JP2015027780A - Wire saw device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a wire saw device which can greatly reduce a processing time of an object.SOLUTION: Reciprocatable sliders 26, 28 are provided along a pair of support posts 16, 18 arranged on both sides of an object W. A pair of sheaves 60, 64 are rotatably supported to the sliders 26, 28, and a wire saw 68 is mounted on the pair of sheaves 60, 64 and rotated by drive of a rotary motor 48. The sliders 26, 28 are independently raised and lowered by raising and lowering motors 38, 42, and the tension change of the wire saw 68 caused by a height difference between the sliders 26, 28 is maintained constant by a tension mechanism. The tension mechanism comprises a movable part 90 which is slidable with respect to the slider 28, a hydraulic cylinder 74 which drives the movable part 90, and guide means. While maintaining the tension of the wire saw 68 constant, the angle of the wire saw 68 is changed to cut the object W, whereby cutting can be performed in a short time.

Description

  The present invention relates to a wire saw device that processes a stone material, a concrete material, or the like using a wire saw.

  As a conventional wire saw processing machine, there exists a thing shown in the following patent document 1, for example. FIG. 7 of the document shows an outline of a wire saw processing machine, in which an endless wire saw is mounted on a pair of sheaves, and the pair of sheaves are supported by a pair of lifting columns so as to be movable up and down. . Then, by rotating one sheave of the pair of sheaves with an electric motor, the wire saw is driven, and the other sheave is also rotationally driven through the wire saw. The object to be cut (for example, stone) is placed on a processing table provided in the approximate center of the pair of lifting columns. The pair of sheaves are configured to move up and down simultaneously.

Utility Model Registration No. 3061128 (FIG. 7)

  In the technique described in Patent Document 1 described above, the wire saw being driven slides on the surface of the stone material by lowering the pair of sheaves toward the object to be cut while the wire saw is being driven. Is cut. In this method, the wire saw always applies a uniform pressure in the horizontal direction to the surface of the stone material, and the time required for cutting is long.

  The present invention focuses on the above points, and an object of the present invention is to provide a wire saw device that can significantly reduce the processing time of an object.

  The wire saw device of the present invention is provided on each of a pair of support means disposed on both sides of an object and the pair of support means, and in an axial direction of the support means or in a direction substantially orthogonal to the support means. A pair of sliders capable of reciprocating along, a reciprocating drive mechanism for independently driving the pair of sliders, and a plurality of sheaves rotatably supported by at least one of the pair of sliders. A reciprocating drive comprising: a wire saw mounted on the plurality of sheaves; a rotation drive mechanism for rotating any of the plurality of sheaves; and a tension mechanism for maintaining a constant tension of the wire saw. The object is processed by the mechanism so that the moving speed or the moving amount of the pair of sliders is different.

  One of the main forms is that when the pair of sliders reciprocate along the axial direction of the support means, the tension mechanism moves the reciprocating direction of the sliders relative to one of the pair of sliders. A movable part movable in a direction orthogonal to the movable part, guide means for moving the movable part along the slider, and the movable part to drive the movable part and keep the tension of the wire saw constant. And a movable part driving means for adjusting the position of the first and second sheaves, wherein one sheave is rotatably supported by the movable part.

  One of the other forms is that when the pair of sliders reciprocate along the axial direction of the support means, the reciprocating drive mechanism includes two motors respectively provided for the pair of sliders; And a transmission mechanism for transmitting the outputs of the two motors to the sliders. Still another embodiment is characterized in that the reciprocating drive mechanism includes a transmission shaft provided between output shafts of the two motors, and a clutch provided on the transmission shaft.

  In still another embodiment, when the pair of sliders reciprocate along the axial direction of the support means, the reciprocating drive mechanism transmits the motor and the output of the motor to the pair of sliders. A transmission shaft for transmitting, a transmission mechanism for transmitting the output of the motor to the slider via the transmission shaft, a gear for transmitting the output of the motor to the transmission shaft, and the transmission shaft; And a pair of clutches sandwiched between the gears.

  One of the other main forms is that the pair of sliders are attached to a pair of first sliders that can reciprocate along the axial direction of the pair of support means, and the first sliders, A reciprocating movement in a direction substantially perpendicular to the axial direction of the pair of support means, and a pair of second sliders on which the plurality of sheaves are rotatably supported. A first reciprocating drive mechanism for driving the pair of first sliders; and a second reciprocating drive mechanism for driving the pair of second sliders. The object is processed by the reciprocating drive mechanism so that the moving speed or the moving amount of the pair of second sliders is different.

  In another embodiment, the tension mechanism is movable in a direction substantially perpendicular to the axial direction of the pair of support means with respect to any one of the pair of second sliders, and one sheave rotates. A movable part supported in a possible manner, and a movable part driving means for adjusting the position of the movable part so as to drive the movable part and keep the tension of the wire saw constant. The sheave supported by the movable part moves in the same plane as the main surface of the other sheave. The above and other objects, features and advantages of the present invention will become apparent from the following detailed description and the accompanying drawings.

  According to the present invention, the pair of support means disposed on both sides of the object is provided with a pair of sliders that can reciprocate in the axial direction of the support means or in a direction substantially perpendicular to the support means. At least one or more sheaves are rotatably supported on each of the sliders, a wire saw is mounted on the plurality of sheaves, and one of the sheaves is rotated by a rotational drive mechanism. The pair of sliders can be independently driven by a reciprocating drive mechanism, and the change in the tension of the wire saw generated according to the position of the slider is kept constant by the tension mechanism. For this reason, by making the moving speed or the moving amount of the pair of sliders different by the reciprocating drive mechanism, it becomes possible to perform processing while changing the angle of the wire saw applied to the object, so that the pressure applied to the object increases. At the same time, since the position where the pressure is applied changes gradually, the processing time of the object can be significantly shortened compared to the conventional case.

