JP2001030103A - Boring device for fluid transporting pipe - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress an action of an overload on a motive power part or a transmission system even abnormal cutting resistance occurs in a boring cutter, to simplify and miniaturize whole the device, and to suppress the deformation of a shaft or a bearing part following long-term use. SOLUTION: A friction transmitting means B for imparting rotating and sending force to a lrinven shaft 10 with the rotation, in a condition of pressedly fvinging the means B into contact with the outer peripheral surface of the shaft 10, is provided on a power transmission system to the shaft 10 rotatable and slidable intergrally with a main shaft 11. Plural rollers 12 of the means b are provided on a casing 9 in conditions of nipping and holding the shaft 10 from the outer side in a diameter direction, and being movable in a far and near direction relatine to the shaft 10. And uniform pressure contacting means G is provided which uniformly or nearly uniformly pressure contact the respective rollers 12 with the outer peripheral surface of the shaft 10, interlocking with pressure contacting operation to the rotation axial core Y side of a part of the rollers 12.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drilling device used for forming a branch hole or the like in a pipe wall of a fluid transport pipe such as a water pipe or a gas pipe.

[0002]

2. Description of the Related Art In a conventional drilling device for a fluid transport pipe, FIG.
As shown in FIG. 8, a main shaft 102 on which a drilling cutter for forming a through hole in a pipe wall of a fluid transport pipe is mounted on a casing 101 so as to be relatively slidable and relatively slidable in the direction of the axis of the rotation axis. The main spindle 102 is provided inside the main spindle 102.
02, a first feed shaft 103 connected only to a relative rotation with respect to a front end portion (feed side end portion) of the first feed shaft 10;
3 and a second feed shaft 104 having a female screw 104a screwed to a male screw 103a formed on the outer peripheral surface of the rear end (return end) of the casing 101. A manual handle 105 is fixed to the rear end of the second feed shaft 104 projecting from the second feed shaft 104. In addition, the spindle 10
The drive cylinder shaft 106, which is spline-fitted to the outer peripheral surface of the rear end portion of the drive cylinder shaft slidably in the direction of the axis of rotation, is supported on the casing 101 so as to be rotatable only.
6, a worm 10 of a drive input shaft 107 linked to a driving unit such as an electric motor or an engine (not shown).
8 and a spur gear 111 externally fixed to the rear end of the second feed shaft 104 from a staggered gear 110 externally fixed to the rear end of the drive cylinder shaft 106. In the middle of the power transmission system, an automatic feed state in which the rotational force on the driving unit side is transmitted to the second feed shaft 104 and a manual feed state in which the rotation operation of the second feed shaft 104 by the manual handle 105 is allowed. The clutch 112 which can be switched freely is provided (for example, an actual open flat 7-24).
507). When the rotational force of the driving unit is transmitted to the driving cylinder shaft 106 while the clutch 112 is being operated to the automatic feed state, the driving cylinder shaft 10
Spindle 1 which is slidably fitted with spline 6
02 is driven and rotated, and at the same time, the second feed shaft 10 which is interlocked with the drive cylinder shaft 106 via the clutch 112.
4 is driven and rotated, the first feed shaft 103 screwed and linked to the second feed shaft 104 is extended, and the main shaft 102 is fed while being driven and rotated.

[0003]

In the conventional drilling device for a fluid transport pipe, the power transmission system from the drive cylinder shaft 106 to the main shaft 102, which is interlocked with the prime mover, includes a rotary transmission system for applying a rotational force to the main shaft 102. The two feed shafts 103 and 104 that are branched into a feed transmission system that applies a feed force to the main shaft 102 and that constitute the feed transmission system are set to a length range corresponding to the maximum operation stroke of the drilling cutter. It is necessary to fit them in a stretchable manner over the entire shaft, and they must be assembled in the main shaft 102 in a concentric state. Further, when an abnormal cutting resistance is generated in the drilling cutter, not only an overload acts on the driving part, but also deformation and breakage of the components of the rotary transmission system and the components of the feed transmission system are likely to occur.

The present invention has been made in view of the above situation, and its main problem is that even when abnormal cutting resistance occurs in the drilling cutter, an overload acts on the driving portion and the transmission system. Can be suppressed, and the entire apparatus can be simplified and downsized.
Even when a work valve or the like is interposed between the outer surface of the pipe wall of the fluid transport pipe and the mounting portion of the drilling device, a fluid that can be easily and advantageously reduced in cost without changing the main configuration of the drilling device. It is an object of the present invention to provide a perforation device for a transport pipe.

[0005]

SUMMARY OF THE INVENTION A feature of the drilling device for a fluid transport pipe according to the present invention resides in that a power is applied to a passive shaft which is slidably supported on a casing and slidably in the direction of the axis of the rotating shaft. The transmission system is provided with friction transmission means for applying a rotational force and a feed force in the direction of the axis of the rotating shaft to the driven shaft along with the driving rotation in a state of being pressed against the outer peripheral surface of the passive shaft. The main shaft on the side on which the drilling cutter for forming a through hole is formed in the pipe wall of the fluid transport tube is relatively slidably fitted in the direction of the rotation axis, which is the direction of relative rotation and cutter feeding. , Between the main axis and the passive axis,
The present invention is characterized in that clamping means is provided which can be switched between an integrated state in which the relative rotation and relative sliding of the two are prevented and a free state in which the relative rotation and relative sliding of the two are permitted. According to the characteristic configuration, the frictional transmission means provided in the power transmission system to the passive shaft allows the casing to rotate and slidably support the rotational force and the feed force in the direction of the rotational axis with respect to the passive shaft supported slidably. Since it can be provided at the same time, unlike the conventional drilling device, the power transmission system to the main shaft does not need to be branched into a rotary transmission system and a feed transmission system, which simplifies the transmission structure and reduces transmission components. The points can be reduced. Moreover, since this friction transmission means transmits by utilizing the frictional force generated by pressing against the outer peripheral surface of the passive shaft, when abnormal cutting resistance is generated in the drilling cutter, slip occurs in the friction transmission portion. In addition, it is possible to suppress the overload from acting on the drilling cutter and the power transmission system. Further, at the time of drilling work, by switching the clamping means provided between the main shaft and the passive shaft, the frictional transmission means is provided by integrating the main shaft and the passive shaft to prevent relative rotation and relative sliding. The rotational force and the feed force applied to the passive shaft are transmitted to the drilling cutter via the main shaft. As a result, the cutter for punching is fed at a predetermined feed amount while being driven and rotated at a predetermined rotation speed set in advance, thereby suppressing breakage of the cutter due to careless cutting or the like as in the case of manual feeding. The through hole can be reliably formed in the pipe wall of the fluid transport pipe. Further, at the time of setting before the start of the drilling operation, by switching the clamp means to the free state, the main spindle is moved until the tip of the drilling cutter comes into contact with or close to the pipe wall of the fluid transport pipe with respect to the passive shaft. Can be freely pushed in, the feed amount due to the driving force is reduced while the sliding stroke of the main shaft with respect to the passive shaft is large, and the transmission mechanism including the friction transmission means to the passive shaft is rotated. It is easy to configure compactly in the core direction. For example, even when a work valve is interposed between the outer surface of the pipe wall of the fluid transport pipe and the mounting portion of the drilling device, there is no need to change the maximum feed amount by the driving force, and only the stroke corresponding to the entire length of the work valve is required. It is only necessary to secure a sliding stroke for manual operation of the main shaft with respect to the passive shaft. Therefore, even when an abnormal cutting resistance occurs in the drilling cutter, it is possible to suppress the overload from acting on the driving unit and the transmission system,
In addition, the entire device can be simplified and downsized, and the main configuration of the drilling device is changed even when a work valve or the like is interposed between the outer wall surface of the fluid transport pipe and the mounting portion of the drilling device. Therefore, it is possible to easily and advantageously cope with the cost.

