it can be implemented in a highly practical configuration that can be attached to existing machines using assembled cutting rollers that have only one drive roller.

Several advantages are achieved when utilizing relatively small size flakes made in accordance with the present invention. Examples of this benefit include reduced material consumption and reduced weight of the final product. In connection with the reduced dimensions of the sheet material that can be produced according to the invention, an increase in machine productivity is also mentioned as an advantage. This is due to the fact that the effective capacity of a given machine increases and the length of the strip to be scored increases proportionately. A machine can run for longer periods between material charges if its effective capacity is increased. In conventional experience, downtime is 20% of the total machine time for material charging, but with the present invention it can be expected to be reduced to 50%, or 10% of the total machine time.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The principles of the invention may also be applied to conventional type machines as described, for example, in the applicant's patents mentioned above. In particular, as will be readily understood by those skilled in the art, the apparatus described herein may be incorporated into various machines of the type described in the aforementioned U.S. Pat. No. 3,688,375, the disclosure of which is incorporated herein by reference. or can be adapted.

The device 10 is a device for making cuts in a continuous strip of sheet material and comprises two cutting rollers 11 and 1.
It is equipped with 2. Both rollers are pivoted so that they can rotate in opposite directions about shafts 13 and 14, respectively. The rollers 11, 12 are provided with serrated cutting teeth 16 along their respective peripheries, each tooth being separated by a space 17 and forming an upper tooth portion 16a and a lower tooth portion 16b, respectively. . As detailed below, the spacing between the axes 13, 14 and the size of the rollers 11, 12 are proportional so that the opposing teeth 16 overlap each other and each tooth has an associated tooth on the opposite roller. As the band 18 (FIG. 4) passes between the rollers, the band can be cut or scored. Rollers 11, 12 score the strip 18 from both ends to form fin members 19 extending perpendicular to the longitudinal direction of the strip. Each fin member 1
9 remains connected to the longitudinal uncut central part 21.

As described in Applicant's U.S. Pat. It is caused by the relative rotational movement of

Torque tube 23 includes a precision-molded internal fin member 26 capable of receiving a complementary or interference-fit external fin member 27 provided at the lower end of main shaft 28. . Main shaft 28
is rotatably supported around a shaft 13 in wear-resistant precision ball bearing units 29 and 31 that are separately provided and spaced apart in the axial direction. The main shaft 28 is fixed to a lower bearing unit 29 by a locking nut 38. Although the cutting roller 11 is generally annular in shape, it has a precision-molded cylindrical hole 32 in its center that achieves a tight fit with the cylindrical end 33 of the main shaft 28. do. The angular position of the roller 11 on the main shaft 28 is adjustable within the limits of slots 34 spaced around the periphery. Through the slot, a threaded bolt 36 fits into a centric threaded hole drilled in a flange 37 on the main shaft 28 near the end 33. bolt 36
After being positioned in the correct angular relationship on the spindle 28, the rollers are tightened to secure the rollers in place. It can therefore be seen that the roller 11 can rotate together with the main shaft 28 and the torque tube 23. A precision-molded spur gear 41 is integrally formed at the upper end of the torque tube 23.

The other cutting roller 12 is rotatably supported on a generally cylindrical pivot column 47 by means of a precision double roller ball bearing unit 46 about an axis parallel to and in close relationship with the axis 14. .
Like the first cutting roller, the second roller 12 has a generally annular shape and includes a precision-molded central cylindrical bore that closely fits the outer race of the ball bearing unit 46. The bore in the inner race of ball bearing unit 46 achieves an interference fit with cylindrical portion 48 of column 47. Although the cylindrical portion 48 is slightly eccentric,
Due to the reasons described later, the central axis 1 of the other parts of the column 47
It is parallel to 4. The inner race of the ball bearing unit 46 is fixed to the pivot column 47 with a lock nut 49. The pivot column 47 has a precision molded bushing 5 surrounding the cylindrical exterior of the column for most of its length.
1 and 52 on the frame assembly 22. The pivot column 47 has a central cylindrical bore 53 in which a tension tube 54 and a torsion rod 56 are disposed concentrically. The lower end of the tension tube 54 is welded to a washer-like plate member 57, and the peripheral portion of the upper surface of the plate member is in contact with the lower bushing 51. The tension tube 54 has a male thread at its upper end and is coupled to a locking nut 58. The nut is also adapted to press against the upper end surface of the pivot column 47.

