JP2011104684A - Rotary cutter of pipe - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pipe rotary cutter with improved cutting efficiency of a pipe by further accelerating rotation of a hollow spindle and a sleeve without enlarging a device and without largely changing a basic structure of a conventional device by reduction of driving force required for cutting the pipe by a disk cutter even if centrifugal force caused by high speed rotation of the hollow spindle and the sleeve works to the disk cutter eccentrically pivoted to one end of the hollow spindle. <P>SOLUTION: A counterweight is provided at an eccentric area of at least one of other eccentric shafts. A relative position between a disk cutter mounted eccentric shaft and the eccentric area of the eccentric shaft from a counterweight mounted eccentric shaft is made in such an arrangement that the eccentric area where the counterweight is mounted is separated and displaced from the center of a bearing plate in association with the cutting of the disk cutter. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention includes a hollow main shaft, a sleeve disposed around the hollow main shaft, elongated holes formed in the hollow main shaft and the respective cylindrical portions of the sleeve, and extending in directions intersecting with each other. It is inserted into the long hole, and is displaced in the extending direction of each long hole by the shifter means, and includes a sliding pin that controls transmission of the rotational driving force from either the hollow main shaft or the sleeve to the other, Two bearing plates are connected in parallel to each other at the end of the hollow main shaft in a mutually separated posture, and a plurality of eccentric shafts are pivotally supported on these two bearing plates, and a sleeve is provided on each eccentric shaft. A pinion gear meshing with an internal gear attached to the end of the bearing is fixed, and at least a pair of opposed eccentric shafts positioned between the two bearing plates with the center of the bearing plate facing each other. Disc cutter And by the shifter means, the sliding pin is displaced in both elongated holes in the extending direction of the elongated hole, thereby causing a relative rotational displacement between the hollow main shaft and the sleeve. The rotary cutting device of the pipe that performs the cutting operation in which the eccentric part that is mounted is displaced toward the center of the bearing plate, in particular due to the high speed rotation of the hollow spindle and sleeve on the disk cutter supported at the end of the hollow spindle A shifter that gives a relative rotational displacement to the hollow main shaft and the sleeve by making the cutting operation of the disk cutter in the radial direction toward the axial direction of the hollow main shaft sufficiently light. Proposes a technology that improves the cutting efficiency of pipes by reducing the burden on the means, etc., and further increasing the speed of rotation of the hollow main shaft and sleeve. Than is.

  As this type of pipe rotary cutting device, there is one described in Patent Document 1 which is the prior application of the applicant. As shown in a longitudinal sectional view in FIG. 5, this cutting device is formed in each of the hollow main shaft 52 and the sleeve 53, and in both of the long holes 54 and 55 extending in the direction intersecting with each other, the sliding pin 56 is inserted and disposed, and under the transmission of rotational power by the sliding pin 56, the hollow main shaft 52 is rotated at a high speed integrally with the sleeve 53, and the elongated holes 54 intersecting with each other using the shifter means 57, In 55, the sliding pin 56 is displaced in the extending direction of the long hole to cause a relative rotational displacement between the hollow main shaft 52 and the sleeve 53, thereby providing an inner portion provided at one end of the sleeve 53. A rotational displacement of the eccentric shaft 60 is caused through a toothed gear 58 and a pinion gear 59 which is disposed at one end portion of the hollow main shaft 52 and meshes with the internal gear, whereby the eccentric portion 60a of the eccentric shaft 60 is provided. The disc bracket attached to 61, together with the displacing toward the pipe inserted disposed in the cylinder body 62 on the inner circumferential side of the hollow main shaft 52, by pressing the pipe, is to cut the pipe.

