EP4059675A1 - Machine à couper comprenant le processus de pressage/découpe à commande forcée - Google Patents

Machine à couper comprenant le processus de pressage/découpe à commande forcée Download PDF

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Publication number
EP4059675A1
EP4059675A1 EP21163028.0A EP21163028A EP4059675A1 EP 4059675 A1 EP4059675 A1 EP 4059675A1 EP 21163028 A EP21163028 A EP 21163028A EP 4059675 A1 EP4059675 A1 EP 4059675A1
Authority
EP
European Patent Office
Prior art keywords
cutting
cutting machine
pressing
cam disc
machine according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP21163028.0A
Other languages
German (de)
English (en)
Other versions
EP4059675B1 (fr
EP4059675C0 (fr
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.)
Krug and Priester GmbH and Co KG
Original Assignee
Krug and Priester GmbH and Co KG
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.)
Filing date
Publication date
Application filed by Krug and Priester GmbH and Co KG filed Critical Krug and Priester GmbH and Co KG
Priority to EP21163028.0A priority Critical patent/EP4059675B1/fr
Priority to CA3148049A priority patent/CA3148049C/fr
Priority to US17/654,590 priority patent/US11491676B2/en
Publication of EP4059675A1 publication Critical patent/EP4059675A1/fr
Application granted granted Critical
Publication of EP4059675B1 publication Critical patent/EP4059675B1/fr
Publication of EP4059675C0 publication Critical patent/EP4059675C0/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • B26D7/01—Means for holding or positioning work
    • B26D7/02—Means for holding or positioning work with clamping means
    • B26D7/04—Means for holding or positioning work with clamping means providing adjustable clamping pressure
    • 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
    • B26D7/01—Means for holding or positioning work
    • B26D7/02—Means for holding or positioning work with clamping means
    • B26D7/025—Means for holding or positioning work with clamping means acting upon planar surfaces
    • 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
    • B26D1/00—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor
    • B26D1/01—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work
    • B26D1/04—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a linearly-movable cutting member
    • B26D1/06—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a linearly-movable cutting member wherein the cutting member reciprocates
    • B26D1/08—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a linearly-movable cutting member wherein the cutting member reciprocates of the guillotine type
    • 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
    • B26D5/00—Arrangements for operating and controlling machines or devices for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B26D5/08—Means for actuating the cutting member to effect the cut
    • B26D5/16—Cam means

