JP2003056288A - Segment joint - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a joint enabling introduction of a design stress on the occasion of fitting thereof, without being affected by an error on the occasion of manufacture or fitting of the joint between segment pieces. SOLUTION: The present joint is provided for the segment pieces and it is constituted of a female joint (11) which has a groove-shaped box draft portion (11) provided in a connecting face of the segment piece so that a projecting part of a male joint (40) be fitted therein by insertion and has a female metal fitting (12) that is provided with a slit (13) guiding the male joint (40) and holds a cushioning damper (20) inside, and of the wedged male joint (40) which has a web (41) so formed as to be wide with a prescribed gradient and is fitted to a joint face of the segment piece so that a flange (42) and the web (41) jut out.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to the structure of a joint used for a segment used when constructing a shield tunnel for water and sewage. For details, use a damper that can control the compression load to a constant value and set the amount of displacement at a constant load, and use a damper that can control the stress level introduced to the segment fittings during segment assembly to a constant value, and a low compression The present invention also relates to a joint in which a rigid elastic body is used and introduced into a segment joint fitting so that the stress level can be controlled to a substantially constant value.

[0002]

2. Description of the Related Art As an alternative joint structure to a bolt fastening type joint, for example, Japanese Patent Laid-Open No. 2000-28722 discloses a joint structure in which a male joint and a female joint are fitted to form a wedge. Fig. 16
Shows an example of this segment. Further, FIG. 17 shows the female joint and the male joint in detail. A male joint 101 and a female joint 103 are attached to the inter-piece joint surface of the segment.
The male joint 101 is provided so as to project outward from the inter-piece joint surface of the segment, and the cross-sectional shape of the projecting portion is a substantially T shape.

The web portion 109 is designed to be wide in the length direction of the joint. The female joint 103 has a substantially C-shaped cross section. Female fitting 10 in contact with the inside of flange 107 of male fitting 101
The thickness (height) of the jaw part 111 of 3 is the web 109 of the male joint 101.
It is designed to be wide in the lengthwise direction as well.

An example of assembling such a segment is shown in FIG. For example, when one segment piece is indicated by an alphabetic symbol, the segments are assembled in the order of A ₂ , A ₁ , B ₁ , B ₂ , and K pieces, and a joint is fitted by a shield jack. Since the contact surfaces of the male and female joints on the joint surface are tapered, the jaws 111 of the female joint are fitted by fitting.
When the male joint and the flange portion 107 of the male joint come into contact with each other, the jaw portion 111 is compressed by the wedge effect. Then, since the flange 107 receives a tensile force as a reaction, a tensile stress is generated in the male member web 109.

Due to this tensile stress, the inter-piece joint surfaces of the two segments are attracted to each other with a sufficiently large force, and the joining is performed. When this joint method is used, tensile stress can be introduced into the web 109 of the male joint when the joints are fitted to each other, so that a segment ring having a large coupling force and strength equal to or higher than that of the bolt joint can be obtained. Moreover, since bolts and nuts are not used for assembly, the work is simple.

[0006]

In the prior art, in order to set the stress required when connecting the joints, that is, the tensile stress generated in the web 109, to a value in the range necessary for design,
The joint dimensions are required to be highly accurate. In addition, the value of the range required for design is a constant value in actual design, but it is difficult to introduce a constant design tensile stress in this joint structure, so there is a certain range of design values. It is the set value.

This will be described with reference to FIG. The male joint 101 and the female joint 103 have dimensional errors during manufacture and dimensional errors during attachment to the segment pieces. Even if the values of these dimensional errors are small, when the segment piece is fitted into the joint, the error of the tensile stress becomes large due to the wedge effect, and it becomes difficult to obtain the stress in the range necessary for design. For example, if the introduced stress is larger than the stress in the range required for design, that is, if the fitting dimensions of the male and female joints are tighter than in the ideal case, the force required for fitting will increase. The bond is not completed, the stress introduced into the web exceeds the yield point, and in extreme cases, the joint breaks.

On the other hand, when the joint size is small, that is, when the fitting dimension is looser than the ideal case, the introduced stress does not reach the design value, so that only a joint having insufficient strength can be obtained. In an extreme case, a gap is created between the joints, which causes not only the problem of the strength of the segment ring but also the problem of water stoppage. Further, in order to introduce the stress of the design value into the web 109 of the male joint 101, it is necessary to make not only the joint manufacturing accuracy but also the mounting accuracy to the segment body, which is a cause of the high segment manufacturing cost. It was.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a joint which can introduce design stress during fitting of the joint without being affected by an error at the time of manufacturing or mounting the segment inter-piece joint.