As shown in FIG. 3, the hole 53 in the pivot column defines a radial clearance for a tension tube 54, and the interior of the tension tube 54 defines a large radial clearance for a torsion rod 56. The lower end of the torsion rod 56 is connected to the spur gear 6
1 and extends axially through an elongated hub 59 that is integrally molded thereon. External teeth 62 are precisely molded on the spur gear 61 and mesh with complementary teeth 63 provided around the periphery of the main shaft gear 41 . The elongated gear hub 59 is rotatably supported by a pair of wear-resistant precision bearings 64 spaced apart in the axial direction. Bearing 6
The outer loin of No. 4 is crimped or otherwise secured to a generally circular bushing 68 with flanges in associated cylindrical holes 66, 67 bored out by a sideburner. The cylindrical holes 66 and 67 are coaxial with each other and slightly eccentric with respect to an outer cylindrical surface 69 extending over the entire length of the bushing 68.

Flange 71 of bushing 68 has a plurality of angularly spaced slots 72 around its periphery for receiving threaded tightening bolts 73. The bolt 73 is threaded into the associated hole in the tube support 24 and, when tightened, tightens the bushing into the desired angular position of the bushing receiving hole in the tube support 24. The elongated gear hub 59 is held in the bearing 64 by a nut 70.
The torsion rod 56 is fixed to the gear 61 by welding or the like at a location 74.

The torsion rod 56 is connected at its upper end to the associated cutting roller 12 by a removable tip drive 75. The tip-shaped driver 75 is provided with a central hole 78 for receiving the upper end of the torsion rod 56 therein. The tip-shaped drive body 75 can be adjustably fixed to the torsion rod 56 with respect to its angular position by tightening a threaded cross bolt 79 (FIG. 1). The cross bolt is adapted to pull the central hole 78 tightly against the torsion bar 56 when tightened. The provision of radial slot 81 allows central hole 78 to press against torsion rod 56 when bolt 79 is tightened. The tip-shaped drive 75 is connected to the associated cutting roller 12 via an annular carrier 86 . The tip-shaped drive body 75 is fixed to the carrier 86 by a plurality of threaded bolts 87. The carrier 86 is a precision molded member that slides onto the outer race of the associated bearing 46 and
It is received in a precision fit in a precision formed hole 88 in cutting roller 12. The cutting roller 12 is removably secured to the carrier 86 by circumferentially spaced bolts 89.

In the present invention, the set of cutting rollers 11 and 2 are radially adjustable with respect to each other, and the set of drive gear members 41 and 61 are also radially adjustable with respect to each other, so that the adjustment of either set does not affect the other set. This can be done independently of the adjustment of the set. Furthermore, the angular relationship between the cutting rollers 11 and 12 can be adjusted independently of the interlocking between the gears 41, 61 by the selective positional tightening function of the tip-shaped drive bore 78 onto the torsion rod 56. By the way, the gear 41 and the associated cutting roller 11 are connected to the shaft 1 of the main shaft 28.
It can be interpreted as rotating around a common axis identified as 3. This shaft 13 is connected to the tube support 24
Fixed to . The axis of rotation of the other cutting roller 12 is in an eccentric relationship with respect to the other cylindrical portion 50 of the pivot column 47 whose cylindrical pivot column surface 48 is received in the bushings 51, 52 (defining the axis 14). Due to this, it is adjustable in the radial direction with respect to the first axis 13.

By manually rotating the pivot post 47 with the pin received in the radial hole 76 drilled in the upper end of the pivot post, the cutting roller 12 (rotating centrically with the eccentric surface 48) is removed. The center can be moved closer or further away from the pair of cutting rollers 11.

After manually rotating the pivot post 47 to an angular position that sets the associated cutting roller 12 in the desired radial position (i.e. center-to-center distance) with respect to the other cutting roller 11, the nut 58 is tightened onto the tension tube 54. The adjustment of the angle of the pivot column 47 with the pin inserted into the hole 76, which clamps the tube to the top of the pivot column and holds it in this position, is carried out before assembling the drive cap to the torsion rod 56. It is better to do it.

