JP2011089584A - Disc spring and method of manufacturing the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide technology for suppressing the characteristic degradation of a disc spring with time passage. <P>SOLUTION: The disc spring 30 is used in the state that a first member abuts on an axial first end 32 and a second member abuts on an axial second end 34. The disc spring 30 includes a spring member 31 which has a partially cone-cylindrical shape where the opening area of the second end 34 is larger than the opening area of the first end 32 and which is cut at one position in the peripheral direction of the partially cone-cylindrical shape in a range from the first end 32 to the second end 34. In the state of being used, the condition is kept in which the first end 32 has line contact with the first member and the second end 34 has line contact with the second member. In the state that no load is applied thereto, the diameter of the second end 34/the width of the spring member 31 is 8.0 or greater and the effective height of the disc spring 30/the plate thickness of the spring member 31 is 1.0 or greater. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present specification discloses a disc spring.

  There is known a method of manufacturing a disc spring by cutting a flat plate material into an annular shape and forming the annular flat plate into a partial conical cylinder shape. In this manufacturing method, since the raw material cut out in the annular shape cannot be used for manufacturing the disc spring, the yield is poor. Therefore, Patent Documents 1 and 2 disclose a method of manufacturing a disc spring that improves the yield of the material.

  The manufacturing methods disclosed in Patent Documents 1 and 2 are a step of bending a strip-shaped flat plate material to form the strip-shaped flat plate into an annular flat plate, and a step of welding both ends of the annular flat plate. And a step of forming an annular flat plate into a partial conical cylinder shape.

JP 2003-329072 A JP 2001-225112 A

  In the disc spring manufactured by the above-described manufacturing method, characteristics such as fatigue resistance and sag resistance at a welded location (that is, resistance to deterioration with the passage of time) are more than characteristics at a location where welding is not performed. Also decreases. For this reason, the disc spring which satisfy | filled use conditions at the time of manufacture no longer satisfy | fills use conditions with progress of time. In this specification, the technique which suppresses the fall of the characteristic with progress of time of a disc spring is provided.

  Inventors considered joining the both ends of the strip | belt-shaped flat plate shape | molded by the methods other than welding in order to suppress the fall of the characteristic with time progress of a disk spring. For example, the inventors have joined both ends of the flat plate using rivets, or formed both ends of the flat plate so that one end of the flat plate is fitted to the other end, and one end is connected to the other end. Attempts were made to join both ends of the flat plate by fitting them to the ends of the plates. However, the disc spring produced by the above joining method cannot satisfy the required durability performance.

  As a result of intensive studies, the present inventors have found that if the disc spring has the following configuration, it is possible to suppress a decrease in characteristics with the passage of time of the disc spring. In other words, in the past, based on the idea that both ends of a strip-shaped flat plate formed into an annular shape must be bonded, a method of joining the two ends of a strip-shaped flat plate molded into an annular shape was examined. . However, as long as both ends of the belt-shaped flat plate formed into an annular shape are joined, it is inevitable that characteristics such as durability are deteriorated at the joined portion. Therefore, the inventors of the present application attempted to change the idea of keeping both ends of the strip-shaped flat plate formed into an annular shape cut, and as a result of further study, cut both ends of the strip-shaped flat plate formed into an annular shape. Even if it is left as it is, when it is made into a specific use mode and a specific shape, the deterioration of the mechanical characteristics due to leaving both ends of the strip-shaped flat plate formed into an annular shape is suppressed to a level with no problem. A new finding was obtained. Based on this finding, the present specification provides an unprecedented novel disc spring.

  The disc spring provided by the present specification has a first member abutting on the first end in the axial direction and a second member abutting on the second end in the axial direction, and a compression load within a predetermined range. It is a disc spring used in a state where the The disc spring has a partial conical cylinder shape in which the opening area of the second end is larger than the opening area of the first end, and from the first end in one circumferential direction of the partial conical cylinder shape. The spring member is cut to the second end. In the state of use, the disc spring maintains a state in which the first end is in line contact with the first member and the second end is in line contact with the second member. This disc spring has a (second end diameter) / (spring member width) of 8.0 or more and (disc spring effective height) / (spring member) when no load is applied. Plate thickness) is 1.0 or more.

  In the above-described disc spring, it is not necessary to weld or join both ends of a belt-shaped flat plate formed in an annular shape. As a result, deterioration in characteristics such as fatigue resistance and sag resistance due to welding or joining is suppressed. Moreover, in the state where this disc spring is used, the first end is in line contact with the first member and the second end is in line contact with the second member. That is, the first end and the second end are not used in such a compressed state that the front and back surfaces of the spring member are in surface contact with the first or second member. Further, the (second end diameter) / (spring member width) of the disc spring is set to 8.0 or more. If a disc spring having a (second end diameter) / (spring member width) of less than 8.0 is manufactured by bending a belt-shaped flat plate into an annular shape, There is a possibility that the circumferential side will wave. As a result, there is a possibility that the mechanical characteristics are deteriorated as compared with the conventional disc spring. On the other hand, in a disc spring satisfying (second end diameter) / (spring member width) of 8.0 or more, an annular flat plate is easily formed by bending a belt-shaped flat plate. And deterioration of mechanical properties can be prevented. Further, by setting (effective height of the disc spring) / (plate thickness of the spring member) to 1.0 or more, as will be described later, (effective height of the disc spring) / (plate thickness of the spring member) is Compared with a disc spring of less than 1.0, the spring constant increases in a region where the amount of deformation of the disc spring is small, but the spring constant is suppressed small in a region where the amount of deformation of the disc spring is large to some extent. Accordingly, by setting (effective height of the disc spring) / (plate thickness of the spring member) to 1.0 or more, the disc spring can be used in a region where the spring constant is small. As a result, the deterioration of the mechanical characteristics due to the cutting of the spring member is suppressed to a level where there is no problem.

