JP2016078168A - Tool comprising spiral shaped shock cushioning region - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bit comprising a spiral shaped torsion part, and is excellent in cam-out prevention performance.SOLUTION: A bit 10 comprises: a cutting edge part 12 (work area); a trunk part 18 (torque transmission part) for fitting to a socket part of a rotary tool for receiving rotary force from the rotary tool; an engagement groove part 16 to which an engagement member on the socket part of the rotary tool is fitted; and a torsion part 14 (shock cushioning region) which is a spiral shaped, and disposed between the cutting edge part 12 and the trunk part 18. A phase of the torsion part 14 is twisted by almost 120° in an opposite direction of a torque transmission direction, with respect to a phase of the trunk part 18.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a tool that is detachably attached to a rotary tool (power source) such as an electric tool or an air tool, and transmits a rotational torque to rotate and tighten a screw member, and in particular, a spiral shape (twisted shape). With the shock buffering area (torsion part) of the tool, it is possible to extend the life of the tool by absorbing the overload to the cutting edge of the tool (bit here) by twisting due to overload, and when the screw member is seated The present invention relates to a tool (a bit, a bit holder, etc.) that can prevent a cam-out from occurring at a (tightening end).

  Bits, bit holders, etc., which are tools that are attached to a rotary tool that is a power source and that are tightened by rotating a screw member, can be attached to the insertion port connected to the drive shaft of an electric tool or air tool with one touch. It is a simple tool. Such a tool has a work area (blade edge or fitting portion) on one end side thereof, and a trunk portion that receives a rotational force from the rotary tool by being fitted in an insertion port of the rotary tool in the middle portion thereof (Torque transmission part), and this trunk | drum has the structure by which the latching groove part in which the spherical latching member in an insertion port fits is provided. If such a tool is called a driver bit, the work area is a cutting edge and has a plus or minus screwdriver shape. If it is called a bit holder, the work area is the body of the bit. In the case of what is called a socket bit, the work area is formed with a hexagon hole that fits into the bolt head.

  When an overload such as an impact load occurs during the use of such a bit, there is a problem in that the tip of the tip is damaged and the life is very short even if it is a consumable item. The utility model registration No. 3118978 (patent document 1) is a slim shape which improves the durability of the bit by preventing the tip of the tool from being lost by absorbing the overload caused by vibration or impact load by the torsion part. A ribbed torsion bit is disclosed.

  In the bit disclosed in Patent Document 1, a square portion having a lateral cross-section formed in an even corner is formed on the center side, and shaft portions having a smaller diameter than the square portion are provided on both ends of the square portion. A torsion bit having a slim shape in which a bit portion is formed at the tip of the shaft portion, and the torsion bit forms a single rib portion (flat plate portion) on the center side of the square portion. The rib portion is formed by being laid between flat surfaces facing each other of the angular portion, and the rib portion and the remaining angular portion are connected in an arcuate surface. Features. According to this slim-shaped torsion bit with ribs, the bit portion is formed in a corner portion of the torsion bit having a slim shape, the bit portion is formed between the flat surfaces of the corner portion, and Since it is connected with the remaining square portions with a smooth arcuate surface, the rotational force is greatly absorbed in the screw tightening operation, and the burden of the rotational force on the bit portion can be reduced.

Utility Model Registration No. 3118978

  However, in the slim torsion bit disclosed in Patent Document 1, the tool (here, the bit) can be extended in its life by being twisted by the overload and absorbing the overload on the cutting edge of the tool. It is impossible to prevent the screw member from coming out when seated (tightened end). In other words, the bit disclosed in Patent Document 1 cannot prevent a cam-out in which the tip of the bit is lifted from the screw hole due to the lift of the tip of the bit when the screw is subjected to the maximum load when the screw is tightened.

In view of such problems, an object of the present invention is a tool for rotating and tightening a screw member attached to a rotary tool that is a power source, and includes a spiral impact buffering region (torsion portion), A tool that can sufficiently absorb the overload such as impact load and extend the life of the bit and prevent the cam member from coming out when the screw member is seated (tightened end) is provided. It is to be.

In order to achieve the above-described object, the present invention takes the following technical means.
That is, a tool according to an aspect of the present invention is a tool for attaching to a rotary tool that is a power source and rotating and tightening a screw member, and a work area and a torque transmission area in which torque is transmitted from the power source And an impact buffering region provided between the work region and the torque transmission region, wherein the shock buffering region is twisted in a direction opposite to the torque transmission direction.

Preferably, the tool can be configured to be a bit or a bit holder.
More preferably, the twist angle of the impact buffering region can be configured to be an angle that is an integral multiple of 60 °.

