Screw thread structure for preventing being pulled out and tool for manufacturing same

The present invention provides a looseness-prevention screw thread structure including a screw thread having a predetermined pitch, a no-load flank which is an inclined surface in a direction in which the screw thread is advanced, and a load flank which is an inclined surface in a direction in which the screw thread is retracted, the no-load flank and the load flank being formed at both sides of the screw thread, in which the no-load flank of the screw thread includes: a first tangential portion which abuts against an arc portion formed at a thread crest of an opposing fastening object; and a second tangential portion which has a preset angle with respect to the first tangential portion and abuts against the arc portion.

CROSS REFERENCE TO PRIOR APPLICATIONS

This application is a National Stage Application of PCT International Patent Application No. PCT/KR2016/000027 filed on Jan. 5, 2016, under 35 U.S.C. § 371, which claims priority to Korean Patent Application No. 10-2015-0048798 filed on Apr. 7, 2015, which are all hereby incorporated by reference in their entirety.

TECHNICAL FIELD

The present invention relates to a looseness-prevention screw thread structure and a tool for machining the same, and more particularly, to a looseness-prevention screw thread structure in which a first tangential portion and a second tangential portion are formed on a no-load flank of a screw thread in order to minimize looseness caused by external impact or vibration, and a tool for machining the same.

BACKGROUND ART

In general, screws include an external thread and an internal thread that basically operate as a pair and have appropriate dimensions, and the screws are mainly used to fasten objects.

As representative fastening means using the screws, there are a bolt having the external thread, and a nut having the internal thread, but there occur the following problems when objects are coupled by using the existing bolts and nuts.

When objects are coupled by using the existing bolts and nuts, a bolt109is inserted into and penetrates two objects30and31to be coupled, and then an internal thread portion105aof a nut105is fastened to a protruding external thread portion109aof the bolt109, as illustrated inFIG. 1.

Here, a flank refers to an inclined surface that connects a thread crest and a thread root, and the flanks are divided into a no-load flank which is an inclined surface in a direction in which the thread is advanced based on the thread crest, and a load flank which is an inclined surface in a direction in which the thread is retracted.

When the bolt109or the nut105is rotated to fasten the internal thread portion105aof the nut105to the external thread portion109aof the bolt109, a no-load flank107of a screw thread106, which constitutes the internal thread portion105aof the nut105, and a no-load flank111of a screw thread110, which constitutes the external thread portion109aof the bolt109, come into surface-to-surface contact with each other by axial force which is applied when fastening the internal thread portion105aof the nut105to the external thread portion109aof the bolt109.

Further, when the internal thread portion105aof the nut105is completely fastened to the external thread portion109aof the bolt109as illustrated inFIG. 2, a load flank108of the nut105and a load flank112of the bolt109strongly and tightly come into surface-to-surface contact with each other by compressive force applied as the bolt109and the nut105are coupled to each other, and for this reason, strong frictional force is applied between the load flank108of the nut105and the load flank112of the bolt109, and as a result, a fastened state of the bolt109and the nut105is maintained.

An assembly tolerance C is typically present between an outer diameter of the bolt109and an inner diameter of the nut105for the purpose of ease of assembly, and in a case in which the fastened state of the bolt109and the nut105is maintained only by frictional force applied between the load flank108of the nut105and the load flank112of the bolt109, there is a problem in that the load flank108of the nut105and the load flank112of the bolt109, which are in close contact with each other, are separated from each other due to a gap caused by the assembly tolerance C when external impact or vibration is applied, such that frictional force, which is applied only when the load flank108of the nut105and the load flank112of the bolt109are in close contact with each other, easily deteriorates or disappears, and as a result, the bolt109or the nut105is often loosened.

To solve the aforementioned problem, in the related art, there has been used a method of coupling the bolt and the nut in a state in which a spring with a looseness-prevention function or a ring with a reverse rotation prevention protrusion is interposed between the bolt and the nut, a method of filling a portion between the outer diameter of the bolt and the inner diameter of the nut with an adhesive, or silicone or nylon, or the like.