Definitions

  • the invention relates to a cutting machine with a cutting support for the material to be cut, with a cutter bar that can be moved in height and carries a knife for cutting the material to be cut on it, with a cutting drive for moving the cutter bar in height, with a press beam that can be moved in height for pressing down the material to be cut, and with a press drive for adjusting the height of the press beam.
  • the clippings can be a stack of paper, for example.
  • the smaller cutting machines occupy a certain special position, since the forces required to actuate the pressing of the cuttings are not as high as in larger machines, so that the operator's muscle strength is often sufficient and no motor support is necessary. These machines are often not production machines that the operator works with all day long. Such machines are typically used in copy shops, for example. Partial or full electrification is often used primarily for increased comfort, since the operator's effort is reduced and work can also be done faster in the long term. Since the segment of small machines is particularly price-sensitive, the focus here is on the manufacturing costs for the respective functional principle and must not be too high in relation to the manual machine variant. For this reason, only simple electrification systems are used here, sometimes only the blade drive is motor-driven. If the clippings pressing device is also driven by a motor, the pressing pressure is generally not adjustable. The devices in this machine group are not the focus of further consideration.
  • Cutting machines of the medium machine group size have a very wide use, starting from the professional copy shop to in-house printers to professional printers. These machines are particularly suitable for small and medium-sized paper formats, which are often used in digital printing processes. For this reason, this medium-sized machine size group has gained in market importance and the required level of professionalism. The market is increasingly demanding equipment features and working speeds that were previously reserved primarily for machines in the large machine size group. In the medium machine group segment, however, the equipment features can usually not be implemented using the techniques of the large machine group size. Reasons for this are, for example, the size, the complexity and the Price for the realization of the equipment features. Machines in medium-sized machine groups should be able to be operated on the standard secured single-phase power grid, as this is available at almost all desired locations.
  • the energy efficiency of such machines is important for several reasons.
  • One reason is that, as with all electrically operated devices, the required energy consumption should be kept as low as possible from the point of view of environmental protection and operating costs.
  • Another reason is that the desired single-phase domestic installation limits the possible power consumption and thus the performance of the machine. This means that the more energy-efficient the machine works, the more power can be used productively for the actual machine function.
  • a foot pressure of the press beam should be decoupled from the electromotive press drive of the press beam.
  • the cutting and pressing drives are formed by a single drive (e.g. an electromotive drive motor) which rotates a cam disk back and forth, and that the cutter bar is movably coupled to the cam disk via a first coupling mechanism which acts on the cam disc eccentrically to its axis of rotation, in particular is articulated, and the press beam is movably coupled to the cam disc via a second coupling mechanism, one first end of which bears against the outer contour of the cam disc.
  • a single drive e.g. an electromotive drive motor
  • the pressing of the cuttings and the cutting of the cuttings are positively coupled via the cam disk and are therefore easier to control in terms of safety.
  • the outer contour of the cam disk is designed in such a way that when the drive motor is running forwards, the press beam always moves down ahead of the knife. This ensures that the knife is always covered by the press bar until it dips into the material to be cut (operating safety, e.g. when the net is disconnected during the pressing/cutting process).
  • the outer contour of the cam disk particularly preferably has a front contour section in the forward direction of rotation and a rear contour section, the front contour section rising more radially outward than the rear contour section.
  • the outer contour of the cam disk is preferably designed in such a way that the build-up of the desired pressing pressure during the pressing process is almost complete by the start of the cutting process and is maintained during the cutting process.
  • the curved contour of the cam begins on the front section of the contour and rises steeply. This builds up pressure as quickly as possible before cutting force is required.
  • both functions can be operated with one drive motor. Since this happens with a time lag, the drive motor does not have to provide the power for both functions at the same time and therefore does not have to be dimensioned larger.
  • the contour of the cam disc only has a slight incline on the rear section of the contour after an initial sharp rise, to compensate for a pressure drop in the hydraulic system of the hydraulic device caused by leakage oil. All in all, the result is an optimized energy efficiency and power distribution during the pressing/cutting process in relation to the maximum available power consumption on a standard secured single-phase mains supply.