  According to the present invention, the spiral shock-absorbing region (torsion portion) can sufficiently absorb an overload such as an impact load and extend the life of the bit, and also when the screw member is seated (tightened end). Can be prevented from coming out.

It is the left view (A), top view (B), and right view (C) of the bit which concerns on embodiment of this invention. It is a perspective view of the bit shown in FIG. It is the left view (A), the top view (B), and the right view (C) of the bit holder which concerns on another embodiment of this invention. It is a perspective view of the bit holder shown in FIG. It is a virtual diagram which shows the state in the screwing process of the bit of FIG. It is a virtual diagram which shows the state at the time of seating of the bit of FIG. It is a figure for demonstrating the camout prevention performance of the bit of FIG.

Hereinafter, a bit 10 according to an embodiment of the present invention and a bit holder 20 according to another embodiment of the present invention will be described in detail with reference to the drawings. In the following description, the same parts (portions) are denoted by the same reference numerals. Their names and functions are also the same. Therefore, detailed description thereof will not be repeated.
1A is a left side view of the bit 10 according to the embodiment of the present invention, FIG. 1B is a plan view of the bit 10, and FIG. FIG. 2 is a right side view, and FIG. 2 is a perspective view of the bit 10. 3A is a left side view of a bit holder 20 according to another embodiment of the present invention, and FIG. 3B is a plan view of the bit holder 20, and FIG. ) Is a right side view of the bit holder 20, and FIG. 4 is a perspective view of the bit holder 20.

First, the bit 10 will be described. As shown in FIGS. 1 and 2, the bit 10 is a double-headed bit in which a pair of cutting edge portions 12 (working areas) are formed on both ends of the main body (a single-headed type may be used). ), The blade edge portion 12 includes, for example, a cross-shaped blade in a plan view.
In addition, the middle part of the main body has a barrel 18 (torque transmission region) that is fitted into the insertion port of the rotary tool and receives the rotational force from the rotary tool. A pair of locking groove portions 16 into which spherical locking members at the insertion ports are fitted are provided.

Specifically, the body portion 18 has a hexagonal cross section (but is not limited to a hexagonal column with an opposite side of 6.35 mm), and is formed between the six corners of the R chamfered shape and the respective corners when viewed in cross section. And six side faces. This body portion 18 can be inserted into a hexagonal mounting hole in the insertion port of the rotary tool.
Locking groove portions 16 having a concave cross section and an arc shape are formed at both ends of the body portion 18 in the circumferential direction of the main body. A spherical locking member at the insertion port projects into the locking groove 16 so as to protrude in the radial direction.

  In FIG. 1B, when the spherical locking member at the insertion port is fitted into the right locking groove 16, the right body portion 18 (along with the hexagonal column portion of the right cutting edge portion 12). The rotary tool is inserted into the insertion slot to receive the rotational force from the rotary tool, and the left blade edge portion 12 is screwed or the like, and the left locking groove 16 has a spherical locking member at the insertion port. When fitting, the left body 18 (with the hexagonal column portion of the left blade tip 12) fits into the insertion port of the rotary tool, receives the rotational force from the rotary tool, and is screwed by the right blade tip 12 Etc. are performed.

Next, the bit holder 20 will be described. As shown in FIG. 3 and FIG. 4, this bit holder 20 is a bit holder in which a bit insertion port 22 (working area) is formed on one end side of the main body. For example, the bit 10 shown in FIGS. 1 and 2 is inserted.
Further, in the middle part of the main body, similarly to the bit 10, there is a body part 28 (torque transmission region) that is fitted into the insertion port of the rotary tool and receives the rotational force from the rotary tool. A pair of locking groove portions 26 into which a spherical locking member at the insertion port of the rotary tool is fitted are provided at the center portion of the rotary tool.

Specifically, the body portion 28 corresponding to the body portion 18 of the bit 10 has a hexagonal cross section (but is not limited to a hexagonal column with an opposite side of 6.35 mm), and has six corners with R chamfered shapes when viewed in cross section. And six side surfaces formed between the corners. The body portion 28 can be inserted into a hexagonal mounting hole at the insertion port of the rotary tool.
An engaging groove portion 26 having a concave cross section and an arc shape corresponding to the engaging groove portion 16 of the bit 10 is formed in the central portion of the body portion 28 in the circumferential direction of the main body. In this locking groove portion 26, a spherical locking member at the insertion port projects and fits in the radially inward direction.