It is a figure which shows the whole structure of the wire saw apparatus of Example 1 of this invention. FIG. 2A is a view showing the lifting mechanism of the first embodiment, and FIG. 2B is a view showing the rotation drive mechanism. 3A and 3B are diagrams illustrating the tension mechanism according to the first embodiment. FIG. 3A illustrates a state in which the wire saw is horizontal, and FIG. 3B illustrates a state in which the wire saw is inclined. It is a figure which shows the mode of the cutting | disconnection of the target object by the said Example 1. FIG. It is a figure which shows the mode of the cutting | disconnection of the target object by the said Example 1. FIG. It is a figure which shows Example 2 of this invention. It is a top view which shows Example 3 of this invention. 7A and 7B are diagrams showing Example 3, wherein FIG. 7A is a side view of FIG. 7 viewed from the direction of arrow F7A, FIG. 7B is a side view of FIG. 7 viewed from the direction of arrow F7B, and FIG. Is a cross-sectional view taken along line # A- # A and viewed in the direction of the arrow, and (D) is a cross-sectional view taken along line # B- # B and viewed in the direction of the arrow. It is a figure which shows the mode of the cutting | disconnection of the target object by the said Example 3. FIG. It is a figure which shows the modification of the said Example 3. FIG.

  Hereinafter, the best mode for carrying out the present invention will be described in detail based on examples.

  First, Embodiment 1 of the present invention will be described with reference to FIGS. FIG. 1 is a diagram showing the overall configuration of the wire saw device of this embodiment. FIG. 2A is a view showing the lifting mechanism of this embodiment, and FIG. 2B is a view showing the rotation drive mechanism of this embodiment. 3A and 3B are diagrams showing the tension mechanism of the present embodiment. FIG. 3A shows a horizontal state of the wire saw, and FIG. 3B shows a state where the wire saw is inclined. 4 and 5 are diagrams showing a state of cutting using the wire saw device of the present embodiment. In the present embodiment, the case of cutting an object has been described as an example, but the present invention can also be applied to a case where processing other than cutting is performed.

  As shown in FIG. 1, the wire saw device 10 of the present embodiment has a substantially U-shaped support formed on a base 12 by a pair of support columns 16 and 18 and a beam 20 provided between the support columns 16 and 18. The body 14 is mainly configured. The sheaves 60 and 64 for mounting the wire saw 68 on the support 14, the mechanism for rotating the sheaves 60 and 64, the mechanism for moving the sliders 26 and 28 supporting the sheaves 60 and 64, and the wire saw 68 The mechanism for adjusting the tension is provided. As shown in FIG. 4, the object W is placed between the columns 16 and 18.

  First, with reference to FIG. 1 and FIG. 2 (A), the raising / lowering mechanism of the sliders 26 and 28 is demonstrated. A guide rail 22 is provided on the side surface of the support column 16 in the vertical direction, and a slider 26 that can be moved up and down along the guide rail 22 is provided. A bearing 33 is provided on the upper surface 16A of the support column 16, and the feed screw 30 is rotatably supported. On the other hand, the slider 26 is provided with a nut portion 34 that engages with the feed screw 30. An elevating motor 38 for elevating the slider 26 is provided on the upper surface of the beam 20. The bevel gear 40 </ b> A at the tip of the output shaft 40 of the lifting / lowering motor 38 meshes with the bevel gear 30 </ b> A at the upper end of the feed screw 30. Therefore, when the elevating motor 38 is driven, the output is transmitted to the feed screw 30 via the output shaft 40 and the bevel gears 40A and 30A. The slider 26 in which the nut portion 34 is screwed to the feed screw 30 moves up and down the column 16 along the guide rail 22.

  The same applies to the column 18 side, and a guide rail 24 is provided on the side surface of the column 18 in the vertical direction, and a slider 28 that can be moved up and down along the guide rail 24 is provided. A bearing 35 is provided on the upper surface 18A of the column 18, and the feed screw 32 is rotatably supported. On the other hand, the slider 28 is provided with a nut portion 36 that is screwed into the feed screw 32. An elevating motor 42 for elevating the slider 28 is provided on the upper surface of the beam 20. A bevel gear 44A at the tip of the output shaft 44 of the lifting motor 42 meshes with a bevel gear 32A at the upper end of the feed screw 32. For this reason, when the elevating motor 42 is driven, the output is transmitted to the feed screw 32 via the output shaft 44 and the bevel gears 44A and 32A. Then, the slider 28 in which the nut portion 36 is screwed to the feed screw 32 moves up and down the column 18 along the guide rail 24. Thus, in the present invention, the sliders 26 and 28 provided on the pair of support columns 16 and 18 are configured to be able to move up and down independently. For this reason, by moving the sliders 26 and 28 so that the moving speeds or the moving amounts thereof are different, it is possible to perform processing with the sliders 26 and 28 having different heights.

  Next, the rotational drive mechanism of the sheaves 60 and 64 will be described with reference to FIGS. 1 and 2B. A bracket 46 is attached to the side surface of the slider 26 on the column 16 side, and a rotation motor 48 is fixed to the upper surface of the bracket 46. A gear 50 </ b> A is provided at the tip of the output shaft 50 of the rotation motor 48. A transmission shaft 52 is rotatably supported by bearings 54 and 56 below the slider 26. A gear 52A is provided at one end of the transmission shaft 52, and a sheave 60 is provided at the other end. A belt 58 is mounted on the gears 50A and 52A, and the output of the rotation motor 48 is transmitted to the transmission shaft 52 via the gear 50A, belt 58 and gear 52A, and the sheave 60 rotates.

