JP4916914B2 - Rail fastening mechanism with wire spring clip - Google Patents

Description

The present invention relates to a wire spring clip capable of fastening rails for a plurality of types of overhead cranes using one type of wire spring clip and a seat base having one type of pedestal height for hooking the wire spring clip. Relates to a rail fastening mechanism.

Conventionally, overhead cranes that are transport equipment are used in factories. This overhead crane has a traverse girder and a runway girder for travel, and travels on traverse rails and travel rails (hereinafter also simply referred to as rails) fixed to each girder. When fixing this rail to the girder, fix the seat with the bolts upright to the girder so that the rail is sandwiched from both sides, and hook the flanges on both sides of the rail at the front side of the presser member. Bolts attached to the seat are inserted through holes formed on the base side of the member. And the presser member is pressed to the seat base side by tightening the nut to the bolt.
As a result, the flange of the rail is pressed to the girder side by the pressing member, and the rail is fastened to the girder.

However, when the overhead crane travels, vibrations are generated, which causes a problem that the nuts gradually loosen due to the vibrations and the fastening force of the rails decreases.
For this reason, (1) periodically check the mounting condition of the presser member and perform additional tightening of the nut as necessary. (2) The loosening resistance of the rail is reduced by the loosening of the nut, and the rail joint portion Increased play gaps and breakage of rails. (3) When regular inspections and maintenance of rails are performed, the factory operation is stopped. Has occurred, causing problems such as complicated process adjustment.
Then, the fastening of the rail which uses a wire spring clip is proposed as a method in which the fastening force of a rail does not fall even if a vibration generate | occur | produces by driving | running | working of an overhead crane (for example, refer patent document 1).

Japanese Utility Model Publication No. 5-7703

Here, for example, when various factories organically cooperate to form one factory group like an ironworks, various standards (for example, JIS standards are determined) in this factory group. 37 kg, 40 kg N, 50 kg N, 60 kg or crane rails of CR 73 kg, CR 100 kg) are used. And if this standard is different, the rail shape is also different, so when applying the invention described in Patent Document 1, the wire spring clip and the wire spring clip are hooked for each rail of the standard used. It is necessary to prepare a seat.
For this reason, it is necessary to prepare and store maintenance parts (paired wire spring clips and seats) for each rail of all standards used in the factory group, and purchase many types of maintenance parts. Economic burden and management burden of storing many types of maintenance parts.

The present invention has been made in view of such circumstances, and uses a type of wire spring clip and a seat plate having one type of pedestal height for hooking the wire spring clip, for overhead cranes of a plurality of types of standards. It aims at providing the rail fastening mechanism by the wire spring clip which can fasten the rail of this.

The rail fastening mechanism using the wire spring clip according to the present invention that meets the above-described object is provided with a rail for a plurality of standard overhead cranes having a weight per meter of 37 kg or more and 100 kg or less at a pitch of 250 mm or more and 960 mm or less. Wire spring clip having an e-shape in plan view with an allowable maximum fastening force of 2000 kg or less and a maximum deformation amount of 30 mm or less, a pedestal on which the central portion of the wire spring clip is placed, and the wire spring A rail fastening mechanism that uses a base plate integrally provided with a latching portion into which a base portion of a clip is inserted, and is fixed to a rail installation location for the overhead crane. ,
The height H (mm) of the pedestal is within the range shown in the following formula, and one type of the wire spring clip and one type of pedestal height with respect to the rails for the plurality of standard overhead cranes. Using said seat.
H ₀ + 0.0039X−0.3 ≦ H ≦ H ₀ +18.0
Here, H ₀ (mm) is the height at which the deformation amount of the wire spring clip becomes 0 when the wire spring clip is installed on a rail for an overhead crane of 37 kg per meter, and X (mm) is It is the pitch of a plurality of wire spring clips.