  • the first coupling mechanism has a connecting rod, which acts on the cam disc eccentrically to its axis of rotation, in particular is articulated
  • the second coupling mechanism has a piston/cylinder hydraulic device or a compression spring, one, first end of which is attached to the outer contour of the cam disc, in particular by means of a guide roller, rests or rolls off.
  • the piston/cylinder hydraulic device preferably has a pressure control valve in order to adjust the (hydraulic) pressure that is required to press a piston into a press cylinder of the hydraulic device.
  • the desired baling pressure is set by adjusting the maximum pressure on the pressure control valve.
  • the adjustment can be made either manually via an adjusting element attached to the pressure control valve or electrically via an adjusting element driven by an electric motor.
  • the piston is only able to displace the oil in the press cylinder into a hydraulic oil tank once the pressure set on the pressure control valve has been reached. This pressure is proportional to the pressing pressure on the clippings.
  • the piston of the piston/cylinder hydraulic unit is permanently, ie during the entire pressing/cutting cycle, subjected to an ejection force which pushes the piston out of the cylinder/hydraulic unit.
  • the ejection force can be provided, for example, by a compression spring or a gas pressure spring unit or by a permanent overpressure in the piston/cylinder hydraulic unit.
  • the pressing beam is pressed onto the cuttings by the ejection force until the cam disk and with it the piston of the piston/cylinder hydraulic unit have moved back so far that it has reached its extended position and is forcibly coupled to move the pressing beam upwards into its starting position.
  • the cutting machine particularly preferably has a foot pedal for manually adjusting the height of the press beam, which is coupled for movement both to the press beam and to the other, second end of the second coupling mechanism in order to lift the first end of the second coupling mechanism from the outer contour of the cam disc by actuating the foot pedal .
  • a foot pedal deflection linkage preferably engages directly in a deflection mechanism that acts between the second coupling mechanism and the press beam. In this way, the clippings can be pressed independently of the cam disc position by pressing the foot pedal in order to manually compress the clippings.
  • Figs. 1a , 1b a cutting machine according to the invention in a front view ( Fig. 1a ) and in a rear view ( Fig. 1b ), where in Fig. 1b a foot pedal for manual operation of a press beam of the cutting machine is not shown.
  • the cutting machine 1 shown comprises a cutting support 2 for the material to be cut, such as a stack of paper, a height-adjustable cutter bar 3 (here diagonally downwards) which carries a knife 4 for cutting the material to be cut on it, a height-adjustable press bar 5 for pressing down the material to be cut and a drive in the form of a drive motor 6 as a cutting drive for moving the cutter bar 3 vertically and as a press drive for moving the press beam 5 vertically.
  • a cutting support 2 for the material to be cut, such as a stack of paper
  • a height-adjustable cutter bar 3 here diagonally downwards
  • a knife 4 for cutting the material to be cut on it
  • a height-adjustable press bar 5 for pressing down the material to be cut
  • a drive in the form of a drive motor 6 as a cutting drive for moving the cutter bar 3 vertically and as a press drive for moving the press beam 5 vertically.
  • the drive motor 6 rotates a cam disk 7 back and forth by approximately 180°.
  • the cutter bar 3 is movably coupled to the cam disk 7 via a first coupling mechanism A in the form of a connecting rod 8 , which is articulated on the cam disk 7 eccentrically to its axis of rotation.
  • the press beam 5 is movably coupled to the cam disk 7 via a second coupling mechanism B in the form of a piston/cylinder hydraulic device 9 , one, first end 9a of which bears against the outer contour 10 of the cam disk 7 .
  • the first end 9a is formed by the free end of a piston or a piston rod 11 of the hydraulic device 9, which carries a guide roller 12 .
  • the guide roller 12 is pressed against the outer contour 10 of the cam disk 7 by means of a spring 13 .
  • the end of a press cylinder 14 of the hydraulic device 9 facing away from the piston rod 11 forms the other, second end 9b of the hydraulic device 9 which is connected to a deflection mechanism 15 which actuates the press beam 5 .
  • the drive motor 6 starts, which rotates the cam disc 7, to which the connecting rod 8 for actuating the blade is also rotatably fastened.
  • the connecting rod 8 is fastened to the cam disk 7 at a distance from the axis of rotation of the cam disk 7, so that the cam disk 7 functions as a crankshaft. Rotates the cam 7, the connecting rod 8 is pulled down.
  • the other end of the connecting rod 8 is rotatably attached to the cutter bar 3 and pulls it down together with the cutter 4 within a sloping guide slot 16 for cutting.
  • the outer contour 10 of the cam disk 7, ie the radial distance from the axis of rotation, is designed in such a way that the press beam 5 always moves down ahead of the blade 4 in the forward run.
  • the press beam 5 therefore always protrudes beyond the blade 4 until it rests on the material to be cut and the actual cutting process begins. This increases operator safety in the event that the pressing/cutting process is stopped (eg by turning off the main switch) before the blade 4 engages with the material to be cut.
  • the outer contour 10 of the cam disk 7 has a front contour section 10a and a rear contour section 10b in the forward direction of rotation.