  On the other hand, as will be described later, the slider 28 on the column 18 side has a movable portion 90 that can reciprocate in a direction orthogonal to the moving direction of the slider 28, that is, a direction in which the distance between the sheaves 60 and 64 is expanded and contracted. Is provided. A shaft 96 is rotatably supported by the movable portion 90 by bearings 94 </ b> A and 94 </ b> B, and the other sheave 64 is provided at the tip of the shaft 96. A wire saw 68 is mounted on the sheaves 60 and 64. For this reason, when the rotation motor 48 is driven, the output is transmitted through the sheave 60 and the wire saw 68, and the sheave 64 also rotates. The sheaves 60 and 64 are provided with protective covers 62 and 66 as required, as indicated by dotted lines in FIG.

  Next, the tension mechanism will be described with reference to FIGS. As described above, in this embodiment, since the slider 26 of the support column 16 and the slider 28 of the support column 18 can be moved up and down independently, the wire saw device 10 is driven with the sheaves 60 and 64 having different heights. can do. In that case, since the interval between the sheaves 60 and 64 changes from the interval I to the interval I ′ as shown in FIG. 3B, it is necessary to keep the tension of the wire saw 68 constant. In this embodiment, the tension mechanism is provided on the support column 18 side. A plate 70 is fixed to the slider 28 on the column 18 side, and a hydraulic cylinder 74 is provided on the plate 70. A connector 78 is fixed to the tip of the rod 76 of the hydraulic cylinder 74. A pair of rails 82A and 82B are provided on the bottom surface 72 side of the plate 70. A movable portion 90 having rail receivers 92A and 92B engaged with the rails 82A and 82B is attached to the bottom surface 72 of the plate 70.

  In addition, a long hole 80 is formed in the plate 70. A connector 78 fixed to the tip of the rod 76 of the hydraulic cylinder 74 passes through the elongated hole 80 and is fixed to the upper surface of the movable portion 90. As described above, the shaft 96 connected to the sheave 64 is rotatably supported on the bottom surface side of the movable portion 90 by the bearings 94A and 94B. Accordingly, when the movable portion 90 is reciprocated by the expansion and contraction of the rod 76 of the hydraulic cylinder 74, the sheave 64 supported by the movable portion 90 can also be reciprocated in a direction perpendicular to the ascending / descending direction of the slider 28.

  For this reason, as shown in FIG. 3A, when the wire saw 68 mounted on the sheaves 60 and 64 is horizontal, the rod 76 of the hydraulic cylinder 74 is contracted and the movable portion 90 is separated from the slider 28. . As shown in FIG. 3 (B), when the sheave 64 is lowered from the sheave 60, the wire saw 68 is inclined, so that the rod 76 of the hydraulic cylinder 74 extends to keep the tension constant. The sheave 64 moves to the slider 28 side together with the movable portion 90. In this embodiment, the tension adjustment by the hydraulic cylinder 74 is automatically performed so that the pressure becomes constant.

  Next, the cutting process according to the present embodiment will be described with reference to FIGS. First, as shown in FIG. 4A, the sliders 26 and 28 are raised, the sheaves 60 and 64 are moved upward, and the wire saw 68 is set to a predetermined tension by the hydraulic cylinder 74. Then, the object W placed on the carriage 98 is sent between the columns 16 and 18. When the object W is in a predetermined position, the rotation motor 48 is driven to transmit the output, the sheaves 60 and 64 are rotated, and the wire saw 68 is rotated. Then, as shown in FIG. 4B, first, only the slider 26 on one side (the sheave 60 side in the illustrated example) is lowered by the elevating motor 38. Then, the wire saw 68 mounted on the sheaves 60 and 64 having different heights is in a state of being inclined from the horizontal state (in a state of rising to the right in FIG. 4B), and in such a state, the wire saw 68 is in contact with the object W. Become. Then, in order to prevent the tension of the wire saw 68 from being changed as the sheave 60 is lowered, the rod 76 is extended by the drive of the hydraulic cylinder 74 and the movable portion 90 is moved to the sheave 60 side. ) Always maintain the same interval I as the interval between the sheaves 60 and 64 in FIG.

  Thus, when one sheave 60 is lowered over a predetermined time (for example, about 5 minutes), the descent of the sheave 60 is then stopped, and the other sheave 64 is lowered by driving the elevating motor 42. . As shown in FIG. 4 (C), the wire saw 68 passes through a horizontal state during the lowering, but during the transition from FIG. 4 (B) to FIG. 4 (C), the hydraulic cylinder 74 of the tension mechanism. As a result, the movable portion 90 moves in a direction away from the sheave 60 so that the distance I between the sheaves 60 and 64 is kept constant and the tension of the wire saw 68 is kept constant. In the present embodiment, the sheave 64 continues to descend without stopping in the state of FIG. Then, the sheave 64 becomes lower than the sheave 60, and the wire saw 68 is inclined downward to the right (see FIG. 5A). In this way, even during the transition from FIG. 4 (C) to FIG. 5 (A), the movable portion 90 is moved by the tension mechanism so that the tension of the wire saw 68 is maintained by keeping the distance between the sheaves 60 and 64 constant. Move to 60 side. The descent only on the sheave 64 side is also performed for a predetermined time (for example, about 5 minutes).

  Finally, as shown in FIG. 5B, in the state where the descending of the sheave 64 is stopped, the cutting of the descending target W is completed by the wire saw 68 while only the sheave 60 is lowered, and the sheave 60 is the same as the sheave 64. Lower to height. Even in the change from the state shown in FIG. 5A to the state shown in FIG. 5B, the movable portion 90 moves away from the sheave 60 by the tension mechanism so as to keep the interval I between the sheaves 60 and 64 constant. . In the example of FIGS. 4 and 5, the case where the sheave 60 side is lowered and the case where the sheave 64 side is lowered are made one time, but the sheaves 60, 64 depending on the size and size of the object W, etc. The distance to be lowered in one descent, the descent time / descent speed may be appropriately changed, or the sheaves 60 and 64 may be alternately lowered.

