• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A block cutting machine having a structural frame (1, 2, 3, 5) in which a cutting blade (L) slides like a guillotine which is held elastically raised and can be dropped under pressure to a support plane (4) by a lever transmission mechanism, the mechanism having at least one lever (12, 13) with a fulcrum on an upper cross member (5) of the frame in a decentralized position, and a push shaft (9) acting on the cutting blade (L) and in a longitudinal position in a support plate (6) is adjustable, wherein the support plate (6) in a vertical plane with respect to the upper cross member (5) pivots, wherein the actuating lever (12, 13) in rotation with a small shaft (10 a) is integral has at least a first (10) and a second (14) cam profile, which cooperates with a portion (6a) of the pivot plate (6).
    公开号:AT13542U1
    申请号:TGM328/2010U
    申请日:2010-05-21
    公开日:2014-03-15
    发明作者:
    申请人:Montolit Brevetti；
    IPC主号:
    专利说明:

    (19) Austrian Patent Office (ίο) AT13 542 U1 2014-03-15 (12) (21) Application number: (22) Date of filing: (24) Start of protection period: (45) Published on:
    Utility Model GM 328/2010 21.05.2010 15.01.2014 15.03.2014 (51) Int. CI. : B28D1 / 22 (2006.01) (30) (56)
    Priority:
    22.05.2009 IT MI2009U000172 claims. References: CN 201044972 Y JP 09295314 A (73)
    Utility model holder: BREVETTI MONTOLIT S.P.A. 21050 CANTELLO (IT) AT13 542 U1 2014-03-15
    (54) BLOCK CUTTER WITH IMPROVED CAM LEVER (57) A block cutting machine comprising a structural frame (1, 2, 3, 5) in which a cutting blade (L) slides like a guillotine, which is held elastically raised and under pressure to a support plane (Fig. 4) can be dropped by a lever transmission mechanism, the mechanism having at least one lever (12, 13) with a fulcrum on an upper cross member (5) of the frame in a decentralized position, and a push shank (9) resting on the Cutting blade (L) and is adjustable in a longitudinal position in a support plate (6), wherein the support plate (6) in a vertical plane with respect to the upper cross member (5) pivots, wherein the actuating lever (12, 13) in rotation with a small shaft (10a) is integral, which has at least a first (10) and a second (14) cam profile, which cooperates with a portion (6a) of the pivot plate (6).
    DVR 0078018
    MerreicfcLvche ;; paiesSitiat AT13 542U1 2014-03-15
    Description: The present utility model relates to an improved block cutter, in particular a block cutter with laterally hinged leverage.
    As is known, a block cutter is a portable machine, typical of applications on construction sites, which is designed to cut small concrete blocks or blocks with significant strength, for example, the components of self-locking pavement for outdoor installation.
    In order to perform such a function, this machine must be robust and allow the user to apply significant breakage pressure without requiring excessive effort. Thus, these machines typically consist of a pair of parallel guide posts that rise vertically from a base, with a razor blade mounted like a guillotine on the uprights slidingly with a lower, wedge-shaped edge. The blade is designed to move firmly down the base, along the stand, until it hits a small block that is laid by hand on the base and cuts it in opposition to a lower blade.
    The upper blade is kept pressed by a spring system upwards, so that the guillotine opening is automatically kept open and facilitates the insertion of the parts to be cut. The opening of the guillotine opening is actuated by adjusting means which determine the blade position relative to the base in the home position. Depending on the situation, the blade can be adjusted in height by adjusting means disposed between the blade and the upper cross member of the machine or between the upper cross member with which the blade is integral and the side posts. In the former case, typically a large screw is provided which engages a corresponding threaded seat in the upper cross member and therefore can lower or rise depending on the screw of the screw on the cross member. In the latter case, the two transverse beam ends are provided with respective threaded flanges, which can be rotated by turning vertically on the two uprights. Although this latter type forces the blade to the upper cross member, which makes the structure intrinsically rigid, but is much more complex to use.
    In order to transmit the fracture action, a lever system is provided which can be operated by the user as desired and moves the blade downwardly away from the upper cross member of the machine.
    So far, two basic configurations for the lever pressure system have been proposed.
    One of them provides the articulation of a long operating lever in a substantially intermediate position (that is, lying transversely on the axis of symmetry of the guillotine structure) on the upper cross member of the machine. On the same pivot axis, a cam is further provided, which pushes the cutting blade by the lever rotation down.