  In the use state described above, one cut end face and the other cut end face of the spring member may be in contact with each other at the place where the spring member is cut from the first end to the second end. When the above-mentioned one cut end face and the above-mentioned other cut end face are displaced in the axial direction and the contact is released, the one cut end face opens beyond the other cut end face by the elastic force of the spring member. You may move in the direction which reduces an area. In this configuration, since the cut end surfaces of the spring members are brought into contact with each other at the cutting position in the use state, internal stress is generated in the spring member in the direction of reducing the diameter of the disc spring. According to this configuration, the load generated by the disc spring can be increased.

  In the above-described disc spring, in the state where no load is applied, the disc height in the circumferential direction of the partial conical cylinder shape may be changed. Usually, the disc spring is used in a state where the disc height is uniform. For this reason, in the disc spring having the above-described configuration, the amount of deformation in the use state increases as the plate height in a state where no load is applied. For example, in a disc spring that has a cut portion and the plate height is uniform when no load is applied, the load generated from the peripheral portion of the cut portion in use is not It may be smaller than the load generated from other parts. In this case, in a state where no load is applied, the dish height of the peripheral portion of the cut portion is generated from the peripheral portion of the cut portion by making it higher than the dish height of the other portion. The applied load can be increased. As a result, it is possible to reduce the difference in the generated load of each part in the circumferential direction of the partial conical cylinder shape.

  A disc spring device provided with the above-described disc spring is also novel and useful. That is, this disc spring apparatus includes the above-described first member, the above-described second member, and the above-described disc spring. At least one of the first member and the second member includes a restraining portion that restrains deformation of the shape of the second end of the spring member. According to this configuration, when the load is applied to the disc spring, the deformation of the second end of the disc spring can be restrained by the first member and the second member. According to this configuration, the load generated by the disc spring can be increased. Moreover, the difference in the generated load in the circumferential direction of the disc spring can be reduced.

  A manufacturing method for manufacturing the above-described disc spring is also novel and useful. That is, this disc spring manufacturing method includes a bending step and a forming step. In the bending step, the belt-shaped flat plate is bent to form the belt-shaped flat plate into an annular flat plate. In the forming step, the material formed into an annular shape is formed into a partial conical cylinder shape.

  According to the technique provided by the present specification, a disc spring can be manufactured without welding or joining. As a result, it is possible to suppress deterioration of characteristics such as durability of the disc spring due to welding or joining.

The longitudinal cross-sectional view of a disc spring apparatus is shown. The perspective view of a disc spring is shown. The figure for demonstrating the manufacturing method of a disk spring is shown. The top view of the cyclic | annular flat plate in the middle of manufacture of a disk spring is shown. The figure for demonstrating the manufacturing method of a disk spring is shown. The perspective view of the modification of a disc spring is shown. The perspective view of the modification of a disc spring is shown. The top view and front view of the modification of a disc spring are shown. The graph which shows the experimental result of 1st experiment is shown. The graph which shows the experimental result of 2nd experiment is shown. The figure for demonstrating the disk spring of 3rd experiment is shown. The graph which shows the experimental result of 3rd experiment is shown. The graph which shows the experimental result of 4th experiment is shown. The graph which shows the analysis result of 5th experiment is shown. The graph which shows the analysis result of a 1st analysis is shown. The graph which shows the analysis result of a 2nd analysis is shown.

The technical features disclosed in this specification will be listed.
(Feature 1) One cutting end surface and the other cutting end surface of the spring member may be separated from each other.
(Feature 2) In the case of Feature 1, one cut end face of the spring member may be located beyond the other cut end face in the circumferential direction of the partial cylindrical shape. That is, the disc spring may have a portion in which the spring member overlaps between the one cut end surface and the other cut end surface of the spring member.
(Feature 3) In the case of Feature 1, in the circumferential direction of the partial conical cylinder shape, the dish height between one cut end face and the other cut end face of the spring member may be the highest.
(Feature 4) The constraining portion of the disc spring device may constrain the deformation of the second end by contacting the outer peripheral end of the disc spring over the entire circumference. Alternatively, the restraining portion may restrain the deformation of the second end by intermittently contacting the outer peripheral end of the disc spring.

  Embodiments will be described with reference to the drawings. FIG. 1 shows a longitudinal sectional view of the disc spring device 10. The disc spring device 10 includes a disc spring 30, a first member 18, a second member 20, a third member 16, and a fourth member 14.