However, according to the threaded engagement method using the looseness-prevention means in the related art, the fastening process cannot be easily performed because the fastening process is performed in a state in which there is almost no assembly tolerance C, the configuration thereof is complicated, and the number of production processes is increased, such that production costs and a selling price are increased overall, and as a result, there is a problem in that the fastening process is limited and applied only to some machines that require precision or to high-priced products, but the fastening process cannot be widely and universally used.

Accordingly, there is a need for a method for solving the aforementioned problems.

DISCLOSURE

Technical Problem

The present invention has been made in an effort to solve the problems in the related art, and an object of the present invention is to effectively prevent looseness caused by external impact or vibration by securely maintaining frictional force applied between load flanks after the threaded engagement.

Technical problems of the present invention are not limited to the aforementioned technical problems, and other technical problems, which are not mentioned above, may be clearly understood by those skilled in the art from the following descriptions.

Technical Solution

To achieve the aforementioned object, the present invention provides a looseness-prevention screw thread structure, including a screw thread having a predetermined pitch, a no-load flank which is an inclined surface in a direction in which the screw thread is advanced, and a load flank which is an inclined surface in a direction in which the screw thread is retracted, the no-load flank and the load flank being formed at both sides of the screw thread, in which the no-load flank of the screw thread includes: a first tangential portion which abuts against an arc portion formed at a thread crest of an opposing fastening object; and a second tangential portion which has a preset angle with respect to the first tangential portion and abuts against the arc portion.

Further, the first tangential portion and the second tangential portion may simultaneously abut against and come into contact with the arc portion in a state in which the screw thread is fastened to the opposing fastening object.

In addition, the second tangential portion may be formed to have a larger angle with respect to a horizontal line than the first tangential portion.

Further, the first tangential portion and the second tangential portion may be formed to have a smaller angle with respect to a horizontal line than the load flank.

In addition, the screw thread may be formed to have a dimension that satisfies the international standard, and the first tangential portion may have an angle of 4° to 6° with respect to a horizontal line.

Further, the first tangential portion may have an angle of 5° with respect to the horizontal line.

In addition, the second tangential portion may have an angle of 35° with respect to the horizontal line.

Further, a tool for machining the looseness-prevention screw thread structure according to the present invention may include machining tools having various shapes for machining the looseness-prevention screw thread structure to make an internal thread or an external thread.

Advantageous Effects

The looseness-prevention screw thread structure and the tool for machining the same according to the present invention for solving the problems have the following effects.

First, the first tangential portion and the second tangential portion, which simultaneously abut against the arc portion formed at the thread crest of the opposing object during the threaded engagement, are formed at the no-load flank which is an inclined surface in the direction in which the screw thread is advanced, such that the frictional force applied between the load flanks is securely maintained after the threaded engagement, and as a result, it is possible to effectively prevent looseness caused by external impact or vibration.

Second, the tool for machining the looseness-prevention screw thread according to the present invention may easily machine the screw thread structure, which has the first tangential portion and the second tangential portion formed at the no-load flank of the screw thread, in order to make an internal thread or an external thread.

The effects of the present invention are not limited to the aforementioned effects, and other effects, which are not mentioned above, will be clearly understood by those skilled in the art from the claims.

BEST MODE

Hereinafter, an exemplary embodiment of the present invention for specifically accomplishing the objects of the present invention will be described with reference to the accompanying drawings. In the description of the present exemplary embodiment, like terms and like reference numerals are used for like configurations, and additional descriptions will be omitted.

FIG. 3is a view illustrating a looseness-prevention screw thread structure according to the present invention.