Japanese Utility Model Publication 5-008002

  By the way, in such a pipe cutting device, when the disk cutter 61 is pressed against the pipe while the hollow main shaft 52 and the sleeve 53 are rotated at a higher speed for the purpose of shortening the time required for the pipe cutting process, the hollow main shaft is used. The disc cutter 61 disposed at the end of 52 via the eccentric shaft 60 is also rotated at a high speed together with the hollow main shaft 52 and the sleeve 53, and FIG. 6 shows the structure of the pipe cutting portion of the device 51. 5, a centrifugal force F (indicated by an arrow on the disk cutter 61 in the figure) that depends on the rotational speed acts on the disk cutter 61 toward the outer side in the rotation direction. It will be.

  On the other hand, in order to cut the pipe, the disc cutter 61 attached to the eccentric portion 60a of the eccentric shaft 60 is directed to the pipe side (not shown), that is, the center of the bearing plate 63 against such centrifugal force. Although it is necessary to displace to the position indicated by the phantom line in the figure, if the rotation of the hollow main shaft 52 and the sleeve 53 is further increased in order to improve cutting efficiency, the centrifugal force acting on the disc cutter 61 increases. Therefore, the relative rotational displacement of the hollow main shaft 52 and the sleeve 53 that gives the disc cutter 61 a displacement in the direction toward the center of the bearing plate 63, that is, the displacement of the sliding pin 56 in the long holes 54 and 55. Therefore, the driving force required for the above-mentioned is enormous, so that the size of the shifter means 57 for displacing the sliding pin 56 is increased. Type conductivity, also is forced to high rigidity, there was an increase in the manufacturing costs associated with size of the apparatus, the securing of a larger installation space problems.

  An object of the present invention is to solve such problems of the prior art, and the object of the present invention is to provide a disc cutter that is eccentrically supported at one end of the hollow main shaft, a hollow main shaft and The basic structure of the conventional device is achieved without increasing the size of the device by reducing the driving force required for the cutting operation of the pipe by the disk cutter even when the centrifugal force due to the high-speed rotation of the sleeve is applied. It is an object of the present invention to provide a rotary cutting device for a pipe that can further increase the speed of rotation of the hollow main shaft and the sleeve without greatly changing the above, and can improve the cutting efficiency of the pipe.

  A rotary cutting device for a pipe according to this application is formed by penetrating through a hollow main shaft, a sleeve disposed around the hollow main shaft, and the respective cylindrical portions of the hollow main shaft and the sleeve, and in directions intersecting each other. Elongated elongated holes, inserted into the elongated holes, displaced by the shifter means in the extending direction of the elongated holes, and transmitting the rotational driving force from either the hollow main shaft or the sleeve to the other It has a sliding pin that controls it, and two bearing plates are connected in parallel with each other at the end of the hollow main shaft, and a plurality of eccentric shafts are pivotally supported on these two bearing plates, A pinion gear that meshes with an internal gear attached to the end of the sleeve is fixed on each eccentric shaft, and the center of the bearing plate is positioned at the eccentric portion of each eccentric shaft that is positioned between the two bearing plates. Oppose apart At least a pair of disc cutters are attached, and the shifter means displaces the sliding pin in both elongated holes in the extending direction of the elongated hole, thereby causing a relative rotational displacement between the hollow main shaft and the sleeve. By doing so, the eccentric part on which the disk cutter is mounted is cut so that the eccentric part is displaced toward the center of the bearing plate, and a counterweight is provided on the eccentric part of at least one other eccentric shaft. The relative position of the eccentric part of the eccentric shaft between the mounting eccentric shaft and the counterweight mounting eccentric shaft is arranged so that the eccentric portion on which the counterweight is mounted is displaced away from the center of the bearing plate with the cutting operation of the disc cutter. It will be.

  Here, preferably, a pair of counterweights is provided in each of the eccentric portions of at least two other eccentric shafts, and the pair of counterweights are positioned to face each other with the center of the bearing plate therebetween.