  The second member 20 has a bottomed cylindrical shape. The second member 20 includes a bottom 24 and a side wall 22. The bottom 24 has a disk shape. The side wall 22 goes around the outer periphery of the bottom 24. A disc spring 30 is placed on the bottom 24 of the second member 20.

  As shown in FIG. 2, the disc spring 30 is comprised by the spring member 31 which has a partial conical cylinder shape. The spring member 31 has a cutting portion 44 at one place in the circumferential direction. The cutting portion 44 extends from the first end 32 of the disc spring 30 to the second end 36. The first end surface 40 and the second end surface 42 of the spring member 31 are separated from each other. In a state where no load is applied, the disc height of the disc spring 30 (the distance from the first end 32 to the second end 36 in the axial direction of the disc spring 30 (vertical direction in FIG. 1)) is disc spring. It is uniform over the entire circumference. The second end 36 is in contact with the bottom 24 of the second member 20. The second end 36 is in line contact with the bottom 24 of the second member 20 over the entire length of the second end 36. The diameter D of the second end 36 is larger than the diameter of the first end 32. The outer peripheral end 34 of the disc spring 30 is in contact with the side wall 22 of the second member 20 over the entire length of the outer peripheral end 34. The side wall 22 restrains the second end 36 from expanding and deforming in the radial direction. The diameter D of the second end 36 / the width b of the spring member 31 (the distance along the spring member 31 between the first end 32 and the outer peripheral end 34) is 8.0 or more.

A first member 18 is placed on the disc spring 30. The first member 18 has a disk shape. The first end 32 of the disc spring 30 is in contact with the first member 18. The first end 32 is in line contact with the first member 18 over the entire length of the first end 32. A third member 16 is placed on the first member 18. The third member 16 has a disk shape. A fourth member 14 is placed on the third member 16. The fourth member 14 is an annular flat plate. The fourth member 14 is fixed to the side wall 22 of the second member 20 by bolts 12. The disc spring device 10 is used in a state where the fourth member 14 is fixed to the side wall 22 by the bolt 12. That is, in a state where the disc spring 30 is set in the disc spring device 10, the deformation of the disc spring 30 is restrained by the second member 20. In a state where the fourth member 14 is fixed to the side wall 22, the distance between the first member 18 and the second member 20 is smaller than the disc height H ₀ of the disc spring 30 when no load is applied. For this reason, the disc spring 30 is deformed between the first member 18 and the second member 20 when the disc spring 30 is in use. As a result, the contact pressure between the first member 18 and the third member 16 is maintained constant by the load generated by the elastic force of the disc spring 30. In addition, if each member 14-20 etc. are worn by use of the disc spring apparatus 10, the deformation amount of the disc spring 30 will also change according to it, and the elastic force which the disc spring 30 will generate will also change. For this reason, the disc spring 30 of the present embodiment is required to have a small change in elastic force generated with respect to the amount of deformation (that is, a low spring constant).

  Then, the manufacturing method of the disc spring 30 is demonstrated in detail. 3 to 5 are diagrams for explaining a method of manufacturing the disc spring 30. FIG. As shown in FIG. 3, the belt-like flat plate 50 for the disc spring 30 is supplied to the bending device 52. The bending device 52 includes a plurality of rollers 54 and a bending guide 56. The belt-like flat plate 50 is sent out in the direction of the arrow pointing to the right from the roll material (not shown) by the rotation of the plurality of rollers 54. The belt-like flat plate 50 delivered from the roller 54 is formed into an annular flat plate 60 (see FIG. 4) by a bending guide 56. When the belt-shaped flat plate 50 is supplied to the bending device 52 by a predetermined length, it is cut by a cutting blade (not shown).

  As shown in FIG. 4, when the bending process described above is completed, the material 50 is formed into an annular flat plate 60. The annular flat plate 60 has a cutting portion 62 extending from the outer peripheral edge 64 to the inner peripheral edge 66 at one place in the circumferential direction. Subsequently, as shown in FIG. 5, the annular flat plate 60 is formed by the press device 70 into the same shape as the partial frustoconical disc spring 30 shown in FIG. 2. The press device 70 includes an upper die 72 and a lower die 74. The press device 70 forms the annular flat plate 60 placed on the lower die 74 by causing the upper die 72 to approach the lower die 74. When the above-described forming process is completed, heat treatment such as quenching and tempering is executed to manufacture the disc spring 30. In addition, the manufacturing method of the disc spring 30 includes a step of welding or joining the cutting portion 62 of the annular flat plate 60 or the cutting portion 44 of the disc spring 30, for example, a step of performing beam welding, chemical, physical, and the like. The process etc. which join to are not included.

  In the manufacturing method of the disc spring 30 described above, the yield is good compared to the conventional manufacturing method of punching a flat plate to manufacture a disc spring. Further, the first end surface 40 and the second end surface 42 of the spring member 31 are not welded or joined. According to the disc spring 30, it can suppress that the characteristics of the disc spring, such as durability of the disc spring 30 and sag resistance, fall with time by welding or joining.

  The above-described manufacturing method of the disc spring 30 does not include a step of welding or joining the cutting portion 62 of the annular flat plate 60 and the cutting portion 44 of the disc spring 30. For this reason, the cost which manufactures the disc spring 30 can be reduced, and manufacturing time can be shortened.