[0010]

A first aspect of the present invention for solving the above-mentioned problems is a segment piece-piece joint characterized by comprising the following members. (a) A pair of wedge-shaped movable wedges provided between the male metal fitting (40) having a substantially T-shaped cross section and (b) the male metal fitting (40) and the substantially C-shaped female metal fitting (12). (21) and (c) A buffer damper (20) provided at the tip of the female fitting (40) to which the tip of the movable wedge (21) is joined.

A second aspect of the present invention is a segment piece-piece joint characterized by comprising the following members. (a) a groove-shaped box removal part (11) provided for inserting the protruding part of the male joint (40) into the coupling surface between the pieces of the segment,
A female joint (11) provided with a slit (13) for guiding the male joint (40) and having a female metal fitting (12) in which a buffer damper (20) is housed, and (b) the male joint (40). ) Between the flange and the female metal fitting (12), provided in a state of being coupled to one end of the buffer damper (20), a pair of identical wedge-shaped movable wedges (21),
(c) Wide web with constant slope (41)
The wedge-shaped male joint (40) is attached to the joint surface of the segment piece so that the flange (42) and the web (41) protrude.

A third aspect of the present invention is to provide the above-mentioned shock absorber.
(20) is an inter-piece joint for a segment, characterized in that it is composed of the following members. (a) a fixed member (22) that fixes the movable wedge (21) and evenly transfers the load, and (b) a piston (25) attached to the opposite side via the fixed member (22), (c) Piston (25)
Cylinder (24) for insertion of (1), (d) Partition wall (27) for partitioning the inside of cylinder (24), (e) Piston (25) and small hole
The cushioning material (23) filled in the space surrounded by the partition wall (27) provided with (28), and (f) the discharge part (29) for storing the cushioning material (23) discharged from the small hole (28) And (g) fix the cylinder and store the buffer material (23) that has flowed into the discharge part (29) (2).
6).

A fourth aspect of the present invention is to provide the buffer damper described above.
(20) is an inter-piece joint for a segment, characterized in that it is composed of the following members. (a) A fixed member (22) that fixes the movable wedge (21) and evenly transfers the load, and (b) a piston (25) attached to the opposite side via the fixed member (22). , (C) Piston (2
5) Insert a cylinder with a larger inner diameter than the outer diameter of the piston (25) so that the cushioning material (23) can be discharged.
(31) and (d) A cushioning material (23) filled in the space surrounded by the piston (25) and the cylinder (31).

A fifth aspect of the present invention is to provide the above-mentioned shock absorber
(20) is a segment piece-to-piece joint characterized in that the displacement increases almost linearly with respect to the compressive force up to a constant load state, and thereafter only the displacement increases under a substantially constant load. Is.

A sixth aspect of the present invention is to provide the above-mentioned cushion damper.
(20) is characterized in that it is possible to arbitrarily set the load when the displacement increases in proportion to the compressive load and when it shifts to a constant load state, and the displacement amount when the displacement is increased while being kept at a constant load. It is a joint between pieces of a segment to be used.

A seventh aspect of the present invention is the movable wedge (21).
Is a joint between pieces of a segment, characterized in that the side close to the joint surface between the segment pieces is formed parallel to the joint surface, and the surface on the opposite side is formed with a constant slope.

An eighth aspect of the present invention is the movable wedge (21).
Is attached to the buffer damper (20) so that it can slide between the contact parts of the female metal fitting (12) and the male joint (40), and is installed from the buffer damper (20) in the direction opposite to the load direction of the male joint (40). The segment-piece joint is characterized in that a wedge action is formed between the female fitting (12) and the male joint (40) in accordance with the reaction force of the.

In a ninth aspect of the present invention, the cushioning material increases in displacement in proportion to the load when a load is applied from the outside in an unsealed container, and breaks when the load reaches a certain size. A segment characterized by the fact that after the start of the fracture, the displacement increases by an amount equivalent to the volume decrease due to the fracture, and the load does not change during the fracture and is almost constant. It is a joint between pieces.

A tenth aspect of the present invention is to provide the above-mentioned buffer damper.
The segment joint between pieces is characterized in that an elastic body is provided in place of (20).

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION According to the present invention, a wedge-fitting type joint is provided in a segment piece-piece joint, and male and female metal fittings are fitted in the tunnel axial direction at the time of connecting segment pieces to form a wedge between both metal fittings. It is a thing.

