TWI678475B - Fastening device and manufacturing method of fastening device - Google Patents

Abstract

A fastening device includes a keyless shaft sleeve, at least two grooves, and at least six screw holes. The keyless sleeve includes the inner surface and the outer surface, and its Young's coefficient is 100GPa-200GPa, and its drop strength is 988.3MPa-1329.8MPa. The at least two trenches are respectively at least one inner trench and at least one outer trench. At least one inner groove is disposed on the inner surface and is an inclined groove, and has an inner groove width, and at least one outer groove is disposed on the outer surface and has an outer groove width. At least six screw holes are provided at the ends of the keyless sleeve. Thereby, the keyless bushing can have a high maximum deformation amount, so as to improve the inner diameter positive force and the outer diameter positive force of the fastening device.

Description

Fastening device and manufacturing method thereof

The invention relates to a fastening device and a manufacturing method of the fastening device, and in particular, to a fastening device having an inclined groove and a manufacturing method of the fastening device.

The keyless bushing is a common fastening device element today. However, the keyless bushing must be equipped with a sleeve and a jig. Therefore, the structure cannot be greatly modified, which causes the fastening device to be unable to improve the fastening. Effect, or in order to enhance the tightening effect, the user applies excessive screw locking force beyond the stress that the keyless bushing can withstand, resulting in permanent deformation and damage of the keyless bushing.

In view of this, it is a development trend in the industry to develop a keyless bushing that has high fastening efficiency and can withstand higher stress.

The fastening device and the manufacturing method of the fastening device provided by the present invention are provided with at least one inner groove through the inner diameter surface of the keyless shaft sleeve, and the inner groove The groove is an inclined groove to increase the maximum deformation of the keyless shaft sleeve, and at least one outer groove is provided on the outer diameter surface to improve the fastening ability of the fastening device.

According to an embodiment of a structural aspect of the present invention, a fastening device includes a keyless sleeve, at least two grooves, and at least six screw holes. The keyless bushing includes an inner surface and an outer surface, and the Young's coefficient of the keyless bushing is 100GPa-200GPa, and the drop strength is 988.3MPa-1329.8MPa. At least two grooves are respectively disposed on the inner surface and the outer surface of the keyless sleeve, and the at least two grooves are at least one inner groove and at least one outer groove, respectively. At least one inner groove is disposed on the inner surface, and the inner groove is an inclined groove and has an inner groove width. At least one outer groove is disposed on the outer surface and has an outer groove width. At least six screw holes are provided at the ends of the keyless sleeve. Thereby, the maximum deformation amount of the fastening device can be increased, and the fastening device can have a large inner diameter positive force and an outer diameter positive force, so as to improve the fastening effect of the fastening device.

According to the fastening device of the aforementioned embodiment, the number of screw holes may be eight.

According to the fastening device of the foregoing embodiment, the width of the inner groove may be 2.5 mm, and the width of the outer groove may be 4 mm.

The fastening device according to the aforementioned embodiment, wherein the outer groove may be a straight groove or an inclined groove.

According to another embodiment of a structural aspect of the present invention, a fastening device includes a keyless sleeve, at least two grooves, and at least six screw holes. The keyless bushing includes an inner surface and an outer surface, and the Young's coefficient of the keyless bushing is 100GPa-200GPa, and the drop strength is 988.3MPa-1329.8MPa. At least two grooves are respectively provided on the inner surface and the outer surface of the keyless sleeve Surface, and the at least two grooves are at least one inner groove and at least one outer groove, respectively. At least one inner groove is disposed on the inner surface, and the inner groove is a straight groove and has an inner groove width. At least one outer groove is disposed on the outer surface and has an outer groove width. At least six screw holes are provided at the ends of the keyless sleeve. Thereby, the maximum deformation amount of the fastening device can be increased, and the fastening device can have a large inner diameter positive force and an outer diameter positive force, so as to improve the fastening effect of the fastening device.

According to the fastening device of the aforementioned embodiment, the number of screw holes may be eight.

According to one embodiment of the method of the present invention, a method for manufacturing a fastening device includes providing a keyless bushing, the Young's coefficient of the keyless bushing is 100GPa-200GPa, and the yield strength of the keyless bushing is 988.3 MPa-1329.8MPa, at least one inner groove is provided on the inner surface of the keyless bushing, and the inner groove has the width of the inner groove. When the outer diameter positive force of the fastening device is smaller than the target value of the outer diameter forward force, The inner groove is set as an inclined groove, and when the forward force of the inner diameter of the fastening device is smaller than the target value of the inner diameter forward force, the inner groove is set as a straight groove, and the outer surface of the keyless sleeve is set. At least one outer groove, and the outer groove has an outer groove width, and at least six screw holes are provided at the end of the keyless bushing, when the inner diameter positive force is smaller than the inner diameter forward force target value or the outer diameter is positive When the force is smaller than the target value of the outer diameter positive force, increase the number of screw holes. Thereby, a fastening device having a high inner diameter positive force, a high outer diameter positive force, and a high bearing force can be manufactured.

According to the method for manufacturing a fastening device according to the foregoing embodiment, the width of the inner groove may be 2.5 mm, and the width of the outer groove may be 4 mm.

According to the method for manufacturing a fastening device according to the foregoing embodiment, the outer groove may be a straight groove or an inclined groove.

According to the method of manufacturing a fastening device according to the aforementioned embodiment, the number of screw holes may be eight.

