JPH0526247A - Shaft fastening tool - Google Patents

Abstract

PURPOSE:To enable the whole size to be reduced and to prevent follow-up rotation of an inner ring during fastening of a fastening nut by a method wherein, concerning at least partial section in the direction of the axis of the inner ring an annular section previously formed in enough roundness is flattened to some extent. CONSTITUTION:An outer ring 2 inserted in the boss 41 of a rotary body 4 is externally engaged in a tapered engaging state with an inner ring 1 externally engaged with a shaft J and a fastening nut 3 is joined in a screwed-in state with the small diameter part of the inner ring 1 to form a shaft fastening tool.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a shaft fastener, and more particularly to a shaft fastener for fixing a rotating body such as a gear to a drive shaft or an output shaft.

[0002]

2. Description of the Related Art As a shaft fastener of the above type, there is already a type shown in FIG. This is the axis (J)
Cylindrical inner ring (1) that fits over the outer ring and outer ring (2) that fits over it
And a tightening nut (3) that is screwed onto the threaded portion at the end of the inner ring (1) on the small diameter side. In this case, the inner ring (1) is fitted onto the shaft (J), the outer ring (2) is inserted into the boss (41) of the rotating body (4) such as a gear, and the tightening nut (3) is tightened.
(J) and the rotating body (4) are fastened so as to rotate integrally. This is because the outer peripheral surface of the inner ring (1) is the taper surface (11) and the inner peripheral surface of the outer ring (2) is the taper surface (21). When tightening the tightening nut (3) screwed into the screw part (12) at the small diameter end of the inner ring (1), the boss (41) and the outer ring ( A radial outward pressure contact force acts on the fitting part with 2), and conversely, a radial inward pressure contact force acts on the fitting part between the shaft (J) and the inner ring (1). As a result, a predetermined frictional force is generated in each fitting portion, and torque can be transmitted from the shaft (J) to the rotating body (4).

However, this conventional device has a problem that the fastening operation is difficult when the entire shaft fastener is downsized. This is because when tightening the tightening nut (3), it is necessary to apply relative rotational force between the inner ring (1) and the tightening nut (3), but the inner ring (1) uses this tightening nut (3). The inner peripheral surface of the inner ring (1) rotates together with the shaft (J).
Is caused by slipping on the surface of. That is, the tightening nut
Since the outer peripheral part of (3) is a tool corresponding part,
As shown in Fig. 3, if the tool corresponding part (K) is provided after the screw part (12) also on the small diameter end of the inner ring (1), by using both tool corresponding parts, the tightening nut (3) and Relative turning power can be applied to the inner ring (1). However, when attempting to realize such a configuration, as shown in the same figure, the screw part (1
It is necessary to make the outer shape of 2) larger, and the diameter of the inner ring (1) becomes larger accordingly, resulting in a larger overall size. In other words, it is necessary to minimize the wall thickness of the threaded portion (12) in order to reduce the diameter of the whole, particularly, the diameter thereof. Since the tool-corresponding part cannot be provided, the above inconvenience occurs.

The present invention has been made in view of the above point, and "the outer ring (2) to be inserted into the boss (41) of the rotating body (4) is attached to the inner ring (1) which is fitted onto the shaft (J)." ) Is externally fitted in a taper fit state, and the tightening nut (3) is screwed onto the small diameter end of the inner ring (1) ''. The issue is to prevent the inner ring (1) from rotating together when tightening.From another point of view, it is not necessary to provide a tool-corresponding part (K) at the end of the inner ring (1) on the small diameter side. The problem is to prevent the inner ring (1) from rotating together when tightening the tightening nut (3).

[0005]

[Technical Means] A technical means of the present invention for solving the above-mentioned problem is to "determine at least a part of the inner ring (1) in the axial direction in an annular cross section formed in advance in a sufficient circularity. The degree was flattened. ”

[0006]

The above technical means operates as follows. Inner ring
At least a part of the cross section of (1) is a flattened annular cross section. Usually, this type of shaft fastener has an inner ring (1)
The inner diameter of is set to the specified fitting tolerance in relation to the shaft (J), so when this inner ring (1) is fitted onto the shaft (J), this flattened part will ) Is strongly pressed against the outer circumferential surface of the inner ring (1), and the inner ring (1) approaches the preset roundness.