According to a second aspect of the present invention, there is provided a drilling device for a fluid transport pipe, wherein the transmission state switching means for switching the friction transmission means between a transmission state and a non-transmission state in which pressure contact with the outer peripheral surface of the passive shaft is released. It is in the point provided. According to the above configuration, when the transmission state switching means is switched from the transmission state to the non-transmission state, the drive rotation and the drive feed of the passive shaft can be stopped, and the passive shaft can slide freely on the casing. Since the operation can be performed, the positioning of the passive shaft at the time of setting before the start of the drilling operation, or the returning operation of the passive shaft after the end of the drilling operation can be performed quickly and easily.

A feature of the drilling device for a fluid transport pipe according to a third aspect of the present invention is that a stopper means for preventing the main shaft from moving to the return side is provided on the casing so that the stopper can be released. . According to the above-mentioned characteristic configuration, at the time of drilling work in a non-disrupted flow state in which the transport of the fluid is not stopped, immediately after the through hole is formed in the pipe wall of the fluid transport pipe by the drill cutter, the fluid pressure in the fluid transport pipe is increased. Even when acting on the cutter for drilling, the friction transmission means is pressed against the outer peripheral surface of the passive shaft, so that the main shaft interlocked with the cutter for punching and the passive shaft integrated therewith may slide toward the return side. Absent. In this state, after operating the stopper means to the stopper state to prevent the main shaft from moving to the return side,
The clamp means is operated in a free state, and then the stopper means is operated to release the stopper while paying attention to the return path side of the spindle, and the spindle is returned to the original standby position and slid. Therefore, sudden return sliding of the main shaft in an unintended state due to the fluid pressure in the fluid transport pipe can be avoided.

According to a fourth aspect of the present invention, there is provided a drilling device for a fluid transport pipe, wherein a feed amount setting means for restricting a maximum feed amount of the main shaft to a set feed amount by contacting a casing with the main shaft or the passive shaft. Is provided. According to the above-mentioned characteristic configuration, at the time of setting before the start of the drilling operation, the clamp means is operated in a free state so that the tip of the drilling cutter abuts or approaches the pipe wall of the fluid transport pipe with respect to the passive shaft. After the spindle is pushed in, the feed amount setting means sets the maximum feed amount of the spindle to a set feed amount necessary for drilling while maintaining this pushed state, and then switches the clamp means to an integrated state. When the drilling operation is started in this state, when the maximum feed amount of the spindle reaches the set feed amount set by the feed amount setting unit, the feed amount setting unit contacts the casing to feed the spindle further. Since this can be prevented, the drilling operation can be made more reliable and simpler. In addition, even if the load on the main shaft increases due to the contact between the feed amount setting means and the casing, the load can be absorbed by the slip in the friction transmission portion of the friction transmission means, and the power transmission system can be overloaded. The operation of the load can be suppressed.

According to a fifth aspect of the present invention, there is provided a fluid transport pipe drilling apparatus wherein an extended rotary shaft is detachably attached to an end of the main shaft opposite to a side where a drilling cutter is mounted. The point is that a shaft connecting means for connecting in a core state is provided. According to the above feature, the sliding of the main shaft with respect to the passive shaft depends on the diameter of the fluid transport pipe or the total length of the working valve interposed between the outer surface of the pipe wall of the fluid transport pipe and the mounting portion of the drilling device. Even if it is necessary to increase the stroke, it can be easily dealt with by a simple operation of mounting the extended rotary shaft via the shaft connecting means provided at the end of the main shaft.

The fluid transmission pipe drilling device according to a sixth aspect of the present invention is characterized in that the friction transmission means sandwiches the outer peripheral surface of the passive shaft from a radially outer side and is arranged in a radial direction with respect to the rotation shaft core. And a plurality of rollers arranged at an angle corresponding to a unit feed amount per rotation with respect to an orthogonal plane at which at least one of the rollers is configured as a driving roller. is there. According to the above characteristic configuration, the plurality of rollers disposed at an angle corresponding to the unit feed amount per rotation are pressed against the outer peripheral surface of the passive shaft in a state of being sandwiched from the radial direction, The passive shaft can be firmly supported during the drilling operation by using a roller for simultaneously applying the rotation force and the feed force in the rotation axis center direction to the passive shaft.

A feature of the drilling device for a fluid transport pipe according to claim 7 of the present invention is that the main shaft is inserted and held over a bearing portion of a casing and a boss portion of a passive shaft. According to the above characteristic configuration, the main shaft and the passive shaft have a dual inner / outer structure, and a part of the main shaft can be supported on the casing using the boss portion of the passive shaft. And simplification of the bearing structure.

According to a eighth aspect of the present invention, there is provided a fluid transport pipe piercing device, wherein the casing has a storage space capable of storing a piercing cutter that has returned to a maximum return position, and the fluid transport pipe has a storage space. The present invention is characterized in that a connection tubular body that can be connected in a gas-tight or liquid-tight state to a branch joint connected to a portion corresponding to a perforation through a work valve that can be freely opened and closed is attached. According to the above-mentioned characteristic configuration, when performing a drilling operation, first, a working valve is attached to a branch joint connected to a portion corresponding to the drilling of the fluid transport pipe, and the working valve is attached to a casing of a drilling device. The connecting cylinders are connected in an air-tight or liquid-tight state. Next, while opening and operating the working valve,
Switching the clamp means provided between the main shaft and the passive shaft to a free state, pushing the main shaft against the passive shaft,
The drilling cutter stored in the storage space of the connecting cylinder is moved to a state in which it comes into contact with or close to the pipe wall of the fluid transport pipe through the working valve and the branch joint. When such setting is completed, the clamp means is switched to an integrated state, and a rotational force and a feed force are applied to the passive shaft by the friction transmission means, and the rotational force and the feed force are used for drilling through the main shaft. The predetermined through-hole can be formed in a portion of the pipe wall of the fluid transport pipe that is transmitted to the cutter and that corresponds to the perforation surrounded by the branch joint. When such a piercing process is completed, after the piercing cutter is stored in the storage space of the connecting cylinder, the working valve is closed, and the connecting cylinder of the piercing device is removed from the working valve to complete the piercing operation. . Therefore, the drilling operation can be performed without stopping the fluid transport in the fluid transport pipe, and the drilling cutter can be stored using the connecting cylinder for connecting to the working valve.