The present invention is, firstly, a metal fitting having a substantially T-shaped cross section, a metal fitting having a substantially C-shaped cross section, and a movable fitting between a male fitting flange and a female fitting jaw. Secondly, a buffer damper or an elastic body is provided in front of the metal fitting in a state in which the action force from the movable wedge can be transmitted (or, the movable wedge has a movable wedge tip, (The movable wedge is provided so as to be connected to the piston of the buffer damper in front of the wedge) (or the movable wedge is provided so that the tip of the movable wedge is connected to the elastic body end portion in front of the wedge). In Fig. 3, the buffer damper has a property that the displacement increases almost linearly up to a certain load, and only the displacement increases with the almost constant load, and in the case of an elastic body, the increase of the load with respect to the displacement is extremely small (low compression rigidity ) Is provided.

At the time of assembling the segments, the characteristic of the damper is utilized, and the wedge action is established between the male and female metal fittings with a certain pushing force, but after the constant load is reached, the wedge action is not established. It is possible to control the degree of stress introduced into the web portion. Further, in the case of an elastic body, the increase in the stress level introduced into the male metal member web is small and a substantially constant stress level can be introduced until the assembly is completed by utilizing the low compression rigidity.

The first embodiment will be described below. In Figure 1,
An example in which the joint of the present invention was used for a segment having a diameter of 3800 mm, a width of 1000 mm and a thickness of 150 mm was shown. The segments were each composed of two sets of A pieces and B pieces and one set of K pieces, and the joint of the present invention was used for the inter-piece joint surface of each segment. Two sets of piece-to-piece joints are provided in the segment width direction, and the distance between the joint center positions of each joint is 450 mm. Further, the female joint 10 is provided with a box removal portion 11 into which the protruding portion of the male joint 40 is fitted at the time of assembly.

FIG. 2 shows a state in which the female joint 11 is arranged on the joint surface between the segment pieces 2. Female fitting 10
A box removing part 11 and a female fitting 12 are provided in the. Box removing part 11
Is for inserting the protruding portion of the male joint 40 at the time of assembly and fitting,
It is a groove provided on the joint surface. The female metal fitting 12 is provided with a slit 13 which serves as a guide for the male joint 40 when the joint portion is fitted, and a movable wedge 21 and a buffer damper 20 are housed in the inner portion of the slit portion.

FIG. 3 shows a schematic view of the female fitting 12. Figure 3 (a) shows
FIG. 3 is a perspective view of a female fitting 12. The location where the slit 13 is provided is a storage portion for the movable wedge, and the upper right portion of the drawing is a buffer damper storage portion. FIG. 3B is a cross-sectional view of the buffer damper 20 inserted in the buffer damper housing portion of the female fitting 12. FIG. 3C is a cross-sectional view of the movable wedge portion in a state where the female metal fitting 12 and the male metal fitting 40 are fitted to each other via the movable wedge.

FIG. 3A will be described. The female metal fitting 12 includes a movable wedge storage portion and a buffer damper storage portion. A cross section of the movable wedge storage portion is approximately C-shaped, and a slit 13 that serves as a guide for the male joint 40 when the joint portion is fitted is provided. The buffer damper housing portion has a hollow cross section, and a circular cylinder-shaped damper is housed therein. The thickness of the slit 13 portion of the female fitting 12 that fits the male joint 40 and the movable wedge 21, that is, FIG.
The thickness of h ₁ of the movable wedge accommodating portion indicated by is larger than the thickness h ₂ of the cushioning damper accommodating portion so that the movable wedge 21 corresponds to approximately the center of the cushioning damper cross section.

FIG. 3 (b) shows a buffer damper 20 that is separately manufactured.
The figure shows an example in which is used by inserting it into the buffer damper housing portion of the female fitting 12. For example, instead of being separately manufactured, the buffer damper housing portion may be formed in a hollow cylindrical shape in advance, and the buffer material may be directly filled therein for use.

FIG. 4 shows a buffer damper 20 having a movable wedge 21.
The perspective view of FIG. A pair of movable wedges 21 is attached to one side of the fixed member 22. The fixed member 22 includes a pair of movable wedges 21.
It evenly transfers the load received by the damper. The other side of the fixing member 22 is a cylinder filled with a cushioning material 23.
A damper consisting of 24 and piston 25 is attached.

A lid member 26 is attached to the end of the cylinder 24 opposite to the piston 25. This lid member 26 is
A buffer damper provided with a movable wedge is inserted from the buffer damper housing portion side of the female metal fitting 12 to be integrated with the female metal fitting. This lid member 26 has a small hole 28 from the inside of the cylinder 24.
It also serves as a lid for the cushioning material discharged through.

