JPH11246172A - Crane - Google Patents

Abstract

PROBLEM TO BE SOLVED: To easily carry out restoration work after calming earthquake without damaging or deforming rail-installed ground to a state incapable of recovery in the earthquake deforming no rail-installed ground, yet causing wheel unseating by rocking and also in the earthquake causing no wheel unseating by the rocking, yet deforming the rail-installed ground. SOLUTION: A hinged leg rocking range regulating device 20 for regulating the rocking range of a hinged leg 52 is provided between the hinged leg 52 and a crane machine casing 14. In a normal state not acting horizontal force in the rocking direction exceeding the design load on the hinged leg 52 owing to the hinged leg rocking range regulating device 20, the displacement in the rocking of the hinged leg 52 is regulated in the regular range. In an abnormal state acting the horizontal force in the rocking direction exceeding the design load on the hinged leg 52, the displacement in the rocking of the hinged leg 52 exceeding the regular range is tolerated. The results follow changes in broad and narrow rail spans, S'1 , S'2 , caused by the deformation of rail-installed ground 11.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a crane having a swinging leg that is swingably connected to a crane machine frame having a rigid structure and configured to run on parallel rails. In particular, it relates to a bridge-type crane or the like that has been subjected to earthquake countermeasures.

[0002]

2. Description of the Related Art For example, as shown in FIG. 17A, a bridge-type crane installed on a quay includes a girder 1, a boom 2 attached to the tip of the girder 1 so as to be able to undulate, and a girder 1
And a traversing device 3 traveling on a series of traveling rails formed on the boom 2, a suspender 4 such as a spreader suspended from the traversing device 3 so as to be able to move up and down, and a seaside leg 5 supporting the girder 2.
And a land-side leg 6, running wheels 7, 8 provided at the lower end of each leg 5, 6, and a horizontal member 9 and a diagonal member 10 for fixedly connecting the two legs 5, 6. In addition, it is configured to run on parallel rails 12 and 13 laid on the quay 11.

Incidentally, the parallel rails 12 and 13 are extremely
Because it is long, parallel rails 12,
13 is the interval in the width direction (hereinafter referred to as “rail span”).
It is difficult to lay so that it is constant as designed
Causes some errors in the rail span (that is, flat
In the row rails 12 and 13, partly according to design values
Wider than rail span (hereinafter referred to as “reference span”) S
Location (hereinafter referred to as “span expansion location”) or
A point narrower than the reference span S (hereinafter referred to as “span narrow
Swelling)) is unavoidable
Yes, such rail span error is unavoidable in construction
Acceptable as long as it arises and is reasonable
Error (hereinafter referred to as “span tolerance”)
ing. The span allowable error ΔS mentioned here is impractical
Maximum rail span S generated by accident ₁(> S) and minimum ray
Luspan S_Two(<S) (ΔS = S₁-S_Two)
(See FIGS. 17A and 18).

Accordingly, both the legs 5 and 6 are rigid legs, and the distance between the running wheels 7 and 8 in the rail width direction (hereinafter referred to as “wheel distance”) is fixed to a certain size corresponding to the reference span S. In each case, each running wheel 7, 8
As shown in FIG. 9, the rails 12 and 13 are provided with flanges 15 and 15 which can be engaged with the rails 12 and 13 in a state where relative displacement in the width direction is prevented (a state in which the rails are not removed). , 13 cannot cope with the change in width, and it becomes difficult for the traveling wheels 7, 8 to travel at a span enlarged portion or a span narrowed portion, and it is necessary to take some measures.

Therefore, in a conventional bridge crane,
As shown in FIG. 17A, the land-side leg 6 is formed as a rigid leg fixed to the girder 1, and the sea-side leg 5 is connected to the girder 1 and the horizontal member 9 at a connection point of the horizontal member 9. And a lower end portion 52 provided with the traveling wheels 7 and the lower end portion 52 is connected to the upper end portion 51 by pins 53 so as to be swingable in the rail width direction. , The rail span becomes the span tolerance ΔS
Therefore, even when the width changes in the range, the crane travel is devised so as to follow the change.