According to a ninth aspect of the present invention, there is provided a boring device for a fluid transport pipe, wherein the clamping means comprises:
The passive shaft and the main shaft are integrated with each other by engaging the interlocking cylinder or the passive shaft fixed to the passive shaft in a state of being fitted to the main shaft from a radially outer side with respect to the passive surface formed on the main shaft. A transmission member, an elastic biasing body that moves and biases the transmission member to a disengagement position in which the transmission member is separated radially outward from the maximum rotation locus of the passive surface of the main shaft, and Rotational operation allows the transmission member to be held in the engaged position against the elastic urging force of the elastic urging member, and allows the transmission member to move to the disengaged position by the elastic urging force of the elastic urging member. And an operation mechanism for switching to a free state. According to the above configuration, when the operating mechanism is rotated to be in a free state, the transmission member held in the engagement position is separated from the maximum rotation locus of the passive surface of the main shaft in a radially outward direction. It moves to the release position by the elastic urging force of the elastic urging body, and the passive shaft and the main shaft are relatively rotatable and relatively slidable.
Further, when the operating mechanism is rotated to switch to the integrated state, the transmission member held at the disengaged position is more than the maximum rotation trajectory of the passive surface of the main shaft against the elastic urging force of the elastic urging body. It is moved to the engagement position that has entered radially inward,
The passive shaft and the main shaft rotate and slide integrally. Therefore,
A transmission member that engages the passive surface of the main shaft from outside in the radial direction with the interlocking cylinder or the passive shaft fixed to the passive shaft in a state of being fitted to the main shaft, and biases the transmission member to the disengagement position. Since the elastic biasing body and the operation mechanism that can rotate around the axis of the main shaft are assembled, the whole clamp means is compact while simplifying the switching operation between the free state and the integrated state. Easy to do.

According to a tenth aspect of the present invention, there is provided a fluid transport pipe perforating apparatus characterized in that an annular urethane rubber is mounted on an outer peripheral surface of the roller. According to the above-mentioned characteristic configuration, it is possible to reliably apply a predetermined rotational force and feed force to the passive shaft over a long period of time by utilizing the excellent rebound resilience, wear resistance, and oil resistance of urethane rubber. it can.

According to a eleventh aspect of the present invention, there is provided a fluid transport pipe piercing device, wherein an outer peripheral surface of the roller is formed with an annular concave portion for holding an annular urethane rubber, and is formed in a width direction of the annular concave portion. The point is that the peripheral wall surfaces facing each other are formed as inclined surfaces that are further apart from each other as they go radially outward. According to the characteristic configuration, when the annular urethane rubber attached to the annular concave portion of the roller is pressed against the outer peripheral surface of the passive shaft, the urethane rubber is formed by the peripheral wall surfaces in the inclined posture located on both sides in the width direction of the annular concave portion. Can be suppressed from expanding outward in the width direction (outward in the direction of the roller rotation axis), and the surface pressure between the urethane rubber and the outer peripheral surface of the passive shaft can be increased.

[0016]

DESCRIPTION OF THE PREFERRED EMBODIMENTS [First Embodiment] FIGS.
(D), FIGS. 2 (e) to 2 (g) show a state in which the fluid flows in the fluid transport pipe P without interruption on the pipe wall 1 of the fluid transport pipe P such as a water pipe or a gas pipe. An example of a drilling method for forming a through hole 2 for use is shown, and a branch joint 3 having a posture orthogonal to the pipe axis X of the fluid transport pipe P is provided on an outer peripheral surface of a portion corresponding to the drilling of the fluid transport pipe P. One of the connecting flanges 4B of the working valve 4 having a valve body 4A that can be opened and closed on the connecting flange 3A of the joint 3 for branching, is mounted in an air-tight or liquid-tight state by appropriate mounting means such as welding or bolts. Is fixedly connected in a gas-tight or liquid-tight manner via bolts and nuts, and a drilling cutter 5 is detachably attached to the other connecting flange 4C of the working valve 4 according to the present invention. A connecting flange 69A is airtight or liquidtight through bolts and nuts. In it is fixedly connected. Then, the perforating cutter 5 of the perforating apparatus A is passed through the opened operation valve 4 and the branching joint 3 so that the pipe wall 1 of the fluid transport pipe P is opened.
After moving to the drilling start position in contact with or close to the drilling device, the electric motor M, which is the driving unit of the drilling device A, is driven to apply a driving rotational force and a forced feeding force to the drilling cutter 5 to transport the fluid. A through hole 2 for branching is formed in the pipe wall 1 of the pipe P. When the drilling process is completed, the drilling cutter 5 is returned to the storage position, which is the original standby position, and then the working valve 4 is returned.
The closing operation of the valve body 4A of the drilling device A
Remove.

As shown in FIGS. 3 to 12, the drilling device A of the present invention used in such a drilling method is supported on the casing 9 so as to be rotatable and slidable in the rotation axis Y direction. The rotational force and the feed force in the Y-axis direction are applied to the power transmitting system to the cylindrical shaft-shaped passive shaft 10 with the driving rotation in a state of being pressed against the outer peripheral surface of the passive shaft 10. A friction transmission means B to be provided is provided.
0, the main shaft 11 on which the drilling cutter 5 for forming the through-hole 2 in the pipe wall 1 of the fluid transport pipe P is relatively rotated and rotated in the rotation axis Y direction which is the cutter feeding direction. The main shaft 11 and the passive shaft 10 are slidably fitted to each other, and an integral state for preventing the relative rotation and relative sliding of the two members 10 and 11 and the relative rotation and relative sliding of the two members 10 and 11 are provided. Clamping means C is provided which can be switched to an allowable free state. Further, a transmission state switching means D for switching the friction transmission means B between a transmission state and a non-transmission state in which the pressure contact with the outer peripheral surface of the passive shaft 10 is released is provided, and the casing 9 is provided on the return side of the main shaft 11. A stopper means E for preventing the movement of the shaft is provided so as to be capable of releasing the stopper, and a casing 9 is provided on the main shaft 11 or the passive shaft 10 side.
Feed amount setting means F for regulating the maximum feed amount of the main shaft 11 to a set feed amount by contact with the main shaft 11 is provided.

As shown in FIGS. 3 to 5, the friction transmission means B is provided so as to sandwich the outer peripheral surface of the passive shaft 10 from the radially outward side and to extend in a plane orthogonal to the rotational axis Y in the radial direction. And three rollers 12 arranged at an angle corresponding to a unit feed amount per rotation (or a skew angle θ between the rotation axis of the main shaft 11 and the roller rotation axis). Two of the upper part (the vertical direction changes depending on the mounting posture of the drilling device A with respect to the fluid transport pipe P, but in this embodiment, the description will be made based on the mounting posture of the drilling device A shown in FIG. 1). The driving roller 12 is rotated by the driving force of the electric motor M, and one of the lower portions is configured as a holding roller 12 that can freely move (slope). Also, of the outer peripheral surface of the passive shaft 10, the passive peripheral surface that is the outer peripheral surface of the large-diameter shaft portion is set so that the friction coefficient between each of the rollers 12 to be pressed is an appropriate set friction coefficient. , A surface roughening treatment such as knurling.