    This first system, which has been provided in different configurations, is simple and quite inexpensive. Provided that the cam profile is configured accordingly, it also causes considerable blade strokes, even at small angles of rotation of the operating lever, so that it is possible to perform the cutting action and opening of the guillotine by means of small pivotal action on the lever, which is convenient for the operator is and allows him to realize a productivity advantage. Conversely, a large stroke of the blade with a small lever travel causes an unfavorable transmission ratio and therefore forces the operator to make a significant effort unless he has a very long lever, which again is awkward for other reasons.
    To compensate for this disadvantage, it is theoretically necessary that the user acts standing on the machine lever and also uses his body weight on the lever, which is not welcomed by tilers who are used to working near the floor, often kneeling. The operators therefore typically use this machine "impulsively"
    This means that they cause the lever to oscillate over successive short strokes and utilize the kinetic energy that can be applied to the lever, and therefore to the transmission mechanism, to line them up of pressure strokes on the blade that will eventually cut through the underlying block.
    However, this operation forces an oversize of the machine organs to avoid premature failure, which is also unfavorable for their weight. The shock also results in setbacks in the system that affect the arm of the operator with undesirable pathological conditions that may arise for the worker. Finally, it has been recognized that this technique makes it very difficult to cut cured concrete blocks, that is, those that have become particularly hard over time.
    A second system instead provides articulation of the operating lever on the cross member on one side of the machine, for example near one of the two stands, and then placing a transfer lever force on a pressure member centrally located above the cutting blade.
    A typical machine of this type is represented by the patterns Art. 4 or Art. 6L, which are marketed by the same Applicant and are the subject of the international sample DM / 031555 and the Italian Utility Model No. 168,000.
    The operation of this machine is excellent and does not require significant force. Conversely, the transmission system is more complex and requires a long movement of the operating lever to achieve a suitable stroke of the cutting lever.
    The actual stroke restriction poses no problem during the block cutting phase, as normally a very short stroke of high pressure is required to break a concrete block. Instead, it presents a disadvantage during the phase of inserting the block into the machine. Since the height or thickness of the block (especially if made of stone instead of cast concrete) will vary widely (two to four millimeters) within the same batch It may be necessary to guarantee a good opening stroke of the guillotine structure each time a block needs to be repositioned on the base after the previous one has been cut. Under these conditions, and when the operator has to perform a wide rotation of the operating lever, an awkwardness arises, which is perceived as slowing down productivity or adding workload.
    A similar disadvantage arises in both types of machines when a brief break occurs in the cutting sequence; in fact, it is not possible to keep the opening stable temporarily in its maximum open position, because the operating lever does not remain in a stable equilibrium position in such a condition (due to its own weight, it always tends to fall, closing the guillotine opening, especially if Bearings and bushings are used which have low inertia and friction). In these cases, the operator is forced to stand up and raise the lever completely and place it in a stable home position, usually folded back to the opposite side to the operating side. This process of folding back the lever is perceived as cumbersome in many circumstances.
    When the lever is finally in a stable starting position, one recognizes a further disadvantage in connection with the setting of the machine.
    Namely, in such a position, the lever is completely freed from the blade and the guillotine opening is wide open and largely exceeds the opening of the break start, that is, the opening which is determined when the lever is in the correct position for the print action returned to the operator.
    The height adjustment of the blade, which can be created under these conditions, is therefore not optimal for working on the blocks. In essence, the adjustment of the opening of the guillotine opening width must be folded back with the folded back to a starting position 2/18
    esteirelchiscsei pitwiarot AT13542U1 2014-03-15
    Lever should be set slightly further than required. Since this oversize can not be determined a priori, the following procedure is operationally applied: The operator inserts a block into the guillotine aperture and adjusts the blade height, leaving a large gap (for example, at least 2 cm) between the blade and the top The surface of the block is left empty; then he brings the lever to a break start position and checks if it is in the immediate vicinity of the block: if this distance is not met, it raises the lever back to a home position and adjusts the adjustment means again. In essence, two or three tries will give you the desired setting, but, as you can imagine, at the cost of a smooth action.
    The object of the present invention is therefore to provide an effective solution to these problems by providing a block cutter of the second type, which allows the cutting blade a significant stroke and also reduced rotations of the operating lever.