That is, at the portion where the span of the parallel rails 12 and 13 is increased, the swinging distance of the swinging leg 52 in the direction away from the rigid leg 6 causes the wheel interval to increase following the change in the rail span. (Fig. 17
(A), see the dashed line in FIG. 18) Conversely, at the span narrowed portion, the swinging distance of the swinging leg 52 in the direction approaching the rigid leg 6 causes the wheel interval to follow the narrowing change of the rail span. (See FIGS. 17 (A) and 18 dashed double-dotted lines.) Accordingly, the traveling wheels 7 and 8 smoothly travel on the parallel rails 12 and 13 while the wheel intervals follow the widening and narrowing of the rail span due to the swing displacement of the swinging leg 52, so that the parallel rails 12 and 13 Even when there are places with wide and narrow spans, good crane traveling can be performed.

As described above, the conventional bridge-type crane includes the girder 1 and the upper end portion 5 of the seaside leg 5 which are rigidly connected to each other.
1. A swinging leg 52 swingably connected 53 to a crane machine frame 14 having a rigid structure composed of a land-side leg 6, a horizontal member 9 and a slant member 10, and a crane machine frame facing the swinging direction. 14
Are provided with rigid legs 6 which form a part of
The parallel rails 1 are provided by running wheels 7 and 8 provided at the lower end of
Since it is configured to be supported on the upper and lower legs 2 and 13, only the running stability such that it can follow the wide and narrow changes of the rail span as described above is compared with the case where both the legs 5 and 6 are both rigid legs. In addition, it is excellent in structural stability such that a horizontal load due to the weight of the crane does not act on both legs 5 and 6.

[0008]

However, with such a conventional bridge-type crane, due to the structure having the swinging legs 52, it is impossible to take all possible measures against earthquakes.

That is, the distance between the opposite wheels of the two legs 52, 6 is regulated by the engagement of the wheels 7, 8 with the flanges 15 with the rails 12, 13 in accordance with the rail span. Even if the swing range of the swing leg 52 is not restricted, the crane supporting posture and the running posture are stable, and no particular problem occurs. For this reason, generally, the swing range of the swing leg 52 is not particularly limited, and the swing leg 52 can freely swing and displace. On the other hand, since the traveling wheels 7 and 8 are merely mounted on the rails 12 and 13, when the crane locks due to an earthquake, there is a possibility that one of the traveling wheels will instantly lift off the rail and be derailed. is there. Therefore, in the case where derailing occurs due to rocking due to an earthquake, if the swing range of the swing leg 52 is not regulated, there is a possibility that the crane may collapse.

Therefore, conventionally, the swing of the swing leg 52 has been
The swing angle of the swing leg 52 corresponding to the swing range is defined as a “reference swing angle θ” such that the allowable change amount of the wheel interval is determined by a stopper, a damper, or the like according to the span tolerance. (See FIG. 18). As described above, if the swing of the swing leg 52 is restricted within the range of the reference swing angle θ, the running stability can follow the wide and narrow changes of the rail span, and the horizontal load due to the crane's own weight does not act. Not only can the stability be maintained, but also in the event of an earthquake in which the crane locks and loses the wheel, the crane does not collapse because the relative distance between the two legs 52, 6 does not change more or less than a certain value. By returning the traveling wheels on the rail after the earthquake has subsided, the crane can be easily restored and restored to the original operable state. Thus, the rail installation ground or the rails 12, 1
Although 3 is not deformed, it is extremely effective for earthquake countermeasures to regulate the swing range of the swing leg 52 in the event of an earthquake in which the crane loses a wheel due to rocking.

However, regulating the swing range of the swing leg 52 in this way is an effective countermeasure against earthquakes in which the crane locks and loses the wheel, but the ground on which the rails are installed is not effective. It cannot respond to deforming earthquakes, but rather increases the damage caused by the earthquake.

That is, the quay 11 which is the ground on which the rail is installed.
An earthquake occurs with a strength that causes the rail itself to be significantly deformed (ground cracks, etc.), and the rail span is changed to the span tolerance Δ
If the width changes greatly beyond S, a horizontal force exceeding the design load acts on at least one of the legs, and the legs or the like may be damaged.