  The disk spring 30 described above satisfies D / b ≧ 8.0. If the disc spring 30 is manufactured by a conventional manufacturing method in which a flat plate is punched and manufactured, the yield is poor and the manufacturing cost increases. For this reason, manufacturing cost can be suppressed by manufacturing the disc spring 30 which satisfy | fills D / b> = 8.0 with the above-mentioned manufacturing method. On the other hand, when the disc spring satisfying D / b <8.0 is manufactured by the conventional manufacturing method and the case where the disc spring is manufactured by the manufacturing method of the present specification described above, However, the manufacturing cost is often suppressed. Moreover, when the disc spring which satisfy | fills D / b <8.0 is manufactured by the conventional manufacturing method, the cyclic | annular inner peripheral side will wave and it will become difficult to form the cyclic | annular flat plate 60. FIG. On the other hand, in the disc spring 30 satisfying D / b ≧ 8.0, the disc spring 30 can be easily manufactured by the manufacturing method described above.

(Modification)
In the disc spring 30 described above, the first end surface 40 and the second end surface 42 of the spring member 31 are separated from each other at the cutting portion 44. However, the disk spring shown below may be sufficient. FIG. 6 is a perspective view of a disc spring 80 according to a modification. The disc spring 80 includes a spring member 84 having a partial conical cylinder shape. The spring member 84 has a cutting portion 82 at one place in the circumferential direction. The cutting portion 82 extends from the first end 86 to the second end 88 of the disc spring 80, and the first end surface 90 and the second end surface 92 of the cutting portion 82 are separated from each other.

  In the disc spring 30 of the above-described embodiment, in a use state, the load generated from the peripheral portion of the cutting portion 44 is smaller than the load generated from other portions. On the other hand, in the disc spring 80, the spring member 84 exists twice around the cutting portion 82. As a result, in the disc spring 80, a decrease in the load generated from the peripheral portion of the cutting portion 82 is suppressed in the use state. Thereby, in the disc spring 80, the deviation of the generated load in the circumferential direction can be reduced.

  Or the disc spring 100 shown in FIG. 7 may be sufficient. FIG. 7 is a perspective view of the disc spring 100. The disk spring 100 has a shape in which the diameter of the disk spring 80 shown in FIG. 6 is increased and the first end surface 90 and the second end surface 92 are brought into contact with each other. That is, when the first end surface 90 and the second end surface 92 are displaced in the axial direction of the disc spring 100 and the contact is released, the first end surface 90 is caused by the elastic force of the disc spring 100 (spring member 84). Moves beyond the second end surface 92 in the direction in which the opening area of the disc spring 100 is reduced. Further, when the first end surface 90 and the second end surface 92 are displaced in the radial direction of the disc spring 100 and the contact is released, the first end surface 90 is caused by the elastic force of the disc spring 100 (spring member 84). Moves beyond the second end 92 and deforms into the same shape as the disc spring 80 shown in FIG. In the disc spring 100 shown in FIG. 7, internal stress in the direction of reducing the diameter of the disc spring 100 is generated in the disc spring 100 in a state where no load is applied. For this reason, when the disc height of the disc spring 30 and the disc spring 100 is the same, the generated load of the disc spring 100 is larger than that of the disc spring 30 in use. Further, in the state of use, the generated load is larger in the peripheral portion of the cutting portion 96 of the disc spring 100 than in the peripheral portion of the cutting portion 44 of the disc spring 30. Thereby, the deviation of the generated load in the circumferential direction of the disc spring can be reduced.

Or the disc spring 110 shown in FIG. 8 may be sufficient. FIG. 8 shows a plan view and a front view of the disc spring 110. The disc spring 110 is formed with a cutting portion 116 extending from the first end 112 to the second end 114. In the disc spring 110, the disc height in a state where no load is applied changes in the circumferential direction of the partial conical cylinder shape. Specifically, both sides of the cutting portion 116, i.e., dish height _{H 1} is the highest at the first end surface 112 and the second end surface 114. In the circumferential direction of the partial conical cylinder shape, the dish height gradually decreases as the distance from the cutting portion 116 increases. In FIG. 8, in the region on the right side of the shaft 118 of the disc spring 110, the plate height is formed constant at a plate height H ₂ that is smaller than the plate height H ₁ .

  Further, in the disc spring device 10 shown in FIG. 1, the second member 20 includes the side wall 22 that restrains the deformation of the second end 36 of the disc spring 30. A restraining portion that restrains deformation of the second end 36 of the spring 30 may be provided. Or both the 1st member 18 and the 2nd member 20 may be provided with the restraint part. In the embodiment shown in FIG. 1, the side wall 22 is provided over the entire circumference of the second member 20, but the side wall 22 is provided intermittently along the outer circumference of the second member 20. Also good.