According to the rotary cutting device for pipes according to this application, at least one eccentric shaft other than the eccentric shaft provided with the disc cutter is provided with a counterweight, and the disc cutter mounting eccentric shaft, The relative position of the eccentric part of the eccentric shaft with respect to the counterweight mounting eccentric shaft is arranged so that the eccentric part mounting the counterweight is displaced away from the center of the bearing plate with the cutting operation of the disc cutter. When the main shaft and sleeve are rotated at a high speed, not only the disc cutter but also the counterweight is subjected to a centrifugal force that is radially outward depending on the rotational speed. Based on the force, this pinio gear is connected to the pinion gear fixed to the eccentric shaft via the eccentric shaft to which the counterweight is attached. Against internal gear to gear meshing, so that the relative rotational force direction to assist the cutting action of the disc cutter is given.
Therefore, when the slide pin is displaced in the long hole by the shifter means for the cutting operation of the disc cutter, and a relative rotational displacement is applied to the hollow main shaft and the sleeve, the pinion with the counterweight attached thereto is provided. The driving force of the shifter means required for the displacement of the sliding pin is effectively reduced by the action of the relative assist turning force between the gear and the internal gear, that is, between the hollow main shaft and the sleeve. be able to.

Therefore, when the centrifugal force acting on the disk cutter increases by further increasing the rotation speed of the hollow main shaft and the sleeve, a larger sliding pin driving force is required for the cutting operation of the disk cutter. In the device according to the present invention, the centrifugal force acting on the counterweight also increases, and due to the action of this large centrifugal force on the counterweight, a large rotational force in the direction assisting the cutting operation of the disc cutter is caused from the pinion gear to the internal teeth. Even in such a case, the burden on the shifter means for causing the relative rotational displacement between the hollow main shaft and the sleeve is not so great.
This makes it possible to further speed up the rotation of the hollow main shaft and the sleeve without increasing the size of the shifter means and the like and without significantly changing the structure of the conventional apparatus, and cutting the pipe. Efficiency can be greatly improved.

  Here, when a pair of counterweights are provided at the eccentric portions of at least two other eccentric shafts, and the pair of counterweights are positioned so as to face each other with the center of the bearing plate therebetween, they are hollow. When the main shaft and the sleeve rotate, the centrifugal force acting on the opposing disk cutter and counterweight balances with the rotation center of the hollow main shaft and sleeve, so that the disc cutter and counterweight are unbalanced when rotating at high speed. Can be removed and smooth and stable high-speed rotation can be performed.

It is a longitudinal section showing a rotary cutting device of a pipe concerning one embodiment of this invention including a central axis. It is a figure which shows the relative relationship of the long hole provided in each of a hollow main axis | shaft and a sleeve of the apparatus shown in FIG. It is sectional drawing which follows the III-III line of the apparatus shown in FIG. It is sectional drawing which follows the IV-IV line of the apparatus shown in FIG. It is a longitudinal cross-sectional view containing the central axis which shows the conventional rotary cutting device. It is sectional drawing which follows the VI-VI line of the apparatus shown in FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
A rotary cutting device 1 for a pipe shown in a longitudinal sectional view in FIG. 1 is arranged inside a hollow main shaft 2, a sleeve 3 surrounding the hollow main shaft 2 concentrically with the hollow main shaft 2, and inside the hollow main shaft 2. The pipe 4 as the work allows the feeding of the pipe 4 to the inner peripheral side, and the two slide pins 5 attached to the slide cylinder described later, and the slide pins 5 As shown in FIG. 2, the hollow main shaft 2 and the cylindrical portions 2a and 3a of the sleeve 3 are formed so as to pass through the elongated holes 6 and 7 extending in directions intersecting with each other. Shifter means 8 that moves in the direction of the central axis XX of the main shaft and an outer frame 9 that supports the cutting device 1 are provided.

  Here, the hollow main shaft 2 has, for example, one long hole 6 formed through the wall surface of the cylindrical tubular portion 2a, for example, on the upper surface and the lower surface that oppose each other in the diameter direction in the drawing. The sleeve 3 is formed by penetrating the wall surface of the cylindrical portion 3a at each position corresponding to the long hole 6 of the hollow main shaft 2 and extends in the direction of the central axis XX. 7.