The cylinder 24 is divided into two chambers by a partition wall 27 having a small hole 28. A cushion 23 is filled in the chamber between the piston 25 and the partition wall 27. The chamber on the opposite side of the partition wall 27 is a discharge part 29 for storing the buffer material 23 that has flowed through the small holes 28 of the partition wall 27.

In FIG. 5, on the joint surface of the segment piece,
A schematic perspective view of the female joint 10 provided so as to be embedded is shown. The female fitting 12 of the female joint 10 includes a buffer damper 20 and a movable wedge.
21 are stored.

FIG. 6 shows a sectional view of the buffer damper 20 provided with a wedge-shaped projecting movable wedge 21 housed in the female fitting 12.
The side close to the joint surface of the segment piece of the movable wedge 21 attached to the fixed member 22 (the lower side in FIG. 6) is the upper surface of the female metal fitting jaw (see FIG.
(See 3) and the opposite surface is formed with a constant slope of 1/20. A piston 25 is attached to the opposite side of the fixing member 22.

The cushioning material 23 filled in the cushioning damper 20 is preferably a rubber material. For example, a cross-linked low hardness rubber material can be used. Since the cylinder 24 is not sealed, when the cushioning material 23 is subjected to compressive stress, the displacement increases in proportion to the increase in stress. That is, a small hole 28 is provided so that the cushioning material 23 in the cylinder can flow,
A gap may be provided due to the dimensional difference between the cylinder inner diameter and the piston outer diameter. Then, the cushioning material 23 behaves substantially elastically with respect to the compressive stress of the piston 25 up to a certain value.

The rubber material begins to break when the compressive stress reaches a certain value. The destroyed rubber material is discharged from the small hole 28 of the partition wall 27 to the discharge portion 29 on the opposite side. After the destruction starts, the piston 25 moves by a distance corresponding to the rubber discharge volume, and the fitting between the joints proceeds. The compressive stress does not change while the rubber is broken, and the deformation proceeds at a substantially constant value until the stroke end of the cylinder 24.

"Elasto-plastic characteristics" can be obtained by appropriately selecting the cylinder 24 diameter, small hole 28 diameter, and cylinder 24 stroke.
While maintaining, the two characteristic values of "elastic limit" and "deformation limit" can be set arbitrarily. The shape of the cylinder 24 filled with the cushioning material is preferably cylindrical, but for example, a piston
The shape may be arbitrary as long as 25 can be slid to apply a compressive stress to the cushioning material 23. Here, the "elastic limit" is the limit at which the compressive stress and the compressive displacement are proportional, and the "deformation limit" is the maximum displacement possible under a constant compressive force after reaching the "elastic limit". is there.

As an example, the cylinder 24 is a steel cylinder having an inner diameter of 27.6 mm, and a partition wall 27 having a small hole 28 having a diameter of 1.83 mm is provided near the center. Piston 25 is a cylinder
It is made so that it can slide smoothly in 24. The inner and outer diameters and lengths are determined so that the buffer damper has the "elastic-plastic property" required for the segment joint design.

FIG. 7 shows a perspective view of the male joint 40. The cross section of the male joint 40 attached to the segment piece is roughly T
A web 41 that is letter-shaped and widens in the length direction at a constant slope.
Is equipped with. The male joint 40 is attached to the joint surface of the segment piece by protruding the flange 42 and the web 41. Figure 8
FIG. 10 shows the male joint 40 attached to the joint surface of the segment piece. This is an example of mounting at two points on the joint surface. Figure 9 shows a more detailed installation situation.

The female fitting 17 and the male joint 40 are preferably manufactured by casting. Of course, it is also possible to assemble and manufacture steel plates by welding or the like. Also, the female fitting 12 is a buffer damper.
It is attached to a segment piece mold in a state of being integrated with 20, and concrete is cast into this mold to produce a segment piece.

The buffer damper will be described. For example,
From the experimental results and the like, it is known that the load required to introduce the design stress of 1400 kgf / cm ² into the web 41 of the male joint 40 used for connecting the segment pieces needs to be 2.1 tf. As a result of repeating the laboratory experiment on the buffer damper of the present invention, the length of the buffer material 23 portion was set to 30 mm, and the partition wall 27
It was confirmed that when the diameter of the small hole 28 was 1.83 mm, the load was a constant 2.1 tf, and that the load hardly changed even when the stroke exceeded 15 mm.

The results are shown in FIG. The horizontal axis represents displacement (unit: mm) and the vertical axis represents load (unit: tf). Up to displacement of 5 mm, load and displacement are almost proportional, and displacement is 5 mm.
In the above, the load is almost constant although there is some variation.