  Moreover, in the manufacturing method of the disk spring 30 described above, after the bending step of forming the belt-shaped flat plate 50 into the annular flat plate 60 is performed, the annular flat plate 60 has the same shape as the disc spring 30 (partial conical cylinder shape). A molding process is performed to form the mold. However, the bending step of forming the belt-shaped flat plate 50 into an annular shape and the forming step of forming the annular shape into the same shape (partial conical cylinder shape) as the disc spring 30 may be performed simultaneously. For example, the bending step and the forming step can be performed simultaneously by supplying the belt-like flat plate 50 to the bending device 52 in a state where the flat plate 50 is inclined with respect to the axial direction of the roller 54.

  The first to fourth experiments were performed on the disc spring 30 disclosed in the present specification, and the fifth experiment was performed on the disc spring 100 disclosed in the present specification. Further, the first and second analyzes were performed on the disc spring 110. Hereinafter, the results of the experiment and analysis will be described in detail.

(First experiment)
The first experiment will be described in detail. The first experiment is an experiment for examining the load characteristic of the disc spring 30, that is, the load generated by the disc spring 30 with respect to the amount of change in the disc height. In the first experiment, the disc spring 30 is sandwiched between two disc-shaped members, the member that contacts the second end 36 of the disc spring 30 is fixed, and the member that contacts the first end 32 is moved. Thus, when the interval between the disk-shaped members is reduced, the load applied to the member that contacts the first end 32, that is, the load generated by the disc spring 30 was measured.

In the following description, the height of the dish when no load is applied (the distance in the axial direction of the disk spring 30 between the first end 32 and the second end 36 in FIG. 1) is H ₀ , and the load is applied. H is the disc height when the load is not applied, h is the effective height of the disc spring when the load is not applied (the distance in the axial direction of the disc spring 30 between the second end 36 and the inner peripheral end 38), and the spring member The plate thickness (distance in the plate thickness direction of the spring member between the outer peripheral end 34 and the second end 36) is t, and the plate width of the spring member (along the surface of the spring member between the first end 32 and the outer end 34). B), and the outer diameter of the disc spring (the diameter of the outer peripheral end 34) is represented by φ.

(Belleville spring shape)
In the first experiment, five disc springs including the first to fourth disc springs and a disc spring for comparison were prepared. The first to fourth disc springs are the same as the disc spring 30 described above, and are configured in a partial conical cylinder shape having a cutting portion 44. The disc spring for comparison is a disc spring manufactured by a conventional manufacturing method in which a flat plate material is punched into an annular shape and formed into a partial conical cylinder shape. That is, the disc spring for comparison is a disc spring which does not have the cutting part 44 and is continuous in the circumferential direction, unlike the disc spring 30, like the conventional disc spring. The load characteristics of the comparative disc springs were also measured in the same manner as the first to fourth disc springs.

The first to fourth and comparative disc springs all have a plate thickness t of 2.7 mm, a plate width b of 13.5 mm, an outer diameter φ of 232 mm, and the material is JIS standard SK85. The disc height H ₀ is 6.20 mm for the second disc spring, 5.87 mm for the first and third disc springs, and 5.70 mm for the fourth disc spring. The disc height H ₀ of the comparative disc spring is 5.87 mm. As shown in FIG. 1, the third and fourth disc springs are constrained so that the second end 36 does not expand.

(Experimental result)
FIG. 9 shows a graph of experimental results of load characteristics of the first to fourth disc springs and the disc spring for comparison. The horizontal axis of FIG. 9 shows the disc height H of the disc spring, and the vertical axis shows the load generated by the disc spring. The experimental result of the first disc spring is on line 124, the experimental result of the second disc spring is on line 122, the experimental result of the third disc spring is on line 126, and the experimental result of the fourth disc spring is on line 128. In addition, the experimental result of the disc spring for comparison is shown by a line 120.

In the experimental results of the first experiment, the load characteristic of the first disc spring (line 124, H ₀ = 5.87 mm) is more than the load characteristic of the disc spring for comparison (line 120, H ₀ = 5.87 mm). It was small. On the other hand, the load characteristic of the second disc spring (line 122, H ₀ = 6.20 mm) having a disc height H ₀ higher than that of the comparative disc spring is that the disc height H is 5.0 mm. In the range of 3.5 mm, it was substantially the same as the load characteristic of the disc spring for comparison (line 120). Further, the load characteristic of the third disc spring (line 126, H ₀ = 5.87 mm) having the same shape as the first disc spring and the outer periphery being constrained is such that the disc height H is 4.0 mm. In the above range, the load characteristics of the disc spring for comparison (line 120) were substantially the same, and when the disc height H was lower than 4.0 mm, it became larger than the disc spring for comparison. In addition, the load characteristic of the fourth disc spring (line 128, H ₀ = 5.70 mm) whose outer periphery is constrained and whose disc height H ₀ is lower than that of the third disc spring is high in the disc height H. In some cases, it was smaller than the load characteristics of the disc spring for comparison (line 120), and became larger than the disc spring for comparison when the disc height was lowered.

From the experimental results of the first experiment, when the disc spring 30 is used in place of the conventional disc spring (the disc spring for comparison) that does not have the cutting portion 44, the disc height H ₀ is set higher than that of the conventional disc spring. By doing so, the disc spring 30 can generate a load substantially equivalent to the conventional disc spring. Alternatively, by constraining the deformation of the second end 36 of the disc spring 30, the disc spring 30 can generate a load substantially equivalent to that of the conventional disc spring.