  What is characteristic is that the bit 10 and the bit holder 20 are located between the work area (the cutting edge part 12 and the bit insertion port 22) and the torque transmission area (the trunk part 18 and the trunk part 28). The spiral torsion torsion part 14 and the torsion torsion part 24 (impact buffering region) are provided. The twisted torsion part 14 and the twisted torsion part 24 basically have the same structure.

  The twisted torsion part 14 and the twisted torsion part 24 are manufactured by forming a flat plate part by cutting using a milling machine or the like and twisting the flat plate part. The flat plate itself is, for example, a rib manufacturing method disclosed in Utility Model Registration No. 3118978 (Patent Document 1) or a flat plate shape disclosed in Japanese Patent Application Laid-Open No. 2014-151374 related to the present applicant. The torsion part is formed by a manufacturing method or the like, and the manufacturing method is not particularly limited.

  For this reason, the cross-sectional areas of the twisted torsion part 14 and the twisted torsion part 24 are smaller than the cross-sectional areas of the body part 18 and the body part 28. Thereby, the torsion torsion part 14 and the torsion torsion part 24 act as a torsion part having a small torsional rigidity, and an excessive load applied to the blade edge part 12 and the bit edge part inserted into the bit insertion port 22 is changed into a twist. The durability of the bits inserted into the bit 10 and the bit holder 20 can be improved.

The cutting edge portion 12 of the bit 10 and the cutting edge portion of the bit fitted into the bit holder 20 are called, for example, a commonly used Phillips type, and the cross-sectional area of the blade in the plane perpendicular to the bit axis line goes to the tip. And a tapered inclined surface (in other words, a shape gradually increasing from the front end to the rear end of the blade).
In addition to such a structure, the bit 10 and the bit holder 20 according to the present embodiment have a characteristic structure in which the twisted torsion part 14 and the twisted torsion part 24 have a spiral shape (twisted shape).

The phases of the twisted torsion part 14 and the twisted torsion part 24 (impact buffering area) are twisted by approximately 120 ° in the direction opposite to the torque transmission direction with respect to the phase of the trunk part 18 and the trunk part 28 (torque transmission area). Yes. Here, in consideration of a general right-hand screw, the torque transmission direction is the screw tightening direction and is the “clockwise” direction, and therefore the spiral (twist) direction of the twist torsion part 14 and the twist torsion part 24 is “ Counterclockwise ”direction.

  Here, since the cross section of the torque transmission region is hexagonal, the twist angle of the twist torsion part 14 is preferably an angle that is an integral multiple of 60 °. With this setting, in the bit 10, the plane of the hexagonal column of the right barrel 18 and the plane of the hexagonal column of the left barrel 18 in FIG. 2B are in the same phase (exist on the same plane). It is preferable in terms of stability because it does not roll when the bit 0 is placed on a flat surface.

The bit 10 and the bit holder 20 are completed by forming a flat plate portion with a milling machine or the like and twisting the torsion torsion portion 14 and the torsion torsion portion 24 to a desired phase, followed by heat treatment for quenching.
In the bit 10 including the spiral torsion portion 14 and the bit holder 20 including the twist torsion portion 24 as described above, the twist torsion portion 14 and the twist torsion portion 24 act as a torsion portion having a small torsional rigidity. Thus, the durability of the bit can be improved and the cam-out prevention performance is provided.

  As for this cam-out prevention performance, the virtual diagram showing the state of the bit 10 shown in FIG. 5 during the screw tightening process, the virtual diagram showing the state when the bit 10 is seated shown in FIG. 6, and the cam-out prevention performance of the bit 10 shown in FIG. A description will be given with reference to the drawings. The twist phase angle of the twisted torsion part 14 and the amount of elongation of the twisted torsion part 14 shown in FIGS. 5 to 7 are shown to be extremely larger than actual so that the camout prevention performance can be easily understood. 7A is a virtual diagram of the bit 10 (bit 10A) in the “screw tightening process” corresponding to FIG. 5, and FIG. 7B is a bit 10 in the “sitting time” corresponding to FIG. It is a virtual diagram of (bit 10B).

  Generally, there is a slight difference between the seating (fastening completion) and the timing when the electric tool stops rotating (the timing when the electric tool stops rotating is slower than the seating (fastening completion)). Thus, the rotational force is further transmitted in a state where the screw member does not rotate any more. For this reason, the cutting edge portion 12 of the bit 10 is lifted (a cam-out in which the tip end of the bit is lifted from the screw hole is generated by the lifting of the cutting edge portion 12 which is the tip of the bit 10). There is a possibility that the blade tip 12 will lick the cross hole of the screw head of the tapping screw, drilling tapping screw, etc.) and damage the screw head.

