JP2017062037A - Joint pin and connection structure using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a joint pin which is excellent in workability and is high in rigidity and strength, and a connection structure using the same.SOLUTION: Applied is a joint pin 4 comprising a spring pin 41 of a hollow structure in which an elastic plate is wound cylindrically while a slit remains, and a shaft member of a round rod shape that is inserted and fixed into a hollow part of the spring pin. In the joint pin, a gap between an inner peripheral surface of the spring pin under no load and an outer peripheral surface of the shaft member is made as an air gap or is filled with an elastomer material 44, so that elastic diameter reduction deformation of the spring pin is made possible. A length of an outer periphery of the shaft member under no load is made equal to or longer than a length of an inner periphery of the spring pin under no load excluding a portion overlapping the slit. The slit is also filled with the elastomer material 44 and, in one end or both ends in an axial direction of the shaft member, flanges 42a are provided.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a joint pin and a connection structure using the joint pin.

Conventionally, a connecting structure of two parts by a joint pin has been widely used.
As described in Patent Documents 1 and 2, a spring pin having a hollow structure in which an elastic plate is wound in a cylindrical shape having a C-shaped cross section is used as a joint pin, leaving a slit.
According to such a spring pin, there is an advantage that it is press-fitted with elastic contraction deformation into a hole or a notch provided in a connected component, and is fastened so as not to come off.
In Patent Document 1, foreign materials are mixed into the hollow portion of the spring pin by adopting a configuration in which an elastic member having a hardness lower than that of the member constituting the spring pin, such as hard rubber or silicone, is inserted and fixed in the hollow portion of the spring pin. It is described that the reduction of the spring effect due to the above is prevented and the detachability is improved.
In Patent Document 2, after a spring pin having both ends bulging in the radial direction is press-fitted into a connecting portion, a reinforcing metal core is driven into the spring pin to improve shear strength and prevent diameter reduction during use. Then, it is described that the reinforcing metal core itself may be a spring pin or a simple round shaft pin.

Japanese Patent Laid-Open No. 7-19216 JP-A-6-74222

However, in the invention described in Patent Document 2, at the time of connection, an operation of press-fitting a spring pin whose end portion swells in the radial direction, and an operation of driving a reinforcing metal core into the spring pin thereafter When uncoupling, it is necessary to take out the reinforcing core and pull out the spring pins with both ends bulging in the radial direction, including both transportation and storage. It is necessary to handle the pins of the book, which is complicated.
In the invention described in Patent Document 1, since an elastic member having a lower hardness than that of a member constituting the spring pin such as hard rubber or silicone is inserted and fixed in the hollow portion of the spring pin, one joint is used at all times. Can be handled as a pin.
However, since the spring pin is also used for connecting parts where large loads and intense vibrations are applied, if the amount of elastic deformation for attaching and detaching can be ensured, the load resistance is improved and the spring effect is improved by high rigidity and high strength that do not deform further. However, depending on the invention described in Patent Document 1, there is a deformation characteristic in a range from no load to an elastic deformation amount for attachment / detachment and a range exceeding the elastic deformation amount. It remains the same and cannot effectively respond to such a request.
Further, in the invention described in Patent Document 1, the slit of the spring pin is not filled with a member, foreign matter enters from the slit, and foreign matter is clogged between the slit and the two parts to be connected. The extraction of the spring pin and the subsequent separation of the two parts may be difficult.

  The present invention has been made in view of the above problems in the prior art, and an object of the present invention is to provide a joint pin with good workability, high rigidity, and high strength, and a connection structure using the same.

The invention according to claim 1 for solving the above-mentioned problem is a spring pin having a hollow structure in which an elastic plate is wound into a cylindrical shape leaving a slit,
A round bar-shaped shaft member inserted and fixed in the hollow portion of the spring pin,
The space between the inner peripheral surface of the spring pin and the outer peripheral surface of the shaft member at the time of no load is a gap, or a shock absorber is installed between the two, so that the elastic pinion deformation of the spring pin is reduced. It is a joint pin enabled.

  In the invention according to claim 2, the length of the outer periphery of the shaft member at the time of no load is equal to or longer than the length of the inner periphery of the spring pin at the time of no load, excluding the portion that engages with the slit. The joint pin according to claim 1.