(Second experiment)
Subsequently, the second experiment will be described in detail. The second experiment is an experiment for examining the relationship between the disc height H ₀ of the disc spring and the generated load of the disc spring. In the second experiment, the load generated by the disc spring was measured when the disc spring having the disc height H ₀ was deformed to the disc height H = 3.5 mm and 4.5 mm. In the second experiment, as in the first experiment, the disc spring was deformed by sandwiching the disc spring between the disc-shaped members, and the load was measured.

(Belleville spring shape)
In the second experiment, two types of disc springs of type 1 and type 2 were prepared. The first type of disc springs, plates and height H ₀ other dimensions and material is the same as the first disc spring of the first experiment described above. That is, the first type disc spring has the same shape as the disc spring 30 and has a cutting portion 44. The second type disc spring has the same dimensions and materials other than the disc height H _{0 as} the disc spring for comparison in the first experiment described above. That is, the second type disc spring is a conventional disc spring that does not have the cutting portion 44. In the first type of disc springs, disc height _{H 0} is prepared 5.69mm, 5.75mm, 5.80mm, 5.83mm, 5.90mm, seven disc springs of 6.06mm and 6.08mm . In the second type of disc spring, the disc height H ₀ is 5.83 mm, 5.86 mm, 5.88 mm, 5.89 mm, 5.93 mm, 6.02 mm, 6.29 mm, 6.33 mm and 6.36 mm. Nine disc springs were prepared.

(Experimental result)
FIG. 10 shows a graph of the experimental results of the second experiment. The horizontal axis in FIG. 10 indicates the dish height H ₀ , and the vertical axis indicates the load generated by the disk spring. The measurement point group 130 is a second type disc spring (conventional disc spring), and shows an experimental result when the disc height H is 3.5 mm. The measurement point group 134 is a second type disc spring (conventional disc spring), and shows an experimental result when the disc height H is 4.5 mm. The measurement point group 132 is a first type disc spring (disc spring 30), and shows an experimental result when the disc height H is 3.5 mm. The measurement point group 136 is a first type disc spring (disc spring 30), and shows an experimental result when the disc height H is 4.5 mm.

In the experimental results of the second experiment, in both the first and second type disc springs, the higher the disc height H ₀ , the higher the load generated by the disc spring in the state of being deformed to the disc height H. became. From the experimental results of the second experiment, it was found that the relationship between the dish height H ₀ and the generated load can be approximated to a straight line. For example, the measurement point group 130 can be approximated to a straight line 131. Similarly, the measurement point groups 132, 134, and 136 can be approximated to straight lines 133, 135, and 137, respectively.

From this relationship, when the disc spring 30 is used instead of the conventional disc spring, it can be estimated how much the disc height H ₀ of the disc spring 30 should be set. For example, when the plate height H in use is 4.5 mm, the plate height H ₀ of the plate spring 30 is H ₀ = 1.34 × (the plate height H ₀ of the conventional plate spring) -1. It can be calculated by calculating 68.

(Third experiment)
Subsequently, the third experiment will be described in detail. The third experiment is an experiment for examining the influence of the size of the gap of the cutting portion 44 of the disc spring 30. In the third experiment, the load characteristic of the disc spring 30 was measured by changing the size of the gap of the cutting portion 44. The experiment method of the third experiment is the same as that of the first experiment. That is, the load which a disc spring produces | generates when a disc spring is arrange | positioned between two members and the space | interval between members is made small was measured.

(Belleville spring shape)
In the third experiment, fifth to seventh disc springs were prepared. The dimensions and materials of the fifth to seventh disc springs are the same as those of the second disc spring of the first experiment described above, except for the size of the gap of the cutting portion 44. As shown in FIG. 11, the size of the gap between the cutting portions 44 of the fifth to seventh disc springs is defined by an angle around the axis of the disc spring 30 (θ in FIG. 11). The fifth disc spring has θ of 60 degrees, the sixth disc spring has θ of 90 degrees, and the seventh disc spring has θ of 120 degrees.

(Experimental result)
FIG. 12 shows a graph of the experimental results of the third experiment. The horizontal axis of FIG. 12 shows the disc height H of the disc spring, and the vertical axis shows the load generated by the disc spring. FIG. 12 also shows an experimental result 120 of a disc spring for comparison in the first experiment. The line 140 shows the experimental results in the case of the fifth disc spring (θ = 60 degrees), and the lines 142 and 144 respectively show the sixth disc spring (θ = 90 degrees) and the seventh disc spring (θ = The experimental results in the case of 120 degrees) are shown.

  In the experimental result of the third experiment, the load characteristic of the disc spring was smaller as θ was larger. When the disc height H of the disc spring is between 3.5 mm and 4.5 mm, the sixth disc spring (line 142) having θ = 90 degrees is substantially the same as the disc spring for comparison (line 120). The load characteristics are shown. From this result, it was found that by adjusting the size of the gap of the cutting portion 44 of the disc spring 30, the disc spring 30 that generates a load similar to that of the conventional disc spring can be obtained.