The two drive rollers 12 are provided on the casing 9.
Is rotatably supported by a first holding body 13 slidable up and down along the inside, and the pressing roller 12 is
The passive shaft 10 is rotatably supported by a second holder 14 pivotally attached to the lower end of the holder 13 so as to be vertically swingable.
The first drive body 13 and the second support body 14, which are linked to each other so as to be relatively movable in the vertical direction, which is also the radial direction, sandwiching the driving roller 12, the pressing roller 12 and the outer peripheral surface of the passive shaft 10. Is configured to be movable in a vertical direction, which is also a perspective direction, with respect to the pressing roller 1.
In association with the pressing operation of the second rotating shaft core Y, a uniform pressing means G for pressing the rollers 12 uniformly or almost uniformly to the outer peripheral surface of the passive shaft 10 is provided.

The first holding member 13 and the second holding member 1
And the friction transmission means B including the uniform pressure contacting means G and the later-described speed reduction mechanism 22 are configured as one unit by linking the passive shaft 10 with the movable shaft 4 so as to be relatively movable in the radial direction. I have. Since the unit feed amount per rotation is fixedly set to the set feed amount for each roller 12 provided in the unitized friction transmission means B, when the unit feed amount per rotation is changed, Means that a plurality of units of friction transmission means B having different unit feed amounts per rotation of the roller 12 are manufactured, and the friction transmission means B is replaced in units of units according to the drilling operation conditions.

The uniform pressure-contacting means G is substantially gate-shaped when viewed in the direction of the rotation axis Y and is linked to the passive shaft 10 so as to be relatively movable in the vertical direction in such a manner as to surround a part of the outer peripheral surface of the passive shaft 10. The second body 13 is substantially flat U-shaped when viewed from the body 13 and the rotation axis Y direction.
A holding member 14 is provided. Between the first holding member 13 and the casing 9, the first holding member 13 is moved upward by the two drive rollers 12 supported by the first holding member 13 and separated from the passive shaft 10. The elastic biasing mechanism 16 for biasing is provided,
As the pressing roller 12 supported by the second holding member 14 is pressed against the outer peripheral surface of the passive shaft 10, the driving roller 12 supported by the first holding member 13 is pressed by the elastic urging mechanism 1.
6 is provided with an operating mechanism 17 that presses against the outer peripheral surface of the passive shaft 10 against the elastic biasing force of 6, and further moves the second holding body 14 toward the passive shaft 10 by the elastic force. An elastic biasing body 15 for biasing is provided.

The first holding member 13 includes a driving roller 12
The front holding plate 13A and the rear holding plate 13 which are arranged opposite to each other in the rotation axis Y direction at an interval corresponding to the mounting space of
B and these two holding plates 13A, 13A.
B, the driving rotation shaft 1 of each driving roller 12
8 is rotatably mounted via a bearing 19, an input shaft 21 that can be connected to the output shaft 20 of the electric motor M in an integrally rotating state, and a power of the input shaft 21 on the front holding plate 13 </ b> A. And a speed reduction mechanism 22 that transmits the driving force to the drive rotation shaft 18 of the drive roller 12.

The speed reduction mechanism 22 includes a transmission case 23 provided between the front holding plate 13A and the inner surface of the casing 9.
And two transmission shafts 24 and 25 parallel to the input shaft 21 and both drive rotation shafts 18 over the front holding plate 13A.
Each is rotatably mounted via a bearing 19, and a first reduction gear 27 having a large diameter meshing with an input gear 26 of an input shaft 21 and a second reduction gear having a small diameter are provided on an upper first transmission shaft 24. The second transmission shaft 25 on the lower side is provided with a third reduction gear 30 that meshes with the passive gear 29 of both drive rotation shafts 18 and the second reduction gear 28 of the first transmission shaft 24. It is configured to be fastened. When the output shaft 20 of the electric motor M is driven and rotated, the driving torque is applied to the input shaft 21, the input gear 26, and the first reduction gear 2.
7, the power is transmitted to the drive rotation shaft 18 of each drive roller 12 via the first transmission shaft 24, the second reduction gear 28, the third reduction gear 30, and both passive gears 29.

As shown in FIG. 4, the elastic biasing mechanism 16 includes a total of four spring receiving portions 13a formed on both sides in the width direction of the lower end portions of both holding plates 13A and 13B.
The bottom wall 9b of the casing 9 opposed to the upper and lower sides of the casing 9
And compression receiving springs 9a mounted between the four spring receiving portions 9a formed at four positions.
The upper surface of the holding body 13 is configured to move and bias upward to a state where the upper surface contacts the inner surface of the ceiling wall 9 c of the casing 9.

One end of the second holding member 14 in the longitudinal direction is
As shown in FIG. 4, a support shaft 32 that is parallel to the rotation axis Y and spans a lower end of one of the holding plates 13 </ b> A and 13 </ b> B of the first holding body 13 that is located at one end in the lateral width direction.
And the other end in the longitudinal direction of the second holding member 14 is mounted on an eccentric cam 36 of an operation mechanism 17 described later. 2
A rotation support shaft 33 of the press roller 12 is rotatably mounted via a bearing 19 in a mounting hole 14 a formed in the center of the holding member 14 in the longitudinal direction and penetrating in the vertical direction.

As shown in FIGS. 3 and 4, the operating mechanism 17 penetrates through a rear side wall 9d of the casing 9 through an operation shaft 35 rotatable around an axis parallel to the rotation axis Y. The pressing roller 12 is mounted on the inner shaft of the operation shaft 35 at a position vertically opposed to the lower surface of the other end in the longitudinal direction of the second holding member 14.
Over a range from a transmission state in which the outer peripheral surface of the passive shaft 10 is pressed to a non-transmission state in which the pressed state is released, in other words, a non-transmission state in which the outer peripheral surface of the passive shaft 10 is separated downward.
An eccentric cam 36 for vertically swinging the holding body 14 around the support shaft 32 is fixed, and an operation tool 37 is attached to an outer shaft portion of the operation shaft 35.

In the operating mechanism 17, when the operating tool 37 is operated to rotate the eccentric cam 36 from the non-transmission state to the transmission state, the pressing roller 12 presses against the outer peripheral surface of the passive shaft 10 in the middle. Further, with the subsequent rotation operation, the second holding member 14 moves the pressing roller 12 and the passive shaft 10
As shown in FIG. 4, the support shaft 32 swings counterclockwise so that the support shaft 32 is displaced downward with the contact point with the outer peripheral surface of the support shaft as a fulcrum. With the swing in the counterclockwise direction, the first holding body 13
The whole is moved downward, which is also on the rotation axis Y side, while being slid and guided by the inner surface of the casing 9 against the elastic urging force of the compression coil spring 16, and the driving roller 12 supported by the first holding body 13 is driven passively. It is pressed against the outer peripheral surface of the shaft 10. The drive roller 12 supported by the first holding member 13 rotates the rotation shaft until the operation force of pressing the pressing roller 12 against the passive shaft 10 by the operation tool 37 and the elastic restoring force of the compression coil spring 16 are balanced. Since the roller 12 moves toward the core Y and is pressed against the outer peripheral surface of the passive shaft 10, each roller 12 can be uniformly or almost uniformly pressed against the outer peripheral surface of the passive shaft 10.