  A third aspect of the present invention is the joint pin according to the first or second aspect, wherein the slit is filled with a buffer material and sealed.

  According to a fourth aspect of the present invention, a flange is provided at one end or both ends in the axial direction of the shaft member, and a neck lower surface of the flange is hung on an axial end surface of the spring pin. It is a joint pin given in any one of them.

In the invention according to claim 5, flanges are provided at both axial ends of the shaft member, and a neck lower surface of the flange is hung on an axial end surface of the spring pin,
The said shaft member is a joint pin as described in any one of Claims 1-3 comprised from two or more components in which the flanges of both ends belong to another components.

  A sixth aspect of the present invention is the joint pin according to the fifth aspect, wherein the connecting surface between the parts constituting the shaft member is located at a position unevenly distributed from the center in the axial direction.

  According to a seventh aspect of the present invention, the radius of the flange exceeds the inner radius of the spring pin when no load is applied, and is equal to or less than the dimension obtained by adding the thickness of the elastic plate to the radius of the shaft member. The joint pin according to any one of Items 6.

The invention according to claim 8 is a connecting structure of two parts by the joint pin according to any one of claims 1 to 7,
The spring pin and the shaft member are both connected to one part, and the connecting structure is a joint pin that holds the other part between fulcrum points of the both ends.

According to the present invention, high rigidity and high strength as a whole joint pin are achieved by a round bar-shaped shaft member, and load resistance is improved.
In addition, according to the present invention, the spring pin can be elastically reduced in diameter, and the amount of deformation by the round rod-shaped shaft member is suppressed, so that plastic deformation and fatigue deterioration are suppressed, and the spring effect is maintained. Detachability (press-fit, fasten, and pull-out performance) can be maintained.
Further, according to the present invention, since the round rod-shaped shaft member is fixed to the spring pin, it can be handled as one joint pin at all times, and the workability of transportation, storage and other is good.

It is a side schematic diagram of an example pile rotary press machine to which the connection structure by the joint pin concerning one embodiment of the present invention is applied. Sectional view (a) perpendicular to the central axis of the connection structure with joint pins according to an embodiment of the present invention (a), sectional view including the central axis (b), BB sectional view (c), A1-A1 sectional view ( d) and a single sectional view (e) of the joint pin. The cross-sectional view of the joint pin for comparison (a), the cross-sectional view (b) including the central axis of the connection structure by the comparative joint pin, and the cross-sectional view (c) of A2-A2, Shows a state in which a shear load is applied to the comparative joint pin. Sectional drawing (a) including the central axis of the connection structure by the joint pin which concerns on one Embodiment of this invention, and A3-A3 side view (b) show the state in which the shear load is applied to the joint pin. Cross-sectional view (a) including the central axis of the connecting structure with the comparative joint pin (a), A4-A4 cross-sectional view (b), and single perspective view (c) of the comparative joint pin. Shows the invasion of earth and sand. FIG. 6A is a cross-sectional view including a central axis of a connection structure using joint pins according to an embodiment of the present invention, FIG. 5A is a cross-sectional view of A5-A5 (b), and FIG. ) Shows the state of sedimentation. A sectional view (a) perpendicular to the central axis of the connection structure by the comparative joint pin and an end sectional view (b) of the comparative joint pin, FIG. Sectional view (a) perpendicular to the central axis of the joint structure with joint pins according to an embodiment of the present invention, and end sectional view (b) of the joint pin, in FIG. Show the state. FIG. 6 is an axial sectional view (a), a left side view (b), and a right side view (c) of a joint pin according to another embodiment of the present invention. FIG. 6 is an axial sectional view (a) showing another example of a joint pin component coupling structure according to another embodiment of the present invention, and an axial sectional view (b) showing still another example. (a) is sectional drawing perpendicular | vertical to the center axis | shaft of the connection structure by the joint pin based on other one Embodiment of this invention, and shows the mode of a press-fit operation | work. (b) is a perspective view of the joint pin. FIG. 6 is a cross-sectional view (a) perpendicular to the central axis of a connection structure with joint pins according to another embodiment of the present invention and a cross-sectional view (b) including the central axis.