The rails for overhead cranes with a weight per meter of 37 kg to 100 kg are, for example, ordinary rails with a weight per meter of 37 kg (JIS standards 37 kg), ordinary rails with a weight per meter of 40 kg (JIS standards) 40kgN) Normal rail with a weight of 50kg per JIS (JIS standard 50kgN) Normal rail with a weight of 60kg (JIS standard 60kg) Crane rail with a weight of 73kg per meter (CR73kg) Weight per m Is a 100 kg crane rail (CR 100 kg).

In the rail fastening mechanism using the wire spring clip according to the present invention, the height H of the pedestal of the seating board is equal to or higher than the height H _{0 at} which the deformation amount of the wire spring clip is 0 plus 2 mm (that is, 0.0039X−0.3 ≧ 2) is preferable.
In the rail fastening mechanism using the wire spring clip according to the present invention, it is preferable that the installation place of the rail for the overhead crane is various factories or warehouses constituting an ironworks, an oil complex, an automobile factory, or a shipyard.

The rail fastening mechanism using the wire spring clip according to any one of claims 1 to 3 includes one type of wire spring clip and one type for each of a plurality of standards for rails for overhead cranes without changing the type of the wire spring clip and the seat. Therefore, it is not necessary to secure a wire spring clip and a seat base for each rail standard as in the prior art, and the economical and administrative burden is reduced.
Moreover, since the rail is fixed by the elastic force of the wire spring clip, even if the rail vibrates during use, the fastening force does not decrease, and the rail can be fixed stably. As a result, the resistance to advance of the rail can be maintained, and the life of the rail joint can be extended. In addition, since the lowering of the fastening force of the rail is prevented, the time required for periodic inspections and maintenance can be shortened, and it is possible to reduce the cost and improve the operating rate of the facility. become.

In particular, in the rail fastening mechanism using the wire spring clip according to claim 2, since the height of the pedestal is not less than a predetermined height, the wire spring clip having an excessively large spring constant is not used, and excessively. The wire spring clip can obtain a force for fixing the rail for the overhead crane without using a seat plate having strict dimensional accuracy because it is thin.
Since the rail fastening mechanism using the wire spring clip according to the third aspect is applied to various factories or warehouses that use a large number of wire spring clips and seats, the above-described effect becomes more remarkable.

Next, embodiments of the present invention will be described with reference to the accompanying drawings for understanding of the present invention.
Here, FIG. 1 is a front sectional view of a rail fastening mechanism using a wire spring clip according to an embodiment of the present invention, FIG. 2 is a plan view of the rail fastening mechanism, and FIGS. 3 to 5 are rails for an overhead crane, respectively. FIG. 6 is a diagram showing the relationship between the fastening force range required to fix the wire to the girder and the deformation amount of the wire spring clip, and FIG. 6 shows the relationship between the tolerance of the spring constant of the wire spring clip and the seat height of the seat base. FIG. 7 is an explanatory diagram showing the relationship between the pedestal height of the seat and the pitch of the seat.

As shown in FIGS. 1 and 2, a rail fastening mechanism (hereinafter simply referred to as a rail fastening mechanism) 10 using a wire spring clip according to an embodiment of the present invention is a rail for an overhead crane (hereinafter simply referred to as a rail). 11) is a mechanism that uses a wire spring clip 12 and a seat 13 that holds the wire spring clip 12 to secure the rail 11 to the installation location of the rail 11, and has a weight per meter of 37-100 kg. Without changing the types of the wire spring clip 12 and the seat base 13 for each rail standard (hereinafter also referred to simply as a standard), one type of wire spring clip 12 and a seat base 13 having one type of pedestal height are used. This is a mechanism for fixing the rail 11. This will be described in detail below.

The installation place of the rail 11 is various factories constituting the steelworks, but may be other places, for example, various factories or warehouses constituting an oil complex, an automobile factory, or a shipyard. In these various factories, a girder 14 as a rail support member is provided, and seats 13 are arranged at a predetermined pitch on both sides of the rail 11 placed on the girder 14 with a space therebetween. ing. In use, the seat 13 is usually installed at a pitch of 250 mm or more and 960 mm or less.

