JP2015145035A - cutting machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cutting machine which can continuously cut a long-length material to desired length at high speed, dispenses with a complicated mechanism for the reciprocal motion of a slider and change of cut length, achieves a mechanism small in the number of part items and compact in size, and can reduce cost.SOLUTION: A cutter comprises: a slider 3 which reciprocates along guide rails 32, 33 parallel with a tube T which is continuously fed; a cutting mechanism 2 having a cutter 22 which performs cutting operation following the reciprocal motion of the slider 3; and a gear connecting drive mechanism 4 which makes the slider 3 reciprocate at constant reciprocation distance. A pinion gear 42 which is arranged eccentrically to a rotating drive shaft 61 of a drive motor 6 rotates while internally contacting with a fixed ring gear 41 having inner teeth, makes a connecting shaft 44 of a gear-side connecting member 43 perform linear motion, and makes the slider 3 perform direct motion at a prescribed speed pattern via a slider-side connecting member 71.

Description

  The present invention relates to a compact cutting machine for continuously cutting a long material such as a tube with a desired cutting length by reciprocating a slider on which a cutter is mounted.

  Patent Document 1 discloses, for example, a cutting machine including a mechanism for cutting a flat tube for a heat exchanger or the like into a predetermined length according to a product standard. The cutting machine reciprocates the slider by a pulse motor via a crank mechanism having an eccentric pin whose eccentric amount can be adjusted, while rotating the rotary cutting teeth attached to the slider via a speed change mechanism by the pulse motor. Cut by following the workpiece at the same speed.

  FIG. 9A is a diagram showing a basic structure of a conventional cutting machine, in which a connecting rod 101 of a crank mechanism connects an eccentric pin 102 and a follower slider 103, and converts crank rotation into linear motion. The follower slider 103 moves forward or backward with respect to the feeding direction of the tube 105, and the slider speed coincides once in one reciprocation with respect to the tube 105 (for example, 150 m / min) fed at a constant speed. When the cutter 104 provided on the side of the tracking slider 103 is rotated at this timing, the tube 105 can be continuously cut.

  In this conventional structure, the cutting length of the tube 105 corresponds to the tracking distance of the tracking slider 103. As shown in the upper diagram of FIG. 9B, the crank mechanism is driven by a cutting motor 106 formed of a servo motor, and the cutting length is adjusted by the rotation diameter (crank diameter) of the connecting rod 101, that is, the eccentric amount of the eccentric pin 102. It becomes possible. Therefore, by providing a mechanism that automatically adjusts the eccentric amount so that the crank diameter is large when the cutting length is long and the crank diameter is small when the cutting length is short, the cutting length can be reduced without stopping the cutting machine. It is considered to change the size. As shown in the lower diagram of FIG. 9B, the slider motor 106 is rotated at a constant speed so that the slider speed changes at a constant cycle, and the cutting timing is adjusted to the maximum speed (tube feed speed).

Japanese Patent Publication No. 3-58847

  However, in the conventional connecting rod system, in order to convert the crank rotation into the reciprocating motion of the follower slider 103 via the connecting rod 101, not only the apparatus is enlarged, but also a mechanism for changing the tube cutting length is provided. It becomes complicated. FIG. 10 is an example of a setup mechanism that changes the crank diameter according to the tube cutting length. The cutting motor 201 that drives the cutter rotating shaft and reciprocates the slider, and the crank diameter (the amount of eccentricity) are changed. A setup motor 202 is provided. The rotational force of the cutting motor 201 is transmitted to the cutter rotating shaft via a plurality of gears 203 to 205, while the gear 207 around the rotating flange tube is connected via a gear 206 mounted around the axis of the setup motor 202. And the internal gear 208 attached to the rotating flange tube rotates.

  The crankshaft 209 is rotatably disposed in the rotating flange tube, and a small gear 210 attached to the crankshaft 209 meshes with the internal gear 208. A connecting rod 211 connected to a slider (not shown) is rotatably connected to an eccentric pin 212 attached to the upper surface of the small gear 210. The small gear 210 revolves along the internal gear 208 and maintains the eccentric amount of the eccentric pin 212. A gear 215 around the crankshaft 209 meshes with a gear 214 connected to the setup motor 202 via a differential gear mechanism 213. The position of the eccentric pin 212 is controlled so as to be displaced by driving the setup motor 202 to generate a differential angle, and to have an eccentric amount corresponding to the cutting length.