It is known from the past results that the manufacturing and mounting accuracy of the joint is ± 0.3 mm. The wedge slope is 1/20
Therefore, the allowance in the mating direction is 2 x 0.3 x 20 = 12
It should be mm. That is, the fitting dimensions of the female fitting and the male joint at the fitting portion after the completion of the segment attachment may be designed so that the stroke difference between the tightest and the loosest is 12 mm. That is, the positional relationship between the female fitting and the male joint may be determined such that the fitting of the segments ends when the proportional portion of FIG.

When the positional relationship is determined as described above, if the fitting dimensions of the female fitting and the male joint are the tightest,
The mating is completed at the position where the 12mm stroke is made. During the stroke of 12 mm, which is the margin, the load is within a certain range, so the stress on the web is also constant without increasing.

A method for fitting the female fitting 12 of the female joint 10 and the male joint 40 to join the segment pieces will be described with reference to FIG. Coarse positioning of segment pieces,
The protruding part of the male joint (40) is inserted into the box removal part (11) of the female joint (10). After that, the shield jack is stroked so that the tip of the male joint 40 and the female fitting 12 can be fitted to each other.

When the shield jack is gradually stroked, the inside of the flange 42 of the male joint 40 and the outside surface of the movable wedge 21 start to come into contact with each other, as shown in FIG. 11 (a).
Up to this position, no force acts on the female fitting 12, the male joint 40 and the movable wedge 21 in the horizontal axis direction. Therefore, the female fitting 12, the male joint 40,
Since the wedge effect does not appear between the movable wedge 21 and the movable wedge 21, the stress introduced into the web portion is zero.

As shown in FIG. 11B, when the stroke further advances, the movable wedge 21 is pushed by the flange 42.
Then, the movable wedge 21 does not move but only the flange 42 moves due to the reaction force of the cushioning material 23 (the force to push back the cushioning material, that is, the cushioning damper. It bites between the flanges 42, and a wedge effect appears between the female fitting and the flange 42. That is, since the web 41 of the male joint 40 is stretched in the width direction, tensile stress starts to act.

Here, the female fitting 12, the flange 42, the movable wedge 21
The origin is the point at which the contact occurs and the wedge effect begins to appear. Depression depth the amount of displacement from the origin of the flange 42 (shield jacks stroke) and X, when the displacement amount of engagement between the movable wedge 21 and the flange 42 and X _1, the displacement amount of the buffer damper and X ₂ X = X ₁ + X ₂ . In the usual case, X ₁ is smaller than X ₂ and has a value of, for example, about 1/10 to 1/20.

This state continues until the load and displacement relationship of the buffer damper reaches the elastic limit, and when the elastic limit is reached,
Stress corresponding to the reaction force at that time is introduced. As shown in FIG. 11 (c), the fitting displacement when the elastic limit displacement X ₂ = X ₂₀ is reached is X ₁ = X ₁₀ . Until the load reaches a certain value (hereinafter referred to as the elastic limit), the cushioning material 23 of the cushioning damper is deformed but not in a broken state, and the broken material is not discharged from the small hole 28. Absent.

Of the stroke corresponding to the elastic limit of the cushioning material 23
After reaching X ₀ = X ₁₀ + X ₂₀ and further increasing the stroke,
The stroke does not increase and the stroke continues while remaining almost constant. As shown in FIG. 11 (d), during this time, the reaction force acting on the movable wedge 21 also becomes constant, the fitting of the female fitting 12 and the flange 42 does not proceed, and only the displacement of the cushioning material 23 proceeds. In other words, after reaching the elastic limit, the increment of the stroke matches the increment of the displacement of the cushioning material 23.

At this stage, destruction of the cushioning material 23 progresses,
The destroyed material is gradually discharged from the small hole 28 as the stroke progresses. This continues until the stroke end at which the fitting is completed. The state where the stroke end is reached is shown in Fig. 11 (e).

As shown in FIGS. 11 (c) to 11 (e), the cushioning material
The reaction force is almost constant while the 23 is destroyed. During this time, the fitting displacement of the movable wedge 21 does not change, and is kept at the fitting displacement X ₁₀ when the damper displacement reaches the elastic limit. Web 4
The tensile stress of 1 does not change, and is kept at the stress value when the damper displacement reaches the elastic limit.

That is, when designing the damper, the first is to set the load at which the reaction force of the damper is constant as the load corresponding to the design stress. Second, set the necessary margin due to manufacturing errors, etc., within the range where the damper reaction force is constant.
This allows the male fitting 40 to be fitted regardless of loose or tight fittings.
The stress introduced into the web 41 of the can be made equal to the design stress.