Then, the rotating body (4) is fitted onto the fastener, and the tightening nut (3) is screwed into the small diameter end of the inner ring (1).
The screw pair portion of the tightening nut (3) and the inner ring (1) at the beginning of the tightening is restored to the predetermined roundness as described above. When the flattened portion is located away from the screw pair, the roundness of the screw pair matches the initial roundness.

In this paired state, the tightening nut
The rotation resistance of the screw pair part of (3) and the inner ring (1) is substantially equal to the screwing resistance of the true circle screw parts. On the other hand, the pre-flattened portion is subjected to an urging force to restore the initial flattened shape, so that the frictional resistance between the inner ring (1) and the shaft (J) is in an increased state. Therefore, even in the initial stage of tightening the tightening nut (3), the relative rotation resistance between the inner ring (1) and the shaft (J) causes the relative rotation of the screw pair between the tightening nut (3) and the inner ring (1). It becomes larger than the resistance, and co-rotation can be prevented. If the tightening degree of the tightening nut (3) increases, the inner ring
Since the relative rotational resistance between (1) and the axis (J) becomes extremely large, co-rotation does not occur at this point. Further, in the final tightened state, the inner peripheral surface of the inner ring (1) is restored to the preset circularity and accurately contacts the shaft (J).

[0009]

[Effect] The relative rotation resistance between the inner ring (1) and the shaft (J) at the early stage of tightening the tightening nut (3) is the tightening nut.
It becomes larger than the relative rotation resistance of the screw pair part of (3) and the inner ring (1), and co-rotation can be prevented, so attach a shaft fastener and tighten the tool with the tightening nut (3). The rotating body (4) can be fastened to the shaft (J) with just this.
That is, it is easy to attach the shaft fastener.

In order to prevent co-rotation of the inner ring (1) at the initial stage of tightening the tightening nut (3),
Since it is not necessary to provide a tool-corresponding part in (1), the diameter of the screw pair element at the small diameter end of the inner ring (1) can be set to a minimum, which simplifies the configuration and reduces the overall size.

[0011]

Embodiments of the present invention described above will now be described in detail with reference to the drawings. The embodiment shown in FIG. 3 and subsequent figures is composed of an inner ring (1), an outer ring (2) and a tightening nut (3) as in the conventional example described above. ) And the tightening nut (3) are connected so as to be rotatable relative to each other. Each part will be described in detail below.

The inner ring (1) has a structure in which a small diameter end of the tapered surface (11) is continuously provided with a threaded portion (12) made of parallel threads, and a tightening nut (3) is screwed into the threaded portion (12). To meet. Incidentally, as shown in FIG. 4, the inner ring (1) is partially formed with a slit (S) which is cut open in the axial direction. The inner ring (1) thus configured is flattened at the tapered surface (11) of the inner ring (1) as shown in FIG.

The inner ring at the stage before the flattening
Similar to the conventional inner ring (1), (1) is finished to a specified roundness, and especially the inner diameter of the inner ring (1) and the shaft (J)
The fitting tolerance with the outer diameter of is finished to about JIS: H-7. As shown in Fig. 4, when the inner ring (1) of this size and accuracy is clamped by a vise with a predetermined pressing force,
The clamping portion is flattened. At the time of this clamping, as shown in (a) of the same figure, the slit (S) is opened and closed in the direction of the clamping body.
(B) (B) is set at right angles to the line connecting
Moreover, a pad (P) (P) made of a synthetic resin having a predetermined hardness, such as polycarbonate resin, which has excellent mechanical strength, is attached to the end surface of the pressing body (B) (B), This pad (P)
The threaded portion (12) of the inner ring (1) is clamped between (P). As a result, deformation or damage of the screw part (12) in which the screw thread is formed in advance is prevented.

When a predetermined pinching force is applied to the pinching bodies (B) and (B), slits are once drawn as shown in (b) of FIG. 5 and (b) of FIG.
When (S) is in the closed state and the clamping pressure is further increased, the cross section is further flattened. After that, when the inner ring (1) is removed from the vise, as shown in (C) of FIG. 5, the slit (S)
The cross section of the screw part (12) is flattened in the opened state.

In the case of the inner ring (1) having a diameter of about 20 mm, if the screw portion (12) having a wall thickness of about 3 mm is clamped with a predetermined clamping pressure, the long diameter of the screw portion (12) will be after machining. Was 0.01 mm larger than the diameter before processing, and the minor axis was reduced by 0.05 mm. At this time, the portions other than the screw portion (12) were deformed significantly less than the above degree.