As illustrated inFIG. 3, the looseness-prevention screw thread structure according to the present invention has a screw thread1having a predetermined pitch, and a no-load flank2, which is an inclined surface in a direction in which the screw thread1is advanced, and a load flank3, which is an inclined surface in a direction in which the screw thread is retracted, are formed at both sides of the screw thread1.

Meanwhile, the flank refers to an inclined surface that connects a thread crest and a thread root, and the flanks are divided into the no-load flank2which is the inclined surface in the direction in which the screw thread1is advanced based on the thread crest, and the load flank3which is the inclined surface in the direction in which the screw thread1is retracted.

The reason why the flanks formed at both sides of the screw thread1are divided into the no-load flank2and the load flank3will be described below.

In general, during the threaded engagement, the no-load flanks2come into contact with each other first, and in this case, no load is applied between the flanks that are in contact with each other. Further, the load flanks3come into contact with each other after the threaded engagement is completed, and in this case, a high load is applied between the flanks that are in contact with each other.

In this screw thread structure, the no-load flank according to the present invention includes a first tangential portion2aand a second tangential portion2b. The first tangential portion2aand the second tangential portion2aare formed to simultaneously abut against an arc portion4aformed at a crest of a screw thread4of an opposing fastening object that corresponds to the screw thread1, and particularly, the second tangential portion2bis formed to form a preset angle with respect to the first tangential portion2a.

In this case, the arc portion4aformed at the crest of the screw thread4refers to a portion made by rounding a crest of a screw thread in order to prevent the occurrence of foreign substances which hinders the fastening process while an end of the crest is easily damaged during the fastening process in a case in which the crest of the screw thread is formed to be pointy during a screw machining process.

In the case in which the first tangential portion2aand the second tangential portion2bare formed at the no-load flank2of the screw thread1as described above, during the threaded engagement, a load flank of the screw thread4of the opposing fastening object comes into close contact with the load flank3of the screw thread1, and simultaneously, the arc portion4aformed at the crest of the screw thread4of the opposing fastening object strongly comes into contact with the first tangential portion2aand the second tangential portion2b.

In this case, when the arc portion4aformed at the crest of the screw thread4of the opposing fastening object strongly comes into contact with the first tangential portion2aand the second tangential portion2bformed at the no-load flank2of the screw thread1, the arc portion4aformed at the crest of the screw thread4of the opposing fastening object locally deforms the first tangential portion2aand the second tangential portion2b, thereby forming a securely fixed state.

In this state, the load flanks, which are in close contact with each other, are not easily separated from each other even though external impact or vibration is applied, and as a result, frictional force applied between the load flanks is securely maintained after the threaded engagement. Therefore, it is possible to effectively prevent looseness caused by external impact or vibration.

Meanwhile, fastening force may be more increased when the first tangential portion2aand the second tangential portion2bsimultaneously abut against and come into close contact with the arc portion4ain a state in which the screw thread1is fastened to the opposing fastening object.

Further, in the present exemplary embodiment, the second tangential portion2bis formed to have a larger angle with respect to a horizontal line than the first tangential portion2a. The reason is to allow the first tangential portion2aand the second tangential portion2bto come into contact with the arc portion4aof the opposing fastening object while surrounding the arc portion4a.

In addition, the first tangential portion2aand the second tangential portion2bare formed to have a smaller angle with respect to the horizontal line than the load flank3. The reason is to allow the load flank3to come into contact with an overall area of the opposing fastening object in the state in which the first tangential portion2aand the second tangential portion2bare in contact with the arc portion4aof the opposing fastening object.

The looseness-prevention screw thread structure according to the present invention, which is configured as described above, may be applied to both an internal thread and an external thread, and first, an exemplary embodiment in which the looseness-prevention screw thread structure is applied to the internal thread will be described with reference toFIGS. 4 to 6.

As illustrated inFIG. 4, in a case in which the looseness-prevention screw thread structure according to the present invention is applied to the internal thread, a first tangential portion7aand a second tangential portion7bare formed at a no-load flank7of a screw thread6provided in an internal thread portion5aof a nut5.