At the other end of the torsion rod 56, the drive gear member 6
1 is a bushing 68 received in the tube support 24.
is positioned so as to be adjustable in the radial direction with respect to the paired gear member 41 by rotating it in the hole 91. Slot 72 has a circumference sufficient to accomplish such bushing positioning operations. After the bushing 68 is properly positioned, the bolt 73 is tightened to prevent movement. On the one hand, the cylindrical hole 66,
67 and the bushing surface 69 are in an eccentric relationship,
As a result, the gear 61 can move in the radial direction relative to the paired gear 41 to a desired location, that is, to a location where there is substantially no backlash between the two gears.

It can therefore be seen that the radial adjustment between the two drive gear members 41 and 61 is independent of the radial adjustment between the two cutting rollers 11 and 12, and vice versa. In FIG. 1, a set of cutting rollers 1
The relationship between 1, 12 and the drive gear assembly 41, 61 is schematically shown. In Figure 1, the torsion rod 5
6 is transverse to the straight line in order to accommodate the rotational movement of the associated cutting roller 12 and drive gear member 61 about parallel and radially offset axes, albeit in a highly exaggerated manner. It is shown in a modified form. The torsion rod 56 (apparatus 1
0 is in operation, once the drive cap 75 is
6), the gear 61 is configured to have sufficient torsional stiffness to maintain the desired fixed angular relationship between the gear 61 and the roller 12.

At the same time, since the torsion rod 56 has a low resistance to lateral deflection or bending, the deformation of the rod in this manner does not involve any additional stresses or bearing loads. A double roller ball bearing unit 46 associated with the cutting roller 12 ensures that the roller is tilted to the ideal axis 1.
of sufficient axial length and stability to prevent deviation from the plane perpendicular to 4. Similarly, the bearing 64 associated with the drive gear member 61 is
The gear 61 is configured to have sufficient axial relative spacing and load to prevent the gear 61 from tilting out of the perpendicular plane with respect to the ideal axis 14 .

Now, in FIG. 2, the interlocking portions of the cutting rollers 11 and 12 are shown in a greatly enlarged state. Second
In the figure, the dimensions indicated by the symbol "S" are the dimensions of the roller 1
1 and 12 in opposing positions and cooperating with each other, measured on the circumference or in relation to an arc; It represents 16 overlaps or degrees of occlusion. The ideal setting for both the circumferential spacing "S" and the radial overlap "d" is
1, 12 depends on a number of factors, including the size and type of material being scored. In fact, in some cases the rollers 11 and 12 are configured such that the dimension "S" is somewhat negative, i.e. the teeth 16 of the rollers 11 and 12 are in contact with each other with a slight interference or preload. Sometimes it is desirable to do so.

From the above explanation, it can be seen that the circumferential spacing "S" between the inter-cooperating cutting teeth 16 in the occlusal region is
5 is adjustable depending on the angular position when tightening the torsion rod 56. This can be better understood by considering that the drive gear members 41 and 61 are radially adjusted relative to each other to a point where no backlash occurs between them, as described above. The degree of overlap "d" allows the device 10 to be set up for production operation and the pivot column 47 to be manually rotated to take advantage of the eccentricity of the pivot column surrounded by the cutting roller 12, as also previously described. If you do this, the state will be determined to be adjustable.

If the circumferential spacing between the teeth 16 is set in the form of a regular gap, as shown in FIG.
Since the opposing teeth do not come into direct contact, the life of the cutting roller is relatively long. However, the spacing "S" can also be very small so that relatively small sized pieces of material can be cut.

Figures 5a and 5b show a modified drive such that the torsion bar can be easily replaced and the associated cutting rollers can be easily adjusted relative to the torsion bar, thus preloading the cutting teeth. The structure is shown. Note that the same reference numerals are used in this modified example, but the symbol "'" is added to clarify the reference to this modified example.

As previously mentioned, it may be desirable to create a small preload between the gear teeth. For example, when cutting ultra-thin aluminum material with a thickness of approximately 0.004 to 0.005 inches (0.10 to 0.13 mm), the cutting equipment typically needs to be adjusted so that the spacing "S" between the two teeth is O. There is. In fact, if the material is relatively ductile, in some cases the material to be cut may bend around the cutting edge and push the cutting teeth apart, with the result that no cut is made. To prevent this from occurring, the teeth must be preloaded in the occlusal direction.

Also, if you want to cut a very narrow fin member from extremely thin material, such as a fin member with a width of about 0.020 inch (0.51 mm) or less, a small amount of preload on the teeth will result in a satisfactory cut. is often not available.