100‧‧‧ Fastening device

110‧‧‧keyless sleeve

120‧‧‧ inside surface

130‧‧‧ outside surface

140‧‧‧Groove

141‧‧‧Inner groove

142‧‧‧outer groove

150‧‧‧Screw holes

160‧‧‧ end

170‧‧‧Screw

180‧‧‧ Jig

190‧‧‧ sleeve

w1‧‧‧Inner groove width

w2‧‧‧outer groove width

s200‧‧‧Manufacturing method of fastening device

s210, s220, s230, s240‧‧‧ steps

if‧‧‧Inner diameter positive force

of‧‧‧outer diameter positive force

mf‧‧‧maximum stress

fs‧‧‧ drop strength

FIG. 1 is a schematic perspective view of a fastening device according to an embodiment of a structural aspect of the present invention; FIG. 2A is a schematic view of a keyless sleeve of a fastening device according to one embodiment of FIG. 1; Fig. 2B shows a schematic diagram of a keyless bushing of a fastening device according to another embodiment of the structural aspect of Fig. 1; Fig. 3A shows a first embodiment and a second implementation of the embodiment according to Fig. 1 Of the maximum deformation amount of the keyless bushing of the fastening device of the first and third embodiments and the curve of the maximum deformation amount of the keyless bushing of the fastening device of the first comparative example; FIG. 3B shows a graph according to the first The maximum stress curve of the keyless bushing of the fastening device of the first, second and third embodiments of the embodiment of the figure and the maximum stress of the keyless bushing of the fastening device of the first comparative example Graph; Fig. 3C shows the inner diameter forward force curve of the fastening device of the first, second and third examples of the embodiment according to Fig. 1 and the fastening of the first comparative example Diagram of the device's internal diameter forward force; Figure 3D shows the implementation according to Figure 1 The first embodiment and the second embodiment of the formula The outer diameter forward force curve of the fastening device of the embodiment and the third embodiment and the outer diameter forward force curve of the fastening device of the first comparative example; FIG. 4A shows the embodiment according to FIG. 1. The maximum deformation curve of the keyless sleeve of the fastening device of the fourth and fifth embodiments and the maximum deformation curve of the keyless sleeve of the fastening device of the second comparative example; FIG. 4B shows The graphs of the forward and inner diameter forces of the inner diameter and the outer diameter of the fastening device according to the fourth and fifth examples of the embodiment according to FIG. 1 and the forward force of the inner diameter of the fastening device of the second comparative example. And outer diameter forward force curve diagram; FIG. 4C shows the maximum stress curve diagram of the keyless bushing of the fourth embodiment and the fifth embodiment of the fastening device according to the embodiment of FIG. 1 and the second comparative example The maximum stress curve of the keyless sleeve of the fastening device of the fastening device; FIG. 5 shows the inner diameter of the fastening device and the outer diameter of the fastening device according to the sixth embodiment and the seventh embodiment of the embodiment shown in FIG. 1. Forward force; FIG. 6A illustrates a keyless shaft of a fastening device according to an eighth embodiment of the embodiment of FIG. 1 Curve of the maximum deformation amount and the curve of the maximum deformation amount of the keyless sleeve of the fastening device of the third comparative example; FIG. 6B shows the inside of the fastening device of the eighth embodiment according to the embodiment of FIG. The forward force and outer diameter forward force curves and the inner diameter and outer force forward force curves of the fastening device of the third comparative example; FIG. 7A shows the exemption of the fastening device of FIG. 1 Schematic diagram of the end of a key sleeve; FIG. 7B shows a graph of the maximum deformation of the keyless sleeve of the fastening device of the ninth and tenth embodiments according to the embodiment of FIG. 1 and a fourth comparative example Maximum deformation curve of keyless bushing of the fastening device; FIG. 7C is a graph showing the forward force curve of the inner diameter of the keyless sleeve of the fastening device according to the ninth and tenth embodiments of the embodiment according to FIG. 1 and the exemption of the fastening device of the fourth comparative example. Forward force curve of the inner diameter of the key sleeve; FIG. 7D shows the forward force curve of the outer diameter of the keyless sleeve of the fastening device according to the ninth and tenth embodiments of the embodiment shown in FIG. 1. FIG. And the forward force curve of the outer diameter of the keyless sleeve of the fastening device of the fourth comparative example; FIG. 8A shows the eleventh, twelfth, and eleventh embodiments of the embodiment according to FIG. Thirteenth embodiment and the fourteenth embodiment of the fastening device of the inner diameter of the positive force and the relationship between the outer diameter of the positive force diagram and the fifth comparative example of the fastening device of the inner diameter of the positive force and the outer diameter of the positive force FIG. 8B shows the eleventh, twelfth, thirteenth and fourteenth embodiments of the fastening device according to the embodiment of FIG. 1 without another inner diameter. Relation diagram of forward force and outer diameter forward force and another diagram of the relationship between the forward force of the inner diameter and the outer diameter of the fastening device of the fifth comparative example; Fig. 9A shows a schematic diagram of a keyless bushing of a fastening device according to still another embodiment of Fig. 1; Fig. 9B shows a keyless bushing of a fastening device according to still another embodiment of Fig. 1 A schematic diagram; and FIG. 10 is a flowchart showing steps of a method for manufacturing a fastening device according to an embodiment of a method aspect of the present invention.

FIG. 1 is a schematic three-dimensional view of a fastening device 100 according to an embodiment of a structural aspect of the present invention, and FIG. 2A is a diagram illustrating one of the first embodiment according to FIG. 1. The schematic diagram of the keyless shaft sleeve 110 of the fastening device 100 according to the embodiment, and FIG. 2B illustrates the schematic diagram of the keyless shaft sleeve 110 of the fastening device 100 according to another embodiment according to the structure of FIG. 1. As can be seen from FIGS. 1, 2A, and 2B, the fastening device 100 may include a keyless bushing 110, at least two grooves 140, and at least six screw holes 150. The keyless bushing 110 includes an inner surface 120 and an outer surface. The surface 130 and the end 160, at least two grooves 140 are respectively disposed on the inner surface 120 or the outer surface 130 of the keyless sleeve 110, and at least six screw holes 150 are disposed on the end 160 of the keyless sleeve 110.

