KR830000563B1 - Joining method of two members - Google Patents

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Description

Joining method of two members

1 is a partial cross-sectional view showing the structure of the member to be joined and the joining member used in practicing the present invention.

2 is a cross-sectional view taken along the line II-II of FIG.

3 is a perspective view showing a coupling member.

4 is a partial cross-sectional view showing the arrangement of the member to be joined and the member before pressing.

5 and 6 are partial cross-sectional views showing the engaging portion after pressing.

7 and 8 are cross-sectional views showing the engaging portions in the case where the depth of the grooves on the mating surface is small and when they are large, respectively.

9 and 10 are partial cross-sectional views showing the engaging portion when the difference between the height of the engaging member and the height of the member to be joined is large.

11 and 12 are cross-sectional views respectively showing engagement portions in the case where the height of the axial groove formed in the groove on the engagement surface is small and large.

13 is a cross-sectional view showing a flywheel magnet to which the present invention is applied.

14 is a perspective view of the boss shown in FIG.

FIG. 15 is a sectional view of the flywheel shown in FIG.

16 to 18 each show an example of a groove processing method.

19 is a view comparing the magnitude of the torque by the coupling method of the present invention with the case of rivet coupling.

20 is a view comparing the repetition frequency by the coupling method of the present invention with the case of rivet bonding.

21 and 22 are cross-sectional views showing another embodiment of the present invention, respectively.

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method in which a third coupling member is inserted, cold pressurized and plastically flowed together between two joining surfaces of a member to be joined.筒 狀 部 材) The present invention relates to a coupling method most suitable for use in the case where the mutual fixing is required and a large torque is required.

)리베트 조임등이 있다.As a general method of joining two members to be joined, welding (including soldering) is injected.

There are rivet tightening.

In the welding method, since the heat is generated together with the member to be joined and the member, thermal deformation occurs, and a high degree of precision is difficult to obtain. In addition, there are limitations on the selection of the member to be joined, the member to be joined, and the welding rod lead material. In addition, there are disadvantages such as low productivity, the need for large-scale facilities, or the likelihood of quality defects caused by the confusion of working conditions.

法)에서는 결합강도를 확보하기 위하여 주철을 휘감는다든가 회전정지기구 등을 설치함으로써 구성이 번잡하게 되어 대형화 한다.Injection method

In the law, the structure is complicated by winding the cast iron or installing the rotation stop mechanism to secure the bonding strength.

In addition, there are limitations in the selection of materials for the joining member and the like, and other disadvantages include low productivity and low precision.

Rivet tightening is used when a large torque transmission is required, such as the coupling of a shaft and a flywheel in a flywheel magnet for ignition or inspection of a small internal combustion engine. However, rivets require a large collar diameter or needless space in the axial direction for rivet mounting.

In addition, since the rivet has a small adhesion, there is a problem of poor lighting reliability.

As a method of directly joining two to-be-engaged members, there is a press-fitting caking method.

法)에서는 강도에 한계가 있고 특히 충격이 약하다. 또한 주철과 같이 신장이 없는 부재의 경우 소요의 강도가 얻어지지 않는다.Indentation Method

In law, the strength is limited, especially the impact is weak. In addition, in the case of a member without elongation such as cast iron, the required strength cannot be obtained.

In the caulking method, there are material restrictions on the member to be subjected to caulking. That is, the material which can be used as a material with little deformation resistance is limited. For example, cast iron cannot be used. Therefore, sufficient bonding strength cannot be obtained in any material configuration.

Moreover, when there is a big difference in the thermal expansion coefficients of two to-be-joined members, there exists a fault that bond strength may fall remarkably depending on a use temperature condition.

The method of inserting a coupling member between two to-be-engaged members and joining a to-be-engaged member according to the plastic deformation of a coupling member is also known. See, for example, U.S. Patent 3,559,946.

According to this known example, grooves each having a joining surface of two members having a rectangular cross-sectional shape are respectively provided, and a coupling member is inserted between two members to be joined. A part is plastic flow in the groove. However, in this configuration, since the cross-sectional shape of the groove is rectangular, the coupling member does not flow completely in the groove, and a gap is generated between the inner surface of the groove and the coupling member.