In case of the above-mentioned preload, the torsion rod 56' has a projection 56 projecting above the tip-shaped drive body.
a′ is provided. This protrusion 56a' is configured with a wrench flat so that a suitable wrench can be placed at the upper end of the torsion rod during adjustment of the tip driver 75'.

If you want to apply a preload between the cutting teeth, first loosen the cross bolt 79' and then
5' and the upper end of the torsion rod 56' to allow relative rotational movement. Next, a spanner is placed on the protrusion 56a' and torque is applied to create a slight twist or rotational strain in the torsion rod. This torque is applied in the direction in which the cutting teeth are biased toward the occlusal state when the wrench torque is released. Next, while continuing to apply the torque with a wrench, rotate the tip-shaped driver 75' until both cutting teeth engage, and tighten the cross bolt 79' to bring the tip-shaped driver and torsion rod to their respective adjustment positions. Fix it. When the wrench torque is released after the screwdriver is secured in place, the torsion or strain in the torsion rod 56' tends to self-relieve, applying only a torsional force to the cutting roller 12; This results in a preload being applied to the teeth of both cutting rollers. If a greater preload is required, a greater torque may be applied to the torsion rod 56' during adjustment, and if a smaller preload is required, a lesser torque may be applied during adjustment.

FIG. 5b shows a modified construction for attaching the lower end of torsion rod 56' to driven gear 61'. In this embodiment, the driven gear 61'
The hole is configured with a precision polygonal opening 61a', and the lower end of the torsion rod 56' is configured with a pair of polygonal protrusions 56b'. Preferably, the opening 61a' and the protrusion 56
b' is preferably configured with a slight taper so that when the torsion rod is attached, a vertical downward pressure can achieve a tightening taper and a zero spacing. On the other hand, if it becomes necessary to remove and replace the torsion rod 56' for some reason, a suitable tool can be placed at the lower end of the torsion rod 56' and the tool can be struck with a hammer or the like to remove the torsion rod. 56' can be removed and moved upwardly until it can be replaced.

From the foregoing description, it can be seen that the present invention allows for the cutting or scoring of thinner materials as well as the formation of narrower width fin members. For example, generally speaking, the thickness of the thinnest conventional aluminum strip that can be cut satisfactorily is about 0.007 inch (0.18 mm), and the narrowest width of a fin member that can be cut satisfactorily is about 0.030 mm. It was inch (0.76mm). In contrast, with the present invention, material thicknesses as small as 0.004 inches (0.10 mm) can be satisfactorily divided or scored, and fins with a width of about 0.017 inches (0.43 mm) can be obtained. Satisfactory scoring of the component is possible. Since reducing the lateral width of the fin can improve heat exchanger efficiency for a given amount of fin material, reducing the lateral width of the fin can further improve efficiency while reducing the thickness of the fin material. By making it smaller, significant material savings can be made.

Therefore, by using the present invention, it is possible to not only improve efficiency but also reduce material costs.

Cutting rollers 11, 12 obtained by the present invention
The independent adjustment of the center-to-center distance of the drive gear members 41, 61 also has the advantage that small-sized materials can be scored satisfactorily.
For example, the machining tolerances in machining the cutting rollers 11, 12 are not directly influenced by similar tolerances in the manufacture of the drive gear members 41, 61, and vice versa. If one of the combinations of the above members deviates from the ideal shape, the position of the combination must be adjusted to compensate for this.
Even in such a case, the conditions of the other combination are not affected thereby.

The invention also allows resharpening of the cutting rollers 11, 12 to be carried out very easily. If the periphery of the cutting rollers 11, 12 is refitted during the sharpening operation, the effective diameter of the rollers can be reduced. With the device 10 of the invention, a new center distance can be set between the cutting rollers 11, 12 without affecting the center distance of the drive gear members 41, 61.

Although preferred embodiments of the present invention are illustrated and disclosed in this application, it is of course possible to make various modifications and reconfigurations of parts without departing from the scope of the invention disclosed and claimed in this application. That's understandable.