In detail, the Young's coefficient of the keyless bushing 110 may be 100 GPa-200 GPa, and its drop strength fs may be 988.3 MPa-1329.8 MPa. The at least two grooves 140 may be an inner groove 141 and an outer groove 142, respectively. The inner groove 141 is provided on the inner surface 120 and is an inclined groove, and has an inner groove width w1. The outer groove 142 is provided on the outer side. The surface 130 also has an outer trench width w2. As can be seen from FIG. 1, the fastening device 100 can further include a screw 170, and the screw 170 is penetrated in the screw hole 150. The screw 170 can apply a screw locking force to the keyless shaft sleeve 110, so that the keylessness of the fastening device 100 is free. The shaft sleeve 110 is locked and deformed to generate an inner diameter forward force if and an outer diameter forward force of. In the embodiment of FIG. 2A, the groove 142 outside the fastening device 100 may be a straight groove, and in the embodiment of FIG. 2B, the groove 142 outside the fastening device 100 may be a diagonal groove; That is, the groove 142 outside the fastening device 100 may be a straight groove or a diagonal groove.

FIG. 3A shows the maximum deformation curve of the keyless sleeve 110 of the fastening device 100 according to the first embodiment, the second embodiment, and the third embodiment according to the embodiment of FIG. 1 and the first comparative example. Keyless bushing for fastening device FIG. 3B is a graph showing the maximum stress curve of the keyless sleeve 110 of the fastening device 100 according to the first, second, and third embodiments of the embodiment shown in FIG. 1. And the maximum stress curve of the keyless bushing of the fastening device of the first comparative example, and FIG. 3C shows the fastening of the first, second, and third embodiments of the embodiment according to FIG. 1. The forward force curve of the inner diameter of the device 100 and the forward force curve of the inner diameter of the fastening device of the first comparative example. FIG. 3D shows the first and second examples of the embodiment according to FIG. 1. The outer diameter forward force curve of the fastening device 100 of the third embodiment and the outer diameter forward force curve of the fastening device of the first comparative example. 3A, 3B, 3C, and 3D, the Young's coefficient of the keyless bushing 110 of the fastening device 100 of the first embodiment is 100 GPa, and that of the fastening device 100 of the second embodiment is 100 GPa. The Young's coefficient of the key sleeve 110 is 150 GPa, the Young's coefficient of the keyless sleeve 110 of the fastening device 100 of the third embodiment is 200 GPa, and the Young's coefficient of the keyless sleeve of the fastening device 100 of the first comparative example. It is 250GPa. It can be seen from FIG. 3A that when the screw tightening force is the same, the maximum deformation amount of the keyless sleeve 110 of the fastening device 100 of the first, second and third embodiments is higher than that of the first comparative example. The maximum deformation of the keyless bushing of the fastening device; that is, the maximum deformation of the keyless bushing 110 increases as the Young's coefficient of the keyless bushing 110 decreases. As can be seen from FIG. 3B, when the screw tightening force is the same, the maximum stress mf of the keyless sleeve 110 of the fastening device 100 of the first, second and third embodiments is smaller than that of the first comparative example. The maximum stress mf of the keyless bushing of the fixing device; that is, when the screw tightening force is the same, the maximum stress mf of the keyless bushing 110 of the fastening device 100 decreases as the Young's coefficient of the keyless bushing 110 decreases. Lower, so the higher the screw tightening force required to reach the reduced strength fs, in other words, a keyless bushing The lower the Young's coefficient of 110, the higher the screw tightening force that the keyless shaft sleeve 110 can withstand. As can be seen from FIG. 3C, when the screw tightening force is the same, the forward force if of the inner diameter of the fastening device 100 of the first, second and third embodiments is higher than that of the fastening device of the first comparative example. That is, when the screw tightening force is the same, the inner diameter positive force if of the fastening device 100 increases as the Young's coefficient of the keyless sleeve 110 decreases. As can be seen from FIG. 3D, when the screw tightening force is the same, the outer diameter forward force of the fastening device 100 of the first, second, and third embodiments is higher than that of the first comparative example. That is, when the screw tightening force is the same, the positive force of the outer diameter of the fastening device 100 increases as the Young's coefficient of the keyless sleeve 110 decreases. Therefore, when the Young's coefficient of the keyless bushing 110 is 100GPa-200GPa, the keyless bushing 110 can withstand a higher screw locking force, and the fastening device 100 can have a higher inner diameter forward force if and outside Radial forward force of, so it can provide better fastening effect.