Moreover, since the coupling force between the two engaged members is only a friction force between the surface of the flat grooved surface wave coupling member, a large torque can be transmitted.

SUMMARY OF THE INVENTION An object of the present invention is to provide a joining method that can freely select the materials of two members to be joined and can deliver a large torque by being mechanically strong, having a small work process, and simplifying a small space.

Features of the present invention are as follows. First, a constant space portion having grooves in the circumferential direction is formed between mutually opposing mating surfaces of the two engaged members.

On the inner surface of the groove again, fewer recesses are formed.

On the other hand, a coupling member having a simpler shape having a deformation resistance lower than that of the member to be joined and having a predetermined mechanical strength and having a height close to or above the space portion is processed. Next, this coupling member is inserted into the space part.

At this time, it is assumed that the coupling member is substantially in a state surrounded by the coupling member and the mold.

In this state, the coupling member is cold pressed by the mold press, and the coupling member is plastically flown in the groove of the space to join the sheepskin coupling member. In particular, the present invention is characterized in that a large torque can be transmitted by forming a shock in the groove formed in the member to be joined again.

1 to 12 illustrate the basic principle of the present invention.

First, in FIG. 1, the first to-be-engaged member 2 and the second to-be-engaged member 4 are both metal disks, such as steel, and the mating surfaces of the members 2 and 4 ( The width t ₀ , the height H ₀ , and the ring-shaped space 10 are interposed between 6) and (8). The engaging surfaces 6 and 8 are formed with grooves 12 and 14 in the circumferential direction, respectively.

As shown in Fig. 2, small grooves 16 in the axial direction are provided on the entire surface of each of the grooves 12 and 14 in the circumference, thereby forming the surface. The average depth h ₁₀ from the mating surface 6 to the center line mm of the groove 16 is 0.2 mm to 1.0 mm. 0.2 mm-0.5 mm are especially preferable.

The height h ₁₁ of the grooves 16 is also 0.2 mm to 1.0 mm, particularly 0.2 mm to 0.5 mm.

The values of h ₁₀ and h ₁₁ described above are preferable values regardless of the dimensions of the member to be joined.

On the other hand, the coupling member 18 is a metal that is more easily plastically deformed, that is, has a lower deformation resistance than the members 2 and 4 to be joined.

Aluminum, brass, copper, mild steel are good examples. In particular, mild steel is preferred in consideration of the demand for mechanical strength.

The width T ₁ is preferably equal to (T ₀ ) or slightly less.

The height H ₁ is preferably equal to or slightly less than (H ₀ ).

For example, even when H ₁ is larger than H ₀ , the difference ΔH is preferably limited to about 0.2 mm to 0.3 mm, if possible.

The reason will be described later. The cross-sectional shape of the coupling member 18 may be a simple shape such as a circle, an ellipse, or a polygon, in addition to the rectangular cross section shown in FIG. It is not necessary to take the shape of the space 10 in order to plastic deformation after insertion. In addition, the coupling member 18 may be bent into a ring shape having a cutout by bending the wire rod, or may be processed into a complete ring by sintering as shown in FIG.

In the joining process, first, as shown in FIG. 4, the space member 10 between the two members 2, 4 to be engaged is inserted into the coupling member 18. As shown in FIG.

Next, as shown in FIG. 5, the pressing portion 24 of the mold 22 having its tip end surface having a width t less than the width T ₀ of the space portion 10 is placed on the mold 20. Pressing the coupling member 18 and the coupling member 18 is introduced into the grooves 12, 14 by plastic deformation. In the state shown in FIG. 4, the coupling member 18 is surrounded by the surfaces of the coupled members 2 and 4 except for the upper and lower portions corresponding to the molds 20 and 22, and the height is high. The difference ΔH is very small, 0.2 mm to 0.3 mm. Therefore, in the state immediately before the pressing, it can be said that the whole of the coupling member 18 is surrounded by the member 2, 4, the mold 20, and 22.