  As described above, the conventional connecting rod system is provided with a setup mechanism for changing the reciprocating distance of the slider by making the motor rotation speed constant and changing the eccentric amount, but the number of parts becomes very large. There was a problem of high costs. Therefore, the present invention can cut a long material continuously to a desired length at a high speed, and eliminates the need for a complicated mechanism for reciprocating the slider and changing the cutting length. The purpose is to reduce the cost by realizing a cutting machine with a small amount.

The invention of claim 1 of the present invention is a cutting machine for cutting a continuously supplied long material into a set length,
A slider that reciprocates along a guide member arranged in parallel with the long material;
A cutting mechanism having a cutter that performs a cutting operation following the reciprocating motion of the slider;
Reciprocating means for reciprocating the slider at a constant reciprocating distance;
Drive means for driving the reciprocating means,
The reciprocating means includes a fixed ring gear having internal teeth and a pinion gear that rotates in contact with the fixed ring gear, and a diameter ratio of pitch circles of the fixed ring gear and the pinion gear is 2: 1. A gear pair, and a connecting portion for connecting the gear pair and the slider, the connecting portion being attached to the pinion gear and rotating integrally, and a gear provided with a connecting shaft on a pitch circle of the pinion gear A slider-side connecting member that is integrally attached to the slider and provided with a holding portion that rotatably holds the connecting shaft, and the slider is connected via the connecting shaft as the pinion gear rotates. Is a linear motion,
The drive means can arbitrarily change a rotation speed of a drive source for rotating the pinion gear, and changes a rotation speed pattern of the drive source in accordance with a set length of a long material.

  According to a second aspect of the present invention, the cutting mechanism includes a cutter driving unit that is attached to a rotary shaft that is pivotally supported by the slider in parallel with a long material as the cutter, and that is coupled to the reciprocating unit. Rotates the cutter and cuts the long material at the set length.

  In the invention according to claim 3 of the present invention, the drive means supports the pinion gear on an eccentric shaft provided on a rotation drive shaft of the drive source, and further includes a belt drive mechanism connected to the rotation shaft. The rotating shaft of the cutter driving means is synchronously rotated through the cutter driving means.

  In the invention of claim 4 of the present invention, the drive means has a maximum speed of the drive source equal to the supply speed of the long material, and the longer the set length of the long material, the slower the minimum speed of the drive source, The rotational speed pattern of the drive source in one reciprocating operation of the slider is set so that the minimum speed of the drive source becomes faster as the set length of the long material is shorter.

  In the invention according to claim 5 of the present invention, the slider has a cutter guide for guiding the cutter mounted on an arm portion projecting from the long material side, and a side opposite to the arm portion. The slider-side connecting member is attached to the portion, and a pair of guide rails arranged with the slider-side connecting member interposed therebetween is used as the guide member.

  In the cutting machine of the present invention, the reciprocating means for reciprocating the slider is a gear coupling drive system, and the coupling shaft provided on the pinion gear meshing with the fixed ring gear is directly coupled to the holding portion provided on the slider side coupling member. . Since the diameter ratio of the ring gear to the pinion gear is 2: 1, the fixed point on the pitch circle of the pinion gear that rolls while meshing with the ring gear that is an inscribed circle, that is, the locus of the connecting shaft is a straight line. Therefore, the slider reciprocates a certain distance via the holding portion that rotatably supports the connecting shaft, and the cutter performs a cutting operation following this. Here, when the drive means changes the rotation speed of the pinion gear, the speed at which the slider reciprocates changes. Thereby, the length of the long material supplied before the cutter performs the cutting operation changes, and the long material can be cut to a desired cutting length.

  Thus, in the gear coupling drive system of the present invention, the reciprocating distance of the slider is constant, the conventional coupling rod is unnecessary, and the entire apparatus becomes compact. In addition, a complicated setup mechanism for changing the cutting length is not necessary, and the number of parts can be greatly reduced to realize a low-cost cutting machine.