FIG. 4A shows a graph of the maximum deformation amount of the keyless bushing 110 of the fastening device 100 according to the fourth embodiment and the fifth embodiment of the embodiment shown in FIG. 1 and the exemption of the fastening device of the second comparative example. The curve of the maximum deformation of the key sleeve, and FIG. 4B shows the inner diameter positive force and the outer diameter positive force of the fastening device 100 according to the fourth and fifth examples of the embodiment shown in FIG. 1. FIG. And the graph of the internal force and the external force of the fastening device of the second comparative example. FIG. 4C shows the fastening of the fourth and fifth embodiments according to the embodiment of FIG. 1. The maximum stress curve of the keyless sleeve 110 of the device 100 and the maximum stress curve of the keyless sleeve of the fastening device of the second comparative example. In FIGS. 4A, 4B, and 4C, the Young's coefficient of the fourth embodiment is 196.1 GPa, the drop strength fs is 988.3 MPa, the inner groove width w1 is 2 mm, and the outer groove width w2 It is 3.5mm, the Young's coefficient of the fifth embodiment is 200.4 GPa, the drop strength fs is 1329.8MPa, the inner groove width w1 is 2mm, and the outer groove width w2 is 3.5mm. The Young's coefficient of the second comparative example is 205.8 GPa, drop strength fs is 770.2MPa, inner groove width is 2mm, and outer groove width is 3.5mm. In detail, the difference between the fourth embodiment, the fifth embodiment, and the second comparative example is that they have different Young's Coefficient and drop strength fs. Please refer to FIG. 4A and FIG. 4B. According to FIG. 4A, when the screw tightening force is the same, the maximum deformation amount of the keyless sleeve 110 of the fastening device 100 of the fourth embodiment and the fifth embodiment is higher than The maximum deformation of the keyless sleeve of the fastening device of the second comparative example, and as can be seen from FIG. 4B, when the screw tightening force is the same, the inner diameter of the fastening device 100 of the fourth and fifth embodiments The forward force if is higher than the inner diameter forward force if of the fastening device of the second comparative example, and when the screw tightening force is the same, the outer diameter of the fastening device 100 of the fourth and fifth embodiments is forward The force of is higher than the outer diameter of the fastening device of the second comparative example, the forward force of, specifically, because the undulating strength fs of the keyless bushing 110 does not affect the maximum deformation of the keyless bushing 110, and the fourth The keyless bushing 110 of the fifth embodiment has a low Young's coefficient, so when the screw tightening force is the same, the keyless bushing 110 of the fastening device 100 of the fourth and fifth embodiments Has a high maximum deformation amount, and the fastening device 100 of the fourth embodiment and the fifth embodiment has a high inner diameter forward force i f and outer diameter positive force of. As can be seen from FIG. 4C, when the screw tightening force is less than 2000 N, since the maximum stress mf of the fourth embodiment, the fifth embodiment, and the second comparative example does not exceed the respective drop strength fs, the tightness of the second comparative example is tight. The maximum stress mf of the keyless bushing of the fixing device is higher than that of the fourth and fifth embodiments, and when the screw tightening force is greater than 2000N, the maximum stress mf of the keyless bushing of the fastening device of the second comparative example is Has exceeded its yielding strength fs, the keyless bushing of the fastening device of the second comparative example has been damaged, and the maximum stress mf of the keyless bushing 110 of the fastening device 100 of the fourth and fifth embodiments has not yet reached their respective In other words, when the deflection strength fs of the keyless bushing 110 of the fastening device 100 is 988.3MPa-1329.8MPa, the keyless bushing 110 of the fastening device 100 can withstand a large screw locking force . Therefore, when the Young's coefficient of the keyless sleeve 110 of the fastening device 100 is 196.1GPa-200.4GPa and the drop strength fs is 988.3MPa-1329.8MPa, the fastening device 100 can have a higher fastening effect, and its The keyless shaft sleeve 110 can withstand high screw locking force.

FIG. 5 illustrates the inner diameter forward force if and the outer diameter forward force of the fastening device 100 according to the sixth and seventh examples of the embodiment shown in FIG. 1. In FIG. 5, the inner groove 141 of the fastening device 100 of the sixth embodiment is a straight groove, and the inner groove 141 of the keyless sleeve 110 of the fastening device 100 of the seventh embodiment is an inclined groove. . It can be seen from FIG. 5 that when the screw tightening force is the same, the outer diameter forward force of the fastening device 100 of the seventh embodiment is higher than the outer diameter forward force of the fastening device 100 of the sixth embodiment. Details In other words, since the inner groove 141 is an inclined groove, the keyless bushing 110 can have a large maximum deformation amount, so that the fastening device 100 has a large outer diameter positive force of; that is, fastening When the inner groove 141 of the keyless shaft sleeve 110 of the device 100 is an inclined groove, the fastening device 100 may have a high outer diameter positive force of.

FIG. 6A shows a graph of the maximum deformation amount of the keyless bushing 110 of the fastening device 100 according to the eighth embodiment of the embodiment of FIG. 1 and the maximum value of the keyless bushing of the fastening device of the third comparative example. Deformation curve, FIG. 6B shows the inside of the fastening device 100 according to the eighth embodiment of the embodiment shown in FIG. 1. A graph of radial forward force and outer diameter forward force and a graph of the inner diameter positive force and outer diameter forward force of the fastening device of the third comparative example. In FIGS. 6A and 6B, the inner groove width w1 of the eighth embodiment is 2.5 mm, and the outer groove width w2 is 4 mm. The inner groove width w1 of the third comparative example is 2 mm, and the outer groove width w2 is 3.5mm. It can be seen from FIG. 6A that when the screw tightening force is the same, the maximum deformation amount of the keyless bushing 110 of the fastening device 100 of the eighth embodiment is higher than that of the keyless bushing of the fastening device of the third comparative example. The amount of deformation; that is, the maximum amount of deformation of the keyless sleeve 110 of the fastening device 100 increases as the width of the inner groove w1 and the width of the outer groove w2 of the fastening device 100 increase. As can be seen from FIG. 6B, when the screw tightening force is the same, the forward force if of the inner diameter of the fastening device 100 of the eighth embodiment is higher than the forward force if of the inner diameter of the fastening device of the third comparative example. The outer diameter positive force of the fastening device 100 of the eighth embodiment is higher than the outer diameter positive force of the fastening device of the third comparative example; that is, the inner diameter of the keyless sleeve 110 of the fastening device 100 The normal force if and the outer diameter of the normal force of increase as the inner groove width w1 and the outer groove width w2 of the fastening device 100 increase. Therefore, when the inner groove width w1 of the keyless bushing 110 of the fastening device 100 is 2.5mm and the outer groove width w2 is 4mm, the keyless bushing 110 has a high maximum deformation amount, so that the fastening device 100 It has a higher inner diameter positive force if and an outer diameter positive force of, and has a better fastening effect.