  Then, by inserting and arranging a common sliding pin 5 in both the long holes 6 and 7 of the cylindrical portions 2a and 3a, the sleeve 3 can be moved around the axis line, for example, from a motor (not shown) via a pulley. When the rotational driving force is inputted, the hollow main shaft 2 can be rotated at a high speed together with the sleeve 3 under the engagement between the hole edges of the long holes 6 and 7 and the sliding pin 5.

Here, the formation of the long holes 6 and 7 extending in the direction intersecting each other with respect to the cylindrical portions 2a and 3a is performed as shown in FIG. While extending along the X direction, the other long hole 6 is inclined at a required angle with respect to the long hole 7, and the other long hole 6 extends along the axis X− of the hollow main shaft 2. It can also be performed by extending along the X direction and inclining one long hole 7 with respect to the long hole 6.
Further, both the long holes 6 and 7 can be inclined with respect to the direction of the axis XX of the hollow main shaft 2 and the sleeve 3 so as to extend in directions intersecting with each other.

  Here, the shifter means 8 mainly includes a power transmission unit 13 provided with a bearing guide 12 via a bearing 11 on the outer peripheral side of the sliding cylinder 10 connected to the sliding pin 5, and this power transmission. The drive unit 14 is connected to the bearing guide 12 of the unit 13 and moves the power transmission unit 13 in the direction of the axis XX.

  As shown in the figure, the drive unit 14 includes a hydraulic cylinder 15, a rod 16 of the hydraulic cylinder 15, and a support member 17 connected to the rod 16 to reciprocate the bearing guide 12. By extending and contracting 16 in the direction of the axis YY parallel to the direction of the axis XX, the sliding pin 5 can be displaced in the direction of the axis XX via the power transmission unit 13.

  Here, the power transmission unit 13 formed by arranging the bearing 11 between the sliding cylinder 10 and the bearing guide 12 is integrated with the sleeve 3 when rotational power is applied to the sleeve 3. The sliding pin 5 and the sliding cylinder 10 that rotate at high speed are smoothly and reliably displaced in the direction of the axis XX without being affected by the high-speed rotation of the sleeve 3 based on the operation of the drive unit 14. Can be made.

  When the sliding pin 5 is moved in the direction of the axis XX in both the long holes 6 and 7 using the shifter means 8 configured as described above, the hollow main shaft 2 in which the long holes 6 are formed; A relative rotational displacement caused by the difference in the extending direction of each of the long holes 6 and 7 occurs between the sleeve 3 in which the long hole 7 is formed. Rotating relatively fast with respect to the sleeve 3.

By the way, at the end of the hollow main shaft 2, for example, four pairs of eccentric shafts 19 having pinion gears 18 attached thereto are pivoted to oppose each other in the diameter direction of the hollow main shaft 2 and surround the hollow main shaft 2. At the end of the sleeve 3, a ring-shaped internal gear 20 having a plurality of teeth formed inside is connected and fixed by, for example, a bolt, and the internal gear 20 is connected to each of the two eccentric shafts 19. Each attached pinion gear 18 is meshed as shown in FIG. 3 showing a cross section taken along line III-III in FIG.
In this figure, each of the four pinion gears 18 is formed with teeth only on half of the peripheral surface, but this is not essential to the present invention.

  Here, each of the eccentric shafts 19 includes a columnar portion 19a penetrating the pinion gear 18, and an eccentric portion 19b provided to be eccentric with respect to the columnar portion 19a. The columnar portions 19a at both ends are pivotally supported by two bearing plates 21 and 22 that are connected to the tip of the hollow main shaft 2 in parallel with each other in a separated posture.

  By the way, this pivotal support of the eccentric shaft 19 to the bearing plates 21 and 22 is directly fixed to the tip of the hollow main shaft 2, and the bearing plate which is separated from the bearing plate 21 in parallel and connected thereto. The eccentric portion 19b of each eccentric shaft 19 is positioned between the two bearing plates 21 and 22, and the columnar portion 19a of the end portion of each eccentric shaft 19 is rotated through the bearing metal 23 on each of the bearing plates 21 and 22. This can be done with possible support.