It is the side view and top view which show the whole structure of the cutting machine in 1st Embodiment. It is a whole perspective view of the cutting machine in a 1st embodiment. It is the side view and top view which show the structure of the gear connection drive mechanism which is the principal part of the cutting machine in 1st Embodiment. It is an expansion perspective view of the gear connection drive mechanism which is the principal part of the cutting machine in 1st Embodiment. It is for demonstrating operation | movement of the gear connection drive mechanism which is the principal part of the cutting machine in 1st Embodiment. It is a typical figure for demonstrating the speed control method of the gear connection drive mechanism by the cutting motor of the cutting machine in 1st Embodiment. It is a figure which shows the example of the cutting motor speed pattern of the cutting machine in 1st Embodiment. It is a principal part enlarged view which shows the structure of the cutting mechanism of the cutting machine in 1st Embodiment. It is a disassembled perspective view which shows the structure of the cutting mechanism of the cutting machine in 1st Embodiment. It is a disassembled perspective view which shows the structure of the cutting mechanism of the cutting machine in 1st Embodiment. It is a figure which shows the basic structure of the conventional cutting machine. It is a figure for demonstrating the basic operation | movement of the conventional cutting machine. It is principal part sectional drawing of the cutting machine by the conventional connection rod system.

  Hereinafter, specific embodiments of the present invention will be described with reference to the drawings. The cutting machine 1 of 1st Embodiment shown to FIG. 1, 2 is comprised in order to cut | disconnect the elongate material used as a to-be-cut object continuously. Here, for example, an elongated flat tube-shaped tube T is used as the long material. The cutting machine 1 is provided on the base 11 so as to be able to reciprocate along the tube T, and a reciprocating means for reciprocating the slider 3 and a slider 3 to which a cutting mechanism 2 for cutting the tube T is integrally attached. The gear connection drive mechanism 4 is provided. The cutting mechanism 2 includes a tube guide 21 that guides the tube T and a cutter 22 that cuts the tube T, and performs a cutting operation following the slider 3.

  On the base 11, a belt drive mechanism 5 constituting cutter driving means for driving the cutter 22 of the cutting mechanism 2 and a cutting motor 6 as a drive source are provided. The cutting motor 6 and its rotation drive shaft 61 constitute a drive means, and drive the gear connection drive mechanism 4 including a gear pair and a connection portion, and the belt drive mechanism 5. The tube T is continuously supplied in a fixed direction at a predetermined speed by a feed mechanism including a feed motor (not shown).

  The slider 3 has a thick plate shape, and a rotary shaft 23 of the cutting mechanism 2 is rotatably supported on a bearing portion 31 provided so as to penetrate through a substantially central portion of the plate surface. Both ends of the rotating shaft 23 are inserted into a pair of standing walls 12 and 13 erected on the base 11, and are rotatably supported by the bearing portions 12a and 13a. One end of the rotating shaft 23 is connected to the belt driving mechanism 5 and is rotationally driven by the cutting motor 6. The cutting mechanism 2 has a housing 24 that is attached to an end portion of the slider 3 on the side of the standing wall 13 and that reciprocates integrally. A cutter 22 and a cutter guide 25 are accommodated in the housing 24, and a tube guide 21 serving as a guide hole including a vertically long hole along the tube T shape is opened at a position opposed to both end surfaces of the housing 24. In FIG. 2, the illustration of the one standing wall 13 and the housing 24 located on the front side of the cutter 22 and the slider 3 is omitted.

  The slider 3 has an arm portion 31 extending laterally from a horizontal upper surface, and a cutter guide 25 is integrally attached to an attachment member 26 fixed to the distal end portion of the arm portion 31. A pair of upper and lower guide cylinders 34 and 35 are provided on the side of the slider 3 opposite to the arm 31 projecting toward the tube, with a vertical side wall 36 interposed therebetween. The guide cylinders 34 and 35 are positioned so as to protrude radially outward of the rotary shaft 23 from the upper and lower edges of the side wall 36, and slidably support guide rails 32 and 33 as a pair of guide members in the cylinder. ing. The pair of guide rails 32 and 33 extend parallel to the axial direction of the rotating shaft 23, and both ends thereof are fixed to the pair of standing walls 12 and 13.