    Further, it is aimed to provide a block cutter in which the operating lever, even with a guillotine opening in an open position, which is suitable for starting the fracture action, can be kept in a stable starting position.
    These objects are achieved by means of a block cutting machine, as described in its essential features in the appended main claim.
    Other inventive aspects of the block cutter are described in the dependent claims.
    In any event, further features and advantages of the machine according to the invention will become more apparent from the detailed description given by way of example and illustrated in the accompanying drawings, wherein: Fig. 1 is a perspective view of the block cutting machine according to the invention; Fig. 2 is a front elevational view of the machine of Fig. 1; Fig. 3 is a side elevational view of the machine of Fig. 1; Figs. 4A to 7A are side elevational views with parts broken away of different operating modes of the machine of Fig. 1, of which Figs. 4B to 7B are enlarged detail views, respectively; Figs. Fig. 8 is a perspective view of a small camshaft according to the invention; Fig. 9 is a schematic view of the cam profile of the small wave of
    Fig. 8 is; Fig. 10A is a perspective view of the machine according to the invention, of which
    Fig. 10B is an enlargement of the detail contained in a circle A; and Fig. 11 is an enlarged view of an operating phase of the cam of the invention.
    A block cutting machine consists, as is known, of a base beam 1, from which two vertical, parallel posts 2 and 3 rise, between which a support plane 4 is provided in the lower part.
    The base beam 1 may be further provided with a pair of idler wheels W1 and W2 capable of improving the portability of the engine.
    In the upper part of the uprights 2 and 3, a fixed cross member 5 is provided parallel to the support plane 4. Advantageously, each of the uprights 2 and 3 consists of a pair of beams, 2a, 2b and 3a, 3b, respectively, which are arranged at a short distance from each other, FIG. so as to define a sliding path for an upper cutting blade L slidably mounted vertically along the stand.
    The blade L has the shape of an elongated rectangular plate with a lower wedge-shaped edge, which is held parallel to the support plane 4. The blade L is kept pressed by an elastic means (not shown) housed between each of the two beam pairs 2a, 2b and 3a, 3b in a raised position.
    Provided below the cutting blade L is a lower stop counter-blade R having an upper, wedge-shaped edge which is substantially flush with the support plane 4. The stop counter blade R is held firmly fixed to the base 1 and to the uprights 2 and 3 to act as a secure stop for the blade L during the cutting of concrete blocks.
    To provide space for the counterblade R, the support plane 4 is divided into two compartments 4a and 4b, which are mounted on the two sides of the plane extending through the stand 2 and 3, projecting. At least one of the two compartments, the left 4a in Fig. 2, is preferably arranged to be folded down to an inclined position, so that one can make bevel cuts on the blocks (the slants facilitate the laying of blocks under certain circumstances). ,
    The upper cross member 5, like the side posts itself, consists of a pair of parallel rods 5a and 5b fixed to the outside of the two posts 2 and 3 and therefore spaced apart so as to leave a pocket free receives a transmission mechanism. The mechanism, better visible in Figures 4B to 7B, consists of a metal plate 6 hinged to the support 5 with a bolt 7 running from one end to the other through the two rods 5a and 5b.
    The plate 6 can rotate freely around the bolt 7. In the center region, it has a core portion 8 which is provided with a through-threaded bore to lie substantially on the center axis of the cross member 5. A threaded shaft 9 is coupled to the threaded bore of the core 8, enters the corresponding bores drilled in the plate 6 and exits therefrom.
    The threaded shaft 9 has an upper operating knob 9a and a rounded lower end 9b, which is connected to the blade L or to a supporting plate L | can come into contact. While the position of the plate 6 is the same, screwing or unscrewing the threaded shaft 9 determines raising or lowering of the blade L, which is resiliently pushed up, and therefore defines an opening adjustment of the guillotine opening, that is, the distance between the two wedge-shaped edges upper blade L and counterblade R.
    According to the invention, the plate 6 has a push portion 6a, on which acts a cam 10 which rotates about an axis of the shaft 10a, which is supported transversely relative to the cross member 5 on respective bearings 11.
    The shaft 10a has two ends extending on both sides of the cam 10 as clearly shown in FIG.