FIG. 7A shows a schematic diagram of the end 160 of the keyless sleeve 110 of the fastening device 100 of FIG. 1, and FIG. 7B shows the ninth and tenth embodiments of the embodiment according to FIG. 1. The maximum deformation curve of the keyless bushing 110 of the device 100 and the maximum deformation curve of the keyless bushing of the fastening device of the fourth comparative example. FIG. 7C illustrates the ninth embodiment according to FIG. The inner diameter of the keyless sleeve 110 of the fastening device 100 of the embodiment and the tenth embodiment is positive The force curve diagram and the forward force curve diagram of the inner diameter of the keyless sleeve of the fastening device of the fourth comparative example. FIG. 7D shows the tightness of the ninth and tenth embodiments according to the embodiment of FIG. 1. The external force forward force curve of the keyless bushing 110 of the fixing device 100 and the external force positive force curve of the keyless bushing of the fastening device of the fourth comparative example. In FIGS. 7B, 7C, and 7D, the number of screw holes 150 in the ninth embodiment is six, the number of screw holes 150 in the tenth embodiment is eight, and the number of screw holes in the fourth comparative example is four. As can be seen from FIG. 7A, the end 160 of the keyless sleeve 110 may have six screw holes 150 for the screws 170 to pass through. It can be seen from FIG. 7B that when the screw tightening force is the same, the maximum deformation amount of the keyless sleeve 110 of the fastening device 100 of the ninth and tenth embodiments is higher than that of the fastening device of the fourth comparative example. The maximum deformation of the key shaft sleeve; that is, when the screw tightening force is the same, the maximum deformation of the fastening device 100 increases as the number of screw holes 150 of the keyless shaft sleeve 110 increases. As can be seen from FIG. 7C, when the screw tightening force is the same, the forward force if of the inner diameter of the fastening device 100 of the ninth and tenth embodiments is higher than the forward direction of the inner diameter of the fastening device of the fourth comparative example. That is, when the screw tightening force is the same, the forward force if of the inner diameter of the fastening device 100 increases as the number of the screw holes 150 of the keyless sleeve 110 increases. As can be seen from FIG. 7D, when the screw tightening force is the same, the outer diameter forward force of the fastening device 100 of the ninth and tenth embodiments is higher than the outer diameter of the fastening device of the fourth comparative example. That is, when the screw tightening force is the same, the positive external force of the outer diameter of the fastening device 100 increases as the number of screw holes 150 of the keyless sleeve 110 increases. Therefore, when the fastening device 100 has at least six screw holes 150, the fastening device 100 has a better fastening effect, and when the number of the screw holes 150 of the fastening device 100 is eight, compared with the six screw holes 150, The fastening device 100 has a better fastening effect.

In order to improve the fastening effect of the fastening device 100, the fastening device 100 can also be used with the fixture 180 and the sleeve 190 shown in FIG. 1. The sleeve 190 is arranged on the outer side of the keyless sleeve 110, and The keyless sleeve 110 is annularly disposed on the outer side of the jig 180, and the keyless sleeve 110, the jig 180, and the sleeve 190 may include a fitting gap in an assembly configuration. When the maximum deformation amount of the keyless sleeve 110 exceeds the fitting clearance, the fastening device 100 applies a positive outer diameter force of and a positive inner diameter force if on the sleeve 190 and the fixture 180 to achieve a tightening effect.

FIG. 8A shows the inner diameter forward force and outer diameter of the fastening device 100 according to the eleventh, twelfth, thirteenth and fourteenth embodiments of the embodiment according to FIG. 1. The relationship diagram of the forward force and the relationship diagram of the forward force of the inner diameter and the outer diameter of the fastening device of the fifth comparative example. FIG. 8B shows the eleventh embodiment of the embodiment according to FIG. Another diagram of the relationship between the positive force of the inner diameter and the positive force of the outer diameter of the fastening device 100 of the twelfth embodiment, the thirteenth embodiment, and the fourteenth embodiment, and the other of the fastening device of the fifth comparative example A diagram of the relationship between the inner diameter positive force and the outer diameter positive force. In FIGS. 8A and 8B, the fitting clearance of the eleventh embodiment is 0 mm, the fitting clearance of the twelfth embodiment is 0.005 mm, the fitting clearance of the thirteenth embodiment is 0.01 mm, and The fit clearance is 0.015mm, and the fit clearance of the fifth comparative example is 0.02mm, in which the screw locking force of FIG. 8A is 1000N, and the screw locking force of FIG. 8B is 3000N. As can be seen from FIGS. 8A and 8B, when the screw tightening force is the same, the inner diameter of the fastening device 100 of the eleventh embodiment, the twelfth embodiment, the thirteenth embodiment, and the fourteenth embodiment is positive. The direction force if is higher than the inner diameter of the fastening device of the fifth comparative example. The forward force if is the fastening device 100 of the eleventh, twelfth, thirteenth, and fourteenth embodiments. OD positive force of high The outer diameter forward force of the fastening device in the fifth comparative example; that is, the inner diameter forward force if and the outer diameter forward force of the fastening device 100 decrease as the fit clearance increases. Therefore, when the fitting clearance between the fastening device 100 and the jig 180 and the sleeve 190 is less than 0.015 mm, the fastening device 100 can have a good inner diameter positive force if and an outer diameter positive force of.

