Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
  • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
  • B26D7/00—Details of apparatus for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
  • B26D7/26—Means for mounting or adjusting the cutting member; Means for adjusting the stroke of the cutting member
  • B26D7/2614—Means for mounting the cutting member
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
  • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
  • B26D7/00—Details of apparatus for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
  • B26D7/26—Means for mounting or adjusting the cutting member; Means for adjusting the stroke of the cutting member
  • B26D7/2628—Means for adjusting the position of the cutting member

Definitions

• the invention relates to a device for fastening perforation lines to cylinders in printing presses with the generic features mentioned in the preamble of claim 1.
• the beam cylinders have a central extension which can be screwed into the thread of the transverse bore; the entire beam cylinder is located outside of the insert and therefore also determines the spacing that the threaded holes in the insert must occupy due to its size, namely its maximum outside diameter.
• the channel system formed in this way is then filled with a pressure medium - conventional hydraulic oil - and the longitudinal bore in the insert or in the clamping strip formed in this way is closed on one side with a normal screw which forms a type of stopper, while on the opposite end of the insert, a special screw is used which, depending on how deeply it is screwed into its associated thread, generates a corresponding pressure in the channel system and thus in the beam cylinders, which first of all provides the preload force for a initially holding and aligning the knives and then applying the final clamping force for holding the knives after adjustment.
• the problem with such a clamping strip design may be that the respective beam cylinders producing the prestressing pressure and finally the final holding pressure for the knife or the perforation line are placed on the insert from the outside, and practically completely fill the corresponding groove of the perforating cylinder in terms of its size, even in the radial direction.
• This can not only lead to injuries in the bar structure during rough operation, but also requires comparatively wide receiving grooves for the entire printing system, so that only a few, for example, a total of six perforation lines receiving grooves are arranged over the circumference of the cylinder can. Due to the width of the grooves, the rounding of the perforating cylinder already plays a role here, so that the inserts or pressure bars are essentially trapezoidal in cross section.
• the beam cylinder can also fulfill the function of a piston movement when the pressure in the interior of the beam increases due to its wavy wall, which is flexible at least in the axial direction .
• injuries to the external elastic beam-cylinder walls can also lead to an immediate loss of pressure in the entire printing system within a perforating strip. Guide groove, so that during operation due to the immediate ejection due to the rapid rotation of the cylinder, not inconsiderable disturbances can occur, especially if parts of the printing system get between the rollers.
• the known device has a considerable sensitivity to leakage oil. It is therefore an object of the invention to avoid the aforementioned disadvantages of the known device and to ensure that the perforation lines are fixed securely to the perforation cylinder while being of simple construction.
• the invention has the advantage, on the one hand, that the required groove width on the perforating cylinder need not be greater than the thickness of the clamping strip plus the thickness of the perforating line, because the clamping strip simultaneously serves as a cylinder housing for the pistons of the clamping devices which it holds . It is also particularly advantageous that precisely where high and very high pressures occur, which can build up to extreme values of several 100 bar to generate the required clamping force, there are no resilient wall areas, but rather the pressure only inside the terminal strip, i.e. in the continuous connection channel and in the pressure chambers of the clamping cylinders. It is particularly advantageous that no leakage oil problems occur, since the result is that a soft-elastic solid body is used as the pressure transmission means, which always remains "coherent".
• Suitable materials and measures for realizing the pressure transmission body are indicated by the features of claims 2 to 7. Since the terminal block according to the invention is small and narrow, it is also subject to a comparatively low weight and less severe effects of gravity when the perforating cylinder is working. Damage to the pressure medium channel system of each terminal strip is practically impossible; Likewise, each clamping strip can be inserted into the groove of the perforating cylinder receiving it in such a way that no protruding parts or parts which then necessarily follow the shape of the perforating cylinder are exposed to the outside, with the exception of the edge of the clamped perforating line.