  Here, a disc-shaped disc cutter 24 is provided on each of the eccentric portions 19b of the pair of eccentric shafts 19 that oppose each other across the center of the bearing plate 21 among the plurality of eccentric shafts 19 in the figure. In the figure, each of the eccentric parts 19b of the two eccentric shafts 19 which are rotatably mounted via a bearing metal and which oppose each other at least one, here the center of the bearing plate 21, are shown in FIG. A disc-shaped counterweight 25 that does not appear in the cross section shown in FIG.

Here, when each of the hollow main shaft 2 and the sleeve 3 is rotated at high speed by a motor (not shown) or the like, the disc cutter 24 and the counterweight 25 are also integrated with the internal gear 20 to be axial X- In this case, the meshing position of each pinion gear 18 and the internal gear 20 does not change.
In this state, the sliding pin 5 is moved in the direction of the axis XX within the long holes 6 and 7 by the shifter means 8, and a relative rotational displacement is artificially made between the hollow main shaft 2 and the sleeve 3. When generated, the pinion gear 18 disposed at the end of the hollow main shaft 2 is rotated by the action of the internal gear 20 that is attached to the end of the sleeve 3 and meshes with the pinion gear 18. The displacement of the cutter 24 toward the center of the bearing plate 21, that is, the cutting operation of the disc cutter 24 is performed.

  And here, the relative position of the eccentric portion 19b of the eccentric shaft 19 with the disc cutter 24 mounted thereon and the eccentric portion 19b of the eccentric shaft 19 with the counterweight 25 mounted is determined by the above-described cutting operation of the disc cutter 24. The eccentric portion 19b to which the counterweight 25 is attached is set in advance so that the eccentric portion 19b is displaced away from the center of the bearing plate 21.

  That is, when the slide pin 5 is moved by the shifter means 8 and the hollow main shaft 2 provided with the eccentric shaft 19 is rotationally displaced relative to the sleeve 3, any of the eccentric shafts 19 4 is rotated based on the meshing between the pinion gear 18 attached to the end of the disc and the internal gear 20, so that the disc cutter 24 and the counterweight 25 before and after the cutting operation of the disc cutter 24 are shown in FIG. When the eccentric portion 19b of the disc cutter 24 is displaced in the direction toward the center of the bearing plate 21, as shown by the solid line and the virtual line, the eccentric portion 19b of the counterweight 25 is The eccentric shafts 19 and the pinion gears 18 attached thereto are arranged so as to be displaced in a direction away from the center of the plate 21.

  When the hollow main shaft 2 and the sleeve 3 are integrally rotated at a high speed, a centrifugal force F in the direction indicated by an arrow in the figure, which opposes the direction of the cutting operation, acts on the disk cutter 24. For the cutting operation of the disc cutter 24, a large inward driving force that overcomes the centrifugal force is required, but the centrifugal force Fc acting on the counterweight 25 causes the eccentric weight 19 to be attached via the eccentric shaft 19 to which the counterweight 25 is attached. Since the pinion gear 18 fixed to the eccentric shaft 19 is given a relative rotational force in the direction assisting the cutting operation of the disc cutter 24 with respect to the internal gear 20, the centrifugal force is applied to the disc cutter 24. Even when F acts, it is possible to effectively reduce the driving force required for the displacement of the sliding pin 5 for cutting the disk cutter 24. Therefore, the pipe cutting efficiency can be improved easily without increasing the size of the apparatus including the shifter means 6 by further rotating the hollow main shaft 2 and the sleeve 3 at a higher speed.

  In such an apparatus 1, in order to make the positioning and holding of the pipe reliable and easy, as shown in FIG. 1, a collet chuck 26 can be disposed at the end of the cylindrical body 4. By holding the pipe at 26, it can always be cut accurately accurately.