  An embodiment of the present invention will be described below with reference to the drawings. The following is one embodiment of the present invention and does not limit the present invention.

  The joint pin according to the present embodiment and the connection structure using the joint pin are preferably used for the auger shaft connection structure 1 shown in FIG. In the auger shaft coupling structure 1, the rotational force transmission shaft 102 from the rotational force output shaft of the auger motor 101 of the pile press-fitting machine 100 to the auger head 103 is fitted into the male shaft and female shaft hole portions at a predetermined portion. The auger shaft connection structure. As shown in FIG. 1, the auger shaft coupling structure 1 can be applied to a position where the blades 104 of the auger screw are formed, but of course, it can also be applied to a position where the auger screw is not formed.

Details of the joint pin 4 according to the present embodiment and the auger shaft coupling structure 1 to which the joint pin 4 is applied are shown in FIGS. 2, 4, 6, and 8. 3, 5, and 7 are views of the comparative joint pin 14 configured by only the spring pin.
The male shaft 2 and the female shaft 3 are formed coaxially with the rotational force transmission shaft 102. Let Y be the central axis. A tunnel-like flow path extending in the axial direction for passing a fluid from the rotational force output shaft side of the auger motor 101 to the auger head 103 side is formed. A part of the flow path 27 constituting the flow path is formed on the male shaft 2.

The auger shaft connection structure 1 includes a joint pin 4 connected to a positioning groove 24 and a positioning hole 34 which communicate with each other in a state where the relative axial position and rotational position of the male shaft 2 and the female shaft 3 are adjusted to predetermined positions. Are connected by being penetrated. The spring pin 41 and the shaft member 42 are both connected to one component (female shaft 3), and the connecting structure is a joint pin 4 that holds the other component (male shaft 2) between the fulcrums of the both ends. The spring pin 41 also exceeds the dimension between the fulcrums, the shaft member 42 also exceeds the dimension between the fulcrums, and there may be a portion where the shaft member 42 is not disposed at the end of the spring pin 41. FIG. As shown in (b), the axial length of the joint pin 4 where the spring pin 41 and the shaft member 42 overlap when viewed in the radial direction of the joint pin 4 exceeds the dimension between the fulcrums. is there.
The male shaft 2 and the female shaft 3 are connected so as to be able to transmit torque by splines formed in a portion not shown. Further, when the rotational force transmission shaft 102 is pushed into the ground, since the surfaces perpendicular to the central axis Y formed on the male shaft 2 and the female shaft 3 abut each other, no load is applied to the joint pin 4. When the rotational force transmission shaft 102 is pulled up, a shear load is applied to the joint pin 4.

The joint pin 4 includes a spring pin 41 having a hollow structure in which an elastic plate is wound into a cylindrical shape having a C-shaped cross section leaving a slit, and a round bar-shaped shaft member 42 inserted and fixed in a hollow portion of the spring pin 41. Is provided. The slit of the spring pin 41 is filled with an elastomer material 43 and sealed.
An elastomer material 44 is filled between the inner peripheral surface of the spring pin 41 and the outer peripheral surface of the shaft member 42. The elastomer material 43 and the elastomer material 44 may be formed of the same material continuously. While accompanying the deformation of the elastomeric material 43 and the elastomeric material 44, the elastic pinion deformation of the spring pin 41 and the diameter expansion deformation that is its recovery deformation are made possible. The same applies to a configuration in which the elastomer material 43 and the elastomer material 44 are not filled, and a gap is formed between the slit of the spring pin 41 and the inner peripheral surface of the spring pin 41 and the outer peripheral surface of the shaft member 42 when no load is applied. In addition, since it is possible to adopt a configuration capable of elastically reducing the diameter of the spring pin 41 and expanding the diameter of the spring pin 41, it is possible to implement such a configuration.
Therefore, if the elastic pinch deformation of the spring pin 41 and the expansion deformation that is the recovery deformation thereof can be configured, it is not limited to the elastomer material, and is not limited to filling to fill all the gaps. A cushioning material that allows the elastic pinion deformation of the spring pin 41 by deforming itself is installed between the inner peripheral surface of the spring pin 41 and the outer peripheral surface of the shaft member 42 (and further, a slit of the spring pin 41). If nothing is installed, it can be left as a gap when no load is applied. Also in the case of installing the buffer material, the spring pin 41 may be coated with the buffer material or / and the shaft member 42 may be coated with the buffer material so that a gap is generated when no load is applied. As will be described later, the material can be selected not only for the elastomer material but also for obtaining sealing performance.
The spring pin 41 and the shaft member 42 are formed with holes that communicate with each other in a direction perpendicular to the shafts. The fixing pins 45 are fitted into the holes so that they are not separated from each other.