  • the front contour section 10a rises radially outward more than the rear contour section 10b.
  • the gradient of the outer contour 10 is therefore very large at the beginning, so that the pressing process is almost complete by the time the cutting process begins.
  • the available motor power of the drive motor 6 is thus divided up over time during the pressing/cutting process in such a way that almost the full motor power is available for both sub-processes.
  • the hybrid functionality of the optimal electromechanical blade direct drive for the cutting process and the optimal, hydraulically adjustable pressure over a wide range for the cutting process is implemented with only one drive motor 6 and one pressure cylinder 14 and thus at low cost.
  • the pressing cylinder 14 is connected directly to the deflection mechanism 15 of the pressing of the cuttings, and the piston rod 11 is coupled to the outer contour 10 of the cam disk 3 via the guide roller 12 .
  • the press cylinder 14 itself thus forms part of the deflection mechanism 15 and moves as a whole until the cuttings are reached during pressing. Subsequently, essentially only the piston rod 11 moves relative to the press cylinder 14 in order to build up the press pressure that has been set.
  • the ejection force can act on the piston, for example, by means of a compression spring 19 or gas pressure spring unit, with the compression spring 19 or gas pressure spring unit inside or, as in Fig. 1a shown, outside the piston / cylinder hydraulic unit 9 may be mounted.
  • a further exemplary embodiment can be achieved by a permanent overpressure in the piston/cylinder hydraulic unit 9, which acts like a corresponding spring acts and pushes the piston out of the piston/cylinder hydraulic unit 9 permanently with a defined force.
  • Fig. 1a shows a foot pedal 20 for manual actuation of the press beam 5. If the foot pedal 20 is moved downwards, the press beam 5 is pulled downwards via the foot pedal deflection linkage 21 , ie in the direction of the clippings inserted.
  • the foot pedal 20 is coupled for movement both to the press beam 5 and to the second end 9b of the hydraulic device 9 in order to lift the first end 9a of the hydraulic device 9 from the outer contour 10 of the cam disk 7 by actuating the foot pedal 20 .
  • the press beam 5 can thus be operated independently of the electrical press/cutting cycle and thus independently of the safety control. This means that the operator can manipulate the stack of paper with lowered pressure when the pressure is actuated by means of the foot pedal 20, although he is moving in the monitored safety area of the machine. This is permissible because the pressure is applied by the operator himself using his leg strength. If necessary, the operator can press out the air between the individual layers of the material to be cut before the automatic pressing/cutting cycle by pressing his foot, or he can see exactly where the cut is being made by the knife 4 directly in front of the pressing beam 5 via the front edge of the lowered press beam 5 becomes. If necessary, the operator can realign the clippings with the press beam 5 lowered.
  • the decoupling of the foot pressure from the automatic pressure is possible because when the foot pressure is actuated, the deflection mechanism 15 of the pressure mechanism is moved in such a way that the pressure beam 5 is lowered in the direction of the material to be cut.
  • the press cylinder 14 fastened to it with the piston rod 11 together with the guide roller 12 also moves with the deflection mechanism 15 .
  • the hydraulic device 9 is thus moved independently of the position of the cam disk 7 .
  • the automatic pressing/cutting process is triggered when the foot is pressed, it runs as described above. However, the guide roller 12 and with it the entire remaining hydraulic device 9 are not in contact with the outer contour 10 of the cam disc 7 at the beginning of the pressing/cutting process. This means that the knife 4 is moved downwards without starting the automatic pressing process until the cam disk 7 has turned so far that the guide roller 12 lifted by the foot pressure comes into contact with the outer contour 10 of the cam disk 7 again. Only then does the set pressure build up in the system and the blade 4 engages with the material to be cut.
  • the foot pedal deflection linkage 21 can have a gas pressure spring 22 .
  • the gas pressure spring 22 does not retract, ie it acts like a rigid linkage, until a specified, maximum actuating force (specified spring force of the gas pressure spring 22) is reached. If this maximum actuating force is exceeded, the gas pressure spring 22 is compressed without the rest of the system being additionally loaded until the foot pedal 20 rests on the floor.
  • a compression spring can alternatively be used, which is compressed during the compression process (instead of the piston 11 being pushed in against the set overflow pressure). The pressing force can then be adjusted within certain limits by preloading the compression spring.
  • the compression spring must - like the piston/cylinder hydraulic unit 9 - be limited in its maximum expansion, since otherwise it would permanently actuate the compression. To do this, it can either be completely relaxed in the rest position (compression is in the upper end position) or preloaded in advance using a spring deflection limiter.
  • a traverse running in the center of the compression spring can be installed as a spring deflection-limiting element, at the ends of which there are discs that limit the compression spring in its maximum extent.
  • the compression spring variant thus also follows the cam disk only when it is prestressed against the outer contour 10 of the cam disk 7 by the force of the spring 13 .