  The gear connection drive mechanism 4 includes a fixed ring gear 41 having internal teeth and a pinion gear 42 that rotates in contact with the fixed ring gear 41, and forms a gear pair. A slider-side connection member 71 and a gear-side connection member 43 serving as a connection portion It is connected to the slider 3. The slider 3 can reciprocate along the guide rails 32 and 33 by mounting the connecting shaft 44 of the gear side connecting member 43 in the holding groove 72 of the slider side connecting member 71 attached to the side wall 36. The fixed ring gear 41 is held and fixed to the support portion 14 installed on the base 11, and a pinion gear 42 is accommodated in the ring so as to be capable of meshing. As described above, when the pair of upper and lower guide rails 32 and 33 are arranged with the connecting portion of the slider side connecting member 71 and the gear side connecting member 43 interposed therebetween, the slider 3 is stably held and the reciprocating operation is smoothly performed. Can do.

  The belt drive mechanism 5 includes a pair of belt wheels 51 and 52 on which the toothed belt 53 is suspended, and a pair of bevel gears 54 and 55 that rotate in synchronization with the rotation drive shaft 61. One of the pair of bevel gears 54, 55 (here, the bevel gear 55) is attached around the rotation drive shaft 61 and meshes with the other bevel gear 54 disposed on the side of the rotation drive shaft 61 to rotate. To communicate. One of the pair of belt wheels 51, 52 (here, the belt wheel 52) is attached around the end of the rotating shaft 23, and the other belt wheel 53 and the other bevel gear 54 are attached to both ends of the rotating shaft 56. It is attached and rotates integrally. Thereby, the rotation shaft 23 of the cutting mechanism 2 can be rotated integrally with the rotation of the rotary drive shaft 61 by the cutting motor 6.

  Next, details of the gear coupling drive mechanism 4 will be described. 3 and 4, the gear coupling drive mechanism 4 has a flange tube 45 mounted around a rotary drive shaft 61 driven by a cutting motor 6 via a bearing portion 62, and is integrally formed with the flange portion of the flange tube 45. A fixed ring gear 41 is attached. On the other hand, a pin-shaped eccentric shaft 46 is provided at the tip of the rotary drive shaft 61, and a pinion gear 42 mounted on the outer periphery of the eccentric shaft 46 is inscribed in the fixed ring gear 41. The pinion gear 42 has external teeth that mesh with the fixed ring gear 41 on the outer periphery, and revolves around the rotation drive shaft 61 while meshing with the internal teeth of the fixed ring gear 41. The fixed ring gear 41 and the pinion gear 42 are formed so that the pitch circle diameter ratio is 2: 1.

  The gear side connection member 43 is a substantially rectangular plate shape whose long side is longer than the outer diameter of the pinion gear 42, and is attached so that the central axis of the connection shaft 44 is located on the pitch circle of the pinion gear 42. The slider-side coupling member 71 facing the gear-side coupling member 43 is provided with a holding groove 72 so that the lower half of the coupling shaft 44 is rotatably accommodated. The holding groove 72 is formed of a concave portion corresponding to the diameter and axial length of the connecting shaft 44, further forms a concave groove along the outer periphery of the intermediate portion of the connecting shaft 44, and has a convex portion on the surface of the corresponding holding groove 72. By forming the protrusions and fitting them into the recesses and protrusions, it can be prevented from coming off in the axial direction.

  At this time, as shown in the lower diagram of FIG. 5, the gear side connecting member 43 rotates following the rotation of the pinion gear 42, and the connecting shaft 44 is displaced in the radial direction of the fixed ring gear 43. This is schematically shown in the upper diagram of FIG. When a circle rolls along the inner circumference of the inscribed circle, if the diameter ratio of the inscribed circle to the rotating circle is 2: 1, the locus of the fixed point on the rotating circle becomes a straight line. That is, when the inscribed circle is a fixed ring gear 41 and the rotating circle is a pinion gear 42, the connecting shaft 44, which is a fixed point on the circle, is between two points facing each other in the horizontal direction across the center of the fixed ring gear 41. It will move in a straight line. In the figure, the pinion gear 42 rotates 3/8, and on a horizontal straight line passing through the center of the fixed ring gear 41 from one end side to the other end side (from the left end side to the right end side in the figure), the fixed ring gear The state which moved to the position equivalent to 3/4 of 41 diameters is shown continuously.