[Brief explanation of drawings]

FIG. 1 is a perspective view of a set of cutting roller shaft members and associated gear drive members constructed in accordance with the present invention. FIG. 2 is a partial axial schematic diagram of the cutting roller.
FIG. 3 shows a diagram of an apparatus using cutting rollers and a drive device for transversely scoring a strip of sheet material to form a fin member and ultimately a heat exchanger tube surrounded by the fin member. FIG. 2 is a more detailed partial cross-sectional view than FIG. 2; FIG. 4 is a partial perspective view of a fin member formed on a strip of sheet material in accordance with the present invention.
FIG. 5a is a partial sectional view of the lower end of the cutting drive member, showing a modification of the cutting drive structure that allows easy adjustment of the drive member for preloading the cutting teeth. FIG. 5b is a partial sectional view of the lower end of the cutting drive member, showing a modification of the torsion rod connection structure. 11, 12... Cutting roller, 13, 14...
Shaft, 16...cutting tooth, 18...band, 29, 31,
46... Ball bearing unit, 41, 61... Gear member, 47... Pivot column body, 48... Cylindrical part,
56...Torsion rod, 66, 67...Cylindrical hole, 68
...butsing.

Claims (1)

[Scope of Claims] 1. An interlocking portion is formed between both cutting rollers, and each roller cooperates with the teeth of the other roller to cut and form a strip at a cutting portion formed in the interlocking portion. a pair of cutting rollers 11 and 12 having circumferential cutting teeth 16a and 16b;
Bearing members 29, 31, 46 that rotatably support the two cutting rollers, which rotate in opposite directions, about shafts 13, 14 provided apart from each other, and the distance between the centers of the two cutting rollers 11, 12 can be adjusted. Shaft members 48, 47 which can be fixed to provide a desired radial spacing between the opposing cutting teeth 16, and the above-mentioned cutting rollers are connected to each other so as to be operable in conjunction with each other, and the above-mentioned interlocking portion is connected to the above-mentioned cutting rollers during reverse rotation. a positive drive member 41, 61 configured to maintain the required circumferential orientation between the opposing cutting teeth 16 passing through;
In addition, the reliable driving member is configured to adjust the distance between the centers of the two cutting rollers by adjusting the distance between the opposing cutting teeth 1 in the occlusion.
Device for making transverse cuts in a strip of sheet material, characterized in that it is equipped with a twisting member 56, which can be achieved independently of the circumferential orientation of 6. 2. Apparatus for making transverse cuts in a strip of sheet material according to claim 1, wherein the positive drive member comprises a pair of interlocking gears 41, 61. 3. Each of said set of gears 41, 61 has an axis 13, 14 respectively associated with one of said cutting rollers 11, 12 and parallel to the axis of the respective associated cutting roller.
Apparatus for making transverse cuts in a strip of sheet material as claimed in claim 2, comprising a pair of gear wheels supported for rotation about. 4 One gear support member 6 of the gears 41 and 61
Reference numerals 6, 67, and 68 are members that adjustably determine the distance between the centers of the pair of gears, and the reliable drive member and the gear support member are connected to the pair of gears 41, 61.
for making transverse cuts in a strip of sheet material according to claim 3, wherein the distance between the centers of the cutting rollers 11, 12 can be adjusted independently of the distance between the centers of the cutting rollers 11, 12; Device. 5 One cutting roller 11 and the associated gear 41 are fixed in a coaxial relationship, and the other cutting roller 12 and the associated gear 61 each have a radius relative to the associated mating cutting roller and gear, regardless of their relative positions. 5. A device for making transverse cuts in a strip of sheet material as claimed in claim 4, which is configured to be directionally adjustable. 6 The adjustable cutting roller 12 and gear 61
6. Apparatus for making transverse cuts in a strip of sheet material as claimed in claim 5, wherein the radially flexible torsion members 56 are connected by a torsionally stiff radially flexible torsion member 56. 7 the radially flexible torsion member 56;
Claim 6, wherein is a relatively elongated shaft member.
Apparatus for making transverse cuts in strips of sheet material as described in paragraph 1. 8. The torsion member 56' has a non-circular tapered portion 5 at one end that fits into the paired opening 61a'.
Claim 7 with a connection having 6b' to achieve a decomposable zero-spacing connection
Apparatus for making transverse cuts in strips of sheet material as described in paragraph 1. 9. The thin plate according to claim 7, comprising an adjusting member 56a' configured to apply a torsional stress to the torsion member 56' and apply a preload in the occlusal direction to both the cutting rollers 11 and 12. A device for making transverse cuts in a strip of material. 10 The torsional stress application adjustment member 56a',