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  • Life Sciences & Earth Sciences (AREA)
  • Forests & Forestry (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shearing Machines (AREA)
  • Sawing (AREA)
EP21163028.0A 2021-03-17 2021-03-17 Machine à couper comprenant le processus de pressage/découpe à commande forcée Active EP4059675B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP21163028.0A EP4059675B1 (fr) 2021-03-17 2021-03-17 Machine à couper comprenant le processus de pressage/découpe à commande forcée
CA3148049A CA3148049C (fr) 2021-03-17 2022-02-04 Machine de coupe ayant un procede de commande de coupe/presse positive
US17/654,590 US11491676B2 (en) 2021-03-17 2022-03-12 Cutting machine with positively controlled pressing and cutting process

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21163028.0A EP4059675B1 (fr) 2021-03-17 2021-03-17 Machine à couper comprenant le processus de pressage/découpe à commande forcée

Publications (3)

Publication Number Publication Date
EP4059675A1 true EP4059675A1 (fr) 2022-09-21
EP4059675B1 EP4059675B1 (fr) 2023-06-21
EP4059675C0 EP4059675C0 (fr) 2023-06-21

Family

ID=74947082

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21163028.0A Active EP4059675B1 (fr) 2021-03-17 2021-03-17 Machine à couper comprenant le processus de pressage/découpe à commande forcée

Country Status (3)

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US (1) US11491676B2 (fr)
EP (1) EP4059675B1 (fr)
CA (1) CA3148049C (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115464692B (zh) * 2022-09-16 2024-06-25 泰安佳路通工程材料有限公司 一种土工膜横切装置及其切割方法
CN116494315B (zh) * 2023-06-30 2023-08-25 深圳市极腾网络科技有限公司 一种小型主机主板加工装置及加工方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB721619A (en) * 1952-05-29 1955-01-12 Albert Robert Gooda Improvements in guillotines
DE1952742A1 (de) * 1969-10-20 1971-04-29 Rudolf Mohr Hydraulisches Kolbenverbundsystem fuer den Antrieb des Pressbalkens von Schneidemaschinen fuer Papier od.dgl.
DE202008013651U1 (de) * 2008-10-17 2010-03-04 Krug & Priester Gmbh & Co. Kg Stapelschneider mit Automatikpressung

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2570873A (en) * 1946-05-31 1951-10-09 E P Lawson Co Inc Paper cutter
US2492330A (en) * 1948-03-05 1949-12-27 James C Smith Cutting machine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB721619A (en) * 1952-05-29 1955-01-12 Albert Robert Gooda Improvements in guillotines
DE1952742A1 (de) * 1969-10-20 1971-04-29 Rudolf Mohr Hydraulisches Kolbenverbundsystem fuer den Antrieb des Pressbalkens von Schneidemaschinen fuer Papier od.dgl.
DE202008013651U1 (de) * 2008-10-17 2010-03-04 Krug & Priester Gmbh & Co. Kg Stapelschneider mit Automatikpressung

Also Published As

Publication number Publication date
CA3148049C (fr) 2022-11-22
CA3148049A1 (fr) 2022-05-03
EP4059675B1 (fr) 2023-06-21
EP4059675C0 (fr) 2023-06-21
US11491676B2 (en) 2022-11-08
US20220297332A1 (en) 2022-09-22

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