  Therefore, when the pinion gear 42 makes one rotation in the fixed ring gear 41, the connecting shaft 44 reciprocates once on a horizontal straight line. Following this, the slider-side connecting member 71 integral with the connecting shaft 44 can reciprocate the slider 3 along the guide rails 32 and 33. In this way, the rotation of the cutting motor 6 is converted into a linear motion through the gear pair and the connecting portion, and the slider 3 moves linearly at a constant reciprocating distance determined by the diameter of the fixed ring gear 41, and the tube T Reciprocate in the feed direction (supply direction) or in the opposite direction.

  On the other hand, the rotation of the cutting motor 6 is transmitted to the cutting mechanism 2 via the belt drive mechanism 5 to rotate the rotating shaft 23 synchronously. Then, the cutter 22 integrated with the rotary shaft 23 follows and rotates, and the tube T is cut by one rotation for each reciprocation of the slider 3. At this time, the cut length of the tube T is a length that is sent while the slider 3 is reciprocated once, and depends on the rotational speed of the drive motor 6 that reciprocates the slider 3. In order to cut the continuously supplied tube T without stopping, the slider 3 that reciprocates along the tube T is controlled to have the same speed as the tube T, and the cutter 22 is cut at that timing. It is desirable to operate.

  Therefore, in the present invention, the rotational speed of the cutting motor 6 can be arbitrarily changed, and further, the rotational speed pattern of the cutting motor 6 is changed according to the set length of the long material. This will be described with reference to FIG. As schematically shown in FIG. 6A, the tube T is continuously supplied at a predetermined feed rate (for example, 150 / min) by a feed motor including a servo motor. On the other hand, the slider 3 that reciprocates only needs to have the same speed when the tube T is cut as described above. Therefore, as shown in FIG. The cutting speed (v1) is set so that it substantially coincides with the speed of the tube T when the maximum speed in the feed direction is reached.

  Then, according to the cutting length of the tube T, specifically, the minimum speed (v2) is fast when the cutting length is short, and the minimum speed (v3) is slow when the cutting length is long. Set the pattern. The speed is gradually changed between the cutting speed (v1) and the minimum speed (v2, v3). As shown in FIG. 6A, a servo controller as a control means is connected to the cutting motor 6, and data switching is performed based on the relationship between the cutting length and the speed pattern stored in advance based on the tube feed amount input from the feed motor. I do.

  That is, the cutting motor 6 performs cutting speed control in synchronism with the feed amount, and the speed pattern is changed for each length so that the minimum rotation speed within one rotation (360 degrees) is slower as the cutting length is longer. Change the setting with. Accordingly, the cutting length can be arbitrarily changed by simply changing the motor speed pattern without stopping the tube T or providing a mechanism for changing the reciprocating distance of the slider 3. it can.

  7 and 8 are detailed configuration examples of the cutting mechanism 2, and the cutter 22 is attached to the rotary plate 27 as a rotary blade that rotates integrally with the rotary shaft 23 that penetrates the slider 3. The rotating plate 27 has an arm portion 27a extending laterally, and a cutter 22 having a plurality of protruding teeth is fixed to the tip thereof. Below the arm portion 31 of the slider 3, a pair of substantially U-shaped members are brought into contact with each other, and a cutter guide 25 provided with a guide groove 25a therebetween is disposed. The cutter 22 is guided by the guide groove 25a. The tube T (not shown) that rotates clockwise and passes through the tube guide 21 is cut. At this time, the cutter 22 cuts the tube T at the cutting speed (v1) shown in FIG. Since this cutting speed (v1) is set to a constant maximum speed regardless of the cutting length, the tube T can be cut constantly and stably.

  Thus, the cutting machine 1 according to the present invention converts the rotation of the drive motor 6 into a linear motion using the gear coupling drive mechanism 4 composed of a gear pair and a coupling portion, and enables the slider 3 to move linearly. The entire device can be made more compact than the conventional connecting rod system. Further, since the cutting length can be arbitrarily changed for each reciprocating operation only by changing the rotational speed pattern of the drive motor 6, for example, a complicated mechanism is unnecessary and the cutting length can be easily controlled.