  Next, the pipe rotary device according to the present invention was prototyped and its performance was evaluated, which will be described below.

The embodiment is an apparatus having the structure shown in FIGS.
A conventional example is an apparatus having the structure shown in FIGS. 5 and 6. Specifically, the counterweight 25 and the eccentric shaft 19 to which the counterweight 25 is attached are not provided, but a pair of eccentric shafts to which the disk cutter 24 is attached. Except for the point that only 19 is provided, the configuration is the same as that of the example.

In both the examples and the conventional apparatus, the driving force for rotating the hollow main shaft 2 and the sleeve 3 at a high speed and displacing the sliding pin 5 in the direction of the axis XX under a supply power of 3.7 kW. The maximum number of rotations at which the disc cutter 24 can be cut off was measured using the shifter means 8 having the same value.
Further, each of the apparatus of the example and the conventional example is rotated at the above-mentioned maximum rotational speed to rotate the hollow main shaft 2 and the sleeve 3 to cut a pipe having an outer diameter of 19.1 mm and a thickness of 2.3 mm. The shortest time required for the cutting operation was measured.
The results are shown in Table 1.

From the results shown in Table 1, the rotational speed at which the disk cutter 24 can be cut and operated using the shifter means 8 having the same driving force in the apparatus of the embodiment as compared with the apparatus of the conventional example in which the counterweight 25 is not provided. As a result, it is understood that the rotation speed of the hollow main shaft 2 and the sleeve 3 can be increased and the time required for one cutting of the pipe can be shortened.
Therefore, according to the apparatus of the Example, it turned out that the cutting efficiency of a pipe can be improved.

DESCRIPTION OF SYMBOLS 1 Pipe rotary cutting device 2 Hollow main shaft 2a Tubular body 3 Sleeve 3a Tubular body 4 Tubular body 5 Sliding pin 6, 7 Long hole 8 Shifter means 9 Outer frame 10 Sliding tubular body 11 Bearing 12 Bearing guide 13 Power transmission Part 14 Drive part 15 Hydraulic cylinder 16 Rod 17 Support member 18 Pinion gear 19 Eccentric shaft 19a Columnar part 19b Eccentric part 20 Internal gear 21, 21 Bearing plate 23 Bearing metal 24 Disc cutter 25 Counterweight 26 Collet chuck

Claims (2)

A hollow main shaft, a sleeve disposed around the hollow main shaft, a long hole formed through each of the cylindrical portions of the hollow main shaft and the sleeve and extending in directions intersecting with each other, and into the long holes Inserted and arranged, and displaced by the shifter means in the extending direction of each elongated hole, including a sliding pin that controls transmission of rotational driving force from either the hollow main shaft or the sleeve to the other,
Two bearing plates are connected in parallel to each other at the end of the hollow main shaft in a mutually separated posture, and a plurality of eccentric shafts are pivotally supported on these two bearing plates, and a sleeve is provided on each eccentric shaft. A pinion gear meshing with an internal gear attached to the end of the bearing is fixed, and at least a pair of opposed eccentric shafts positioned between the two bearing plates with the center of the bearing plate facing each other. A disc cutter is attached,
An eccentric portion mounted with a disc cutter by displacing the slide pin in both elongated holes in the extending direction of the elongated hole by the shifter means to cause a relative rotational displacement between the hollow main shaft and the sleeve. In the rotary cutting device of the pipe that performs the cutting operation that is displaced toward the center of the bearing plate,
A counterweight is provided on the eccentric part of at least one other eccentric shaft,
The relative position of the eccentric part of the disc cutter mounting eccentric shaft and the counterweight mounting eccentric shaft is displaced away from the center of the bearing plate by the disc cutter cutting operation. Pipe rotary cutting device as an arrangement.   The pair of counterweights are provided in each eccentric portion of at least two other eccentric shafts, and the pair of counterweights are positioned to face each other with the center of the bearing plate therebetween. Pipe rotary cutting device.

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