The length of the outer periphery of the shaft member 42 at the time of no load is equal to or longer than the length of the inner periphery of the spring pin 41 at the time of no load, excluding the portion that is applied to the slit. In the process of gradually reducing the diameter of the spring pin 41, when the slit disappears at the latest, the entire inner periphery of the spring pin 41 reaches the outer peripheral position of the shaft member 42 to further deform the spring pin 41. It is for suppressing. Of course, the length of the outer periphery of the shaft member 42 when there is no load is less than the length of the inner periphery of the spring pin 41 when there is no load (the entire circumference including the portion that hangs on the slit). Therefore, by receiving external pressure on the outer peripheral surface of the spring pin 41, it is possible to reduce the diameter without being restrained by the shaft member 42, and at the time when the slit disappears at the latest in the process of gradually increasing the external pressure, the spring pin 41 is restrained by the shaft member 42 and deformation is suppressed. Even when the elastomer material 43 is interposed between the spring pin 41 and the shaft member 42, the deformation amount suppressing effect equal to or greater than that can be obtained. The setting is made so as to ensure the attachment / detachment function in the deformation range of the spring pin 41 up to this point, and the deformation amount in the deformation range is set by the width dimension of the slit. After the spring pin 41 is restrained by the shaft member 42, the composite structure of the spring pin 41 and the shaft member 42 can withstand external pressure.
Therefore, the amount of deformation for attaching / detaching the spring pin 41 to / from the positioning groove 24 and the positioning hole 34 is ensured, and plastic deformation and fatigue deterioration of the spring pin 41 are suppressed by suppressing the amount of deformation by the round bar-shaped shaft member 42. The spring effect is maintained. For this reason, it is possible to maintain good detachability (performance of press-fitting, fastening, and extraction) due to the elastic pinion deformation of the spring pin 41. Even when subjected to vibration during auger driving, the joint is ensured by a pressing force pressing the inner surfaces of the positioning groove 24 and the positioning hole 34 by the elastic recovery force of the spring pin 41 to expand the diameter. The pin 4 is held without dropping from the positioning groove 24 and the positioning hole 34.
As described above, after the spring pin 41 is restrained by the shaft member 42, the composite structure of the spring pin 41 and the shaft member 42 can withstand external pressure. Therefore, high rigidity and high strength of the joint pin 4 as a whole are achieved by the round bar-shaped shaft member 42, and an improvement in load resistance is achieved.

The joint pin 4 is completed before it is used after being fitted into the positioning groove 24 and the positioning hole 34, and the shaft member 42 is fixed to the spring pin 41. The shaft member 42 is inserted into the hollow portion of the spring pin 41 and fixed so as not to be displaced in the axial direction. This fixing is performed so that the spring pin 41 and the shaft member 42 are not displaced from each other in the axial direction even if the outer peripheral surface of the spring pin 41 and the inner peripheral surface of the shaft member 42 are separated or in contact with each other. To be fixed.
Therefore, it can be handled as one joint pin 4 from start to finish, and in addition to attachment and detachment, workability such as transportation, storage and the like is also good.