(4th experiment)
Next, the fourth experiment will be described in detail. The fourth experiment is an experiment for examining the effective height h / thickness t. The experimental method is the same as in the first experiment. That is, the load which a disc spring produces | generates when a disc spring is arrange | positioned between two members and the space | interval between members is made small was measured.

(Belleville spring shape)
In the fourth experiment, similarly to the disc spring 30, a plurality of disc springs having a cutting portion and having a h / t value of 0.38 to 1.80 were prepared.

(Experimental result)
FIG. 13 shows a graph of the experimental results of the fourth experiment. The horizontal axis of FIG. 13 shows the contact deflection ratio indicated by the deflection of the disc spring 30 / the deflection at the time of contact. The deflection at the time of close contact is the deflection when the effective height of the disc spring 30 is 0 mm, and is the same as the effective height h when no load is applied. The vertical axis in FIG. 13 indicates the contact load ratio indicated by the load generated by the disc spring 30 / the load at the time of contact. The close load is a load generated by the disc spring when the effective height of the disc spring 30 is 0 mm. Line 150 shows the experimental results for h / t = 1.0. The line group 152 shows the experimental result of the disc spring 30 satisfying h / t> 1.0, and the line group 154 shows the experimental result of the disc spring 30 satisfying h / t <1.0.

  From the experimental results of the fourth experiment, the disc spring 30 satisfying h / t ≧ 1.0 is smaller in the region where the deformation amount of the disc spring 30 is smaller than the disc spring 30 satisfying h / t <1.0. In a region where the load change (spring constant) with respect to the change in deflection is large and the amount of deformation is large, there is a region where the spring constant is small. For this reason, when it is desired to apply a certain load using the disc spring 30, the disc height H in the usage state of the disc spring 30 is slightly different from the wear of the portions 14 to 20 of the disc spring device 10 described above. If the disc spring 30 is approximately h / t ≧ 1.0, the load change from the required load is small. That is, the disc spring 30 satisfying h / t ≧ 1.0 has a larger load generated by the disc spring 30 in proportion to the disc height H, like the disc spring 30 satisfying h / t <1.0. Unlike the so-called disc spring washer, which requires this, it is preferably used when a constant load is to be applied using the disc spring 30.

(Fifth experiment)
Next, the fifth experiment will be described in detail. The fifth experiment is an experiment for examining the load characteristics of the disc spring 100 shown in FIG. The experimental method is the same as in the first experiment. That is, the load which a disc spring produces | generates when a disc spring is arrange | positioned between two members and the space | interval between members is made small was measured.

(Belleville spring shape)
In the fifth experiment, six disc springs were prepared. The plate thickness t, plate width b, outer diameter φ, material, and plate height H ₀ of the six disc springs are the same as those of the first disc spring of the first experiment. The six disc springs have two spring members 84 when the contact between the first end surface 90 and the second end surface 92 is released and the first end surface 90 moves beyond the second end 92. The overlapping overlap length L (see FIG. 6) is different. The overlap length L of the six disc springs is 2.0 mm, 3.4 mm, 5.3 mm, 7.6 mm, 11.0 mm, and 15.3 mm, respectively.

(Experimental result)
FIG. 14 shows a graph of the experimental results of the fifth experiment. The horizontal axis of FIG. 14 indicates the disc height H of the disc spring, and the vertical axis indicates the load generated by the disc spring. FIG. 14 shows experimental results 120 and 124 of the disc spring for comparison and the first disc spring in the first experiment. The experimental results for the six disc springs are shown in line group 156. In the line group 156, the experimental results of the disc springs having the overlapping length L of 2.0 mm, 3.4 mm, 5.3 mm, 7.6 mm, 11.0 mm, and 15.3 mm are shown in order from the smallest generated load. Show.

In the experimental results of the fifth experiment, when internal stress in the direction of reducing the diameter of the disc spring 100 is generated when no load is applied, the disc spring 30 is compared with the disc spring 30 in which no internal stress is generated. Even when the height H ₀ was the same, the generated load increased. Further, the longer the overlap length L, the greater the generated load.

From the experimental results of the fifth experiment, when using the disc spring 100 instead of the conventional disc spring (comparative disc spring) that does not have the cutting portion 44, the disc spring 100 is adjusted by adjusting the overlap length L. Can generate substantially the same load as a conventional disc spring.

(First analysis)
Subsequently, the first analysis will be described in detail. The first analysis is an FEM analysis for examining the load characteristics of the disc spring 110 shown in FIG.

(Belleville spring shape)
The disc spring 110 has a plate thickness t of 2.7 mm, a plate width b of 13.5 mm, an outer diameter of 232 mm, and a material set to JIS standard SK85. Dish height _{H 1} is 6.67Mm, dish height _{H 2} was set to 5.87mm.

(Analysis result)
FIG. 15 shows a graph of the analysis result of the first analysis. The horizontal axis of FIG. 15 shows the disc height H of the disc spring, and the vertical axis shows the load generated by the disc spring. In FIG. 15, a line 120 that is the experimental result of the comparative disc spring of the first experiment and a line 124 that is the experimental result of the first disc spring are shown as the comparison results.