The seat 13 has a rectangular shape in plan view, a top portion protruding in a semicircular shape when viewed from the side, and a latching portion 16 having a through-hole (an example of an insertion hole) 15 formed therein, and the latch A pedestal 17 having a rectangular shape as viewed from the side is provided. Note that the seat is not limited to this shape as long as it has the latching portion and the pedestal.
Further, a groove (not shown) for welding is integrally formed around the lower portion of the seat 13. And the latching | locking part 16 is arrange | positioned on the rail 11 side on the girder 14, and the seat base 13 is welded and fixed on the girder 14 using this groove | channel. A chamfered portion (not shown) is formed around the opening of the through hole 15 and the upper corner of the pedestal 17.

The wire spring clip 12 is configured by using, for example, a spring steel wire, and a straight portion 18 of a base portion and a short portion of a tip portion connected to the straight portion 18 via a curved intermediate portion 19. The shape part 20 is provided. Thereby, it is in an “e” shape in plan view.
A flat surface 21 is formed under the short straight portion 20 by processing. Then, by inserting the straight portion 18 of the wire spring clip 12 into the through hole 15 of the seat base 13 and hooking it, the central portion of the wire spring clip 12 at a position facing the straight portion 18 substantially in parallel ( That is, the base side portion of the intermediate portion 19 abuts on the pedestal 17 of the seat 13 while being deformed against the elastic force, and the flat surface 21 of the short straight portion 20 also resists the elastic force. In the deformed state, it contacts the upper surface of the flange 22 of the rail 11.

Thereby, the flange 22 of the rail 11 can be pressed by the wire spring clip 12, and as a result, a downward force can be applied to the flange 22 of the rail 11, and the rail 11 can be fastened on the girder 14. .
In this way, by attaching the wire spring clip 12 to the seat 13, the wire spring clip 12 is also installed at a pitch of 250 mm or more and 960 mm or less along the longitudinal direction of the rail 11.
In addition, as the wire spring clip 12 for fixing the rail 11 of a plurality of standards (for example, 37 kg, 40 kg N, 50 kg N, 60 kg, CR 73 kg, and CR 100 kg according to JIS standards), the maximum allowable fastening force in use is usually 2000 kg. In the following, those having a maximum deformation amount of 30 mm or less are used. The lower limit values of the maximum fastening force and the maximum deformation amount are not defined, but the maximum fastening force is 200 kg and the maximum deformation amount is 10 mm. Therefore, a wire spring clip having a maximum fastening force and a maximum deformation amount within this range can be used.

As shown in FIG. 1, when the same rail spring 11 with the same wire spring clip 12 is fastened on the girder 14, the height of the through hole 15 of the seat 13 from the bottom of the seat 13 is not changed. As the height H of 17 increases, the rotation angle of the wire spring clip 12 (the rotation angle around the axis of the straight portion 18) when the straight portion 18 is inserted into the through hole 15 and hooked is increased. Thus, the short straight portion 20 of the wire spring clip 12 approaches the upper surface of the girder 14.
Therefore, when the flat surface 21 of the short straight portion 20 is brought into contact with the upper surface of the flange 22 of the rail 11, the deformation amount δ (linear spring tip displacement) applied to the wire spring clip 12 becomes large. A large elastic force is generated, and the flange 22 of the rail 11 is pressed against the girder 14 with a large force by this reaction force.

When the same wire spring clip 12 is hooked on the same seat 13 and the rail standard changes from 37 kg to CR 100 kg, the flange thickness of the rail 11 gradually increases. The amount of deformation δ required for the flat surface 21 to contact the upper surface of the flange 22 also increases, and the flange 11 is pressed toward the girder 14 with a greater force as the rail 11 has a thicker flange.
Based on these matters, as an example, each rail 11 having a rail standard of 37 kg, 50 kgN, CR73 kg, and CR100 kg is provided with one type of wire spring clip 12 and one type of seat 13 for latching the wire spring clip 12. A method for determining the pedestal height of the seat 13 that can be fixed using the above will be described below.