In the case in which the first tangential portion7aand the second tangential portion7bare formed at the no-load flank7of the screw thread6provided in the internal thread portion5aof the nut5as described above, the no-load flank7of the screw thread6, which constitutes the internal thread portion5aof the nut5, comes into contact with a no-load flank11of a screw thread10, which constitutes an external thread portion9aof a bolt9, by axial force applied during the engagement when the nut5is rotated to fasten the internal thread portion5aof the nut5to the external thread portion9aof the bolt9as illustrated inFIG. 5.

In this case, the bolt9and the nut5are not fastened in a state in which the no-load flank11of the screw thread10, which constitutes the external thread portion9aof the bolt9, and the no-load flank7of the screw thread6, which constitutes the internal thread portion5aof the nut5, are in surface-to-surface contact with each other over a large area, but the bolt9and the nut5are fastened in a state in which an arc portion10aformed at a crest of the screw thread10of the bolt9is in point-to-point contact with the second tangential portion7bof the no-load flank7provided in the screw thread6of the nut5.

Further, as illustrated inFIG. 6, when the internal thread portion5aof the nut5is completely fastened to the external thread portion9aof the bolt9, compressive force is applied due to the engagement between the bolt9and the nut5, a load flank8of the nut5and a load flank12of the bolt9strongly and tightly come into surface-to-surface close contact with each other, and simultaneously, the arc portion10aformed at the crest of the screw thread10of the bolt9strongly comes into contact with the first tangential portion7aand the second tangential portion7bformed at the no-load flank7of the screw thread6of the nut5.

In this case, when the arc portion10aformed at the crest of the screw thread10of the bolt9strongly comes into contact with the first tangential portion7aand the second tangential portion7bformed at the no-load flank7of the screw thread6of the nut5, the arc portion10aformed at the crest of the screw thread10of the bolt9locally deforms the first tangential portion7aand the second tangential portion7b, thereby forming a securely fixed state.

In this state, the load flanks, which are in close contact with each other, are not easily separated from each other even though external impact or vibration is applied, and as a result, frictional force applied between the load flanks is securely maintained after the threaded engagement, thereby effectively preventing looseness caused by external impact or vibration.

Hereinafter, a process of machining the screw thread and optimum angles of the first tangential portion7aand the second tangential portion7bwill be described.

FIGS. 7 and 8are views illustrating a process of machining the looseness-prevention screw thread structure according to the present invention, andFIG. 9is a view illustrating angles of the first tangential portion and the second tangential portion optimized for the looseness-prevention screw thread structure according to the present invention.

As illustrated inFIGS. 7 and 8, the process of machining the looseness-prevention screw thread structure according to the present invention will be described below.

First, as illustrated inFIG. 7, a non-machined screw thread N is primarily machined so that the screw thread abuts against a reference curve S, thereby forming the second tangential portion. The reference curve S is set to correspond to the arc portion of the opposing fastening object in consideration of an effective diameter of the bolt or the nut.

Further, the second tangential portion is machined in a straight line shape from the load flank so that the second tangential portion abuts against the reference curve S.

Thereafter, as illustrated inFIG. 8, the non-machined screw thread N with the machined second tangential portion is secondarily machined so that the screw thread abuts against the reference curve S, thereby forming the first tangential portion. Similar to the second tangential portion, the first tangential portion is also machined in a straight line shape from the load flank in a direction of the second tangential portion so that the first tangential portion abuts against the reference curve S.

As illustrated inFIG. 9, in the machined screw thread structure, the first tangential portion7aand the second tangential portion7bmay simultaneously come into close contact with the screw thread10of the opposing fastening object in a case in which the first tangential portion7ahas an angle of 5° with respect to the horizontal line and the second tangential portion7bhas an angle of 35° with respect to the horizontal line.