Therefore, as shown in FIG. 5, the coupling member 18 hardly escapes to the space 10 during pressurization.

6 is a view showing a state in which the coupling is completed.

In the drawing, a stress P acts on the inside of the coupling member 18, and the groove 12 of the groove 12 of the first to-be-engaged member 2 and the groove of the second to-be-engaged member 4 14) The engaging surface 8 is firmly widened.

Next, the critical factors for enhancing the effect of the invention will be specifically discussed.

That is, the element is (I) the inclination angle (θ) of the side of the pressing section 24 of the mold 22, (II) the groove 12 is provided on the engaging surface of the member 2, (4), Position of (14), (III) average depth (h ₁₀ ) of the grooves (12), (14), (IV) inclination angle α _1, α ₂ , (V) coupling of the side of the grooves (12), (14) The relationship between the height H ₁ of the member 18 and the height H ₀ of the member 2 and 4, (VI) the finer grooves 16 provided in the grooves 12 and 14; height (h _11), (ⅶ) it is the tip angle β of the groove 16.

(I) The inclination angle (theta) of the side part of the press part 24 of the 1st metal mold | die 22 is examined.

As shown in FIG. 5, the side surface of the press part 24 of the metal mold | die 22 is inclined by (theta) with respect to the direction orthogonal to the front end surface (same as the insertion direction of the mold 22). The inclination angle θ is preferably about 3 ° to 15 °. In particular, 6 degrees-15 degrees are preferable.

This is because if the θ is small, the mold 22 is hard to come out after joining. If the θ is too large, the coupling member 18 easily flows out of the mold 22 in the opposite direction to the insertion direction of the mold 22, and the insertion depth cannot be deepened. Cannot be produced and therefore it is difficult to obtain a large bonding force.

(II) The positions of the grooves 12 and 14 provided in the engagement surfaces 6 and 8 of the second to-be-engaged members 2 and 4 will be examined.

As shown in FIG. 5, the pressing portion 24 of the mold 22 has a distance S between the tip end face and the upper end of the grooves 12 and 14 of the member 2 and 4 to be engaged. It is desirable to insert as small as possible, in other words, as deep as possible as close to the end face as possible. Since S represents the length of the frictional force between the member 2, 4 and the engaging member 18, S decreases the friction loss due to plastic flow and decreases the grooves 12, ( 14, which can sufficiently introduce the coupling member (18).

The insertion depth of the mold 22 is a dimension sufficient to sufficiently fill the grooves 12 and 14 with the coupling member 18, and the stress required inside the coupling member 18 to remain.

(III) The average depth h ₁₀ of the third grooves 12 and 14 is examined. As a result of the experiment, when the depth h ₀ is 0.2 mm or less, as shown in FIG. 7 when the axial force is applied to one of the member 2 to be engaged, the coupling member 18 includes the groove 12, Slip occurs within 14, and shear force of the engaging member 18 does not act. Therefore, the to-be-engaged members 2 and 4 deflect in the axial direction without opposing the axial force. In addition, when the depth h ₁₀ of the grooves 12 and 14 is 1.0 mm or more, the coupling member is formed in the grooves 12 and 14 even when the coupling member 18 generates plastic deformation by pressing as the mold 22. (18) does not flow enough.

As shown in FIG. 8, a gap is generated between the inner surfaces of the grooves 12 and 14 and the engaging member 18. As shown in FIG.

Therefore, when the force in the axial direction is applied to one of the member 2 to be engaged, the coupling member 18 causes plastic deformation and the member 2 and 4 to be engaged are axially mutually similar to the case of 0.2 mm or less. Missing In view of the above, the depth h ₁₀ of the grooves 12 and 14 is preferably 0.2 mm to 1.0 mm.

(IV) The inclination angles α ₁ and α ₂ of the side surfaces of the grooves 12 and 14 in FIG. ₄ will be examined.