Please refer to FIG. 1, FIG. 9A, and FIG. 9B. FIG. 9A shows a schematic diagram of the keyless sleeve 110 of the fastening device 100 according to still another embodiment of FIG. 1, and FIG. 1 is a schematic view of a keyless sleeve 110 of a fastening device 100 according to yet another embodiment. As can be seen from FIG. 1, FIG. 9A, and FIG. 9B, the fastening device 100 may include a keyless bushing 110, at least two grooves 140, and at least six screw holes 150 (labeled in FIG. 7A), among which the keyless bushing 110 includes an inner surface 120, an outer surface 130, and an end 160. At least two grooves 140 are respectively provided on the inner surface 120 or the outer surface 130 of the keyless bushing 110, and at least six screw holes 150 are provided on the keyless bushing 110.端 部 160。 The end 160.

In detail, the Young's coefficient of the keyless bushing 110 may be 100 GPa-200 GPa, and its drop strength fs may be 988.3 MPa-1329.8 MPa. The at least two grooves 140 may be an inner groove 141 and an outer groove 142, wherein the inner groove 141 is provided on the inner surface 120 and is a straight groove, and has an inner groove width w1, and the outer groove 142 is provided on the outer side. The surface 130 also has an outer trench width w2. As can be seen from FIG. 1, the fastening device 100 can further include a screw 170, and the screw 170 is penetrated in the screw hole 150. The screw 170 can apply a screw locking force to the keyless shaft sleeve 110, so that the keylessness of the fastening device 100 is free. The shaft sleeve 110 is locked and deformed to generate an inner diameter forward force if and an outer diameter forward force of. In the embodiment of FIG. 9A, the groove 142 outside the fastening device 100 may be Is a straight groove, and in the embodiment of FIG. 9B, the groove 142 outside the fastening device 100 may be a diagonal groove; that is, the groove 142 outside the fastening device 100 may be a straight groove or an inclined groove Trench.

The relationship between the Young's coefficient of the keyless bushing 110 of the fastening device 100 in which the inner groove 141 is a straight groove, the forward force of the inner diameter if, the forward force of the outer diameter of, and the withstandable screw locking force is related to Figures 3A, 3B, 3C, and 3D are the same, and are not repeated here.

The relationship between the magnitude of the undulating strength fs of the keyless bushing 110 of the fastening device 100 with the inner groove 141 being a straight groove and the withstandable screw locking force is the same as that of Figs. 4A, 4B, and 4C. Here, Do not go into details.

Please refer to FIG. 5, wherein the inner groove 141 of the fastening device 100 of the sixth embodiment is a straight groove, and the inner groove 141 of the keyless sleeve 110 of the fastening device 100 of the seventh embodiment is inclined Trench. It can be seen from FIG. 5 that the forward force if of the inner diameter of the fastening device 100 of the sixth embodiment is higher than the forward force if of the inner diameter of the fastening device 100 of the seventh embodiment. In detail, since the straight groove has The larger contact area can make the fastening device 100 have a larger inner diameter forward force if, that is, when the inner groove 141 of the fastening device 100 is a straight groove, the fastening device 100 can have a relatively large High inner diameter forward force if.

The inner groove width w1 and outer groove width w2 of the fastening device 100 in which the inner groove 141 is a straight groove, and the relationship between the inner diameter forward force if and the outer diameter forward force of are the same as those in FIGS. 6A and 6B , I wo n’t repeat them here.

The inner groove 141 is a straight groove of the fastening device 100, and the relationship between the number of screw holes 150, the inner diameter forward force if and the outer diameter forward force of, and FIG. 7A, FIG. 7B, FIG. 7C, and FIG. 7D The same is not repeated here.

The relationship between the fitting gap between the inner groove 141 is a straight groove fastening device 100, the jig 180, and the sleeve 190, and the forward force of the inner diameter if and the forward force of the outer diameter are the same as those in FIGS. 8A and 8B , I wo n’t repeat them here.

Please refer to FIG. 10, which illustrates a flowchart of steps in a method s200 for manufacturing a fastening device according to an embodiment of a method aspect of the present invention. It can be seen from FIG. 10 that the manufacturing method s200 of the fastening device includes step s210 to provide a keyless sleeve 110; step s220, at least one inner groove 141 is provided on the inner surface 120; and step s230 is to provide at least one outer surface 130 The groove 142; and step s240, at least six screw holes 150 are provided in the end 160 of the keyless sleeve 110. In the embodiment shown in FIG. 10, the numbers of the components in the fastening device 100 in the embodiment shown in FIG. 1 may be corresponded, but the fastening device 100 in the embodiment shown in FIG. 1 is not limited.

In detail, the Young's coefficient of the keyless bushing 110 may be 100GPa-200GPa, and the yield strength fs of the keyless bushing 110 may be 988.3MPa-1329.8MPa. In order to achieve the tightening effect, the inner diameter forward force if of the fastening device 100 must be higher than the target value of the inner diameter forward force, and the outer diameter forward force of of the fastening device 100 must be higher than the outer diameter forward force target value , Where the target value of the positive force of the inner diameter is 35000N, and the target value of the positive force of the outer diameter is 47000N.