An outer ring (2) fitted onto the inner ring (1) having the above structure
As shown in FIG. 3, it is composed of outer ring halves (2a) and (2b). These halves are once formed into a tubular body having a brim portion at one end. It is manufactured by vertically dividing the. In addition, at the time of this division, since the tubular body is divided into two parts in a manner of partially cutting in the axial direction, the arc of the cross section of each half body is slightly smaller than the arc of a semicircle. Then, the collar portion (22) extends from the outer peripheral portion of the inner periphery of each half body that coincides with the end portion on the small diameter side of the tapered surface (21).

The tightening nut (3), which is rotatably connected to the outer ring halves (2a) (2b), has a hook-shaped tubular portion (32) connected to one end of the female screw portion (31). An annular groove (33) is formed on the inner circumference of the hook-shaped tubular portion (32).
The groove width of 3) is slightly larger than the thickness of the collar portion (22). In this case, the collar portion (22) of each of the pair of outer ring halves (2a) (2b) is inserted into the annular groove (33) as shown in (c) of FIG. 3 and FIG. Insert the inner ring (1) into the assembly of the tightening nut (3) and the outer ring halves (2a), (2b) and screw the tightening nut (3) into the threaded part (12) to assemble the shaft fastener. Be done. At this time, the outer ring (2) is the outer ring half (2a) (2b)
However, when the collar (22) is housed in the annular groove (33) and the outer ring halves (2a) and (2b) are fitted onto the inner ring (1), these outer ring halves are divided into two parts. The bodies (2a) and (2b) will not come off.
This is the same as long as the outer ring (2) is divided into three or more parts, and the tongue portion (22) is inserted into the annular groove (33).

As shown in FIG. 3, this shaft fastener has a shaft (J)
When it is externally fitted to the shaft (J), the threaded part (12) of the shaft (J) is flattened.
Is strongly pressed against the surface of. Since the flattened part is only the screw part (12), the parts other than the screw part (12) are hardly flattened when externally fitted to the shaft (J). The operation of fitting the shaft fastener onto the shaft (J) from the end can be performed relatively easily.

Then, the rotating body (4) is mounted so that the outer circumference of the outer ring (2) is housed in the boss (41) of the rotating body (4), and the tightening nut (3) is tightened. (4) is fastened to the shaft (J). In the initial tightening of the tightening nut (3), the inner threaded portion (12) of the inner peripheral surface of the inner ring (1) is strongly pressed against the shaft (J). For the reason described in, the tightening nut (3) can be tightened without the tightening nut (3) and the inner ring (1) rotating together.

Further, in this embodiment, the tightening nut is
Since the end face of the hook-shaped tube part (32) of (3) is set at right angles to the axis of the shaft fastener, the rotating body (4)
When the tightening nuts (3) are tightened with the side faces of the rotor facing each other, the rotating body (4) is mounted in a posture that is at a right angle to the outer peripheral surface of the outer ring (2) of the shaft fastener. Further, in the above-mentioned embodiment, since the collar portion (22) of the outer ring (2) is fitted into the annular groove (33), when the tightening nut (3) is loosened, the side wall outside the annular groove (33) is Since the outer ring (2) is pulled out in a manner in which the collar portion (22) is engaged, the rotating body (4) can be easily removed.

At this time, one side wall of the annular groove (33), that is, the protruding piece (34) at the end of the hook-shaped tubular portion (32) and the brim portion (2).
The larger the degree of engagement with 2), the larger the pull-out force of the outer ring (2) can be set. In this embodiment, the outer ring (2) is divided into two parts, and the outer ring halves (2a) and (2b) are each provided with a brim (22).
As shown in FIGS. 6 to 8, since the method of press-fitting into the annular groove (33) is adopted, the engagement margin of the collar portion (22) becomes large. Therefore, in the assembled state of the shaft fastener, there is no concern that the parts will be inadvertently disassembled, and in particular, there will be no concern that the outer ring halves (2a) (2b) will come off.