As shown in FIG. 4, the elastic biasing member 15 is provided between a concave portion 14b formed on the lower surface of the other end of the second holding member 14 in the longitudinal direction and an eccentric cam 36 of the operating mechanism 17. It is composed of a compression coil spring interposed. More specifically, one end of a bolt 53 is fixed to the pressure receiving piece 52 abutting on the eccentric cam 36, and the bolt 53 is screwed into the recess 14b by a nut 54 screwed to the other end thereof. The compression coil spring 15 is mounted between the seat plate 55 and the pressure receiving piece 52. Then, a return, an operation error, or the like due to vibration or the like of the operation mechanism 17 occurs,
Even when the pressing force of the pressing roller 12 supported by the second holding member 14 against the passive shaft 10 is loosened (the pressing force is reduced), the elastic force of the compression coil spring 15 provided in the operating mechanism 17 is provided. As a result, the pressing roller 12 on the second holding body 14 is pressed against the outer peripheral surface of the passive shaft 10, so that the pressing roller 12 on the second holding body 14 and the driving roller 12 on the first holding body 13 are It is possible to maintain a pressure-contact state in which transmission is possible with respect to the outer peripheral surface of the shaft 10, and it is possible to reliably apply the predetermined rotational force and the feed force to the passive shaft 10.

The operating mechanism 17 of the uniform pressing means G
The above-mentioned transmission state switching means D for switching the friction transmission means B between the transmission state and the non-transmission state is also configured, and the outer peripheral surface of each roller 12 is provided on the outer peripheral surface of each roller 12 as shown in FIGS.
As shown in FIG. 3, an annular concave portion 12a for holding an annular urethane rubber 40 is formed, and, among the rollers 12, peripheral wall surfaces 12b opposed to each other in the width direction of the annular concave portion 12a (the direction of the axis of rotation of the roller). However, the inclined surfaces are configured such that they are separated from each other toward the radially outward side. In addition, by utilizing the excellent rebound resilience, wear resistance, and oil resistance of the urethane rubber 40, it is possible to reliably apply a predetermined rotational force and feed force to the passive shaft 10 for a long period of time. Not
When the annular urethane rubber 40 attached to the annular concave portion 12a of the roller 12 is pressed against the outer peripheral surface of the passive shaft 10,
The peripheral wall surfaces 12b in the inclined posture located on both sides in the width direction of the annular concave portion 12a can suppress elastic deformation of the urethane rubber 40 bulging outward in the width direction.
The surface pressure between the zero and the outer peripheral surface of the passive shaft 10 can be increased.

As shown in FIGS. 6 to 8, the clamping means C is provided at two places in the circumferential direction of the
1a is cut and formed on each passive surface 11a.
A large number of V-shaped engaging grooves 11b are formed at a constant pitch in the direction, and the passive shaft 10 is externally fitted to the main shaft 11.
Interlocking cylinder 45 screwed into
A pair of transmission members 46 that engage the engaging grooves 11b of both the passive surfaces 11a of the main shaft 11 from the outside in the radial direction, thereby bringing the passive shaft 10 and the main shaft 11 into an integrated state.
An elastic urging body 47 for urging the two transmission members 46 to move to a disengaged position in which the two transmission members 46 are separated radially outward from the maximum rotation locus of the passive surface 11a of the main shaft 11; The two transmission members 46 are resiliently biased by
The operating mechanism 48 switches between an integrated state in which the elastic member 47 is held at the engagement position against the elastic urging force and a free state in which the transmission member 46 is allowed to move to the disengaged position by the elastic urging force of the elastic urging member 47. And is assembled.

The elastic urging member 47 includes a pair of transmission members 4.
6 is formed by a pair of arcuate spring wires engaged and held over the pair 6, and the pair of transmission members 46 are made to have a diameter larger than the maximum rotation locus of the passive surface 11a of the main shaft 11 by the elastic restoring force of the two spring wires 47. It is configured to bias the movement to a position separated outward in the direction.

The operating mechanism 48 includes an operating cylinder 49A which is rotatably fitted in the inner peripheral surface of the interlocking cylinder 45 so as to freely rotate.
And an annular operating plate 49B extending from one end of the operating cylinder 49A along the end surface of the interlocking cylinder 45, of two operating members 49A in the circumferential direction of the operating cylinder 49A. Each of them has a concave holding portion 49a for holding both transmission members 46 so as to be relatively movable only in the radial direction, and is formed on the inner peripheral surface of the interlocking cylinder 45 and in the circumferential direction.
At each of the portions deviated by 80 degrees, the two transmission members 46 are engaged at the engagement positions (in an integrated state) against the elastic urging force of the two spring wires 47.
And a second cam surface 45c that allows the transmission members 46 to move to the disengaged position (free state) due to the elastic restoring force of the spring wires 47, and that the first cam surface 45b is continuously formed. The operation plate 49B of the operation member 49 includes
The engagement with the arc-shaped long hole 45a formed on the end surface of the interlocking cylinder 45 restricts the rotation operation range of the operation member 49 around the rotation axis to the range between the engagement position and the disengagement position. The control pin 50 is provided.

During the drilling operation, the operating member 49 of the clamping means C provided between the main shaft 11 and the passive shaft 10 is switched to prevent relative rotation and relative sliding between the main shaft 11 and the passive shaft 10. In this case, the rotational force and the feed force applied to the passive shaft 10 by the friction transmission means B are transmitted to the drilling cutter 5 via the main shaft 11. As a result, the punch 5 is fed at a predetermined feed amount while being driven and rotated at a predetermined rotation speed set in advance, so that the cutter tip is damaged due to an inadvertent cutting or the like as in the case of manual feed. The through hole 2 can be reliably formed in the pipe wall 1 of the fluid transport pipe P while suppressing the pressure.
At the time of setting before the start of the drilling operation, the operating member 49 of the clamping means C is switched to the free state so that the tip of the drilling cutter 5 is moved to the pipe wall 1 of the fluid transport pipe P with respect to the passive shaft 10. Since the spindle 11 can be freely pushed into the contacting or approaching drilling start position, the feed amount by the driving force is reduced while the sliding stroke of the spindle 11 with respect to the passive shaft 10 is increased, and the friction transmission is performed. The transmission mechanism including the means B to the passive shaft 10 can be easily made compact in the rotation axis Y direction. Further, as in the present embodiment, the branching joint 3 attached to the outer surface of the pipe wall 1 of the fluid transport pipe P and the connecting flange 69A of the drilling device A.
Even when the working valve 4 is interposed between the working valve 4 and the working valve 4, there is no need to change the maximum feed amount by the friction transmission means B, and the stroke corresponding to the sum of the total length of the working valve 4 and the flow path length in the branch joint 3 It is only necessary to secure a sliding stroke for manual operation of the main shaft 11 with respect to the passive shaft 10 by the amount.