For example, as shown in FIG. 17B, when a ground crack occurs in the quay wall 11 due to an earthquake, the rails 12 and 13 move away from the ground along with the ground crack, and the rail span increases. On the other hand, each of the running wheels 7, 8 is provided with a flange 15, 15 (see FIG. 19) so as not to easily come off the rails 12, 13.
Therefore, when the rails 12 and 13 move away from each other, the legs 5 and 6 are also moved via the running wheels 7 and 8 following the movement of the rails 12 and 13 with which the legs 5 and 6 engage. , The wheel interval is also increased by the same amount. In this case, the rail span is
In the case of only expanding in the range corresponding to the reference swing angle θ of 2, the enlarged change in the wheel interval can be absorbed by the swing displacement of the swing leg 52, and there is no particular problem. When the rail span, that is, the wheel interval is greatly expanded beyond the range of the reference swing angle θ due to the ground crack, the interval between the two legs 5 and 6 is greatly expanded beyond the range allowed by the swing displacement of the swing leg 52. That is, a horizontal force exceeding the design load (horizontal force in the swinging direction) acts on at least one of the legs. As a result, FIG.
As shown in (B), when the rail span S ₁ ′ (> S ₁ ) greatly exceeds the span allowable error ΔS, the crane machine frame 14 and the like are damaged or deformed to an unrecoverable state. In fact, many bridge-type cranes that were damaged or deformed to an unrepairable state as shown in Fig. 17 (B) due to the direct impact of the Hyogoken-Nanbu Earthquake that occurred shortly before January 17, 1995 were found. Most of them were caused by changes in the rail span due to deformation of the rail installation ground (quay etc.).

If the swing range of the swing leg 52 is not restricted, the running wheels 7 can be maintained within the range of mechanical stability in consideration of the position of the center of gravity of the crane, even if the rail span changes greatly as described above. The crane itself will not be damaged or deformed to an irreparable state as long as the .8 does not disengage from the rails 12 and 13. The crane operation can be resumed by restoring and restoring the rail installation ground and the parallel rails 12 and 13. Becomes That is, it can be said that not restricting the swing range of the swing leg 52 is effective for earthquake countermeasures against an earthquake in which the rail installation ground itself is deformed.

The present invention has been made in view of the above points, and does not deform the rail-installed ground, but does not cause the earthquake such as rocking to lose the wheel and the rocking does not cause the rail-mounting ground to deform. An object of the present invention is to provide a crane such as a bridge crane that can be easily restored after earthquake mitigation without being damaged or deformed to an irreparable state in any case of an earthquake. It is.

[0016]

According to the present invention, there is provided a crane comprising a swinging leg which is swingably connected to a crane machine frame having a rigid structure and configured to run on parallel rails. In order to achieve the object of the present invention, in particular, a swinging-leg swing range regulating device for regulating the swinging range of the swinging leg is interposed between the swinging leg and the crane machine frame, and this is configured as follows. It is suggested to put it.

That is, this rocking-leg swing range restricting device comprises:
A cylinder body connected to one of a swinging leg and a crane machine frame, wherein the cylinder body is formed by connecting a first cylinder portion and a pair of second cylinder portions communicating with both ends thereof in series; A first piston member connected to the swinging leg and the other of the crane machine frame so as to be able to move relative to each other in the cylinder direction in series in the cylinder body in conjunction with the swing displacement of
The cylinder portion is movably mounted only in the second cylinder portion, and is pressed and moved by the first piston body when the first piston body relatively moves from the first cylinder portion to the second cylinder portion. A second piston body and the second cylinder body in a second cylinder area, which is a rear side area of the second piston body in each second cylinder portion and is closed by the second piston body; In order to press and hold at a stopper function position, which is a boundary position with the first cylinder portion, a sealed incompressible fluid and a second cylinder region of the second cylinder portion are provided in each of the second cylinder portions. The first piston body is moved by the second piston only when the incompressible fluid sealed in the piston is subjected to a horizontal force in the swing direction exceeding the design load on the swing leg. A pressure holding mechanism capable of gradually leaking along with the relative movement so as to be relatively movable from the first cylinder portion to the second cylinder portion in a state of abutment with the tongue body. In a normal state in which the horizontal force in the swing direction exceeding the design load does not act on the swing leg, the swing displacement of the swing leg is restricted to a range in which the first piston body relatively moves within the first cylinder portion. In the event of an abnormal horizontal force exceeding the design load,
The first piston body is configured such that relative movement from the first cylinder portion to one of the second cylinder portions is allowed, and the swing leg is swingably displaced beyond the above range.

In such a swing leg swing range restricting device,
Both side regions of the first piston body in the first cylinder portion are made into a first cylinder region sealed by the first piston body and both second piston bodies, and both first cylinder regions are communicated by a communication passage having a throttle portion. At the same time, it is preferable that a fluid having a lower pressure than the incompressible fluid in each of the second cylinder regions is sealed in the first cylinder regions. In addition, it is preferable that each pressure holding mechanism be provided with a relief passage for opening the second cylinder region in the second cylinder portion, and a relief valve and a throttle valve provided in the relief passage.