The bit 10 according to the present embodiment is provided with a spiral twisted torsion portion 14, and when the twisted torsion portion 14 is unwound (or a movement similar to unwinding acts), a reaction force is generated at the time of sitting and twisted. The total length will be slightly longer due to the phase being set back). As a result, the blade edge portion 12 is pushed into the screw head (the lifting of the blade edge portion 12 can be avoided), and damage to the screw head can be prevented. That is,
(1) At the moment when the screw member is seated, the twisted phase portion of the twisted torsion part 14 can be released.
(2) As a result, the total length of the bit 10 is slightly increased, and the screw head is pressed downward.
(3) As a result, the cam-out can be prevented and the screw head can be prevented from being damaged.

In particular, when the pressing force of the electric power tool is weak in a place where the scaffold is unstable and / or in the horizontal driving operation, the entire length of the bit 10 is momentarily increased slightly when sitting, so that the blade edge portion 12 is placed on the screw head. It is preferable in that it can be pushed in (the lifting of the blade edge portion 12 can be avoided) and the screw head can be prevented from being damaged.
In this way, it was confirmed that the total length of the bit 10 was increased by measuring the total length of the bit 10 while simulating use as follows. Here, the measurement simulating use is because it is difficult to measure the elongation of the bit 10 in the actual screw tightening process (during use), and therefore an assumed load in the use rotation direction is applied to the portion of the twisted torsion part 14. After the deformation, the assumed load was released and the total length of the bit 10 was measured to confirm the elongation of the full length of the bit 10. Accordingly, it is considered that it is possible to confirm whether or not the entire length is extended during the screw tightening process and the cam-out is prevented when the seat is subjected to the maximum load. In actual use, it is considered that the full length of the bit 10 is longer than the elongation measured in a simulated manner (because the load is continuously applied).

  Specifically, the body 18 (torque transmission region) at both ends of the bit 10 is fixed, and the difference in the total length of the bit 10 before and after applying an assumed load (torque) of 32 N · m “clockwise” is measured. . The total length of the bit 10 that was 119.89 mm before application of the assumed load is 119.95 mm after application of the assumed load, and the total length of the bit 10 before and after application of the assumed load is 0.06 mm (0.05% = (119). .95-119.89) /119.89×100) was confirmed.

  Furthermore, when a plane photograph of the bit 10 was taken and analyzed before and after the load application, it was confirmed that the twist angle (phase) of the twist torsion portion 14 was small. Expressing these differences extremely, it is the state of the virtual diagram (before load application) shown in FIG. 5 and the virtual diagram (after load application) shown in FIG. It has been clarified that the loosening of the twist in the twisted torsion part 14 is a factor that slightly increases the overall length of the bit 10.

As described above, according to the bit and the bit holder according to the present embodiment, the spiral shock absorbing region (torsion part) is provided, and the shock absorbing region sufficiently absorbs an overload such as an impact load and is durable. In addition, the cam-out can be prevented when the screw member is seated (tightened end), and the screw head can be prevented from being damaged.
The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims. For example, the tool according to the present invention may be other tools of a bit and a bit holder, and examples thereof include a socket bit provided with a twisted torsion part. Furthermore, in the case where it can be assumed that the characteristic structure described above (the structure in which the twisted torsion part 14 and the twisted torsion part 24 have a spiral shape (twisted shape)) express the torsion effect in addition to the camout prevention effect, The cross-sectional areas of the twisted torsion part 14 and the twisted torsion part 24 are not limited to those smaller than the cross-sectional areas of the body part 18 and the body part 28.

  INDUSTRIAL APPLICABILITY The present invention can be suitably applied to a tool for rotating and tightening a screw member, and an impact buffering area (torsion part) having a spiral shape (twisted shape) is twisted by overload and applied to the cutting edge part of the tool. By absorbing the overload, the life of the tool can be extended, and it can be particularly suitably applied in that it can be prevented from coming out when the screw member is seated.

10 bit 20 bit holder 12 cutting edge (work area)
22-bit insertion slot (work area)
14, 24 Twisted torsion part 16, 26 Locking groove part 18, 28 Torso part (torque transmission region)

Claims (3)

A tool for rotating and tightening a screw member attached to a rotary tool as a power source,
A work area, a torque transmission area where torque is transmitted from the power source, and an impact buffering area provided between the work area and the torque transmission area,
The tool according to claim 1, wherein the shock buffering region is twisted in a direction opposite to a torque transmission direction.   The tool according to claim 1, wherein the tool is a bit or a bit holder. The torque transmission region has a hexagonal cross section,
The tool according to claim 1 or 2, wherein the twist angle of the impact buffering region is an integer multiple of 60 °.