The actual condition of the outer ring press-fitting will be described based on its specific example. Now the outer diameter is 29 mm and the inner diameter of the small diameter end is 24.6 mm.
In the outer ring (2) of the
1.75mm, thickness of this collar (22) 1.75mm, annular groove (33)
When the width of the groove is 2.25 mm, when inserting the collar portion (22) into the annular groove (33), one end of the collar portion (22) is inserted into the annular groove (33), From the state of (a) of FIG.
When the posture shown in (b) is adopted, the overlap margin is
(D) becomes 0.5 mm, and if it is pressed in as it is, the collar (2
The cut surface on the outer circumference of the end face of 2) exerts a guiding function, and
As shown in (c), the entire collar portion (22) is securely press-fitted into the annular groove (33), and serves as an engagement margin between the protruding piece (34) and the collar portion (22).
1.0 mm was secured. This engagement margin is larger than that in the case of the outer ring (2) having an integral structure with slits (S) as shown in FIG. Almost 2
Doubled.

In the conventional structure shown in FIG. 9, as shown in FIG. 10, the outer ring (2) must be press-fitted in a state in which the outer ring (2) and the tightening nut (3) are coaxial with each other, and the engagement margin is increased. This is because, in some cases, this press-fitting cannot be done.
In the case of the outer ring composed of the outer ring halves (2a) and (2b) in the above embodiment, when the outer ring (2) is pulled out by loosening the tightening nut (3),
The problem of defective drawing due to insufficient engagement between the (22) and the protruding piece (34) can be solved.

In the case where the outer ring (2) has an integral structure having a slit (S) and has a collar portion (22) as shown in FIG. 11, the collar portion (22) ) And the protruding piece (34) can be increased in engagement margin. In this embodiment, as shown in FIG. 11 (a), the collar portion (22) has outer peripheral portions facing each other across the slit (S) as cut portions (23) (23) parallel to each other. Yes, the interval between the cut portions (23) and (23) is set to be equal to or slightly smaller than the inner diameter of the protruding piece (34). Then, as shown in FIG. 12, the outer ring (2) is inclined so that a part of the flange portion (the side opposite to the slit (S)) is housed in the annular groove (33), and the outer ring (2) is provided with the slit (S). If the collar portion (22) on the side to be pressed is press-fitted, the entire collar portion (22) is housed in the annular groove (33).

Also in this case, when the outer ring (2) shown in FIG. 9 is housed in the annular groove (33) with the tightening nut (3) and the outer ring (2) being in the coaxial posture as shown in FIG. Collar compared to
The width of the (22) can be increased, and the engagement margin between the protruding piece (34) and the collar portion (22) can be increased. In the embodiment shown in FIGS. 3 to 8, the screw portion (12) of the inner ring (1) is flattened, but the inner ring (1) is flattened and the screw portion (12) is flattened. The same effect can be obtained by partially flattening other parts.

[Brief description of drawings]

FIG. 1 is an explanatory diagram of a conventional example.

FIG. 2 is an explanatory view of a modification of this conventional example.

FIG. 3 is a sectional view of an embodiment of the present invention.

FIG. 4 is an explanatory view of work for partially flattening the inner ring (1).

FIG. 5 is an explanatory view of a cross-sectional change of the inner ring (1) at this time.

[Fig. 6] Tightening nut for the outer ring (2) adopted in this embodiment
Plan view when assembled in (3)

FIG. 7 is an explanatory view of the step of incorporating the outer ring.

FIG. 8 is an enlarged view of a main part of FIG.

FIG. 9 is an explanatory view of a conventional outer ring (2).

FIG. 10 is an explanatory diagram of a process of assembling the outer ring.

FIG. 11 is an explanatory diagram of another type of outer ring (2).

FIG. 12 is an explanatory view of the step of incorporating the outer ring.

[Explanation of sign]

 (J) ・ ・ ・ Shaft (1) ・ ・ ・ Inner ring (4) ・ ・ ・ Rotating body (41) ・ ・ ・ Boss (2) ・ ・ ・ Outer ring (3) ・ ・ ・ Tightening nut

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Katsuhiro Tachibana 1-37 Minamiuematsucho, Yao-shi, Osaka Prefecture Aisel Co., Ltd.

Claims (1)

[Claims] [Claim 1] The inner ring (1) externally fitted to the shaft (J) has a rotating body.
The outer ring (2) to be inserted into the boss (41) of (4) is externally fitted in a taper fitting state, and the tightening nut (3) is attached to the small diameter end of the inner ring (1).
A shaft fastener in which at least a part of a cross section of the inner ring (1) in the axial direction is flattened to a predetermined degree by an annular cross section formed in advance to have a sufficient roundness.