The screw threads of the bolt and the nut are standardized based on the international standard (ISO), and thus a pitch, an inner diameter, an effective diameter, a root diameter, and the like of the screw thread are increased at a predetermined rate in accordance with sizes of the bolt and the nut. The following Table 1 shows dimensions in accordance with sizes of the nut based on ISO68 and ISO268.

As described above, a ratio of the thread height to the pitch of the screw thread is constant regardless of the sizes of the bolt and the nut, and the angle of the screw thread is fixed to 60°, such that an optimum angle of the screw thread may be equally calculated even though the bolt and the nut depend on any standard.

That is, an optimum condition having maximum fastening force may be obtained in a case in which the first tangential portion7ais machined to have an angle of 5° and the second tangential portion7bis machined to have an angle of 35°.

To prove the result, an experiment was performed while changing the angles of the first tangential portion7aand the second tangential portion7b.

FIG. 10is a view illustrating a state of a contact point in accordance with a change in angle of the first tangential portion7aof the looseness-prevention screw thread structure according to the present invention, andFIG. 11is a view illustrating a state of the contact point in accordance with a change in angle of the second tangential portion7bof the looseness-prevention screw thread structure according to the present invention.

As can be seen from bothFIGS. 10 and 11, in a case in which any one condition of the first tangential portion7aand the second tangential portion7bis fixed and the other condition is changed, any one of the first tangential portion7aand the second tangential portion7bis separated from the screw thread10of the opposing fastening object without abutting against the screw thread10of the opposing fastening object.

That is, the first tangential portion7aand the second tangential portion7bsimultaneously abut against the screw thread10of the opposing fastening object in a case in which the first tangential portion7ais machined to have an angle of 5° and the second tangential portion7bis machined to have an angle of 35°, and as a result, maximum fastening force may be generated.

FIG. 12is a graph illustrating the amount of change in fastening torque with respect to a change in angle of the first tangential portion of the looseness-prevention screw thread structure according to the present invention.

As illustrated inFIG. 12, a differential value of the graph is rapidly increased when the angle of the first tangential portion is between 4° and 6°, and therefore, it can be seen that fastening force is significantly increased when the angle of the first tangential portion is between 4° and 6°.

In addition, it can be confirmed that in a case in which the angle of the first tangential portion is 5°, the first tangential portion and the second tangential portion simultaneously abut against the screw thread of the opposing fastening object such that maximum fastening force is obtained.

From the foregoing, optimum angles of the first tangential portion and the second tangential portion and reference data have been described, and hereinafter, an example in which the looseness-prevention screw thread structure according to the present invention is applied to an external thread will be described.

As illustrated inFIG. 13, in a case in which the looseness-prevention screw thread structure according to the present invention is applied to the external thread, a first tangential portion11aand a second tangential portion11bare formed at the no-load flank11of the screw thread10provided in the external thread portion9aof the bolt9.

In the case in which the first tangential portion11aand the second tangential portion11bare formed at the no-load flank11of the screw thread10provided in the external thread portion9aof the bolt9as described above, the no-load flank11of the screw thread10, which constitutes the external thread portion9aof the bolt9, comes into contact with a no-load flank15of a screw thread14, which constitutes an internal thread portion13aof an opposing object13, by axial force applied during the engagement when the bolt9is rotated to fasten the external thread portion9aof the bolt9to the internal thread portion13aof the opposing object13as illustrated inFIG. 14.

In this case, the bolt9and the opposing object13are not fastened in a state in which the no-load flank11of the screw thread10, which constitutes the external thread portion9aof the bolt9, and the no-load flank15of the screw thread14, which constitutes the internal thread portion13aof the opposing object13, are in surface-to-surface contact with each other over a large area, but the bolt9and the opposing object13are fastened in a state in which the second tangential portion11bof the no-load flank11of the screw thread10of the bolt9and an arc portion14aformed at a crest of the screw thread14of the opposing object13are in point-to-point contact with each other.