A flange 42 a is provided at one end in the axial direction of the shaft member 42, and a neck lower surface of the flange 42 a is hung on an axial end surface of the spring pin 41. That is, since the radius of the flange 42a exceeds the inner radius of the spring pin 41 when no load is applied, the lower surface of the neck of the flange 42a is prevented from entering the hollow portion of the spring pin 41. It is hung on the axial end surface of the.
Further, the radius of the flange 42a is equal to or less than the dimension obtained by adding the thickness of the elastic plate member constituting the spring pin 41 to the radius of the shaft member 42. Under such conditions, the flange 42a can be exerted with sufficient spring force by the spring effect of the spring pin 41 without interfering with the inner surface of the positioning hole 34, and the flange 42a is disposed in the positioning hole 34. Thus, the end of the joint pin 4 can be arranged so as not to protrude outward from the positioning hole 34. Thereby, it is not necessary to provide the convex part by the joint pin 4 in the outer periphery of the rotational force transmission shaft 102.
The flange 42a may be provided at both ends of the shaft member 42 in the axial direction. In that case, since the shaft member 42 is fixed to the spring pin 41 so as to sandwich the spring pin 41 in the axial direction by the flanges at both ends, the fixing pin 45 may be removed. The fixing pin 45 may also be applied to form a double safety structure.

(Examples of manufacturing methods and materials)
Next, an example of a manufacturing method and material examples of the joint pin 4 will be described.
As a material of the spring pin 41, for example, a spring steel material is applied. As a material of the shaft member 42, for example, a tool steel material is applied.
The joint pin 4 is preferably highly rigid and strong enough not to be deformed any more as long as the amount of elastic deformation of the spring pin 41 for attachment and detachment can be secured. Therefore, it is preferable that the shaft member 42 is configured as a solid round bar having a high section modulus and a high rigidity by applying a material having a high elastic coefficient. Thereby, the whole joint pin 4 becomes more rigid. As the material of the shaft member 42, the same material as that of the spring pin 41, the material having the same elastic modulus as that of the spring pin 41, and the material having a higher elastic modulus than that of the elastomer material 44 are applied even when applying a material having a lower elastic coefficient than that of the spring pin 41. By doing so, it is possible to achieve higher rigidity as the joint pin 4 as a whole rather than using an elastomer material for the entire spring pin 41. Preferably, the shaft member 42 is made of a material having a higher elastic coefficient than that of the spring pin 41.
The material of the elastomer material 43 and the elastomer material 44 may be natural rubber, synthetic rubber, or the like, which is provided as an adhesive (polyurethane elastomer adhesive, nitrile rubber adhesive, etc.).

As a manufacturing method, first, an unsolidified elastomer material is poured into the spring pin 41, a shaft member 42 having a flange 42a formed at one end is inserted therein, a fixing pin 45 is fitted therein, and a slit of the spring pin 41 is inserted. Also, an unsolidified elastomer material is filled, the exposed surface of the elastomer material is molded, and the elastomer material is solidified.
As another manufacturing method, a shaft member 42 having a flange 42a formed at one end is inserted into the spring pin 41, and another flange is welded and fixed to the other end of the shaft member 42. Thereafter, an unsolidified elastomer material is poured into the slit of the spring pin 41, the shaft member 42 is rotated, and the elastomer material is passed into the gap between the inner peripheral surface of the spring pin 41 and the outer peripheral surface of the shaft member 42. The exposed surface of the material is molded to solidify the elastomer material.

(Comparison explanation)
Next, the characteristics of the joint pin 4 according to the present embodiment will be described in comparison with the comparative joint pin 14 configured by only the spring pin shown in FIGS.

As described above, when the rotational force transmission shaft 102 is pulled up, a shear load is applied to the joint pin. However, in the comparative joint pin 14 as shown in FIG. Therefore, it is concerned that the male shaft 2 comes off from the female shaft 3.
On the other hand, according to the joint pin 4 according to the present embodiment, the spring pin 41 and the shaft member 42 are integrated to withstand a shear load as shown in FIG. Is sufficiently large, and the male shaft 2 can be sufficiently prevented from coming off from the female shaft 3.