  In the above-described embodiment, the cutter 22 of the cutting mechanism 2 is rotationally driven by the belt drive mechanism 5 connected to the drive motor 6. However, the cutter drive means is not limited to this and may have another configuration. Further, the cutter 22 may be configured to be cut by a driving means different from the drive motor 6, and the shapes of the cutter 22 and other components can be changed. In these cases as well, it is desirable to synchronize the operation of the cutter 22 with the reciprocating operation of the slider 3.

  In the above embodiment, the slider 3 is configured to reciprocate along the pair of guide rails 32 and 33. However, the number of guide rails is not limited to this, and it is sufficient that the slider 3 can be stably operated. At least one or any number of 2 to 3 or more can be used, and the arrangement and configuration can be changed.

  The cutting machine of the present invention is not limited to flat tubes for heat exchangers, but can be applied to tubes of various shapes and other long materials, and can be continuously cut at high speed to any set length. Useful.

T-tube (long material)
DESCRIPTION OF SYMBOLS 1 Cutting machine 2 Cutting mechanism 21 Tube guide 22 Cutter 23 Rotating shaft 3 Slider 31, 32 Guide rail (guide member)
4 Gear drive mechanism (reciprocating means)
41 Fixed ring gear (gear pair)
42 Pinion gear (gear pair)
43 Gear side connection member (connection part)
44 Connection shaft 5 Belt drive mechanism (cutter drive means)
6 Cutting motor (drive means)
61 Rotation drive shaft (drive means)
71 Slider side connecting member (connecting part)
72 Holding groove (holding part)

Claims (5)

A cutting machine (1) for cutting a continuously supplied long material (T) into a set length,
A slider (3) that reciprocates along a guide member (32, 33) arranged in parallel with the long material;
A cutting mechanism (2) having a cutter (22) that performs a cutting operation following the reciprocating motion of the slider;
Reciprocating means (4) for reciprocating the slider at a constant reciprocating distance;
Drive means (6, 61) for driving the reciprocating means;
The reciprocating means comprises a fixed ring gear (41) having internal teeth and a pinion gear (42) rotating inscribed in the fixed ring gear, and a diameter ratio of pitch circles of the fixed ring gear and the pinion gear. A gear pair having a ratio of 2: 1 and a connecting portion for connecting the gear pair and the slider, and the connecting portion is attached to the pinion gear and rotates integrally with the pinion gear on the pitch circle of the pinion gear. A gear side connection member (43) provided with a connection shaft (44) and a slider side connection member (71) provided integrally with the slider and provided with a holding portion (72) for holding the connection shaft rotatably. Provided, and the slider is linearly operated via the connection shaft as the pinion gear rotates.
The drive means can arbitrarily change the rotation speed of the drive source (6) for rotating the pinion gear, and changes the rotation speed pattern of the drive source according to the set length of the long material. And cutting machine.   In the cutting mechanism, a rotary blade is attached to a rotary shaft (23) supported by the slider in parallel with a long material to form the cutter, and a cutter driving means interlocking with the reciprocating means rotates the cutter. The cutting machine according to claim 1, wherein the long material is cut at a set length.   The drive means supports the pinion gear on an eccentric shaft (46) provided on a rotation drive shaft of the drive source, and further includes the cutter drive means provided with a belt drive mechanism (5) connected to the rotation shaft. The cutting machine according to claim 1 or 2, wherein the rotating shaft is rotated synchronously via the rotation.   In the drive means, the maximum speed of the drive source is the same as the supply speed of the long material, and the longer the set length of the long material, the slower the minimum speed of the drive source, and the shorter the set length of the long material, the above The cutting machine according to any one of claims 1 to 3, wherein a rotational speed pattern of the drive source in one reciprocating operation of the slider is set so that a minimum speed of the drive source is increased. The slider has a cutter guide (24) for guiding the cutter mounted on an arm portion (31) projecting on the side on the long material side, and the slider on the side opposite to the arm portion. The cutting machine according to any one of claims 1 to 4, wherein a side connecting member is attached and a pair of guide rails (32, 33) arranged with the slider side connecting member interposed therebetween are used as the guide members.

Images