A segment assembling method will be described with reference to FIG. Female and 10 male fittings for segment pieces
The arrangement of 40 is such that, when the segment pieces are assembled, for example, the female joint 10 is provided on the existing side joint and the male joint 40 is provided on the newly assembled segment joint as shown in FIG.

At the time of assembly, the new segment piece is moved by using an erector or the like, and the center of the male joint 40 is almost the female joint.
Adjust so that it is located at the center of the box removal part 11 of 10. Next, the new segment is horizontally moved by the erector until the joint surface of the existing side segment and the joint surface of the new side segment contact each other (direction of arrow). After the movement, the projecting portion of the male joint 40 (the portion projecting from the surface of the segment joint surface) is set in the box removal portion 11 of the female joint 10.

Next, a shield jack or the like is used to push in the upward direction of the drawing (the direction of the arrow) to fit the female fitting 12 of the female joint 10 and the male joint 40. That is, as shown in FIG. 12, the shield jack is stroked by d until the assembly is completed.

The same operation can be repeated in sequence to assemble one ring. If the arrangement of the female joint 10 and the male joint 40 is as shown in FIG. 18, and the order of assembling the segments is A ₂ , A ₁ , B ₁ , B ₂ , and K, the segments are ring-shaped by the above method. Can be assembled into The last K piece has male joints on both joint surfaces, but K
Insertion angle of piece, wedge angle of male joint 40 (taper amount),
By considering the shape of the box removal part 11 of the female joint 10,
It can be fitted in the same way as the A-piece and B-piece joints. Generally, the joint shape of K piece is different from that of A piece and B piece.

Although two sets of joints are provided in the segment width direction, one set may be used when the segment width is small or when the joint design stress is not so large. When one set of joints is provided in the width direction, make the end of the female fitting coincide with the end of the joint surface as shown in Fig. 16 and
It is also possible to adopt a structure in which 11 is not provided. In this case, the length of the male fitting does not necessarily have to match the length of the pushing metal fitting. A conceptual diagram is shown in FIG. In the example of FIG. 12, it is applied to a segment having a rectangular shape, but the present joint can be applied to a segment having another shape, for example, a hexagonal segment.

FIG. 14 shows a buffer damper according to the second embodiment. The structure of the metal fitting part other than the buffer damper part is the same as that of the first embodiment. A pair of movable wedges 21 is attached to one side, and a damper including a piston 25 and a cylinder 31 filled with a cushioning material 23 is provided on the other side. The end of the cylinder 31 opposite to the piston 25 is closed. There is a gap due to the dimensional difference between the outer diameter of the piston 25 and the inner diameter of the cylinder 31.
23 is discharged.

That is, when a load is applied to the piston 25,
The compressed cushioning material 23 is discharged from the gap between the piston 25 and the cylinder 31. It has been confirmed that the same “elasto-plastic characteristics” as in FIG. 10 can be obtained also in this example. Although not shown, it is desirable to provide a guide so that the central axis of the piston 25 does not shift in the cylinder when the piston 25 is compressing the cushioning material.

The third embodiment of the present invention will be described below. FIG. 15 shows a sectional view of the female fitting 12 in this embodiment. A pair of movable wedges 21 are attached to one side, and an elastic body 51 is provided on the other side. In this example, the diameter is 35 mm and the length is
An elastic rubber with a small compression rigidity of 50 mm was used, but it is also possible to use an elastic rubber of another shape, plastics or the like depending on the design conditions. The structure of the metal fittings other than the elastic body 51 is the same as in the first and second embodiments.

When assembling the segment, the pushing amount of the male metal fitting after the male and female metal fittings come into contact with each other and the wedge effect appears is X.
And the displacement amount due to the fitting of the movable wedge 21 and the flange 42
If X ₁ and the compressive displacement of the elastic body are X ₂ , then X = X ₁ + X ₂ .
X ₁ is simply a value obtained by dividing the amount of elongation of the male metal member web by the wedge slope. When a compression test was performed on the elastic body and the compression elastic modulus was determined, it was about 100 kgf / cm ² in the low load region. This was about 1 / 20,000 of the steel material used for the wedge.

Therefore, since the compression rigidity of the elastic body is small, X ₁ becomes a negligibly small value as compared with X ₂ . As a result, at the time of segment assembly, the relationship between the pushing amount and the pushing force after the contact of the male and female fittings is close to the relation between the compressive force and the compressive displacement of the elastic body. That is, the change amount of the pushing force with respect to the change amount of the pushing amount becomes close to that of the elastic body.