In general, when laying rails on girders, use rails of the standard specified according to the capacity of the overhead crane, and prevent the rails from floating even if the overhead crane travels on the rails It is necessary to press and fix the rail against the girder so that the rail does not turn back easily or the rail moves in the axial direction (longitudinal direction) due to advancement.
Therefore, with respect to the rail 11 having the rail specifications of 37 kg, 50 kg N, CR 73 kg, and CR 100 kg, the use conditions such as the wheel load, the lateral pressure, the pitch of the wire spring clip in the above-described various factories under repair management, The fastening force required for each rail 11 is obtained as a fastening force corresponding to the stricter condition by comparing the full force and the small return force of the rail 11.

In this case, when the pitch of the wire spring clips was 500 mm, the required fastening force was 265 kg for JIS standard 37 kg, 444 kg for JIS standard 50 kgN, 693 kg for crane rail standard CR73 kg, and 938 kg for crane rail standard CR100 kg. Accordingly, in the various factories, the condition range of the fastening force required to fix the rails 11 of rail specifications 37 kg, 50 kg N, CR 73 kg and CR 100 kg to the girder 14 is 265 kg or more at 37 kg, 444 kg or more at 50 kg N, CR 73 kg. Is set to 693 kg or more, and CR 100 kg is set to 938 kg or more.

When the wire spring clip 12 is hooked on the seat base 13, the thickness (height) D of the flange 22 at the position where the central portion of the flat surface 21 provided on the short straight portion 20 of the wire spring clip 12 abuts. The difference between the height h of the flat surface 21 (the distance between the upper surface of the girder 14 and the flat surface 21) when the wire spring clip 12 hooked on the seat 13 is in a free state is that the wire spring clip 12 is Can be approximated to the amount of deformation δ generated in the wire spring clip 12 when tightened.
In addition, since the fastening force of the wire spring clip 12 increases as the deformation amount δ increases, the deformation amount of the wire spring clip 12 is fixed when the rail 11 having a weight per meter of 37 kg is fixed in the present embodiment. The height of the pedestal 17 of the seat 13 at which δ becomes zero, that is, the height of the wire spring clip 12 in a free state was defined as H ₀ (mm).

This H ₀ is a pedestal height at which “deformation amount δ = 0” determined by the height position of the flange 22 of the rail 11 having a weight per meter of 37 kg and the height position of the through hole 15, It is lower than the pedestal 17 height H of the seat 13 and is, for example, about 20 to 35 mm. If the fulcrum of the wire spring clip 12 (the pedestal 17 height H of the seat 13) is increased by 1 mm, the deformation amount δ of the wire spring clip 12 at the operating point is also increased by 1 mm. Moreover, although the height position of the upper end of the through-hole 15 is based also on the diameter of the wire spring clip 12, about 18-40 mm is suitable. This is formed when the diameter of the wire spring clip 12 is normally about 10 to 25 mm, the welded portion is provided about 6 to 12 mm below the through hole 15, and the wire spring clip 12 is inserted into the through hole 15. By setting the gap to 2 to 3 mm.

Here, when a wire spring clip having a maximum allowable fastening force in use of 1400 kg (2000 kg or less) is installed at a pitch of 500 mm, a method for selecting a wire spring clip having a necessary spring constant will be described first. To do.
In order for the selected wire spring clip to fasten all the rails from 37 kg to 100 kg, each rail needs to have a spring constant that satisfies the required fastening force without exceeding the maximum fastening force of the wire spring clip. is there.
That is, in order to fasten rails of all standards from 37 kg to 100 kg, the straight line L (thick solid line) indicating the spring constant is within the range of the deformation amount δ when fastening the rails of 37 kg and 100 kg. 3 to 5 must be within the hatched area shown in FIG.