As shown in FIG. 5, in the comparative joint pin 14, the earth and sand 9 enter from the hollow portion and the slit. The earth and sand 9 are clogged in the hollow portion and slit of the comparative joint pin 14 and further clogged between the male shaft 2 and the female shaft 3. Even when the hollow portion of the comparative joint pin 14 is filled with a member, the slit of the comparative joint pin 14 becomes an intrusion path, and the earth and sand 9 is also formed between the slit and the male shaft 2 and the female shaft 3. Clogged. In this case, both the extraction of the comparative joint pin 14 and the subsequent separation work of the male shaft 2 and the female shaft 3 may be difficult.
On the other hand, according to the joint pin 4 according to the present embodiment, the earth and sand 9 can adhere to the end face of the joint pin 4, but the hollow portion is the shaft member 42 and the elastomer material 44 as shown in FIG. Are buried with the elastomer material 43, the earth and sand 9 do not enter the inside of the connection structure, and the joint pin 4 can be easily pulled out and the subsequent separation of the male shaft 2 and the female shaft 3 from each other. It can be confirmed from FIG. 2 (c) that there is no gap to enter.
As described above, the joint pin 4 obtains a sealing property that prevents foreign matters such as earth and sand from entering the connection structure by the shaft member 42 and the elastomer materials 43 and 44.

As shown in FIG. 7, in the comparative joint pin 14, the end face is easily crushed and deformed by hitting during press-fitting and withdrawal. Further, since the comparison joint pin 14 in a state of protruding outward from the positioning hole 34 is hit by the hammer at the time of press-fitting, the comparison joint pin 14 may be bent and deformed. Therefore, it is difficult to withstand repeated reuse.
On the other hand, according to the joint pin 4 according to the present embodiment, the end face of the spring pin 41 is protected without being directly hit by hitting the flange 42a during press-fitting and withdrawal as shown in FIG. Further, during press-fitting, the joint pin 4 that protrudes outward from the positioning hole 34 is hit by a hammer, but the straightness of the entire joint pin 4 is maintained by the shaft member 42. Even if the shaft member 42 is hit, it is held by the elastomer material 44 so that the center axis of the shaft member 42 and the center axis of the spring pin 41 coincide. Therefore, deformation due to impact is suppressed and it is easy to reuse repeatedly. In addition, since the spring pin 41 can be used without causing plastic deformation due to impact, sealing performance can be maintained without generating a gap as a foreign matter entry path on the outer peripheral side of the spring pin 41 or the like.

(Another embodiment)
Still another embodiment will be described.
The joint pin 4B shown in FIG. 9 is provided with a shaft member 52 composed of a two-end flange type and composed of two parts, and the spring pin 51 is the same as the spring pin 41 of the above embodiment. The illustration of the elastomer material is omitted. Except for the matters described below, application of the elastomer material, dimension setting, and the like are the same as in the above embodiment.

  The shaft member 52 includes a part 52a and a part 52b. Since the flange 52a1 is formed on the part 52a and the flange 52b1 is formed on the part 52b, flanges 52a1 and 52b1 are provided at both ends in the axial direction of the shaft member 52. 51 is hung on the axial end surface. As described above, when the flanges 52a1 and 52b1 are provided at both axial ends of the shaft member 52, it is difficult to assemble the spring pin 51. Therefore, the shaft member 52 has two or more flanges 52a1 and 52b1 belonging to different parts. Parts 52a and 52b. It is also possible to comprise three or more parts including a part to which one end flange belongs, a part to which the other end flange belongs, and a shaft part between them.

The component 52a is formed with a female screw 52a2 in the axial direction from the opposite end surface of the flange 52a1, and the component 52b is formed with a male screw 52b2 protruding in the axial direction at the opposite end of the flange 52b1. The shaft member 52 is assembled by screwing and fastening the female screw 52a2 and the male screw 52b2. By performing this screw fastening in the spring pin 51, the assembly with the spring pin 51 is completed, and the joint pin 4B is configured. Thus, the assembly of the joint pin 4B can be disassembled after the assembly by using a screw type, and the joint pin 4B can exchange parts including the spring pin 41 for each part.
In order to engage a fastening tool such as a wrench for screw fastening, the outer peripheral surface 52a4 of the flange 52a1 and the outer peripheral surface 52b4 of the convex portion 52b3 are formed with two parallel surfaces, hexagons and other tool engaging surfaces. Yes. Of course, the tool engagement surface is not limited to a flat surface, and may have a special shape. In addition, although the convex part 52b3 which protrudes to an axial direction outward from the center part is formed in the flange 52b1, and the flange 52a1 does not have such a convex part formed, the structure of the flange 52a1 and the flange 52b1 is explained. A configuration in which the same convex portion is formed on both sides, a configuration in which the same convex portion is not formed on both sides, a configuration in which the same convex portion is formed on one flange 52a1, and the same convex portion is not formed on the other flange 52b1 are also possible.