In this embodiment, in order to secure a sliding stroke for manual operation of the main shaft 11 with respect to the passive shaft 10, as shown in FIG. Is provided at the rear end located on the opposite side with a shaft connecting means 42 for connecting the extended rotary shaft 41 in a detachable and concentric manner. The shaft connecting means 42 includes a female screw 42 a formed at the rear end of the main shaft 11 and a male screw 42 b formed at the front end of the extended rotary shaft 41. If necessary, the rear end of the main shaft 11 and the front end of the extended rotary shaft 41 may be secured by a pin or the like to prevent the rear end from being screwed.

As shown in FIGS. 3, 9, and 10, the stopper means E is provided with an arm 5 fixed to the casing 9.
8 is fixed to a distal end portion of a holder 59 having a cylindrical shape through which the main shaft 11 can be inserted, and a circumferential portion of which is cut out in a slit shape along the rotation axis Y direction. Connecting pieces 59a,
A tightening screw shaft 61 with an operating lever 60 for elastically deforming the holder 59 to the reduced-diameter side until the main shaft 11 is clamped and held non-slidably is provided over 59b. The fastening screw shaft 61 is inserted from one connecting piece 59a side, and then screwed into a female screw formed on the other connecting piece 59b.

In the drilling operation in a non-disrupted flow state where the transportation of the fluid is not stopped, immediately after the through hole 2 is formed in the pipe wall 1 of the fluid transport pipe P by the drill cutter 5, the fluid transport pipe P Is applied to the cutter 5 for drilling, the main shaft 11 interlocked with the cutter 5 and the passive shaft integrated therewith because the friction transmission means B is pressed against the outer peripheral surface of the passive shaft 10. 10 does not slide to the return side. In this state, after the stopper means E is operated in the stopper state to prevent the movement of the main shaft 11 to the return side, the clamp means C is operated in the free state, and thereafter, while paying attention to the return path side of the main shaft 11, The stopper means E is gradually released from the stopper so that the return speed of the main shaft 11 becomes an appropriate speed, and the main shaft 11 is returned and slid to the original standby position at an appropriate return speed.

The feed amount setting means F is provided in FIG. 11 and FIG.
When the main shaft 11 is moved by the set feed amount by the friction transmission means B, the front end face of the interlocking cylinder 45 of the clamp means C is moved from the rotation axis Y direction to the rear wall 9d of the casing 9 as shown in FIG. A scale 66 for setting the maximum feed amount is formed on the outer peripheral surface of a shaft portion of the passive shaft 10 that protrudes outside from the casing 9 while being configured to also serve as the stopper surface 65 that comes into contact with the stopper shaft 65. ing. Then, at the time of setting before the start of the drilling operation, the clamp means C is operated in a free state so that the tip of the drilling cutter 5 contacts or comes close to the pipe wall 1 of the fluid transport pipe P with respect to the passive shaft 10. After the spindle 11 has been pushed down to
As shown in the figure, the main shaft 11 is pushed into the pushing end position so that the distance L between the rear wall 9 d of the casing 9 and the surface facing the stopper surface 65 of the interlocking cylinder 45 becomes the maximum feed amount of the main shaft 11. The passive shaft 10 is slidably adjusted with respect to the casing 9 while looking at the graduation 66. After the setting of the maximum feed amount of the spindle 11 by the feed amount setting means F is completed, the clamp means C is switched to an integrated state. Therefore, as shown in FIG. 12, when the maximum feed amount of the spindle 11 reaches the set feed amount set by the feed amount setting means F, the front end face of the interlocking cylinder 45 of the clamp means C is used. The configured stopper surface 65 is
Since it can contact the rear side wall portion 9d to prevent further feeding, it is possible to ensure and facilitate the drilling operation. In addition, the stopper surface 6 of the feed amount setting means F
Even if the load on the passive shaft 10 and the main shaft 11 increases due to the contact between the casing 9 and the rear wall portion 9d, the load can be absorbed by the slip in the friction transmission portion of the friction transmission means B. In addition, it is possible to suppress an overload from acting on the power transmission system.

A bearing portion 9e for rotatably and slidably supporting a cylindrical shaft 10 is formed on a rear wall portion 9d of the casing 9, and a front wall portion 9f of the casing 9 has a front wall portion 9f. A bearing 9g is formed to rotatably and slidably support the front end of the main shaft 11 inserted and held in the boss 10a on the small diameter side of the passive shaft 10. Further, on the front surface of the front side wall 9f of the casing 9, A connection space that can store the drilling cutter 5 that has returned to the maximum return position, and that can be connected to the connection flange portion 4C of the working valve 4 in a gas-tight or liquid-tight state via a bolt or the like. A connecting cylinder 69 having a portion 69A is attached in an airtight or liquid tight state via a bolt or the like.

As shown in FIG. 5, the casing 9 is composed of divided casings 9A and 9B that can be divided into two parts in the front-rear direction (the direction of the rotational axis Y). The first holding member 1 of the unitized friction transmission means B is separated and disassembled in the axis Y direction.
The third and second holders 14 are configured to be detachable from the casing 9. Since the first holding body 13 and the second holding body 14 of the unitized friction transmission means B can be collectively removed from the casing 9, maintenance of the friction transmission means B and the uniform pressure contact means G can be easily performed. Not only can it be performed, but also, for example, when the unit feed amount per rotation is changed according to various perforation conditions such as the pipe diameter and the material of the fluid transport pipe P, the unitized friction with respect to the casing 9 is obtained. The replacement can be performed in units of the transmission means B, and the replacement work accompanying the change in the unit feed amount can be performed efficiently and easily as compared with the case where the roller 12 itself is replaced.

The drilling cutter 5 is composed of a center drill 5A and a cylindrical cutter 5B, and a screw type for detachably mounting the drilling cutter 5 on the tip of the main shaft 11. A mounting portion 11A is formed.

[Second Embodiment] FIGS. 13 to 15 show an integrated state in which the relative rotation and relative sliding of the main shaft 11 and the passive shaft 10 are prevented, and the relative rotation and relative sliding of both the main shaft 11 and the passive shaft 10 are permitted. Another embodiment of the clamping means C which can be switched to a free state in which a flat passive surface 11a is cut and formed at two locations in the circumferential direction of the main shaft 11, and each passive surface 1a is cut.
1a, a large number of V-shaped engaging grooves 11b are formed at a constant pitch in the direction of the rotation axis Y, and are screwed to the passive shaft 10 while being externally fitted to the main shaft 11 and pulled out with screws 70 or the like. On the interlocking cylinder 71 fixed and fixed, both passive surfaces 11a of the main shaft 11 are provided.
A pair of transmission members 72 for engaging the passive shaft 10 and the main shaft 11 in an integrated state by engaging with the engagement grooves 11b from the outside in the radial direction, respectively.
An elastic urging member 73 for moving and urging to a disengaged position radially outwardly separated from the maximum rotation locus of the passive surface 11a of
By the rotation operation of the main shaft 11 around the axis, the two transmission members 72 are held in the engagement position against the elastic urging force of the elastic urging member 73, and the transmission is performed by the elastic urging force of the elastic urging member 73. An operation mechanism 74 for switching to a free state in which the member 72 is allowed to move away from the disengagement position is assembled. The elastic biasing member 73 is constituted by a pair of arc-shaped spring wires engaged and held over the pair of transmission members 72, and the pair of transmission members 72 are rotated by the elastic restoring force of both spring wires 73. It is configured to move and bias to a position radially outwardly separated from the maximum rotation locus of the passive surface 11a of the eleventh passive surface 11a.