    The two ends of the shaft are supported by the two bearings 11 (which are mounted on the two cross member sections 5a and 5b), emerge from the two opposite ends of the cross member 5 and are made integral with the operating lever 12. Although the operating lever 12 can be integrally made to rotate with only one outer end of the shaft 10a, in order to better balance the loads on the machine, it is preferable that the lever is fixed to both outer ends of the shaft 10a. For this purpose, the lever 12 has a fork portion which is disposed outside of the carrier 5 and the respective uprights 2 and 3, which is then connected to a single handle 13, on which the operator is to act. By way of example, the shaft 10a has square cross-section machined ends on the shaft 10a for realizing the attachment of the lever 12 to the shaft 10a, to which a corresponding bracket 12a (see FIG. 1) is machined. the lever 12 can be attached.
    As can be seen from Figs. 4 to 7, the cam 10 has an original profile designed with two objectives. On the one hand, it increases steeply (high radial gradient) in varying the angle of rotation to determine another stroke on a relatively small arc: For example, on a circular arc of about 30 ° (that is, in the transition from the position of the application of force, Fig. 4A and 4B, at break, Figs. 5A and 5B), the profile increases radially by about 10 mm. On the other hand, the cam is positioned on the shaft 10a so as to have a bearing point on the pawl 6a as close to the fulcrum axis as possible in the direction parallel to that of the lever 12: this fact allows to have a small force arm (between the rotational axis of FIG Shaft 10a and the bearing point of the cam on the portion 6a) and therefore a lever arm (class 2 lever), which is advantageous to apply the desired pressure. In other words, the distance between the contact point of the cam 10 on the pawl 6a of the plate 6 and the axis of rotation of the shaft 10a must preferably always be shorter than 5 mm, when this distance is calculated along the force application axis calculated on the lever 13 (the is the line connecting the axis of rotation of the shaft 10a with the force application point on the handle 13). The angle a (Fig. 11) formed between a vertical axis and the line connecting the support point with the center of rotation of the cam is set small, for example, smaller than 30 °.
    Starting from this consideration, it must be considered that the cam 10 does not act directly on the shaft 9 to determine the thrust pressure on the blade L, but acts through the further lever which moves from the plate 6 about the fulcrum 7 is formed (again a class 2 lever), which again makes the leverage more advantageous.
    With a suitable size of the cam 10 and the distance between the cam and the fulcrum 7, one can define a transmission mechanism which, in addition to an excellent lever arm, provides a good stroke of the shaft 9 and therefore of the blade L, and that despite small angle of rotation of the cam 10.
    According to an original aspect of the present invention, a second cam profile 14 is provided on the camshaft 10a, which is substantially opposite to the first and can cooperate with the portion 6a of the plate 6 in a stable initial position of the lever 12. In essence, when the lever is folded back by about 100 ° from its usual operating position (Figures 6A and 6B), it assumes a stable position because its equilibrium center shifts to the opposite side of the axis of the bearing 11 (ie, left from the bearing in the drawings) and pushes it to abut against a stop. In this lever position, the cam profile 14 engages in the section 6a. This cam profile 14 is designed to displace the plate 6 by the same amount that it is displaced in the fracture start phase, that is, that illustrated in Figures 4A or 4B: in this position, the guillotine opening is not complete open (as illustrated in Figs. 7A and 7B, that is, in the position in which the insertion of the blocks into the guillotine opening smoothly proceeds), but is in the ideal position for adjusting the height of the blade L with respect to the exemplary block height.
    In all other intermediate positions of the lever L, there is no relief cam profile which acts on the portion 6a, and the plate 6 therefore remains in its highest raised position, in which it is pressed by the elastic means, which also the blade L. push up, causing the maximum opening of the guillotine opening.
    According to another original aspect of the present invention, elastic thrust means are provided between the upper cross member 5 and the fork 12. They are intended to act between the fork 12 and the cross member 5 so as to determine an upward thrust which substantially compensates for the weight of the fork, preferably with an elastic upward thrust proportional to the lever rotation amount. For this and as shown in Figs. 10A and 10B visible, the elastic means are formed as a coil spring 15, the 5/18
    The greater the downward rotation of the lever 12, the greater the elastic response of the spring 15.
    This determines a return force calibrated to return the lever to a cutting start position (Figure 4a) or higher when released from the fracture end position (Figure 5A). Operationally, this gives an advantage to the operator, who at the end of each fracture need not support the lever 12 but can release it and, in any case, find it again in a position where it has a suitable width of guillotine opening for insertion of the next block.
    This arrangement makes it possible to keep the lever stable even in a position in which the guillotine opening is substantially open, which relieves the operator from necessarily bringing the lever into the other stable position, which, as shown in FIG 6A, completely folded back.