  As described above, the sheaves 60 and 64 are alternately lowered so that the wire saw 68 changes from the right-up state to the right-down state through the horizontal state, and from the right-down state to the right-up state again through the horizontal state. By alternately performing the steps, the pressure applied to the contact portion increases compared to the case where the wire saw 68 is brought into contact with the object W in a horizontal state, and the state is gradually changed. In addition, cutting can be performed in a time of 1/4 to 1/5.

  As described above, according to the first embodiment, the pair of sliders 26 and 28 that can reciprocate along the pair of support columns 16 and 18 arranged on both sides of the object W are provided, and the pair of sliders 26 and 28 can be rotated on the slider. The sheaves 60 and 64 are supported, a wire saw 68 is mounted on the pair of sheaves, and the sheave 60 is rotated by driving the rotation motor 48. The pair of sliders 26 and 28 can be independently driven by the lifting motors 38 and 42, and the tension change of the wire saw 68 generated according to the position of the sliders 26 and 28 is kept constant by the tension mechanism. It was decided. For this reason, since it becomes possible to cut while changing the angle of the wire saw applied to the object W, the pressure applied to the object W increases, and the position where the pressure is applied changes gradually. This can be greatly shortened compared to the prior art.

  Next, Embodiment 2 of the present invention will be described with reference to FIG. In addition, the same code | symbol shall be used for the component which is the same as that of Example 1 mentioned above or respond | corresponds. In the first embodiment, the sheaves 60 and 64 can be moved up and down independently. However, in addition to the mechanism that can move up and down independently, this embodiment can also be used in the same manner as in the prior art in which two sheaves move up and down simultaneously. It has a configuration. In the example shown in FIG. 6A, as in the first embodiment, the sheave 60 is provided with the elevating motor 38, and the sheave 64 is provided with the elevating motor 42. However, transmission between the output shafts of these motors is performed. The shafts 100 and 102 are connected, and a clutch 104 is provided between the transmission shafts 100 and 102.

  The bevel gear 40A of the output shaft 40 of the lifting / lowering motor 38 meshes with the bevel gear 30A of the feed screw 30 for the slider 26 and the bevel gear 100A at the tip of the transmission shaft 100. The bevel gear 44A of the output shaft 44 of the other lifting / lowering motor 42 meshes with the bevel gear 32A of the feed screw 32 for the slider 28 and the bevel gear 102A of the transmission shaft 102. When the sheaves 60 and 64 are moved up and down separately, the transmission of rotation between the transmission shafts 100 and 102 is blocked by the clutch 104. When the sheaves 60 and 64 are simultaneously lifted and used in the same manner as a normal wire saw device, only one of the lifting motors 38 and 42 is driven while the transmission shafts 100 and 102 are connected by the clutch 104. The output is transmitted to the feed screws 30 and 32, and the sheaves 60 and 62 are moved up and down simultaneously.

  In the example shown in FIG. 6B, the two sheaves 60 and 64 are moved up and down independently by one lifting motor. As shown in FIG. 6 (B), a lifting / lowering motor 110 is provided on the beam 20 of the support 14, and the bevel gear 112 A of the output shaft 112 of the lifting / lowering motor 110 is provided near the center of the transmission shaft 114. The bevel gear 114A thus engaged is engaged. Further, the bevel gear 30A of the feed screw 30 for the sheave 60 is screwed to the bevel gear 114B on one end side of the transmission shaft 114, and the bevel gear 32A of the feed screw 32 for the sheave 64 is screwed to the bevel gear 114C on the other end side. Match. The transmission shaft 114 is provided with a pair of clutches 116 and 120 with the bevel gear 114A interposed therebetween, so that the output of the lifting motor 110 can be transmitted and cut off.

  When used as a normal wire saw device, when the output of the lifting motor 110 is transmitted to the feed screws 30 and 32 by the clutches 116 and 120, the transmission shaft 114 is rotated by the bevel gear 114A, and the sheaves 60 and 64 are rotated. Are raised and lowered at the same time. Further, when the sheaves 60 and 64 are lifted and lowered independently as in the first embodiment, when the one sheave 60 is lifted and lowered, the output of the lifting and lowering motor 110 is transmitted to the feed screw 30 by the clutch 116, and the clutch 120 Connection is cut off. When the sheave 64 is moved up and down, the clutch 116 is disconnected and the output of the lifting motor 110 is transmitted to the feed screw 32 by the clutch 120. According to the present embodiment, in addition to the effects of the first embodiment described above, the sheaves 60 and 64 can be lifted and lowered simultaneously, and there is an advantage that it can be used as a normal wire saw device.

  Next, Embodiment 3 of the present invention will be described with reference to FIGS. The first and second embodiments described above are examples in which the sheave moves up and down to cut the object W in the vertical direction, but in this embodiment, the sheave moves back and forth in the horizontal direction. The object W is cut in the horizontal direction. FIG. 7 is a plan view of the wire saw device of this embodiment. 8A is a side view of FIG. 7 viewed from the direction of arrow F7A, FIG. 8B is a side view of FIG. 7 viewed from the direction of arrow F7B, and FIG. 8C is the side view of FIG. FIG. 8D is a cross-sectional view taken along the line A- # A and viewed in the direction of the arrow, and FIG. 8D is a cross-sectional view taken along the line # B- # B and viewed in the direction of the arrow. FIG. 9 is a diagram showing a state of cutting using the wire saw device of this example.