The inclination angle α ₁ of the upper surfaces of the grooves 12 and 14 is preferably set to 45 ° in the plastic flow direction of the coupling member 18, but can be practically provided if it is in the range of 20 ° to 70 °. In this embodiment, the upper side forms a flat surface, but the flat surface is the most preferred embodiment and may be a curved surface.

In this case, it selects so that the tangential direction at the uppermost end may be less than a right angle, and it may fall in the range of 20-70 degrees in a space area.

Since the inclination angle α ₂ of the lower side is not connected to the rear face and the coupling member 18 flows out, the inclination angle α ₂ may be formed within 90 degrees including 90 degrees. The lower side is not limited to a flat surface but may be a curved surface, but a flat surface is most preferred.

(V) The relationship between the height H ₁ of the engaging member 18 in FIG. 5 and the height H ₀ of the space portion of the engaged members 2 and 4 will be examined.

The volume of the coupling member 18 may be about the volume of the space 10 so as to sufficiently introduce the coupling member 18 into the space 10 of the member 2, 4 to be engaged.

However, as shown in FIG. 9, if the height difference [Delta] H is coupled using a relatively large coupling member 18, as shown in FIG. 10, the end of the coupling member 18 is deformed.

Therefore, even if the volume of the coupling member 18 is greater than or equal to the volume of the space portion 10, in the vicinity of the grooves 12 and 14, an interval of? ₁ and? ₂ remains.

The same result as that of the conventionally known riveting method is achieved. This is for the following reason.

Claim 10 is also in the mold 20, 22. Compressing the coupling member 18 of a ring shape by axially coupling member 18. ln shown σ ₂ (the σ ₁ the circumferential direction to the axial direction are not in Generates internal stress σ ₃ in the radial direction.

On the other hand, if the deformation resistance of the coupling member 18 is Kf,

sigma ₁ = (1 to 1.5) Kf... … … … … … … … … … … … … … … … … … … … … … … … (One)

There is a relationship.

Near the both ends at the time of pressure bonding member 18 does not act in a non-binding radial σ ₁ is the largest size σ ₃ is the minimum. Therefore, the following relationship is established by the formula of TRESCA which gives a yield condition.

Kf = sigma _1- sigma ₃ ... … … … … … … … … … … … … … … … … … … … … … … … (2)

Substituting equation (1) into equation (2),

σ ₃ = σ ₁ -Kf... … … … … … … … … … … … … … … … … … … … … … … … (2')

= (1 to 1.5) Kf)-Kf = (0 to 0.5) Kf... … … … … … … … … … … … … … (3)

That is, the stress sufficient to plastically deform the coupling member 19 radially, that is, in the grooves 12, 14 of the member 2, 4 to be engaged does not occur.

On the other hand, according to the method of the present invention, as shown in FIG. 5, the coupling member 18 is substantially entirely in the coupling member 2, 4 and the mold 20, 20 when pressurized. Because it is bound by

sigma ₁ = (2 to 4) Kf... … … … … … … … … … … … … … … … … … … … … … … … (4)

If you substitute in the equation (2)

σ ₃ = (2 to 4) Kf-Kf

= (1 to 3) Kf

And a stress of strain resistance Kf or higher occurs.

Therefore, the coupling member 18 flows completely into the grooves 12 and 14.

In this way, in order to restrain when the coupling member 18 is pressed, the height H ₀ of the coupling member 18 may be substantially equal to or less than the height H ₀ of the space 10. However, if the height H ₁ of the coupling member 18 is too low, it is necessary to increase the insertion stroke of the molds 20 and 22 in order to sufficiently flow into the grooves 12 and 14, but the mold pressurization is required. The stroke has a limit because the side inclination angle θ of the part 24 cannot be made very small. Therefore, the coupling member 18, the volume of the space portion 10 at a slightly lesser extent than the volume of the space portion 10, the width (T ₀₎ and a height in consideration of the inclination angle (θ), such as a mold pressing portion (24) (H in ₁ ) needs to be determined.

(VI) The average depth h ₁₁ of the more detailed grooves 16 formed in the grooves 12 and 14 of FIG. 6 is examined.