Specifically, when the hatched area is at the position shown in FIGS. 4A, 4B, and 5, the dotted line L1 (the maximum spring constant of the wire spring clip) and the solid line L2 (the minimum of the line spring clip) A wire spring clip having a spring constant existing between them is selected.
The maximum spring constant of the wire spring clip (inclination of the dotted line L1) is indicated by a straight line connecting the origin of the fastening force of 0 kg (ie, H ₀ ) with a deformation of 0 mm and the point of the maximum fastening force of 1400 kg on the 100 kg rail. It is. If the slope of this straight line (dotted line L1) is further increased, it means that the deformation amount δ of the wire spring clip exceeds the maximum use deformation amount corresponding to the maximum use load, and a stable fastening force cannot be maintained. .
The minimum spring constant of the wire spring clip (inclination of the thin solid line L2) is indicated by a straight line connecting the above-described origin and the point of the required fastening force of 265 kg on the 37 kg rail or the required fastening force of 938 kg on the 100 kg rail. It is. If the inclination of the straight line (thin solid line L2) is further reduced, it means that the fastening force necessary for fixing the rail cannot be satisfied.

In the hatched area described above, the difference in flange height between the 37 kg rail and the 100 kg rail is 9 mm (the rail flange height increases as the rail standard increases), and the wire spring clip Since the maximum fastening force of the rail is 1400 kg, and the fastening force required for the rail is the same as long as the pitch of the wire spring clips does not change, the pedestal height of the seat base increases (the deformation amount of the wire spring clips (Increase) and translate in the direction in which the amount of deformation increases (the right direction of the x-axis).
For this reason, as shown in FIG. 3A, the amount of deformation δ when the 37 kg rail is fastened is small (the area shown by hatching is larger than the position of FIG. 4A and is on the origin side). In the case of the height, the inclination of the solid line L2 is larger than the inclination of the dotted line L1. At this time, since the solid line L2 may exceed the maximum fastening force of 1400 kg, there is no wire spring clip having a spring constant capable of fastening all the standard rails.
Next, when the pedestal height is increased (the region indicated by the oblique line increasing the deformation amount δ approaches the position in FIG. 4A), the slopes of the solid line L2 and the dotted line L1 both decrease, Since the amount of change in the slope of the solid line L2 is larger than that of the dotted line L1, the slope becomes the same as shown in FIG. 3B.

Then, by further increasing the pedestal height (further increasing the deformation amount δ), the slope of the solid line L2 becomes smaller than the slope of the dotted line L1, resulting in the situation shown in FIG. At this time, the straight line L existing between the dotted line L1 and the solid line L2 is a spring constant that can fasten all the standard rails from 37 kg to 100 kg.
By further increasing the pedestal height (increasing the deformation amount δ), as shown in FIG. 4 (B), the solid line L2 indicates the above-described origin and the required fastening force of each of the 37 kg and 100 kg rails. The slope has a point, that is, a straight line passing through three points.
Here, when the pedestal height is further increased (the deformation amount δ is further increased), the necessary fastening force of the 100 kg rail cannot be obtained on the straight line connecting the origin and the minimum fastening force of the 37 kg rail. This time, the straight line connecting the origin and the required fastening force of the 100 kg rail is the solid line L2. Then, the situation shown in FIG. 5 is obtained.

Thereafter, since the amount of change in the inclination of the solid line L2 is smaller than the amount of change in the inclination of the dotted line L1, the range between the dotted line L1 and the solid line L2 is gradually narrowed.
From the above results, a wire spring clip having a spring constant that falls within the range between the dotted line L1 and the solid line L2 is selected. In addition, although it is preferable to select the spring constant (kg / mm) within the range of 15 or more and 200 or less, for example, the wire spring clip has an upper limit of 180, more preferably 150, while the lower limit is 20, It is preferable to select 25 within this range.
Subsequently, the pedestal height of the base is determined. The deformation amount δ of the wire spring clip corresponds to the amount of change in the seat base height H, that is, H-H ₀ (hereinafter, also simply referred to as H ₁ ). Taking 4 (A) as an example, the validity determination of the pedestal height of the stool (method for determining the pedestal height) will be described below.