Further, when the external thread portion9aof the bolt9is completely fastened to the internal thread portion13aof the opposing object13as illustrated inFIG. 15, compressive force is applied because of the engagement between the bolt9and the opposing object13.

Therefore, a load flank16of the opposing object13and the load flank12of the bolt9strongly and tightly come into surface-to-surface close contact with each other, and simultaneously, the arc portion14aformed at the crest of the screw thread14of the opposing object13strongly comes into contact with the first tangential portion11aand the second tangential portion11bformed at the no-load flank11of the screw thread10of the bolt9.

In this case, when the arc portion14aformed at the crest of the screw thread14of the opposing object13strongly comes into contact with the first tangential portion11aand the second tangential portion11bformed at the no-load flank11of the screw thread10of the bolt9, the arc portion14aformed at the crest of the screw thread14of the opposing object13locally deforms the first and second tangential portions11aand11b, thereby forming a securely fixed state.

Therefore, the load flanks, which are in close contact with each other, are not easily separated from each other even though external impact or vibration is applied, and as a result, frictional force applied between the load flanks is securely maintained after the threaded engagement, thereby effectively preventing looseness caused by external impact or vibration.

Hereinafter, the comparison between fastening force of the looseness-prevention screw thread structure according to the present invention and fastening force of a general screw thread structure in the related art will be described.

Basically, when tightening torque (fastening torque) is provided to fasten the screw, the external thread receives tensile force, and the internal thread receives compressive force. Force, which is initially applied during the engagement, refers to a preload, and an axial load caused by the tightening torque is expressed by the following Expression 1.

Here, T means tightening torque, q means a preload in the form of axial force, dp and dn mean diameters of the external thread and the internal thread, respectively, and β means a lead angle of the screw thread. ρ is a friction angle, and is expressed by the following Expression 2.
ρ=tan μp[Expression 2]

Here, μp and μn mean frictional coefficients of the external thread and the internal thread, respectively.

The fastening force of the screw is also changed in accordance with a fastening torque value, and the tightening torque required for the engagement is made with reference to a specification table of a standard screw. In addition, because the tightening torque value is changed in accordance with the lead angle of the screw thread, the fastening force is also changed in accordance with the lead angle of the screw thread. Further, it can be proved that the change in fastening force provides an effect of preventing looseness in the event of vibration.

In the present invention, tightening torque (kgf·cm) corresponding to the standard screw was applied, and the preload (kgf) was calculated by inputting the tightening torque to Expression 1 and Expression 2.

In addition, in all cases, a deformable body-deformable body contact condition is provided to a boundary between the external thread and the internal thread, and the frictional coefficient of the screw thread is applied with reference to relevant documents.

Further, based on the aforementioned proposed optimum design, a screw having the screw thread with the first tangential portion and the second tangential portion was manufactured and subjected to a vibration test together with a screw used in the related art.

The test was performed under a vibration test condition based on ISO7481 of the International Organization for Standardization, andFIGS. 16 and 17illustrate vibration test jigs50and60used for the present experiment. Further, the experiment condition and the experiment process using the vibration test jigs50and60will be described below.

First, screw portions of a bolt and a nut are lubricated in a first jig50and a second jig60inFIGS. 16 and 17, and the bolt is fastened to a first fastening unit52and a second fastening unit62until the nut to be tested including a chamfered portion protrudes by at least 2 pitches.

Further, the assembly is heated to a maximum operating temperature ±5° C. specified in the dimension standard of the nut or the drawings, and this temperature is maintained for about 6 hours. Thereafter, the assembly is extracted from an oven and then slowly cooled to an ambient temperature, and the nut is separated.

In addition, under the same lubrication condition, a spacer and a washer are fitted and the nut is assembled to the same bolt, and then the nut is tightened by applying torque specified in the supply standard. Thereafter, the nut is loosened so that a looseness-prevention part is completely pulled out, the assembly is mounted to a block slot, tightening and loosening are repeated three times, and the same bolt is tightened at the fourth time.