Claims 79 and 79 further include a clamping member 79' for applying a torsional stress to the torsion member 56' and securing the associated cutting roller 12 to the torsion member 56' while applying a torque to the torsion member 56'. 9
Apparatus for making transverse cuts in strips of sheet material as described in paragraph 1. 11 transverse to the strip of sheet material according to claim 3, comprising a clamping member 79 for adjustable fixing of the angular position of one of the cutting rollers 11, 12 relative to the associated gearwheel 41, 61; A device for making directional cuts. 12. Circumferential cuts made to form an interlock between the cutting rollers and each cutting roller cooperating with the teeth of the other cutting roller to cut and form the strip at the cutting site formed in the interlock. Teeth 16a, 16b
A pair of cutting rollers 1 comprising:
1, 12, and gears 41, 61 coupling said cutting rollers in opposite directions of rotation, the coupling member between at least one gear and the associated cutting roller comprising:
The strip of thin plate material is characterized in that it is a torsion member 56' that applies biased pressure to both the cutting rollers 11 and 12 in a direction that maintains the engagement between the opposing cutting teeth 16 with a predetermined preload applied thereto. A device for making transverse cuts. 13 The member that biases the cutting rollers 11 and 12 is a twisting member 56' and both the cutting rollers 11 and 12.
13. A device for making transverse cuts in a strip of sheet material according to claim 12, comprising an adjusting member 56a' for adjusting the torsional pressure applied to the sheet material. 14 said torsion member 56' is an elongated bar member connected between at least one cutting roller 12 and its associated gear 61;
is pivoted for rotation about an axis spaced from the axis of rotation of the associated gear 61, and said torsion member 56' has sufficient lateral flexibility to provide a driving connection between the two axes. Apparatus for making transverse cuts in a strip of sheet material as claimed in claim 13. 15 The rotation axis of the one cutting roller 12 is adjustable with respect to the rotation axis of the other cutting roller 11, and the rotation axis of the related gear 61 is adjustable independently of the rotation axis of the other gear 41. Apparatus for making transverse cuts in a strip of sheet material as claimed in claim 14. 16 First cutting roller 11 and first drive gear 41
and the first cutting roller 11 and the first drive gear 4
bearing members 29 and 31 for supporting the rotary roller 1 in a rotatable state around a fixed common shaft 13; and a main shaft 28 for reliably transmitting rotation at the same rotation angle between the first cutting roller 11 and the first driving gear 41. and the second
Cutting roller 12 and second driving gear 61, with the second cutting roller 12 facing the first cutting roller 11 and the second driving gear 61 meshing with the first driving gear 41, the second cutting roller 12 and the second driving gear 61 so as to be rotatable about their respective axes parallel to the fixed shaft 13; and the second cutting roller 1.
2 and the torsion member 56' that reliably transmits rotation at the same rotation angle to the second driving gear 61, and the supporting member of the second cutting roller 12, regardless of the position of the second driving gear 61. The second cutting roller 12 is provided with shaft members 48 and 47 for positioning the second cutting roller 12 in a radially adjustable manner with respect to the first cutting roller 11, and the supporting member of the second drive gear 61 is provided with the second cutting roller 12. Gear support members 66, 67, 68 are provided for radially adjustable positioning of the second drive gear 61 with respect to the first drive gear 41 independent of the position of the cutting roller 12; Apparatus for making transverse cuts in a strip of sheet material, characterized in that it consists of: 17. A strip of sheet material according to claim 16, characterized in that it is provided with a clamping member 79 by which the angular position of said one cutting roller 12 can be fixed adjustably with respect to its associated second drive gear 61. A device for making transverse cuts in 18 Peripheral cutting teeth 16a arranged such that an interlock is formed between the rollers and each roller cooperates with the teeth of the other roller to cut and form the strip at the cutting site formed in the interlock. , 16b, and bearing members 29, 31, 46 that rotatably support the cutting rollers 11, 12 that rotate in opposite directions about shafts 13, 14 separated from each other. , a set of interlocking gears 41, 61 operatively connected to the cutting rollers so as to maintain the required circumferential spacing between the opposing cutting teeth 16 passing through the interlocking portions during counter-rotation of both cutting rollers; and shaft members 48, 47 that support the center-to-center distance of the cutting rollers 11, 12 so as to be adjustable without affecting the interlocking distance between the gears 41, 61. A device for making transverse cuts in strips of sheet material.