  As shown in FIGS. 7 and 8, the wire saw device 200 of this embodiment is formed by a pair of support columns 202 and 208 erected on a base 201 and a beam 214 provided between the support columns 202 and 208. It is configured around a substantially U-shaped support. Sheaves 280 to 286 for mounting the wire saw 290 on the support, a mechanism for rotating the sheaves 280 to 286, horizontal sliders 240 and 262 for supporting the sheaves 280 to 286, and driving mechanisms thereof, the horizontal slider Elevating sliders 230 and 232 for supporting 240 and 262, its elevating mechanism, and a tension mechanism 300 for adjusting the tension of the wire saw 290 are provided. On the other hand, as shown in FIG. 7, the object W is placed on a carriage 322 or the like that can move on rails 320 </ b> A and 320 </ b> B provided between the columns 202 and 208, and the horizontal direction (the vertical direction in FIG. 7). ) Can be moved. The driving mechanism of the carriage 322 is well known and will not be described.

  The column 202 includes a pair of poles 204A and 204B and a feed screw 206 provided therebetween. The upper end of the feed screw 206 passes through the beam 214 and is rotatably supported by a bearing (not shown) provided on the beam 214. A bevel gear 206 </ b> A is provided at the upper end of the feed screw 206. The column 202 is provided with an elevating slider 230 (first slider) that passes through the pair of poles 204A and 204B and can move up and down along the poles 204A and 204B. The elevating slider 230 is provided with a nut portion (not shown) that is screwed with the feed screw 206.

  The other column 208 is composed of a pair of poles 210A and 210B and a feed screw 212 provided therebetween. An upper end of the feed screw 212 passes through the beam 214 and is rotatably supported by a bearing (not shown) provided on the beam 214. A bevel gear 212 </ b> A is provided at the upper end of the feed screw 212. The column 208 is provided with an elevating slider 232 (first slider) that passes through the pair of poles 210A and 210B and can move up and down along the poles 210A and 210B. The elevating slider 232 is provided with a nut portion (not shown) that is screwed with the feed screw 212.

  On the beam 214, a transmission shaft 220 is supported by bearings 224A and 224B so as to be substantially parallel to the beam 214 and to be rotatable. A lifting motor 216 for rotating the transmission shaft 220 is fixed to one end side (right side in the example of FIG. 7) of the beam 214. An output shaft 218 of the lifting motor 216 is joined to the back surface of a bevel gear 222A provided on one end side of the transmission shaft 220 so that the transmission shaft 220 can be rotated. The bevel gear 222A meshes with the bevel gear 206A of the feed screw 206. A bevel gear 222B is also provided on the other end side of the transmission shaft 220, and the bevel gear 222B meshes with the bevel gear 212A of the feed screw 212.

  These bevel gears mesh with each other to form a gear mechanism, whereby the rotation of the elevating motor 216 is simultaneously transmitted to the feed screws 206 and 212 via the transmission shaft 220. That is, when the feed screws 206 and 212 are rotationally driven by the lift motor 216, the lift sliders 230 and 232 screwed to the feed screws 206 and 212 can be lifted and lowered simultaneously with respect to the support columns 202 and 208. ing.

  The elevating sliders 230 and 232 are provided with horizontal sliders 240 and 262 (second sliders) extending in a direction substantially orthogonal to the axial direction of the support columns 202 and 208. The sheaves 280, 282, 284, and 286 rotatably supported at both ends of the horizontal sliders 240 and 262 are disposed at substantially the same horizontal position, and the wire saw 290 is mounted on the sheaves 280 to 286. Has been. Of these sheaves, the shaft 280A of the sheave 280 is rotatably attached to one end portion 240B of the horizontal slider 240 by a bearing 280B. Similarly, shafts 284A and 286A of sheaves 284 and 286 are rotatably attached to end portions 262B and 262C of horizontal slider 262 by bearings 284B and 286B. Further, the shaft 282A of the sheave 282 is rotatably supported by the bearing 282B on the end 302B side of the movable arm 302 constituting the tension mechanism 300 described later.

  Next, the reciprocation mechanism of the horizontal sliders 240 and 262 will be described. As shown in FIGS. 8A and 8C, the horizontal slider 240 is disposed substantially parallel to the side surface of the elevating slider 230. A guide bar 234 is slidably supported on a side surface of the elevating slider 230 by a pair of bearings 236A and 236B. One end side (left end side in the example of FIG. 8C) of the guide bar 234 is fixed to the end portion 240C side of the horizontal slider 240 by a fixture 238. A reciprocating motor 244 is provided on the upper surface 240 A of the horizontal slider 240 via a fixed base 242. A gear 246 </ b> A is provided at the tip of the output shaft 246 of the reciprocating motor 244. A feed screw 248 is disposed along the longitudinal direction of the upper surface 240A. The feed screw 248 is rotatably supported by the bearing 250 with respect to the upper surface 240A, and is also supported by a bearing 252 provided on the side surface of the elevating slider 230. Inside the bearing 252, a screw portion that is screwed with the feed screw 248 is formed.

  A gear 248 </ b> A is provided on one end side of the feed screw 248, and a belt 254 is mounted between the gear 246 </ b> A of the output shaft 246 of the reciprocating motor 244. Therefore, the output of the reciprocating motor 244 is transmitted to the feed screw 248 via the gear 246A, the belt 254, and the gear 248A, and the feed screw 248 rotates. Then, the feed screw 248 moves in the horizontal direction with respect to the lift slider 230, and the horizontal slider 240 to which the feed screw 248 is rotatably attached reciprocates in the horizontal direction. At this time, the horizontal movement of the horizontal slider 240 is guided by the guide bar 234 provided between the elevating slider 230 and the horizontal slider 240. The tension mechanism 300 provided on the end 240C side of the horizontal slider 240 will be described later.