• the pressure screw when screwed in which the pistons arranged displaceably in the terminal block in the transverse direction are pressurized, is accessible radially from the outside, ie seen from the circumferential direction of the perforating cylinder. It is also particularly advantageous to design the terminal strip with a lower shoulder or a collar on which the perforating line, which extends over the length of the perforating cylinder, is seated, so that the height adjustment of the terminal strip and its subsequent non-positive and, if necessary, positive locking Anchoring also mediates the height adjustment of the assigned perforation line and its anchoring.
• FIG. 4 shows an enlarged representation of the pressure screw serving to increase the pressure of the pressure medium within the terminal block in a sectional view along the line IV / IV of FIG. 3;
• Fig. 5 is a sectional view of one of the pistons sealed in a cylinder bore of the terminal block in cross section along the line V / V of Fig. 3 and
• FIGS. 1 to 6 also schematically shows in cross section a detail of a shoulder screw arrangement which initially serves to insert the terminal strip loosely into the receiving cylindrical groove.
• FIGS. 1 to 6 Purpose of the device according to the invention shown in FIGS. 1 to 6, to the details of which reference is expressly made in its entirety, designated overall by 10, for fastening one or more perforation lines 11 to the perforation cylinder 26, one in FIG Printing machine represented by the anvil cylinder 26 ', by means of which prepresses prepared in a continuous printing process by transverse perforations for separating from one another can be produced without the need for major screwing work to be set quickly and without complications with high precision and securely with respect to the anvil cylinder 26'.
• This fastening device 10 is designed as a clamping strip, which can be inserted into a groove 25 of the perforating cylinder 26, into which the perforating line 11 is also inserted, and can be clamped in this groove 25, as a result of which the perforating line 11 also fixes in its desired position becomes.
• Such a perforation line 11 is designed in a typical design as a flat bar-shaped knife, the - straight line - cutting edge 11 'of which runs very precisely parallel to the surface line 33 of the anvil cylinder 26', which in turn runs parallel to the axis of rotation 32 of the anvil cylinder 26 ' along which the perforation to be created, for example in a paper tape, in each case in the longitudinal format spacing of a form to be produced.
• the perforating line 11 Since the cutting edge should generally push through to the outer surface 34 of the anvil cylinder 26 ', the perforating line 11 must be fixed very firmly in the groove 25 of the perforating cylinder -26, since a large number of cutting or Perforation operations are to be carried out.
• the groove 25 provided for receiving the perforation line 11 and the clamping strip 10 extends, viewed in the direction of the axis of rotation 34 of the perforation cylinder 26, over its entire axial length and is in the steel cylinder 26 with the profile cross section shown in FIG. 1, milled in.
• This groove 25 has a substantially U-shaped clear cross section, the one groove cheek 36, against which the perforation line 11 is pressed by means of the clamping strip 10, runs exactly radially, ie along a radial plane containing the axis of rotation 34 of the perforating cylinder.
• the groove cheek 37 which runs parallel to this groove cheek 36 and on which the clamping strip can be supported by means of clamping elements to be explained in more detail below, is measured somewhat from the lateral surface 37 of the perforating cylinder and is somewhat shorter than the radial groove cheek 36 and closes via an obliquely extending cheek section 38 on the groove base 39 running at right angles to the radial groove cheek 36, so that the cross section of the groove 25 tapers somewhat in the radially inner part of the groove.
• the clamping strip is designed as a prismatic steel rod which has boundary surfaces parallel to the groove cheeks 36 and 37, the oblique cheek section 38 and the groove bottom 39 and in this respect has a cross section geometrically similar to the clear cross section of the groove 25, the clamping strip 10 is designed so that it "largely” fills the clear cross section of the groove 25, in such a way that only gaps with a small width remain between the terminal strip 10 and the boundary surfaces of the groove 25.
• the groove 25 has a clear width w of 22.5 mm measured between its parallel groove flanks 36 and 37 and a depth t of 33 mm measured along its radial groove flank 36.
• the sloping cheek section 38 forms an angle o of 60 ° with the radial plane in which the radial groove cheek 36 runs.
• the range t 1 of the depth t of the groove 25, over which the sloping cheek section 38 extends, is 6 mm in the illustrated special embodiment.
• the terminal strip 10 is realized, for example, with the following dimensions:
• the tensioning devices 13, by means of which the clamping strip 10 and with this also the perforation line 11 in the groove 25 can be fixed in a load-proof manner, are, as can best be seen from FIG. 3, as at regular intervals over the length of the clamping strip 10 distributed pressure cylinders 13 'are formed, the pistons 13 of which are displaceably guided in transverse bores 12 of the clamping strip 10, the central bore axes 42 of which are perpendicular to the mutually parallel groove cheeks 36 and 37 of the groove or the boundary surfaces 36' and 37 'parallel thereto the terminal strip 10.
• the transverse bores 12 are formed as, seen in the position of use of the terminal strip 10, blind bores open to the narrower groove cheek 37 of the groove 25, from which the pistons 13 protrude. Pressure spaces 43 delimited axially by the pistons 13 and fixed to the housing through the inner sections of the blind bores 12 are in communicating connection with one another via a longitudinal bore 14 penetrating the terminal strip 10 in its longitudinal direction.
• the longitudinal bore 14 can be hermetically sealed at its ends by plugs 14 '.
• the longitudinal bore 14 connecting the pressure chambers 43 of the pressure cylinders 13 'to one another is also, as shown in detail in FIG.
• a piston 16a in communication with a pressure chamber 19 which is fixed to the housing through the inner section of a further blind bore 19' and is axially movable a piston 16a is delimited, which is guided in a pressure-tight manner in the blind bore 19 *.
• This piston 16a is sealed against the bore 19 'by means of an annular seal 20 designed as a sliding seal.
• the central axis 44 of this blind bore 19 runs at right angles to the boundary surfaces 39' and 41 of the terminal strip 10 which run parallel to the groove base 39.
• the blind bore 19 opens out on the surface 41 of the terminal block 10 facing the anvil cylinder 26 * with a Threaded section 21, the clear diameter of which is somewhat larger than the diameter of that section of the blind bore 19 'in which the piston 16a is displaceably guided in a pressure-tight manner.
• This threaded section 21 is offset by a thread undercut 22 of conventional design against the section of the blind bore 19 'which forms the housing-fixed boundary of the pressure chamber 19 and in which the piston 16a is displaceably guided in a pressure-tight manner.
• a pressure screw 16 which is designed as an Allen screw with a hexagon socket in the illustrated embodiment and is supported on the piston 16a via an axial extension 46, is screwable.
• the pressure spaces 43 of the pressure cylinders 13 * communicating with one another via the bore 14 and the pressure space 19 also communicating with these spaces through the piston 16a are completely filled with a pressure medium in which the pressure screw 16 is turned in the sense of a ver reduction of the pressure chamber 19, a high pressure can be built up, with which - via the bore 14 - the pressure chambers 43 of the pressure cylinder 13 * are also acted upon and thereby their pistons 13 are pressed against the groove cheek 37 and in response thereto the clamping strip against the perforation line 11 is pushed, which, depending on the size of the pressure generated by turning the pressure screw 16, is pressed more or less firmly against the radial groove flank 36 and thereby fixed in its desired position.
• the axial extension 46 of the pressure screw 16, with which it is axially supported on a flat end face 47 of the piston 16a, is of flat-spherical design, so that there is only one support point lying on the central axis 44 and when the pressure is twisted is ⁇ screw 16 in the sense of a pressure increase no torque exerted on the piston 16a to allow rotation "of the piston 16a itself, and a resulting wear Ver ⁇ 20 to prevent the ring seal.
• the terminal strip 10 is provided at its ends with a stepped bore, designated overall by 17, the arrangement of which can best be seen in FIG. 3 and the design is best shown in FIG. 6, to the details of which reference is hereby made.
• the central axes 47 of these stepped bores viewed in the position of use of the clamping strip 10, run perpendicular to the groove base 39 of the groove 25 of the perforating cylinder 26.
• stepped bores comprise a minimum diameter of the central section 17 'corresponding to the stepped bore 17, to each of which a radial ring is attached ⁇
• Shoulder 48 and 49 connect an outer, outwardly open bore section 17 "or an inner, open to the groove base 39 outward bore section 17"'of larger diameter.
• the outer bore section 17 “serves for the recessed reception of the head 49 of a shoulder screw, generally designated 28, which has a bolt-shaped shaft 51 which adjoins the head and which is slightly smaller in diameter than the diameter of the central section 17 '. of the respective stepped bore 17.
• This cylindrical-bolt-shaped shaft 51 of the respective shoulder screw 28 is followed by the smaller, smaller threaded section 52 of the shoulder screw 28, with which the latter screws into a threaded hole starting from the base 39 of the groove 25 53 is screwed in until the shoulder screw with the annular end face 54 of its bolt-shaped shaft 51, which sets it against the threaded section 52, sits on the bottom 39 of the groove 25 of the perforating cylinder 26.