From the relationship between the pushing force and the pushing amount obtained by carrying out the fitting test of the male and female fittings using the same elastic body as that used in the present embodiment, the change of the pushing force with respect to the changing amount of the pushing amount. The amount was about 80 kgf / mm. From this, the amount of change in web stress with respect to the amount of indentation is calculated to be 50 kgf / cm2 / mm.

Even if the wedge state start position changes by 5 mm from the design at the time of segment assembly due to the manufacturing error of the joint fitting, the amount of change in the stress introduced into the web is 250 kgf / cm2.
This is a problem-free amount compared with the target introduction stress of 1400 kgf / cm2. In this way, according to the method of providing the elastic body having the low compression rigidity at the tip of the movable wedge as in the present embodiment, even if there is some error in the metal fitting manufacturing, the pulling force close to the target tensile force degree is exerted on the male metal web. Power can be introduced.

[0064]

The piece-to-piece joint of the segment of the present invention is composed of a joint metal fitting including a male and female metal fitting and a movable wedge, and a damper. The damper is composed of a cylinder, a piston, and a cushioning material. The cylinder is not completely sealed,
A cushioning material such as rubber is filled. When a compressive stress is applied, the cushioning material behaves elastically up to a certain value, then a continuous fracture phenomenon occurs and the deformation progresses with a constant compressive stress, and it is compressed to the stroke end of the cylinder. Since the stress level does not fluctuate, the structure is such that the force from the movable wedge is transmitted to the damper, so that the stress level introduced into the male fitting web when the segment joint is fitted is designed stress. It can be equal to degree.
Further, even if an elastic body having a small compression rigidity is used instead of the buffer damper, the stress level introduced into the male metal web can be made substantially the same as the design stress level.

[Brief description of drawings]

FIG. 1 is a diagram showing a female joint and a male joint mounted on a segment piece according to a first embodiment of the present invention.

FIG. 2 is a view of a female joint mounted on a segment piece.

FIG. 3 is a view showing a case of a female joint fitting.

FIG. 4 is a schematic diagram of a movable wedge and a shock absorber.

FIG. 5 is a schematic view of a female joint in which a buffer damper is housed.

FIG. 6 is a sectional view of a movable wedge and a buffer damper.

FIG. 7 is a perspective view of a male joint.

FIG. 8 is a view in which a male joint is attached to a segment piece.

FIG. 9 is a view in which a male joint is attached to a segment piece.

FIG. 10 is a diagram showing a relationship between a load and a displacement of the damper material.

FIG. 11 is a diagram showing the displacement of the female fitting of the damper, the male joint, and the movable wedge.

FIG. 12 is a view showing a fitting procedure of the female joint and the male joint.

FIG. 13 is a fitting diagram of a female joint and a male joint having a structure in which a box removing part is not provided.

FIG. 14 is a diagram showing a damper according to a second embodiment.

FIG. 15 is a diagram showing a damper according to a third embodiment.

FIG. 16 is a prior art example of assembly of segment pieces.

FIG. 17 is a prior art example of a male joint.

FIG. 18 is an example of a combination of segment pieces when the segment pieces are assembled into segments.

[Explanation of symbols]

1 shield segment 2 segment piece 3 A ₁ segment piece 4 A ₂ segment piece 5 B ₁ segment piece 6 B ₂ segment piece 7 K segment piece 10 female joint 11 box removal part 12 female metal fitting 13 slit 20 buffer damper 21 movable wedge 22 fixed Member 23 Buffer material 24 Cylinder 25 Piston 26 Lid member 27 Partition wall 28 Small hole 29 Discharge part 30 Gap 31 Cylinder 32 Female metal fitting jaw upper surface 40 Male joint 41 Web 42 Flange 51 Elastic body 101 Male joint 103 Female joint 107 Flange portion 109 Web 111 jaw

   ─────────────────────────────────────────────────── ─── Continued front page    (71) Applicant 591000506             Hayakawa Rubber Co., Ltd.             5351 Minamioka, Minooshima-cho, Fukuyama City, Hiroshima Prefecture (72) Inventor Nobuyuki Takamatsu             778-5 Taio-cho, Kohoku-ku, Yokohama-shi, Kanagawa (72) Inventor Masakazu Uraura             1-507-2 Mitsuhashi, Saitama City, Saitama Prefecture (72) Inventor Masato Honda             1-3 2-3 Otemachi, Chiyoda-ku, Tokyo             Well Construction Co., Ltd. (72) Inventor Akihiko Suzuki             1-9-1, Nakase, Mihama-ku, Chiba City, Chiba Prefecture             Mitsui Construction Co., Ltd. Makuhari Office (72) Inventor Hiroshi Toida             6-14-11 Tsukushino, Abiko City, Chiba Prefecture (72) Inventor Masayuki Fujii             Hayakawago, 5351 Minamioka, Minooshima-cho, Fukuyama City, Hiroshima Prefecture             Mu Co., Ltd. (72) Inventor Kozo Fujii             Hayakawago, 5351 Minamioka, Minooshima-cho, Fukuyama City, Hiroshima Prefecture             Mu Co., Ltd. F-term (reference) 2D055 BA01 GC04                 3J001 FA05 GA01 HA04 JD18 KA21                       KB04                 3J069 AA50 BB01 CC10 DD49 EE19