  The other horizontal slider 262 basically has the same configuration, and is disposed substantially parallel to the side surface of the lift slider 232 as shown in FIGS. A guide bar 256 is slidably supported on a side surface of the elevating slider 232 by a pair of bearings 258A and 258B. One end side (right end side in the example of FIG. 8D) of the guide bar 256 is fixed to the end portion 262C side of the horizontal slider 262 by a fixture 260. A reciprocating motor 266 is provided on the upper surface 262 A of the horizontal slider 262 via a fixed base 264. A gear 268A is provided at the tip of the output shaft 268 of the reciprocating motor 266. A feed screw 270 is disposed along the longitudinal direction of the upper surface 262A. The feed screw 270 is supported by the bearing 272 so as to be rotatable with respect to the upper surface 262A, and is also supported by a bearing 274 provided on a side surface of the elevating slider 232. Inside the bearing 274, a screw portion that is screwed with the feed screw 270 is formed.

  A gear 270A is provided on one end side of the feed screw 270, and a belt 276 is mounted between the gear 268A of the output shaft 268 of the reciprocating motor 266. The output is transmitted to the feed screw 270 via the gear 268A, the belt 276, and the gear 270A, and the feed screw 270 rotates. Then, the feed screw 270 moves in the horizontal direction with respect to the lift slider 232, and the horizontal slider 262 to which the feed screw 270 is rotatably attached reciprocates in the horizontal direction. At this time, the horizontal reciprocation of the horizontal slider 262 is guided by the guide bar 256 provided between the elevating slider 232 and the horizontal slider 262.

  A rotation motor 292 for rotating the sheaves 280 to 286 is fixed to the side surface of the horizontal slider 262. A gear 296 is provided at the tip of the output shaft 294 of the rotation motor 292. A gear 288 is provided on the upper end side of the sheave 284 that is rotatably supported on the end 262B side of the horizontal slider 262. A belt 298 is mounted on the gear 296 and the gear 288, and the output of the rotating motor 292 is transmitted to the shaft 284A via the gear 296, the belt 298, and the gear 288, and the sheave 284 rotates. Then, the other sheaves 280, 282 and 286 also rotate through the wire saw 290. The sheaves 280 to 286 may be provided with a protective cover or the like as necessary.

  In this embodiment, since the pair of horizontal sliders 240 and 262 can be independently reciprocated in the horizontal direction, the moving speeds or moving amounts (or moving directions) of the horizontal sliders 240 and 262 are different. By moving the wire saw, the processing can be performed in a state in which the wire saw 290 is tilted differently. In that case, the wire saw 290 may be loosened by adopting a configuration in which the horizontal sliders 240 and 262 can be driven independently. Therefore, in this embodiment, the tension of the wire saw 290 is kept constant by providing the tension mechanism 300 on the horizontal slider 240 side.

  As shown in FIGS. 7, 8A and 8C, the tension mechanism 300 changes the movable arm 302 provided on one end 240C side of the horizontal slider 240 and the inclination of the movable arm 302. A hydraulic cylinder 308 is included. One end 302A side of the movable arm 302 is rotatably attached to a bearing 304B provided on the end 240C side of one main surface of the horizontal slider 240 via a shaft 304A. The sheave 282 is rotatably supported on the other end 302B side of the movable arm 302 via a bearing 282B. Further, the hydraulic cylinder 308 is attached by a fixing member 306 to the end portion side 240 </ b> C side of the other main surface of the horizontal slider 240. The distal end side of the rod 310 of the hydraulic cylinder 308 is connected to the movable arm 302 via a rotation connector 312. Therefore, when the rod 310 is expanded and contracted by driving the hydraulic cylinder 308, the movable arm 302 is rotated about the shaft 304A, and the position of the sheave 282 supported by the movable arm 302 is shifted according to the expansion and contraction of the rod 310. Thereby, the tension of the wire saw 290 can be kept constant.

  For this reason, as shown in FIG. 9 (A), when the wire saw 290 mounted on the sheaves 282 and 286 is orthogonal to the traveling direction of the object W, the rod 310 of the hydraulic cylinder 308 extends and becomes horizontal. The inclination of the movable arm 302 with respect to the slider 240 is increased, and the sheave 282 is separated from the sheave 286. 9B and 9D, when the wire saw 290 is inclined with respect to the traveling direction of the object W, the rod 310 of the hydraulic cylinder 308 is contracted, and the movable arm 302 is moved relative to the horizontal slider 240. The inclination is reduced, and the sheave 282 approaches the sheave 286. In this embodiment, the tension adjustment by the hydraulic cylinder 308 is automatically performed so that the pressure becomes constant.

  Next, the cutting process according to this embodiment will be described with reference to FIG. First, the elevating sliders 230 and 232 are raised by driving the elevating motor 216 to adjust the sheaves 280 to 286 to a desired height. Then, the wire saw 290 is set to a predetermined tension by the hydraulic cylinder 308, and the sheave 280 to 286 is rotated by the rotation motor 292 to rotate the wire saw 290. Then, the object W placed on the carriage 322 on the rails 320A and 320B between the columns 202 and 208 is sent at a predetermined speed in the direction indicated by the arrow F9 in FIG. Further, the horizontal sliders 240 and 262 are driven in different directions by driving the reciprocating motors 244 and 266, and the wire saw 290 is inclined with respect to the traveling direction of the object W as shown in FIG. Contact with. Further, in order to prevent the tension of the wire saw 290 from changing due to a change in the position of the horizontal sliders 240 and 262, the rod 310 is contracted by driving the hydraulic cylinder 308 to move the sheave 282 to the sheave 286 side. In the state of FIG. 9B, one horizontal slider 240 moves in the same direction as the moving direction of the object W, and the other horizontal slider 262 moves in the direction opposite to the moving direction.