The operating mechanism 74 allows the two transmission members 72 to move relative to each other only in the radial direction at two circumferential positions of the cylindrical portion of the interlocking cylindrical body 71 protruding from the end surface of the passive shaft 10. The holding portion 71a for holding is formed to penetrate, and the inner circumferential surface of the rotary operation ring 75 rotatably fitted to the interlocking cylinder 71, and 180 ° in the circumferential direction.
The first cam surface 75a holding the two transmission members 72 in the engaged position (in an integrated state) against the elastic urging force of the two spring wires 73, and the elasticity of the two spring wires 73 A second cam surface 75b that allows the two transmission members 72 to move to the disengaged position (free state) by the restoring force is continuously formed, and the rotation operation ring 75 is screwed to the end surface of the interlocking cylinder 71. An arcuate shape that restricts the rotation operation range of the rotation operation ring 75 around the rotation axis Y to the range between the engagement position and the disengagement position by engagement with the fixed fixing pin 76 which is also used as a stopper. It is formed by forming a long hole 71b. Since other configurations are the same as those described in the first embodiment, the same components are denoted by the same reference numerals as those in the first embodiment, and description thereof will be omitted.

[Third Embodiment] FIGS. 16 and 17 show an integrated state in which the main shaft 11 and the passive shaft 10 prevent relative rotation and relative sliding, and allow relative rotation and relative sliding of both the main shaft 11 and the passive shaft 10. Another embodiment of the clamping means C which can be freely switched to a free state is shown, in which flat passive surfaces 11a are cut and formed at two circumferential positions of the main shaft 11, and each passive surface 11a has A large number of V-shaped engagement grooves 11b are formed at a constant pitch in the direction of the rotation axis Y, and the passive shaft 1
The holding portions 10b penetratingly formed at two locations in the circumferential direction of 0
A pair of transmission members 80 are provided for engaging the passive shaft 10 and the main shaft 11 with each other by engaging radially outward with the engagement grooves 11b of both the passive surfaces 11a of the main shaft 11, respectively. The two transmission members 80 are connected to the passive surface 11 of the main shaft 11.
The two transmission members 80 are elastically attached to each other by an elastic urging body 81 that moves and urges the engagement member to a disengaged position radially outwardly separated from the maximum rotation locus of a. An integrated state in which the urging member 81 is held in the engagement position against the elastic urging force of the urging member 81 and the transmission member 80 by the elastic urging force of the elastic urging member 81
And an operation mechanism 82 for switching to a free state in which a separation movement to a disengagement position is permitted. The elastic biasing member 81 is composed of a pair of arc-shaped spring wires engaged and held over a pair of transmission members 80, and the pair of transmission members 80 are elastically restored by the elastic restoring force of both spring wires 81.
To a position radially outwardly away from the maximum rotation locus of the passive surface 11 a of the main shaft 11.

The operating mechanism 82 is rotatable around the axis of the main shaft 11 on an interlocking cylinder 83 screwed to the passive shaft 10 in a state of being externally fitted to the main shaft 11 and secured by a screw 87 or the like. The rotation transmission ring 84 is attached to each of the portions on the inner peripheral surface of the rotation rotation ring 84 that are deviated by 180 degrees in the circumferential direction. The first cam surface 84a, which is held against the engagement position (integrated state), and the second transmission member 80, which allows the two transmission members 80 to move to the disengagement position (free state) due to the elastic restoring force of both spring wires 81. It is configured by continuously forming the cam surface 84b. The rotation operation ring 84 can be screw-connected to a first rotation operation body 84A having a first cam surface 84a and a second cam surface 84b, and to an outer peripheral surface of the first rotation operation body 84A. A second rotary operating body 84B having an engaging flange 84c for retaining the first rotary operating body 84A in a rotatable manner relative to the connecting flange 83a of the interlocking cylinder 83 during the screw connection. In addition, the first rotation operating body 84A is engaged with an arc-shaped long hole 83b formed on the end surface of the interlocking cylindrical body 83 to rotate the rotation operation ring 84 about the rotation axis. A restriction pin 85 for restricting the range to a range between the engagement position and the disengagement position is provided, and furthermore, an engagement flange portion 84c of the second rotary operation body 84B is provided.
When the rotation operation ring 84 is operated to the engagement position and the disengagement position, the connection flange 83 a
And a compression coil spring 86b which is an example of an elastic urging member for urging the positioning ball 86a to move in the engagement direction. Positioning means 86 is provided. That is, the positioning means 86 is
Are temporarily held at an engagement operation position where they are integrated and a disengagement position where they are free. Since other configurations are the same as those described in the first embodiment, the same components are denoted by the same reference numerals as those in the first embodiment, and description thereof will be omitted.

[Other Embodiments] (1) In the above embodiment, the friction transmission means B is
The passive shaft 10 is composed of a plurality of rollers 12 arranged so as to sandwich the outer peripheral surface from the radially outer side. However, the passive shaft 10 is arranged so as to sandwich the outer peripheral surface from the radially outer side. It may be composed of a plurality of belts. in short,
As the friction transmission means B, it is possible to simultaneously apply a rotational force and a feed force in the rotation axis Y direction to the passive shaft 10 with driving rotation in a state of being pressed against the outer peripheral surface of the passive shaft 10. Any structure may be used. (2) The clamping means C provided between the main shaft 11 and the passive shaft 10 includes an integrated state in which the relative rotation and relative sliding of the two members 10 and 11 are prevented, and the relative rotation and relative sliding of the two members 10 and 11. Any structure may be used as long as it can be switched to a free state in which the state is allowed. (3) In the above embodiment, the transmission state switching means D for switching the friction transmission means B between the transmission state and the non-transmission state.
Is shared by the operation mechanism 17 of the uniform pressure contact means G, but the operation mechanism 17 of the uniform pressure contact means G does not have a function of switching the friction transmission means B to the non-transmission state,
A dedicated transmission state switching unit D for switching the friction transmission unit B between the transmission state and the non-transmission state may be separately provided and implemented. (4) In the above-described embodiment, the first holding member 13
A punching device A that can be connected to the output shaft 20 of the electric motor M in an integrally rotating state;
Although the speed reduction mechanism 22 for transmitting to the drive rotation shaft 18 is assembled, the speed reduction mechanism 22 may be disposed at a portion other than the first holding body 13 such as the casing 9 and implemented. (5) In the above embodiment, the driving unit M such as an electric motor is provided in the punching device A, but only the input shaft 21 that transmits power to the driving roller 12 is provided on the punching device A side. An output shaft of the portable electric tool may be connected to the input shaft 21 during the drilling operation. (6) In the above embodiment, the mounting portion 11 </ b> A is formed at the tip of the main shaft 11, and the drill 5 is directly mounted on the main shaft 11. The cutter mounting shaft provided with a mounting portion for detachably mounting the cutter may be detachably fixedly connected. (7) In the above-described embodiment, of the three (plural) rollers 12 constituting the friction transmission means B, the upper two are driven to rotate, but the three (plural) rollers 12 are driven. May be configured to drive and rotate all of the rollers 12. (8) In the above-described embodiment, the feed amount setting unit F that regulates the maximum feed amount of the main shaft 11 to the set feed amount by contact with the casing 9 is provided on the passive shaft 10 side. The means F may be provided on the main shaft 11 side. (9) In the above embodiment, the feed amount setting means F for regulating the maximum feed amount of the main shaft 11 to the set feed amount by contact with the casing 9 is provided.
A position detection sensor for detecting the position of the main shaft 11 with respect to
When the maximum feed amount of the main spindle 11 becomes the set feed amount based on the feed amount setting means for setting the maximum feed amount of the main spindle 11 and the position detection information of the position detection sensor and the feed amount set by the feed amount setting means. A feed amount setting control device including feed control means for stopping the drive rotation of the main shaft 11 and the forced feed may be provided.