    As can be seen from the above description, the machine according to the invention makes it possible to perfectly solve the problems set forth in the preamble. In fact, the combination of two Class 2 levers in the cam transmission mechanism makes it possible to achieve a good stroke despite moderate lever rotation angles, while ensuring effective pressure transfer to the blade with reduced operator force. The presence of a second cam profile on the transmission shaft of the lever allows the correct opening width, cutting start position of the blade to be defined even with the lever in a stable starting position in order to be able to carry out the height adjustments of the movable upper blade.
    Finally, and due to the arrangement of the elastic thrust means, it is possible to hold the blade in the maximum opening position without having to support the lever by hand.
    However, it is to be understood that the protection of the invention described above is not limited to the particular configuration shown, but extends to any other design variation giving the same benefit. 6.18
    权利要求:
    Claims (6)
    [1]


    Claims 1. A block cutting machine comprising a structural frame (1, 2, 3, 5) in which slides a cutting blade (L), such as a guillotine, which is held resiliently raised and under pressure Supporting plane (4) can be dropped by a lever transmission mechanism, said mechanism having at least one lever (12, 13), with a fulcrum on an upper cross member (5) of the frame in a decentralized position, and a push shaft (9) acting on the cutting blade (L) and adjustable in a longitudinal position in a support plate (6), the plate (6) pivoting in a vertical plane relative to the upper cross member (5), characterized in that the actuating lever (12, 13) is integral in rotation with a small shaft (10a) having at least first (10) and second (14) cam profiles cooperating with a portion (6a) of the pivot plate (6).
    [2]
    2. Machine according to claim 1, wherein the first cam profile (10) determines the maximum displacement of the pivot plate on a rotation arc smaller than 90 ° and with the portion (6a) of the pivot plate (6) cooperates in a cutting pressure phase.
    [3]
    3. A machine according to claim 1 or 2, wherein the cam profile (10) rests in the maximum open position of the cutting blade (L) on the plate portion (6 a) at a point in the vicinity of a vertical line.
    [4]
    A machine according to any one of the preceding claims, wherein the second cam profile (14) cooperates with the portion (6a) of the plate (6) in a condition in which the operating lever (12, 13) is in a stable folded-back starting position.
    [5]
    A machine according to claim 4, wherein the second cam profile (14) is capable of determining a displacement of the pivot plate (6) to an extent such that the upper blade (L) falls to a cutting start level suitable for adjusting the height of the blade (6). L) by means of the Einsteilschafts (9) to define.
    [6]
    A machine according to any one of the preceding claims, further comprising elastic thrust means (15) provided between the operating lever (12, 13) and the upper cross member (5) which can support the lever in a condition such that the upper blade (L ), wherein the elastic supporting action of the elastic pushing means (15) can be overcome by applying a downward force on the lever (12, 13). For this 11 sheets drawings 7/18
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    同族专利:
    公开号 | 公开日
    ES1073069Y|2011-02-07|
    ITMI20090172U1|2010-11-23|
    ES1073069U|2010-10-22|
    FR2945763A3|2010-11-26|
    FR2945763B3|2011-05-13|
    ES1073069U8|2011-08-16|
    CN201833462U|2011-05-18|
    DE202010007124U1|2010-08-26|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    JPH09295314A|1996-05-07|1997-11-18|Itatsuku Eng:Kk|Tile cutting machine|
    CN201044972Y|2007-05-18|2008-04-09|宁波三鼎爱迪实业有限公司|Stone cutting apparatus|
    CN102423883A|2011-11-03|2012-04-25|无锡市伟丰印刷机械厂|Cam cutoff mechanism for tongue depressor machine|
    CN103507147A|2013-03-29|2014-01-15|洛阳新火种节能技术推广有限公司|Handle cutting machine|
    ES2633609B1|2016-03-21|2018-06-27|Germans Boada, S.A.|SEPARATOR DEVICE APPLICABLE TO CERAMIC MANUAL CUTTERS|
    法律状态:
    2019-01-15| MM01| Lapse because of not paying annual fees|Effective date: 20180531 |
    优先权:
    申请号 | 申请日 | 专利标题
    ITMI20090172|ITMI20090172U1|2009-05-22|2009-05-22|BLADE BLADES WITH PERFORMED CAM LEVERISM.|
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