  After the horizontal sliders 240 and 262 are moved in the direction shown in FIG. 9B over a predetermined time (for example, about 5 minutes), the horizontal sliders 240 and 262 are moved in the opposite direction. During the movement, as shown in FIG. 9C, the wire saw 290 once passes through a state substantially orthogonal to the traveling direction of the object W, but the transition from FIG. 9B to FIG. 9D is performed. During this, the positions of the movable arm 302 and the sheave 282 are adjusted by the hydraulic cylinder 308 so as to keep the tension of the wire saw 290 constant. In this embodiment, the horizontal sliders 240 and 262 continue to move without stopping in the state shown in FIG. Then, as shown in FIG. 9 (D), the wire saw 290 comes into contact with the object W while being inclined in the direction opposite to the state of FIG. 9 (B). Even during such reciprocating drive of the horizontal sliders 240 and 262, the conveyance of the object W placed on the carriage 322 is continued. When the cutting of the object W is completed, the driving of the wire saw 290 is stopped, the lifting sliders 230 and 232 are raised, and the carriage 322 is moved backward.

  In the example of FIGS. 9A to 9D, the state in which the wire saw 290 is tilted is set to twice. However, depending on the size and shape of the object W, the reciprocating distance of the horizontal sliders 240 and 262 The time, speed, and number of times may be changed as appropriate. As described above, the horizontal sliders 240 and 262 are alternately reciprocated in the traveling direction of the object W and the opposite direction, and the machining is performed while changing the inclination of the wire saw 290, so that the moving direction of the object W is changed. Compared with the case where the wire sheath 290 is brought into contact with each other in an orthogonal state, the pressure applied at the time of contact is increased, and the processing time can be greatly reduced as compared with the conventional case by gradually changing the state. In this embodiment, the pressing force is increased by bringing the object W into contact with the outside of the loop formed by the wire saw 290, but if necessary, as in the example shown in FIG. It does not prevent the object W from being placed inside the loop of the wire saw 290 and contacting the object W from the inside of the loop.

  <Modification> Next, a modification of the present embodiment will be described. In the example shown in FIGS. 7 to 9, four sheaves 280, 282, 284, and 286 are used. However, this is also an example, and the wire saws shown in FIGS. 10 (B-1) to (B-3) are used. A configuration using three sheaves 402, 404, and 406 as in the apparatus 400 may be adopted. In the illustrated example, two sheaves 402 and 404 are provided on one horizontal slider 240 and reciprocate in conjunction with the traveling direction of the object W and the opposite direction. The other horizontal slider 262 is provided with one sheave 406 and reciprocates in the traveling direction of the object W and in the opposite direction. These reciprocating mechanisms are the same as those described above. In addition, a motor for rotating the sheaves 402 to 406 is provided on the horizontal slider 262 side (not shown), for example. At that time, for example, the tension of the wire saw 410 is kept constant by a mechanism similar to the tension mechanism 300. For example, as shown in FIG. 10 (B-1), from the state where the wire saw 410 between the sheaves 406 and 404 is substantially orthogonal to the traveling direction of the object W, FIG. 10 (B-2) or ( As shown in B-3), when the tilted state is reached, the length of the rod 310 is adjusted by the hydraulic cylinder 308. Thereby, the tension | tensile_strength of the wire saw 410 can be kept constant and the effect similar to the Example mentioned above can be acquired.

In addition, this invention is not limited to the Example mentioned above, A various change can be added in the range which does not deviate from the summary of this invention. For example, the following are also included.
(1) The shapes, dimensions, and materials shown in the above embodiments are examples, and may be changed as appropriate.
(2) In the first embodiment, the other sheave is moved up and down while one sheave is stopped. However, the wire saw 68 is driven by driving the lifting speed or the lifting amount different between the left and right sheaves. An inclination may be provided.
(3) The elevating mechanism, various transmission mechanisms, and the rotational drive mechanism shown in the above embodiment are merely examples, and the design may be changed as appropriate so as to achieve the same effect. Similarly, in the first embodiment, the hydraulic cylinder 74 is used for the tension mechanism, but this is also an example, and the design may be changed as appropriate so that the same effect can be obtained, such as using a pneumatic cylinder. Various transmission mechanisms such as a chain and a belt may be used in place of the gear shown in the above embodiment. Moreover, the moving direction of the sheave by the tension mechanism shown in the embodiment is also an example, and the main surface of the sheave is in the same plane as the main surface of the other sheave and does not interfere with the processing of the object W. If so, it may be moved in any direction.
(4) The time for lowering each sheave in the cutting step shown in the above embodiment is also an example, and can be changed as necessary.

(5) In the first embodiment, the sheaves 60 and 64 move up and down along the columns 16 and 18, but the sliders 26 and 28 reciprocate along the horizontal plane, and the wire saw 68 rotates in the horizontal plane. It is good also as a structure which cut | disconnects the target object W in the horizontal direction with the wire saw 68. FIG.
(6) Also in the first embodiment, the left and right sheaves 60 and 64 are simultaneously lowered at the same speed, so that it is possible to perform processing with a horizontal wire saw as in the conventional case. The same applies to Example 3.
(7) The moving direction of the sheaves and the number of sheaves shown in the above embodiments are merely examples, and may be changed as appropriate. The arrangement of the sheave and the arrangement of the object shown in the above embodiment are also examples, and the object may be arranged inside the wire saw. Which of the wire saw and the object to move is a relative problem and may be set as appropriate. For example, in the third embodiment, the object W is moved with respect to the sheaves 280 to 286. However, this is also an example. The object W is fixed, and the sheaves 280 to 286 rotate the wire saw 290. However, it may be configured to move relative to the object W.
(8) In the above embodiment, the object W is cut. However, this is also an example, and the present invention can be applied to processing other than cutting.

  According to the present invention, the pair of support means disposed on both sides of the object is provided with a pair of sliders that can reciprocate in the axial direction of the support means or in a direction substantially perpendicular to the support means. At least one or more sheaves are rotatably supported on each of the sliders, a wire saw is mounted on the plurality of sheaves, and one of the sheaves is rotated by a rotational drive mechanism. Then, the pair of sliders can be driven independently by a reciprocating drive mechanism so that the moving speed or amount of movement of the pair of sliders is different, and the change in the tension of the wire saw that occurs according to the position of the slider is changed. It was decided to keep it constant by the tension mechanism. For this reason, it is possible to process while changing the angle of the wire saw applied to the object, the pressure applied to the object increases, and its position changes gradually, so the processing time of the object is greatly reduced compared to the conventional method. can do. For this reason, it can be applied to the use of a wire saw device for processing stone or concrete.