  In the analysis result of the first analysis, the disc spring 110 exhibited substantially the same load characteristics as the disc spring for comparison (conventional disc spring) of the first experiment when the disc height H was lower than 5.87 mm. When the disc height H of the disc spring 110 is higher than 5.87 mm, the disc spring 110 generates a load only from a portion where the disc height is higher than 5.87 mm when no load is applied. For this reason, the generated load with respect to the dish height is small. On the other hand, when the disc height of the disc spring 110 is lower than 5.87 mm, a load is generated in the entire circumferential direction of the disc spring 110. As a result, it is estimated that the disc spring 110 generates substantially the same load as the conventional disc spring.

The load generated by the disc spring 30 is larger than the load generated by the first disc spring. Whereas the disc height H ₀ of the first disc spring is 5.87 mm, the disc spring 30 has a portion where the disc height is 5.87 mm or more when no load is applied. Therefore, it is estimated that the load generated by the disc spring 30 is larger than that of the first disc spring.

(Second analysis)
The second analysis is an FEM analysis for examining the moment around the axis 118 (see FIG. 8) generated by the disc spring.

(Belleville spring shape)
In the second analysis, an eighth disc spring (disc height H ₀ = 5.87 mm) having the same dimensions and material as the first disc spring of the first experiment described above, an eighth disc spring and the disc height. only H ₀ is performed analyzed three disc springs of the disc spring 110 used in the different ninth disc spring and the first analysis. The disc height H ₀ of the ninth disc spring is 6.67 mm.

FIG. 16 shows a graph of the analysis result of the moment about the axis 118 generated by the disc spring. The horizontal axis in FIG. 16 indicates the dish height, and the vertical axis indicates the moment around the axis 118. A line 160 indicates the analysis result of the disc spring 110, a line 162 indicates the sixth disc spring, and a line 164 indicates the seventh disc spring. In the analysis result of the second analysis, in the region where the disc height H is 5.87 mm or less, the disc spring 110 has a shaft 118 as compared with the eighth and ninth disc springs where the disc height H ₀ is constant. The moment becomes smaller. Eighth dish the height H ₀ is fixed, in the ninth disc spring, generated load in the periphery of the cutting portion 44, to become smaller than the generated load in the other portions, the moment is increased. On the other hand, in the disc spring 110, since the dish height of the peripheral part of the cutting part 116 is high, the fall of the generated load by the cutting part 116 can be suppressed, and the moment became small. From this result, the disc spring 110 can be suitably used particularly for a disc spring device that requires a small moment around the shaft 118.

From the experiment and analysis results described above, the disc springs 30, 80, 100, and 110 restrain the disc height H ₀ , the form (the disc spring 30, 80, 100, or 110), and the deformation of the second end of the disc spring. It was found that it can be used in place of a conventional disc spring by appropriately selecting whether or not to do so.

As mentioned above, although embodiment of this invention was described in detail, these are only illustrations and do not limit a claim. The technology described in the claims includes various modifications and changes of the specific examples illustrated above.
The technical elements described in this specification or the drawings exhibit technical usefulness alone or in various combinations, and are not limited to the combinations described in the claims at the time of filing. The technology illustrated in this specification or the drawings achieves a plurality of objects at the same time, and achieving one of the objects itself has technical utility.

10: disc spring device 18: first member 20: second member 22: side walls 30, 80, 100, 110: disc spring 31: spring member 32: first end 36: second end 40: first end face 42: 2nd end surface 44: Cutting part 50: Material 52: Bending device 70: Press device

Claims (5)

A dish that is used in a state in which a first member abuts on the first end in the axial direction and a second member abuts on the second end in the axial direction, and a compressive load within a predetermined range acts. A spring,
The opening area of the second end has a partial conical cylinder shape that is larger than the opening area of the first end, and the first end is located at one place in the circumferential direction of the partial conical cylinder shape. A spring member cut to the second end,
In the use state, the first end is in line contact with the first member, and the second end is in line contact with the second member.
In a state where no load is applied, (diameter of the second end) / (width of the spring member) is 8.0 or more and (effective height of the disc spring) / (of the spring member) A disc spring having a thickness of 1.0 or more.   In the use state, at the place where the spring member is cut from the first end to the second end, one cut end surface of the spring member and the other cut end surface are in contact with each other, When the cutting end surface and the other cutting end surface are displaced in the axial direction and the contact is released, the one cutting end surface exceeds the other cutting end surface by the elastic force of the spring member and the opening area The disc spring according to claim 1, wherein the disc spring moves in a direction of reducing the size of the disc spring.   The disc spring according to claim 1 or 2, wherein a disc height in a circumferential direction of the partial conical cylinder shape changes in a state where no load is applied. The first member;
The second member;
A disc spring according to any one of claims 1 to 3,
A disc spring device comprising:
At least one of the first member or the second member is a disc spring device provided with a restraining portion that restrains deformation of the second end of the spring member. It is a manufacturing method of the disc spring according to any one of claims 1 to 3,
A bending step of bending the belt-shaped flat plate to form the belt-shaped flat plate into an annular flat plate;
And a forming step of forming the flat plate formed into the annular shape into a partial conical cylinder shape.

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