The average depth of the grooves 16 can be said to be the same as in the case of the grooves 12 and 14. That is, the average depth h ₁₁ of the grooves 16 is preferably 0.2 mm to 1.0 mm, and more preferably 0.2 to 0.5 mm.

Particularly, in the case of forming the groove 16 close to the cross-section triangle by the process of the kneading tool, when the depth h ₁₁ of the groove 16 becomes 0.2 mm or less, it flows into the groove 16 as shown in FIG. The shear force of the engagement member 18 is determined as the partial cross-sectional area of A, which is a relatively small area. Therefore, the shear force is relatively small and the coupling member 18 can shear shear to transmit a large torque.

When the depth h ₁₁ exceeds 1.0 mm, as shown in FIG. 12, the engagement member 18 is less likely to enter the groove 16 due to the frictional force of the inner surface B of the groove 16, and the groove 16 A gap 26 is generated at the tip of the head.

As a result, the coupling member 18 causes plastic deformation due to the force in the circumferential direction and cannot transmit a large torque.

(Iii) The tip angle β of the groove 16 shown in FIG. 2 of FIG. 7 is preferably 60 ° to 120 °.

In the case of 60 degrees or less, when the coupling member 18 is 120 degrees or more which is hard to flow in the groove 16, the torque transmission effect by the groove 16 is small. As apparent from the embodiments described above, the present invention can be applied to a case where the space part is maintained in a constant state by two members to be joined. For example, the second edition's concentric shaft and the original. On the other hand, if the space is not held in a fixed state by the two members to be joined, such as only two flat plates, the coupling force is obtained even when the coupling member is inserted between the two members. I do not lose.

In other words, a stress must be applied between the member to be joined by the insertion of the member.

In the invention as described above, the following effects are obtained. By forming fine grooves again on the inner surface of the grooves on the engagement surfaces of the two engagement members, a large torque of one engagement member can be reliably transmitted to all the engagement members. Since the internal stress P required for the mating surface and the groove can be generated, a mechanically stable bonding force is obtained.

In addition, since the coupling member is filled in the groove, the axial pull force Q becomes the value of the shear strength of the material of the coupling member and the product of the shear area, which is very large. In addition, since the first to be joined member and the second to-be-joined member are materials having a higher deformation resistance than the joining member, the first and second to-be-engaged members are welded without distortion by welding and plastic flow. Since there is no thermal deformation, high accuracy is maintained.

This can be said to be an advantageous joining method in the case of the present joining method, since the member to be joined can be used in a form in which the final product is dimensioned and surface treated in advance. This means that the first and second to-be-engaged members can select materials necessary for the product configuration. This is because the coupling member can be selected by selecting a material having a lower deformation resistance than the member to be joined.

In addition, the joining member may have a simple shape, the production process is simple to join by cold press, the productivity is high, and the equipment is sufficient on the scale of the hydraulic press for press.

Embodiments described above relate to the basic configuration of the present invention.

The application example of the practical use of a product is shown below, and the effect is written together.

As shown in FIG. 13, the coupling method of the present invention is adapted as a main portion of the flywheel magnet. In FIG. 13, since the shaft 40 is driven by an internal combustion engine, one end thereof becomes a taper portion 42. As shown in FIG.

The boss 44 is fixed to the shaft 40 at the nut 46. The flywheel 48 is fixed to the boss 44 by the coupling method of the present invention.

The magnet 50 is fixed to the flywheel 48, while the coil 53 is fixed to the fixed plate 52.

Since the rotational force of the internal combustion engine varies intermittently, a large torque transmission is required for engagement between the boss 44 fixed to the shaft 40 and the flywheel 48. The boss 44 and the flywheel 48 are engaged as a coupling member 55.

As shown in FIG. 14, the circumferential groove 54 is provided in the outer peripheral surface of the engaging part of the boss 44, and the fine groove 56 of the axial direction is provided in the bottom face of the groove 54. As shown in FIG.

Also in the flywheel 48, as shown in FIG. 15, a small groove 60 in the axial direction is formed in the main direction groove 58. As shown in FIG.