  As in the illustrated example, it is preferable that the connection surfaces of the parts 52a and 52b constituting the shaft member 52 be located at a position unevenly distributed from the center in the axial direction. This is for ensuring high rigidity and high strength of the joint pin 4B against bending load received from the two parts (2, 3) connected by the joint pin 4B as shown in FIG. 12 (b).

As shown in FIG. 9A, the connection surface between the component 52 a and the component 52 b around the threaded portion of the female screw 52 a 2 and the male screw 52 b 2 can be implemented as a plane perpendicular to the central axis of the shaft member 52. .
On the other hand, as shown in FIG. 10 (a), the connection surface 53 between the component 52a and the component 52b around the threaded portion of the female screw 52a2 and the male screw 52b2 may be formed in a wedge shape. With such a wedge shape, the effect of suppressing loosening of the threaded portion of the female screw 52a2 and the male screw 52b2 is enhanced.
Moreover, the coupling | bonding of the components 52a and the components 52b may be implemented not only as a screw type but as a snap fit type as shown in FIG.10 (b). As shown in FIG. 10 (b), the male coupling portion 52b6 having a retaining claw formed at the tip is elastically deformed, and is fitted into the female coupling portion 52a6 having the nail receiving portion. Elasticity of the male coupling portion 52b6 for retracting the retaining claw when inserting the male coupling portion 52b6 into the female coupling portion 52a6 and for fitting the retaining claw into the nail receiving portion of the female coupling portion 52a6 when the insertion is completed The male connecting portion 52b6 is provided with a slit 52b7 formed in the axial direction from the tip so that the deformation is possible. If such a snap fit type is adopted, disassembly due to vibration or the like can be prevented, and the use of the fastening tool and the formation of the tool engagement surface described above are not necessary, and simplification is achieved in the work surface and the structure surface.

  In the joint pin 4B in which the flanges 52a1 and 52b1 are provided at both ends of the shaft member 52 as described above, the flange 52a1 or the flange 52b1 is hit by the joint pin 4B during the press-fitting and withdrawing operations. Suitable for use to hit. That is, it is suitable for the usage in which the press-fitting direction and the extracting direction of the joint pin 4B are opposite to each other. Therefore, as shown in FIG. 11 (a), a stepped portion 34a for locking the joint pin 4B is formed on the inner surface of the positioning hole 34 on the back side in the press-fitting direction of the joint pin 4B, and can be press-fitted only from one direction. And it can implement as a connection structure which does not escape in the press-fit direction.

  Further, a groove 34b is formed in the inner surface of the positioning hole 34 on the opposite side to the positioning hole 34 in which the step portion 34a for engaging the joint pin 4B is formed. Then, as shown in FIG. 12 (a), after the press-fitting of the joint pin 4B is completed, a locking member 54 such as a C ring is provided in the groove 34b, and the locking member 54 is fitted and fixed in the groove 34b. Is applied to the end surface of the joint pin 4B, so that the joint pin 4B can be reliably prevented from coming out. Of course, since it is latched also by the elastic force of the spring pin 41, it is arbitrary whether the latching member 54, such as C ring, is applied.