• the difference in lengths 1 and 1 ' determines the radial range of variation within which the position of the cutting edge 11' of the perforation line 11 can be changed or adapted to the course of the surface line 33 of the anvil cylinder 26 'along which the perforation line - sitting on the lateral surface 35 of the anvil cylinder 26 '- piercing or cutting through the material web lying against it - not shown -.
• FIG. 6 shows a "middle" position of the cutting edge 11 'of the perforation line 11, from which the perforation line 11 can, if necessary, be disengaged from the groove 25 by a small distance h or by a small distance h 'could be lowered further into the groove 25 in the radial direction.
• a position corresponding approximately to the "center position" of the perforation line 11 shown is the position suitable for the cutting processing of the material web.
• the position of the perforation line 11 in the correct position is considerably facilitated by the design of the terminal strip 10 and its arrangement in the groove 25 of the perforating cylinder 26.
• the pressure acting on the pistons 13 of the tensioning devices is increased to such an extent that when the two cylinders 26 and 26 'are rotated in phase with respect to one another, the perforating strip does move somewhat into the groove 25 and thus its desired Position can assume that, however, if the line contact of the perforation line 11 with the jacket 35 of the anvil cylinder 26 'is canceled again by rotating the two cylinders 26 and 26' again, the terminal strip 10 is not pushed back into its radially outer position, but by the Pressurization of the piston 13 of the clamping cylinder 13 'remains in its target position.
• the pressure in these rooms will increase so far, for example to 300 bar or more, that the perforation line 11 remains absolutely secure and only in its desired position due to the clamping effect achieved thereby. If a paper web of any thickness then gets between the two cylinders 26 and 26 ', the cutting edge 11' of the perforation line 11 perforates the paper web at this point up to the outer surface 35 of the anvil cylinder 26 '.
• set screws 31 are provided which are screwed into threaded bores 30 whose axes 58 run parallel to the axes 47 of the stepped bores 17.
• the pressure transmission body should have a Shore A hardness between 20 and 70, preferably between 30 and 50, at operating temperature.
• the elastic pressure transmission body filling the pressure chambers can also consist of soft PVC material or of a softened copolymer of vinyl chloride and vinyl acetate.
• Low density soft polyethylene (PE-LD) is also suitable for realizing the pressure transmission body.
• a cold-crosslinking material can also be used to produce the pressure body, for example a polysiloxane, the liquid starting products of which immediately after Mixing can be poured into the pressure chambers and sealed there network these filling rubber-elastic pressure transmission bodies.
• a pressure transmission body based on polysiloxa can no longer be removed from the terminal strip 10, but has the advantage of cheaper pressure transmission shafts and a high long-term stability, which makes "replacing" the pressure transmission body seem superfluous anyway.
• Suitable polysiloxane materials are also described on page 223 ff. Of the publication mentioned.
• the fastening device according to the invention which consists of the clamping strip 10 and - on the machine side - each of a receiving groove 25 for this clamping strip, is constructed in a sufficiently space-saving manner that, distributed over the circumference of a perforating cylinder 26, several clamping strips 10 can be arranged, whereby the distance of the clamping strips 10 or the perforation lines 11 measured along the circumference of the perforating cylinder is at least 2 inches.
• the oblique course of the groove cheek section 38 of the groove 25 ensures that there is always enough "meat" of the cylinder material between successive grooves, as seen in the circumferential direction, to reliably prevent damage to the cylinder walls extending between two grooves 25 .

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Life Sciences & Earth Sciences (AREA)
• Forests & Forestry (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• General Engineering & Computer Science (AREA)
• Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)
• Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)

Priority Applications (2)

Applications Claiming Priority (2)

Publications (1)

Family

ID=6336637

Family Applications (1)

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Citations (5)

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• 1987
  • 1987-09-23 DE DE19873731957 patent/DE3731957A1/de active Granted
• 1988
  • 1988-09-23 EP EP88908140A patent/EP0335926B1/de not_active Expired - Lifetime
  • 1988-09-23 DE DE8888908140T patent/DE3866696D1/de not_active Expired - Lifetime
  • 1988-09-23 AT AT88908140T patent/ATE69988T1/de active
  • 1988-09-23 WO PCT/DE1988/000588 patent/WO1989002813A1/de not_active Ceased

Patent Citations (5)

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