Here, in the case of FIG. 4A, the pedestal height is (H ₀ +3) mm. Using this pedestal height, the amount of deformation δ of the 37 kg rail wire spring clip is 3 mm. Further, in the 100 kg rail, the flange of this rail is 9 mm higher than the flange of the 37 kg rail, so the deformation amount δ of the wire spring clip is 12 mm. In order to carry out rail fastening without any problems using a seat plate having one kind of pedestal height and using a wire spring clip of one kind of spring constant for a 37 kg to 100 kg rail, a wire spring constant is used. Requires a wire spring clip having an inclination of the straight line L shown in FIG. That is, the inclination of the straight line L is located between the inclination of the dotted line L1 and the solid line L2, and the wire spring can hold a stable fastening force (that is, the inclination of the straight line L is smaller than the inclination of the dotted line L1). ), Which exhibits the necessary fastening force (that is, the inclination of the straight line L is larger than the inclination of the solid line L2). The dotted line L1 is determined by the maximum allowable fastening force when using the wire spring clip and the deformation amount of the 100 kg rail wire spring clip (ie, δ amount: 12 mm in this case). The solid line L2 is determined by the required fastening force of the 37 kg rail (in this case, 265 kg) and the amount of deformation of the wire spring clip of the 37 kg rail (ie, the amount of δ: 3 mm in this case).
From the above, the wire spring clip in which the relationship of (L1 inclination)> (L2 inclination) is satisfied, and further the relationship of (L1 inclination)> (L inclination)> (L2 inclination) is satisfied. If it can be selected, the pedestal height (H ₀ +3) mm is a stool having one kind of pedestal height and one kind of wire spring clip, and the wire spring clip can exhibit a stable and necessary fastening force. Thereby, the pedestal height can be selected (determined).

Since FIG. 4A is used, the solid line L2 is determined by the required fastening force of the 37 kg rail and the spring deformation amount δ of the 37 kg rail. In the case of FIG. 938 kg) and 100 kg rail spring deformation δ (14 mm in this case). In the case of FIG. 5, when the solid line L2 is determined by the required fastening force of the 37 kg rail and the spring deformation amount δ of the 37 kg rail, when a linear spring clip equal to the solid line L2 is adopted, the required fastening force of at least 100 kg rail is 938 kg. This is because cannot be realized.
The above judgment is based on 37 kg to 100 kg rails at various pedestal heights.
αn = (required fastening force on nkg rail) / (linear spring clip deformation amount δ on nkg rail)
However, n = 37, 40, 50, 60, 73, 100
Can be determined by adopting the largest numerical value α _max as the slope of the solid line L2.

Actually, for example, there is an error in the spring constant or a dimensional tolerance between the pedestal and the rail. Therefore, considering these factors, it is practically possible to widen the range of the spring constant applicable to the wire spring clip to be used. is necessary. Specifically, the angle formed by the dotted line L1 and the solid line L2 shown in FIGS. 4A, 4B, and 5 is increased.
Since the error of the spring constant generally has an inclination of at least ± 5% with respect to the inclination of the straight line L, it is sufficient to consider this inclination.
Here, for each pitch of the seat, even if there is an error of ± 5% in the spring constant, the result of studying the region that can enter between the dotted line L1 and the solid line L2 will be described with reference to FIG. To do. FIG. 6 shows the results when wire spring clips having a maximum allowable fastening force during use of 2000 kg are installed at pitches of 250 mm, 500 mm, 700 mm, and 960 mm. Tables 1 and 2 show the calculation results when drawing FIG. 6 for the pitches of 500 mm and 700 mm, respectively.