These grooves 56 and 60 are formed by a knurling tool processing as shown in FIG. 16 or by cutting using a bite as shown in FIGS. 17 and 18.

In FIG. 16, a small groove 56 in the axial direction is formed on the bottom surface of the groove 54 by pressing the kneading tool commer 62 in the direction of the arrow 66 against the boss 44 that rotates in the direction of the arrow 64. ) Is formed.

In Fig. 17, the boss 44 is held on the swivel table 68 via a shaft, and the swivel table 68 is rotated and processed while applying the vibration in the direction of the arrow 72 to the one-way bite 70.

As shown in FIG. 18, the bite 74 can be processed while applying the vibration in the oblique direction as shown by the arrow 76. FIG.

According to this method, the groove 54 and the groove 56 can be formed simultaneously.

FIG. 19 shows the test results obtained by obtaining the magnitude of the torque T with respect to the coupling structure A of the present invention shown in FIG. 13 and the coupling structure B by six rivets.

The joining member is made of mild steel with a boss outer diameter of 38 mm, a flywheel inner diameter of 42 mm, an outer diameter of 102 mm, an average depth of the main groove (h ₁₀ ) and an average height of the axial groove (h ₁₁ ), respectively, 0.3 mm The inclination angles α ₁ and α ₂ were both static torque tests under the condition of 45 ° and the width of the grooves in the circumferential direction was 2 mm.

As a result, a torque of 135 kgm was obtained.

On the other hand, a torque of 92.5 kg · m was obtained under the tightening conditions by adding a boss outer diameter of 38 mm, a flywheel inner diameter of 42 mm, an outer diameter of 102 mm, a rivet diameter of 6 mm, a rivet mounting position diameter of 60 mm, and six, resulting in breakage at the joint.

In addition, in the case where the microgrooves in the axial direction are formed on the inner surfaces of the grooves of the boss and the flywheel, the torque can be three times larger than in the case where the axial grooves are not formed.

20 shows the results of repeated impact tests (angular acceleration) on the structure having the same structure as in FIG.

The flywheel weighs 1.4 kg and the angular acceleration W is 5 red / sec ² .

According to the joining structure (A) of the present invention, the number of repetitions is 5 × 10 ^{4 in} the case of the joining structure (B) by riveting, while the number of repetitions (N) until reaching the joint breakage is 6 × 10 ⁶ . .

In Fig. 13, there are only 14 positions where the boss and the flywheel are engaged, but as shown in Fig. 21, when the boss and the flywheel are engaged in two places (78) and (80) in the axial direction, a larger engagement force is obtained.

22 is a view showing an example in which the present invention is applied to the coupling of the cog wheel and the shaft.

The gear 82 has a ball in the center thereof, the diameter of which is equal to the outer diameter of the shaft 84. A part of the hollow surface is provided with a groove at a certain distance from the cross section of the cog wheel, and under the groove, another groove in the axial direction is formed as described above.

On the other hand, the shaft 84 is provided with the groove corresponding to the said groove, and the other groove 16 of the axial direction is provided in the bottom part.

In the coupling method, as in the above-described example, the gear 82 is press-fitted into the shaft 84 and then the coupling member 88 is press-inserted into the space including the groove.

The coupling structure obtained in this way can transmit a large torque, and the coupling state does not deteriorate even if the rotational force accompanying an impact is applied.

In addition to the above-described applications, the present invention can act on a combination of a cylinder, a shaft, a disk such as a shaft and a plate, a cylinder, a shaft, a circumference, a plate, a rod, and the like.

Claims (1)

The first member 2 and the second member 4 having the grooves 12 and 14 formed on the entire circumference of the mating surfaces 6 and 8 are opposed to each other at intervals, and the first and second described above are spaced apart. In the joining method of the two members formed by bonding the joining member 18 having a deformation resistance smaller than the second members 2 and 4 and having a predetermined mechanical strength by plastic deformation by pressing, the groove 12 described above. 14 is formed on the bottom surface of the two members, and the coupling member 18 is filled in the recess 16 and the grooves 12 and 14 by plastic deformation and fixed. Joining method.

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