In the present embodiment, the convex portion 52b3 is smaller in diameter than the flange 52b1, and the locking member 54 is engaged with the flange 52b1. The convex portion 52b3 is smaller in diameter than the flange 52b1 so that the locking member 54 can be attached and detached. A taper 52b5 is attached to the tip of the convex portion 52b3 from the outer peripheral surface 52b4. Since the locking member 54 is guided toward the groove 34b by the taper 52b5 when the locking member 54 is attached, workability is good.
Moreover, the convex part 52b3 becomes a part which receives a hit when the joint pin 4B is press-fitted. The portion subjected to the impact is deformed by repeated impacts and projects outward in the radial direction. However, since the convex portion 52b3, which is a portion that receives the impact, has a small diameter, it is prevented from projecting until it comes into contact with the inner peripheral surface of the positioning hole 34 due to deformation during impact. Furthermore, since the tip of the convex portion 52b3 has a smaller diameter due to the taper 52b5, the protrusion of the convex portion 52b3 is prevented from projecting until it comes into contact with the inner peripheral surface of the positioning hole 34 due to deformation at the time of impact. Even if deformation occurs in the convex portion 52b3 due to the impact for press-fitting in the first time or reuse, the inner peripheral surface of the positioning hole 34 or the groove 34b is not contacted with the inner peripheral surface of the positioning hole 34. Damage is prevented. Further, since there is the convex portion 52b3, the hammer and the hitting rod used for hitting do not reach the groove 34b and do not damage the groove 34b. Since the groove 34b is not damaged, the groove 34b can be repeatedly used as a groove into which the locking member 54 such as a C-ring is fitted.
In the state shown in FIG. 12 connected using the joint pin 4B, the projection 52b3 prevents the earth and sand from directly and strongly hitting the locking member 54 such as the C ring, and the locking member 54 such as the C ring. Is protected.

  In order to extract the joint pin 4B from the state shown in FIG. 12, after removing the locking member 54 such as a C-ring, the end of the shaft member 52 provided with the flange 52a1 is hit. The end portion of the shaft member 52 provided with the flange 52a1 is a portion that receives a hit when being pulled out, but is similarly provided with a taper 52a5 and stretches until it comes into contact with the inner peripheral surface of the positioning hole 34 due to deformation at the time of hitting. Protruding is prevented, damage to the inner peripheral surface of the positioning hole 34 and the groove 34b is prevented, and repeated usability is ensured. Further, since the taper 52a5 is provided at the tip when the joint pin 4B is inserted into the positioning hole 34, it acts as a guide for insertion of the joint pin 4B and improves workability.

  In the above embodiment, the joint pin is applied to the auger shaft connection structure, but the present invention is not limited to this, and the joint pin may be applied to the connection between the excavation claw and its holder, and various other types. It can be applied to a two-part connecting structure.

Reference Signs List 1 auger shaft connection structure 2 male shaft 3 female shaft 4 joint pin 9 earth and sand 24 positioning groove 34 positioning hole 41 spring pin 42 shaft member 42a flange 43 elastomer material 44 elastomer material 45 fixing pin 4B joint pin

Claims (8)

A spring pin with a hollow structure in which an elastic plate is wound into a cylindrical shape leaving a slit, and
A round bar-shaped shaft member inserted and fixed in the hollow portion of the spring pin,
The space between the inner peripheral surface of the spring pin and the outer peripheral surface of the shaft member at the time of no load is a gap, or a shock absorber is installed between the two, so that the elastic pinion deformation of the spring pin is reduced. Enabled joint pin.   2. The joint pin according to claim 1, wherein a length of the outer periphery of the shaft member at the time of no load is equal to or longer than a length of an inner periphery of the spring pin at a time of no load excluding a portion that is applied to the slit. .   The joint pin according to claim 1, wherein the slit is filled with a buffer material and sealed.   The joint according to any one of claims 1 to 3, wherein a flange is provided at one or both ends in the axial direction of the shaft member, and a neck lower surface of the flange is hung on an axial end surface of the spring pin. pin. Flange is provided at both axial ends of the shaft member, and the neck lower surface of the flange is hung on the axial end surface of the spring pin,
The joint pin according to any one of claims 1 to 3, wherein the shaft member includes two or more parts in which flanges at both ends belong to different parts.   The joint pin according to claim 5, wherein a connection surface between the parts constituting the shaft member is a position that is unevenly distributed from the center in the axial direction.   The radius of the flange exceeds the inner radius of the spring pin when no load is applied, and is equal to or less than the dimension obtained by adding the thickness of the elastic plate to the radius of the shaft member. The described joint pin. It is a connection structure of two parts by the joint pin according to any one of claims 1 to 7,
A connection structure using a joint pin in which the spring pin and the shaft member are both supported by one component and the other component is held between fulcrums of the both components.

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