Further, a reference line is indicated from the end of the bolt to the nut, a friction portion is lightly lubricated with synthetic oil, and whether the spacer may be freely moved in the slot is tested.

The assembly is mounted into an appropriate vibration generator, and the assembly is vibrated in a vibration region for sixteen minutes and forty seconds corresponding to 30,000 cycles. Further, during the entire test process, whether the assembly may be freely moved in the slot is tested.

When the time has elapsed and the nut is completely loosened, the test is stopped, the nut with a defect and a fractured part are removed from the assembly, and another nut is continuously tested for the remaining time. When the time has again elapsed, the test is stopped, the assembly is taken out of the vibration generator, and a state (rotational speed) of the nut with respect to the assembly and the bolt is tested.

Finally, the nut is released and tested with the naked eye, and if necessary, the nut is cut, and a cross section of the nut, which is magnified ten times, is tested to inspect conformity with requirements of the supply standard.

During the entire process, the fastening torque was set to 150 kgf·cm which is an usual screw reference, and how the lead angle of the screw thread is changed is calculated when changing the lead angle of the screw thread. The following Table 2 shows a result of comparing vibration tests for the product to which the screw thread according to the present invention is applied and the screw manufactured by other companies in the related art.

As shown in Table 2, the number 1 product, the number 2 product, and the number 3 product are the existing products that have been tested, and the number 4 product is a product designed according to the present invention.

According to the result, the looseness occurred in the number 1 product, the number 2 product, and the number 3 product at 28,050 cycles, 22,740 cycles, and 16,050 cycles during the vibration test, but the looseness occurred in the number 4 product designed according to the present invention at 30,000 cycles, and a result, which shows significantly improved looseness-prevention performance, could be obtained.

As the foregoing, the experiments for proving the looseness-prevention performance of the screw thread structure according to the present invention have been described, and hereinafter, machining tools for machining the looseness-prevention screw thread structure according to the present invention will be described.

FIGS. 18 and 19are views illustrating machining tools for machining the looseness-prevention screw thread structure according to the present invention to make an internal thread.

The machining tool illustrated inFIG. 18is a machining tool which is formed in the form of a tap and has a spiral cutting blade that is formed at an outer circumferential surface of a cylindrical body so as to correspond to the looseness-prevention screw thread structure according to the present invention, and the machining tool illustrated inFIG. 19is formed in the form of a cutting bite.

The tools for machining the looseness-prevention screw thread, which have the aforementioned shapes, may easily machine the looseness-prevention screw thread structure according to the present invention to make an internal thread on an inner circumferential surface of the nut or an inner circumferential surface of a hole formed in an opposing object.

Further,FIGS. 20 to 23are views illustrating machining tools for machining the looseness-prevention screw thread structure according to the present invention to make an external thread.

The machining tool illustrated inFIG. 20is formed in the form of dies in which cutting blades, which correspond to the looseness-prevention screw thread structure according to the present invention, are formed radially on an inner circumferential surface of a body, and the machining tool illustrated inFIG. 21is formed in the form of a cutting bite. Further, the machining tools illustrated inFIGS. 22 and 23are formed in the form of rolling dies.

The tools for machining the looseness-prevention screw thread, which have the aforementioned shapes, may easily machine the looseness-prevention screw thread structure according to the present invention to make an external thread on an outer circumferential surface of the bolt or an outer circumferential surface of a cylindrical object.

While the exemplary embodiments according to the present invention have been described above, it is obvious to those skilled in the art that the present invention may be specified in other particular forms in addition to the aforementioned exemplary embodiments without departing from the spirit or the scope of the present invention. Accordingly, it should be understood that the aforementioned exemplary embodiments are not restrictive but illustrative, and thus the present invention is not limited to the aforementioned description, and may be modified within the scope of the appended claims and the equivalent range thereto.