[0046]

[Brief description of the drawings]

FIGS. 1A to 1D are process diagrams of a drilling method using a drilling device of the present invention.

FIGS. 2 (e) to (g) are process diagrams of a drilling method using the drilling device of the present invention.

FIG. 3 is a longitudinal sectional view showing a first embodiment of the punching device of the present invention.

FIG. 4 is a cross-sectional view of each part of the punching device.

FIG. 5 is an exploded sectional view of a casing.

FIG. 6 is an exploded perspective view of a clamp unit.

FIG. 7 is a longitudinal sectional view of a clamping unit.

8 (a) and 8 (b) are cross-sectional views showing an integrated state and a free state of the clamp means.

FIG. 9 is a cross-sectional view of the stopper means.

FIG. 10 is a side view of the stopper means.

FIG. 11 is a plan view showing the feed amount setting means at the start of drilling.

FIG. 12 is a plan view showing the feed amount setting means at the end of drilling.

FIG. 13 is an exploded perspective view of a clamping unit according to a second embodiment of the present invention.

FIG. 14 is a longitudinal sectional view of a clamping unit.

15 (a) and (b) are cross-sectional views showing an integrated state and a free state of the clamp means.

FIG. 16 is a longitudinal sectional view of a clamping means showing a third embodiment of the present invention.

17A and 17B are cross-sectional views showing an integrated state and a free state of the clamp means.

FIG. 18 is a longitudinal sectional view showing a conventional punching device.

[Explanation of symbols]

 B Friction transmission means C Clamping means D Transmission state switching means E Stopper means F Feed amount setting means P Fluid transport pipe Y Rotating shaft core 1 Casing 2 Through hole 3 Branching joint 4 Working valve 5 Drilling cutter 9 Casing 9g Bearing 10 Passive shaft 10a Boss portion 11 Main shaft 11a Passive surface 12 Roller 12a Annular concave portion 12b Peripheral wall surface 40 Urethane rubber 41 Extended rotating shaft 42 Shaft connecting means 45 Interlocking cylinder 46 Transmission member 47 Elastic biasing body 48 Operating mechanism 68 Storage space 69 Connecting cylinder body

Claims (11)

[Claims] 1. A power transmission system for a passive shaft, which is rotatably supported on a casing and slidable in the direction of the axis of rotation of the casing, is driven by a drive rotation while being pressed against an outer peripheral surface of the passive shaft. Along with providing the passive shaft with friction transmission means for applying a rotational force and a feed force in the direction of the axis of the rotating shaft, the passive shaft includes:
The main shaft on the side on which the drilling cutter for forming the through hole for forming the through hole in the pipe wall of the fluid transport tube is relatively slidably fitted in the direction of the rotation axis which is the relative rotation and cutter feeding direction. A fluid transport device is provided between the main shaft and the passive shaft, which is capable of switching between an integrated state for preventing relative rotation and relative sliding of the two and a free state for allowing relative rotation and relative sliding of the two. Pipe piercing device. 2. The drilling device for a fluid transport pipe according to claim 1, further comprising a transmission state switching unit that switches the friction transmission unit between a transmission state and a non-transmission state in which the pressure contact with the outer peripheral surface of the passive shaft is released. 3. The perforation device for a fluid transport pipe according to claim 1, wherein the casing is provided with stopper means for preventing movement of the main shaft to the return side so that the stopper can be released. 4. A feed amount setting means for restricting a maximum feed amount of a main spindle to a set feed amount by contacting a casing with the main shaft or the passive shaft side, according to claim 1, 2, or 3. Perforator for fluid transport pipe. 5. An end of the main shaft, which is located on the side opposite to the side where the drilling cutter is mounted, is provided with shaft connecting means for connecting the extended rotary shaft in a detachable and concentric manner. The perforation device for a fluid transport pipe according to any one of claims 1 to 4. 6. A unit feed amount per rotation with respect to a radially orthogonal plane with respect to a rotation shaft center in a state where the friction transmission means sandwiches the outer peripheral surface of the passive shaft from a radially outer side. The perforation for a fluid transport pipe according to any one of claims 1 to 5, comprising a plurality of rollers disposed at a corresponding angle, and at least one of the rollers being a drive roller. apparatus. 7. The main shaft is inserted and held between a bearing of a casing and a boss of a passive shaft.
7. The perforation device for a fluid transport pipe according to any one of 6. 8. The casing has a storage space capable of storing a drilling cutter that has returned to a maximum return position, and opens and closes a branch joint connected to a location corresponding to the drilling of the fluid transport pipe. The drilling device for a fluid transport pipe according to any one of claims 1 to 7, wherein a connecting cylinder body that can be connected in an airtight or liquid tight state via an operable work valve is attached. 9. The clamping means is configured such that the clamping means is engaged with an interlocking cylinder or a passive shaft fixed to the passive shaft in a state of being fitted to the main shaft from a radially outer side with respect to a passive surface formed on the main shaft. By the combination, a transmission member that brings the passive shaft and the main shaft into an integrated state, and the transmission member is biased to move to an engagement release position that is radially outwardly separated from the maximum rotation locus of the passive surface of the main shaft. The elastic urging body and the integral operation of holding the transmission member in the engagement position against the elastic urging force of the elastic urging body by the rotation operation about the axis of the main shaft, and the elastic urging force of the elastic urging body The drilling device for a fluid transport pipe according to any one of claims 1 to 8, further comprising: an operation mechanism configured to switch to a free state in which the transmission member is allowed to move away from the engagement position. 10. The perforation device for a fluid transport pipe according to claim 6, wherein an annular urethane rubber is mounted on an outer peripheral surface of the roller. 11. An outer peripheral surface of the roller is provided with an annular concave portion for holding an annular urethane rubber, and peripheral wall surfaces of the annular concave portion facing each other in the width direction are arranged closer to each other in a radially outward direction. The drilling device for a fluid transport pipe according to claim 10, wherein the drilling device is formed on a separated inclined surface.