In Tables 1 and 2, the maximum fastening force is basically calculated as 2000 kg, but there are some exceptions.
As described above, the maximum deformation amount of the wire spring clip is generally about 30 mm. In the case of a wire spring clip having a maximum fastening force of 2000 kg, a spring constant of 2000 / 30≈66.67 (kg / mm) or less can be obtained. Judged not.
Therefore, when the slope of the solid line L2 (ie, α _max ) is 66.67 (kg / mm) or less, a wire spring clip with a maximum fastening force of 2000 kg may not be applicable. In this case, α _max × The calculation was made on the assumption that a wire spring clip with a maximum fastening force of 30 was applied.
The cases that are exceptions as described above, that is, the case where α _max is 66.67 or less in Table 1, is the case where the deformation amount δ at the 37 kg rail is 6.0 mm or more, and in Table 2, the deformation at the 37 kg rail. This is the case where the amount δ is 11.0 mm or more.

Α ₃₇ and α ₁₀₀ are values obtained by dividing the required fastening force of the 37 kg rail and the 100 kg rail by the respective deformation amounts, and a large value among these values is shown as a maximum value α _max of 37-100 kg. ing. That is, this numerical value corresponds to the aforementioned solid line L2.
The fastening force (maximum) is a numerical value obtained by dividing the maximum fastening force of the wire spring clip by the deformation amount (maximum deformation amount) of the 100 kg rail. That is, this numerical value corresponds to the aforementioned dotted line L1.
Furthermore, the average value is the table showing the geometric mean value of the inclination of the center line obtained from the geometric mean of the solid line L2 indicating the maximum value of the 37-100 kg rail and the dotted line L1 indicating the fastening force (maximum). The angle formed by the solid line L2 and the dotted line L1 with respect to this numerical value is shown as an allowable error (absolute value of ± 5%).

As a result, the seat constant H ₁ (= H−H ₀ ) for satisfying the spring constant of 5%, which is an allowable error, is H ₁ when the pitch is 250 mm and H ₁ is 0.71 mm or more and 500 mm. _In the case where ₁ is 1.55 mm or more and 700 mm pitch, H ₁ is 2.3 mm or more, and in the case of 960 mm pitch, H ₁ is 3.5 mm or more.
Here, as shown in FIG. 7, H ₁ and the pitch have a proportional relationship in which H ₁ increases as the pitch increases. Therefore, although both the rail bottom surface and the mounting surface on which the rail is laid may be painted, it is used without any special surface treatment (as roll), for example, providing irregularities, and as described above, the allowable stress limit When using a wire spring clip of 2000 kg and an allowable deformation amount of 30.0 mm, with a seating plate pitch of 250-960 mm, and a 10 m unit length rail, the lower limit value of H ₁ is Indicated by
H ₀ + 0.0039X-0.3

On the other hand, since the maximum deformation amount of the wire spring clip is 30.0 mm, the difference between this 30.0 mm and the necessary deformation amount 9.0 mm (the height difference between the flange of the 100 kg rail and the 37 kg rail) is 21. If the error is 5%, the upper limit value is 18.0 mm from FIG.
From the above, the pedestal height needs to satisfy the following formula.
H ₀ + 0.0039X−0.3 ≦ H ≦ H ₀ +18.0
Here, H ₀ (mm) is the height at which the deformation amount of the wire spring clip becomes 0 when the wire spring clip is installed on a rail for an overhead crane of 37 kg per meter, and X (mm) is It is the pitch of a plurality of wire spring clips.