Please refer to FIG. 3C and FIG. 3D. According to FIG. 3C, when the screw tightening force reaches 3000N, the inner diameter of the fastening device 100 of the first, second, and third embodiments is positive. The force if is higher than the target value of the inner diameter forward force, and the inner diameter forward force if of the fastening device 100 increases as the Young's coefficient of the keyless bushing 110 decreases. As shown in FIG. 3D, when the screw locking force When it reaches 3000N, the fastening of the first, second and third embodiments The outer diameter forward force of the device 100 is higher than the target value of the outer diameter forward force, and the outer diameter forward force of the fastening device 100 increases as the Young's coefficient of the keyless sleeve 110 decreases. Therefore, when the Young's coefficient of the keyless sleeve 110 of the fastening device 100 is 100 GPa-200 GPa, the fastening device 100 can have a higher inner diameter forward force if and an outer diameter forward force of. Please refer to FIG. 4C again. When the screw tightening force is 2000N, the maximum stress mf of the keyless bushing of the fastening device of the second comparative example is higher than the undulating strength fs of the keyless bushing, which may cause the second comparison. The keyless bushing of the fastening device of the conventional example is damaged, while the keyless bushing 110 of the fastening device 100 of the fourth and fifth embodiments does not reach its respective drop strength fs. When the step-down strength fs of the keyless sleeve 110 is 988.3 MPa-1329.8 MPa, the fastening device 100 can withstand a higher screw locking force.

Please refer to FIG. 1 and FIG. 5. In order to lift the inner diameter forward force if or the outer diameter forward force of of the fastening device 100, the inner groove 141 of the keyless sleeve 110 has an inner groove width w1, and The outer groove 142 of the key sleeve 110 has an outer groove width w2. As can be seen from FIG. 5, when the screw tightening force reaches 3000, the outer diameter forward force of the seventh embodiment is higher than the outer diameter forward force of the sixth embodiment, and the inner diameter of the sixth embodiment is positive. The force if is higher than the inner diameter forward force if of the seventh embodiment; that is, when the inner groove 141 is a diagonal groove, the fastening device 100 may have a higher outer diameter forward force of, and when the inner groove When the groove 141 is a straight groove, the fastening device 100 may have a higher inner diameter forward force if. Therefore, when the outer diameter forward force of of the fastening device 100 is smaller than the target value of the outer diameter forward force, the inner groove 141 may be set as an inclined groove, and when the inner diameter forward force of the fastening device 100 is less than When the inner diameter forward force target value, the inner groove 141 may be set as a straight groove.

Please refer to FIGS. 2A, 2B, 6A, and 6B. In FIGS. 2A and 2B, the inner groove 141 of the fastening device 100 has an inner groove width w1, and the outer groove 142 has an outer groove. Slot width w2. In FIGS. 6A and 6B, the inner groove width w1 of the eighth embodiment is 2.5 mm, and the outer groove width w2 is 4 mm. The inner groove width w1 of the third comparative example is 2 mm, and the outer groove The width w2 is 3.5 mm. It can be seen from FIG. 6A that when the screw tightening force reaches 3000 N, the maximum deformation amount of the keyless sleeve 110 of the fastening device 100 of the eighth embodiment is higher than that of the keyless sleeve of the fastening device of the third comparative example. Deformation. As can be seen from FIG. 6B, when the screw tightening force reaches 3000N, the inner diameter forward force if of the fastening device 100 of the eighth embodiment is higher than the target value of the inner diameter forward example, and the fastening device of the eighth embodiment The outer diameter positive force of 100 is higher than the target value of the outer diameter positive example, and the inner diameter positive example and the outer diameter positive example of the fastening device 100 vary with the inner groove width w1 and the outer groove of the fastening device 100. The width w2 increases. Therefore, when the inner diameter forward force if of the fastening device 100 is smaller than the inner diameter forward force target value or the outer diameter forward force of is smaller than the outer diameter forward force target value, the inner groove width of the fastening device 100 can be increased. w1 or outer groove width w2, and when the inner groove width w1 of the keyless bushing 110 is 2.5 mm, and the outer groove width w2 is 4 mm, the fastening device 100 may have a higher maximum deformation amount, inner diameter Forward force if and outer diameter forward force of.

Please refer to FIG. 7A, FIG. 7B, FIG. 7C, and FIG. 7D. In order to raise the inner diameter forward force if and the outer diameter forward force of the fastening device 100, the end 160 of the keyless bushing 110 may be provided. At least six screw holes 150 are provided for the screw 170 to pass through. The screw 170 can apply the screw-locking force of the keyless bushing 110, and the keyless bushing 110 of the fastening device 100 is deformed to generate an inner diameter forward force if and Positive force of outer diameter of. In FIG. 7A, the number of the screw holes 150 is six. In Figure 7B, 7C and 7D, the number of the screw holes 150 of the fastening device 100 of the ninth embodiment is six, the number of the screw holes 150 of the fastening device 100 of the tenth embodiment is eight, and the tightening of the fourth comparative example is tight. The number of screw holes of the fixing device is four. It can be seen from FIG. 7B that when the screw tightening force is the same, the maximum deformation amount of the ninth embodiment and the tenth embodiment is higher than that of the fourth comparative example; that is, the maximum deformation of the keyless sleeve 110 The amount increases as the number of screw holes 150 of the keyless bushing 110 increases. As can be seen from FIG. 7C, when the screw tightening force reaches 3000 N, the inner diameter forward force if of the ninth and tenth embodiments is higher than the target value of the inner diameter forward force, and the inner diameter of the tenth embodiment is positive. The forward force if is higher than the inner diameter forward force if of the ninth embodiment; that is, when the number of screw holes 150 of the keyless bushing 110 is eight, the fastening device 100 may have a higher inner diameter forward force if The positive force if of the inner diameter of the fastening device 100 increases as the number of screw holes 150 of the fastening device 100 increases. As can be seen from FIG. 7D, when the screw tightening force reaches 3000N, the outer diameter forward force of the ninth and tenth embodiments is higher than the target value of the outer diameter forward force, and the outer diameter of the tenth embodiment is positive. The force of is higher than the outer diameter forward force of the ninth embodiment; that is, when the number of screw holes 150 of the keyless bushing 110 is eight, the fastening device 100 may have a higher outer diameter forward force of, And the outer diameter positive force of the fastening device 100 increases as the number of screw holes 150 of the fastening device 100 increases. Therefore, when the number of the screw holes 150 of the keyless bushing is eight, the fastening device 100 can have a good inner diameter positive force if and an outer diameter positive force of, and when the inner diameter of the fastening device 100 is positive If the forward force if is less than the target value of the inner diameter forward force or the outer diameter of the fastening device 100 is less than the target value of the outer diameter forward force, the number of screw holes 150 can be increased to increase the inner diameter forward force if and the outer diameter. Positive force of.