10: wire saw device 12: base 14: support 16, 18: support 16A, 18A: upper surface 20: beam 22, 24: guide rail 26, 28: slider 30, 32: feed screw 30A, 32A: bevel gear 33, 35: Bearings 34, 36: Nut portions 38, 42: Lifting motors 40, 44: Output shafts 40A, 44A: Bevel gears 46: Brackets 48: Rotating motors 50: Output shafts 50A: Gears 52: Transmission shafts 52A: Gears 54, 56 : Bearing 58: Belt 60, 64: Sheave 62, 66: Cover 68: Wire saw 70: Plate 72: Bottom surface 74: Hydraulic cylinder 76: Rod 78: Connecting tool 80: Long hole 82A, 82B: Rail 90: Movable part 92A, 92B: Rail bearing 94A, 94B: Bearing 96: Shaft 98: Dolly 100, 102: Transmission shaft 100A, 102A: Bevel gear 104: Clutch 110: Lifting motor 112: Output shaft 112A: Bevel gear 114: Transmission shaft 114A, 114B, 114C: Bevel gear 116, 120: Clutch 200: Wire saw device 201: Base 202, 208: Prop 204A, 204B, 210A, 210B: Paul 206, 212: Feed screw 206A, 212A: Bevel gear 214: Beam 216: Lifting motor 218: Output shaft 220: Transmission shaft 222A, 222B: Bevel gear 224A, 224B: Bearings 230, 232: Elevator slider (first slider)
234, 256: guide bars 236A, 236B, 258A, 258B: bearings 238, 260: fixtures 240, 262: horizontal slider (second slider)
240A, 262A: upper surface 240B, 240C, 262B, 262C: end portions 242, 264: fixed base 244, 266: reciprocating motors 246, 268: output shafts 246A, 268A: gears 248, 270: feed screws 248A, 270A: gears 250, 252, 272, 274: bearings 254, 276: belts 280, 282, 284, 286: sheaves 280A, 282A, 284A, 286A: shafts 280B, 282B, 284B, 286B: bearings 288: gear 290: wire saw 292: rotation Motor 294: output shaft 296: gear 298: belt 300: tension mechanism 302: movable arm 302A, 302B: end 304A: shaft 304B: bearing 306: fixed member 308: hydraulic cylinder 310: rod 312: rotating connector 320A , 32 B: Rail 322: carriage 400: a wire saw device 402, 404, 406: sheave 410: wire saw W: object

Claims (7)

A pair of support means disposed on both sides of the object;
A pair of sliders that are provided in each of the pair of support means and are capable of reciprocating along the axial direction of the support means or in a direction substantially orthogonal to the support means;
A reciprocating drive mechanism for independently driving the pair of sliders;
A plurality of sheaves rotatably supported by at least one of each of the pair of sliders;
A wire saw mounted on the plurality of sheaves;
A rotation drive mechanism for rotating any of the plurality of sheaves;
A tension mechanism for keeping the tension of the wire saw constant;
With
The wire saw device, wherein the object is processed by the reciprocating drive mechanism such that the moving speed or moving amount of the pair of sliders is different. When the pair of sliders reciprocate along the axial direction of the support means,
The tension mechanism is
A movable part movable in a direction perpendicular to the reciprocating direction of the slider with respect to any one of the pair of sliders;
Guide means for moving the movable part along the slider;
A movable part driving means for adjusting the position of the movable part so as to drive the movable part and keep the tension of the wire saw constant;
Have
The wire saw device according to claim 1, wherein a sheave is rotatably supported by the movable part. When the pair of sliders reciprocate along the axial direction of the support means,
The reciprocating drive mechanism is
Two motors respectively provided for the pair of sliders;
A transmission mechanism for transmitting the outputs of the two motors to the sliders;
The wire saw device according to claim 1 or 2, characterized by comprising: The reciprocating drive mechanism is
A transmission shaft provided between the output shafts of the two motors;
A clutch provided on the transmission shaft;
The wire saw device according to claim 3, comprising: When the pair of sliders reciprocate along the axial direction of the support means,
The reciprocating drive mechanism is
A motor,
A transmission shaft for transmitting the output of the motor to the pair of sliders;
A transmission mechanism for transmitting the output of the motor to the slider via the transmission shaft;
A gear for transmitting the output of the motor to the transmission shaft;
A pair of clutches provided between the transmission shaft and the gear;
The wire saw device according to any one of claims 1 to 3, wherein The pair of sliders are
A pair of first sliders capable of reciprocating along the axial direction of the pair of support means;
A pair of second sliders attached to the first slider and capable of reciprocating in a direction substantially perpendicular to the axial direction of the pair of support means, wherein the plurality of sheaves are rotatably supported; ,
Composed by
The reciprocating drive mechanism is
A first reciprocating drive mechanism for driving the pair of first sliders;
A second reciprocating drive mechanism for driving the pair of second sliders;
Consists of
The wire saw device according to claim 1, wherein the object is processed by the second reciprocating drive mechanism so that the moving speed or the moving amount of the pair of second sliders is different. The tension mechanism is
A movable part that is movable in a direction substantially perpendicular to the axial direction of the pair of support means with respect to any one of the pair of second sliders, and in which one sheave is rotatably supported;
A movable part driving means for adjusting the position of the movable part so as to drive the movable part and keep the tension of the wire saw constant;
Have
The wire saw device according to claim 6, wherein the sheave supported by the movable portion moves in the same plane as a main surface of another sheave.

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