Claims (10)

[Claims] 1. A segment piece-piece joint comprising the following members. (a) A pair of wedge-shaped movable wedges provided between the male metal fitting (40) having a substantially T-shaped cross section and (b) the male metal fitting (40) and the substantially C-shaped female metal fitting (12). (21) and (c) A buffer damper (20) provided at the tip of the female fitting (40) to which the tip of the movable wedge (21) is joined. 2. A segment inter-piece joint, comprising the following members. (a) a groove-shaped box removal part (11) provided for inserting the protruding part of the male joint (40) into the coupling surface between the pieces of the segment,
A female joint (11) provided with a slit (13) for guiding the male joint (40) and having a female metal fitting (12) in which a buffer damper (20) is housed, and (b) the male joint (40). ) Between the flange and the female metal fitting (12), provided in a state of being coupled to one end of the buffer damper (20), a pair of identical wedge-shaped movable wedges (21),
(c) Wide web with constant slope (41)
The wedge-shaped male joint (40) is attached to the joint surface of the segment piece so that the flange (42) and the web (41) protrude. 3. The segment piece-piece joint according to claim 1, wherein the buffer damper (20) is formed of the following members. (a) a fixed member (22) that fixes the movable wedge (21) and evenly transfers the load, and (b) a piston (25) attached to the opposite side via the fixed member (22), (c) Piston (25)
Cylinder (24) for insertion of (1), (d) Partition wall (27) for partitioning the inside of cylinder (24), (e) Piston (25) and small hole
The cushioning material (23) filled in the space surrounded by the partition wall (27) provided with (28), and (f) the discharge part (29) for storing the cushioning material (23) discharged from the small hole (28) And (g) fix the cylinder and store the buffer material (23) that has flowed into the discharge part (29) (2).
6). 4. The segment piece-to-piece joint according to claim 1, wherein the buffer damper (20) is made of the following members. (a) A fixed member (22) that fixes the movable wedge (21) and evenly transfers the load, and (b) a piston (25) attached to the opposite side via the fixed member (22). , (C) Piston (2
5) Insert a cylinder with a larger inner diameter than the outer diameter of the piston (25) so that the cushioning material (23) can be discharged.
(31) and (d) A cushioning material (23) filled in the space surrounded by the piston (25) and the cylinder (31). 5. The buffer damper (20) has a characteristic that the displacement increases substantially linearly with respect to a compressive force up to a constant load state, and thereafter, only the displacement increases with a substantially constant load. The segment piece-piece joint according to any one of claims 1 to 4, which is characterized. 6. The buffer damper (20) comprises a load when the displacement increases in proportion to a compressive load and a constant load, and a displacement amount when the displacement is maintained at the constant load and the displacement increases. The segment inter-piece joint according to any one of claims 1 to 5, characterized in that it can be set arbitrarily. 7. The movable wedge (21) is formed such that a side close to the joint surface between the segment pieces is parallel to the joint surface and an opposite surface is formed with a constant slope. The joint between the pieces of the segment according to any one of claims 1 to 4. 8. The movable wedge (21) includes a female fitting (12) and a male joint.
It is attached to the buffer damper (20) so that it can slide between the contact parts with (40), and the female metal fitting (12) is installed according to the reaction force from the buffer damper (20) in the direction opposite to the load direction of the male joint (40). ) And the male joint (40) are formed so as to produce a wedge action, The segment piece-piece joint according to any one of claims 1 to 4 or 7. 9. The cushioning material, in a non-sealed container,
When a load is applied from the outside, the displacement increases in proportion to the load, and when the load reaches a certain size, the fracture starts, and after the fracture starts, the displacement increases by an amount equivalent to the volume reduction due to the fracture, and the fracture The piece-to-piece joint according to claim 3 or 4, characterized in that the load does not change while the load is advancing and is substantially constant. 10. The segment piece-piece joint according to claim 1, wherein an elastic body is provided in place of the buffer damper (20).