In addition, the fastening device 100 of the manufacturing method s200 of the fastening device of FIG. 10 can be further applied with the fixture 180 and the sleeve 190 shown in FIG. 1 to improve the fastening effect of the fastening device 100. Please refer to FIG. 1, FIG. 8A, and FIG. 8B. As can be seen from FIG. 1, the sleeve 190 is set on the outside of the keyless sleeve 110, and the keyless sleeve 110 is set on the outside of the fixture 180. In addition, the keyless shaft sleeve 110, the jig 180, and the sleeve 190 may include a matching gap when assembling and matching. In FIGS. 8A and 8B, the fit clearance of the eleventh embodiment is 0 mm, the fit clearance of the twelfth embodiment is 0.005 mm, the fit clearance of the thirteenth embodiment is 0.01 mm, and the fourteenth embodiment The mating gap of the screw is 0.015mm, and the mating gap of the fifth comparative example is 0.02mm, in which the screw locking force of FIG. 8A is 1000N, and the screw locking force of FIG. 8B is 3000N. It can be known from FIG. 8A and FIG. 8B that when the screw tightening force is the same, the inner diameter forward force if and the outer diameter forward force of the fastening device 100 decrease as the fit clearance increases, and when the screw tightening force reaches At 3000N, the inner diameter forward force if of the fastening device 100 of the eleventh embodiment, the twelfth embodiment, the thirteenth embodiment, and the fourteenth embodiment is higher than the target value of the inner diameter forward force, and The outer diameter forward force of of the fastening device 100 of the eleventh embodiment, the twelfth embodiment, the thirteenth embodiment, and the fourteenth embodiment is higher than the target value of the outer diameter forward force. Therefore, when the fitting clearance between the fastening device 100, the jig 180, and the sleeve 190 is less than 0.015 mm, the fastening device 100 may have a good inner diameter positive force if and a positive outer diameter force of.

Although the present invention has been disclosed in the above embodiments, it is not intended to limit the present invention. Any person skilled in the art can make various modifications and retouches without departing from the spirit and scope of the present invention. Therefore, the protection of the present invention The scope shall be determined by the scope of the attached patent application.

Claims (10)

A fastening device includes a keyless bushing including an inner surface and an outer surface, and the Young's coefficient of the keyless bushing is 100GPa-200GPa, and the yield strength of the keyless bushing is 988.3MPa- 1329.8MPa; at least two grooves are respectively provided on the inner surface and the outer surface of the keyless bushing, wherein the at least two grooves are respectively including: at least one inner groove provided on the inner surface, the inner surface The groove is an inclined groove and has an inner groove width; and at least one outer groove is provided on the outer surface and has an outer groove width; and at least six screw holes are provided in the keyless bushing. One end. The fastening device according to item 1 of the scope of patent application, wherein the number of the screw holes is eight. The fastening device according to item 1 of the scope of patent application, wherein the width of the inner groove is 2.5 mm, and the width of the outer groove is 4 mm. The fastening device according to item 1 of the patent application scope, wherein the outer groove is a straight groove or an inclined groove. A fastening device includes a keyless bushing including an inner surface and an outer surface, and the Young's coefficient of the keyless bushing is 100GPa-200GPa, and the yield strength of the keyless bushing is 988.3MPa- 1329.8MPa; at least two grooves are respectively provided on the inner surface and the outer surface of the keyless bushing, wherein the at least two grooves are respectively including: at least one inner groove provided on the inner surface, the inner surface The groove is a straight groove and has an inner groove width; and at least one outer groove is provided on the outer surface and has an outer groove width; and at least six screw holes are provided in the keyless bushing. One end. The fastening device according to item 5 of the scope of patent application, wherein the number of the screw holes is eight. A method for manufacturing a fastening device includes providing a keyless bushing, wherein the Young's coefficient of the keyless bushing is 100GPa-200GPa, and the yield strength of the keyless bushing is 988.3MPa-1329.8MPa; At least one inner groove is provided on an inner surface of one of the key sleeves, and the inner groove has an inner groove width. The inner groove is set as an inclined groove; when one of the inner diameter forward force of the fastening device is smaller than a target value of the inner diameter forward force, the inner groove is set as a straight groove; on the keyless shaft At least one outer groove is provided on an outer surface of the sleeve, and the outer groove has an outer groove width; and at least six screw holes are provided at one end of the keyless sleeve, when the forward force of the inner diameter is smaller than the inner diameter When the radial forward force target value or the outer diameter forward force is smaller than the outer diameter forward force target value, the number of the screw holes is increased. The method for manufacturing a fastening device according to item 7 of the scope of patent application, wherein the width of the inner groove is 2.5 mm, and the width of the outer groove is 4 mm. The method for manufacturing a fastening device according to item 7 of the scope of patent application, wherein the outer groove is a straight groove or an inclined groove. The method for manufacturing a fastening device according to item 7 of the scope of patent application, wherein the number of the screw holes is eight.