In addition, it is preferable to select the pedestal height H of the stool within a range equal to or higher than the height H _{0 in} which the deformation amount of the wire spring clip is 0 plus 2 mm. Here, if the thickness added to the height H ₀ is too thin, it is necessary to increase the processing accuracy of the seating board, and it is necessary to excessively increase the spring constant of the wire spring clip, which is not practical. Thus, the pedestal height H of the seat board, but not less than the height plus 2mm to the height H _0, it is preferable that the height or the addition of 3mm to height H _0. Further, the pedestal height H of the stool is set to be equal to or less than the height obtained by adding 18 mm to the height H ₀ , but is preferably set to be equal to or less than the height obtained by adding 15 mm, and more preferably less than the height obtained by adding 10 mm It is preferable to do.
By configuring as described above, each standard using one type of wire spring clip 12 and seat base 13 is used without changing the type of wire spring clip and seat base for each rail standard for an overhead crane. The rail 11 for the overhead crane can be fixed.

As described above, the present invention has been described with reference to the embodiment. However, the present invention is not limited to the configuration described in the above embodiment, and the matters described in the scope of claims. Other embodiments and modifications conceivable within the scope are also included. For example, a case where the rail fastening mechanism using the wire spring clip of the present invention is configured by combining some or all of the above-described embodiments and modifications is also included in the scope of the right of the present invention.
Moreover, the rail fastening mechanism by the wire spring clip shown in the said embodiment is applicable to both a transverse rail and a running rail.

It is a front sectional view of a rail fastening mechanism by a wire spring clip concerning one embodiment of the present invention. It is a top view of the rail fastening mechanism. (A), (B) is explanatory drawing which shows the relationship between the fastening force range required in order to fix the rail for overhead cranes to a girder, and the deformation amount of a wire spring clip, respectively. (A), (B) is explanatory drawing which shows the relationship between the fastening force range required in order to fix the rail for overhead cranes to a girder, and the deformation amount of a wire spring clip, respectively. It is explanatory drawing which shows the relationship between the fastening force range required in order to fix the rail for overhead cranes to a girder, and the deformation amount of a wire spring clip. It is explanatory drawing which shows the relationship between the tolerance of the spring constant of a wire spring clip, and the base height of a seat. It is explanatory drawing which shows the relationship between the base height of a seating board, and the pitch of a seating board.

Explanation of symbols

10: Rail fastening mechanism by wire spring clip, 11: Rail for overhead crane, 12: Wire spring clip, 13: Seat base, 14: Girder, 15: Through hole (insertion hole), 16: Hook, 17: Pedestal, 18: straight part, 19: intermediate part, 20: short straight part, 21: flat surface, 22: flange

Claims (3)

Rails for overhead cranes of multiple standards with a weight per meter of 37 kg or more and 100 kg or less are installed at a pitch of 250 mm or more and 960 mm or less, the maximum allowable fastening force when used is 2000 kg or less, and the maximum deformation is 30 mm or less A wire spring clip having an e-shape in plan view, a pedestal on which a central portion of the wire spring clip is placed, and a latching portion in which a fitting hole into which a base portion of the wire spring clip is inserted is formed. A rail fastening mechanism that is fixed to the installation location of the rail for the overhead crane, using a seat provided integrally.
The height H (mm) of the pedestal is within the range shown in the following formula, and one type of the wire spring clip and one type of pedestal height with respect to the rails for the plurality of standard overhead cranes. A rail fastening mechanism using a wire spring clip, characterized by using the above-mentioned seating board.
H ₀ + 0.0039X−0.3 ≦ H ≦ H ₀ +18.0
Here, H ₀ (mm) is the height at which the deformation amount of the wire spring clip becomes 0 when the wire spring clip is installed on a rail for an overhead crane of 37 kg per meter, and X (mm) is It is the pitch of a plurality of wire spring clips. The rail fastening mechanism using a wire spring clip according to claim 1, wherein the height H of the pedestal of the seating board is equal to or higher than a height H _{0 at} which the deformation amount of the wire spring clip is 0 plus 2 mm. A rail fastening mechanism using a wire spring clip. The rail fastening mechanism using the wire spring clip according to any one of claims 1 and 2, wherein the rail for the overhead crane is installed at various factories constituting an ironworks, an oil complex, an automobile factory, or a shipyard. A rail fastening mechanism using wire spring clips, characterized by being a warehouse.

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