[0019]

FIG. 1 is a block diagram showing an embodiment of the present invention.
This will be specifically described with reference to FIGS. This embodiment relates to an example in which the present invention is applied to the bridge type crane described at the beginning. The meanings of the reference swing angle θ, the reference span S, the allowable span error ΔS, the maximum span S ₁ , and the minimum span S _{2 in} the following description are the same as those described above.

The bridge-type crane shown in FIG. 1 has the same configuration as that of FIG.
It has the same structure as the conventional bridge type crane shown in FIG. That is, as shown in FIG. 1, a bridge type crane according to this embodiment has a crane machine frame 1 having a rigid structure.
4 (a girder 1 rigidly connected to each other, an upper end portion 51 of the sea-side leg 5, a land-side leg 6, a horizontal member 9 and a diagonal member 10), which are swingably connected by pins 53. And a rigid leg 6 which forms a part of the crane machine frame 14 facing the swinging direction (the left-right direction in FIG. 1). 15,15
The traveling wheels 7 and 8 are provided so as to travel on parallel rails 12 and 13 laid on the quay 11. A boom 2 is attached to the tip of the girder 1 so that the boom 2 can be raised and lowered, and a traversing device that suspends and suspends a lifting tool 4 such as a spreader on a series of traveling rails formed on the girder 1 and the boom 2. 3 is rampant.
In addition, the sea-side leg body 5 is separated and configured at a connection point of the horizontal member 9 into an upper end portion 51 connected to the girder 1 and the horizontal member 9 and a swing leg 52 as a lower end portion provided with the traveling wheel 7. ing.

The swinging-leg swing range regulating device 20 regulates the swinging range of the swinging leg 52 in the rail width direction (the left-right direction in FIG. 1). It is interposed between the horizontal member 9 which is a part of 14 and has the following structure according to the present invention.

That is, the swing leg swing range restricting device 20
As shown in FIGS. 1 to 9, each of the cylinder members 21 is connected to the horizontal member 9 which is a part of the crane machine frame 14, and includes a first cylinder portion 22 and a pair of second cylinder portions 23 a and 23 b. The second piston bodies 24a and 24b arranged on the second cylinder portions 23a and 23b are connected to the swing leg 52 so as to linearly move in the cylinder body 21 in accordance with the swing displacement of the swing leg 52. First piston body 2
5 and a pair of pressure holding mechanisms 27a and 27b for holding the pressure of the incompressible fluids 26a and 26b sealed in the second cylinder portions 23a and 23b.

As shown in FIGS. 3 to 6, the cylinder body 21 has a closed-end cylindrical shape extending vertically and has a first cylinder portion 22 and a pair of upper and lower ends connected to the first cylinder portion 22. A bracket 28 comprising a second cylinder portion 23a, 23b and a middle portion in the vertical direction provided on the horizontal member 9;
The pin 28a is swingably connected and supported by a pin 28a. The inner diameter of the first cylinder portion 22 is
a, 23b are set slightly smaller than the inner diameter of
Cylinder part 22 and each second cylinder part 23a, 23b
The annular step portions 29a and 29b are formed at the boundary between the two.

Each of the second piston bodies 24a and 24b is shown in FIG.
As shown in the figure, the outer cylinder has a disk shape having an outer diameter substantially matching the inner diameter of the second cylinder portions 23a and 23b. , 29b so as to be movable up and down. That is,
Each of the second piston bodies 24a, 24b can move in the vertical direction only in the second cylinder portions 23a, 23b, and is in a stopper function position (FIG. 6, FIG. 7 (solid line position) and a non-stopper function limit position where the end walls 30a and 30b of the second cylinder portions 23a and 23b are abutted and locked (the upper second piston body 24a is indicated by a chain line in FIG. 9; (The position indicated by the solid line in the figure) is movable. Each second piston body 24
a, 24b, the second cylinder portion 23
An annular sealing material (not shown) capable of sealing between the inner peripheral portions of the second cylinder portions 23a and 23b while permitting vertical movement in the second cylinder portions 23a and 23b is provided. , 23b in the second piston body 2
4a, 24b, the second piston body 24a,
24b, the second cylinder regions 31a, 3 sealed by
1b (in the upper second cylinder portion 23a, the upper surface side region 31a of the second piston body 24a;
In the cylinder portion 23b, it is the lower surface side region 31b of the second piston body 24b). Incompressible fluids (oil is used in this example) 26a, 26b of an appropriate pressure P are sealed in each of the second cylinder regions 30a, 30b, and the pressure (oil pressure) P of the sealed fluids 26a, 26b causes As shown in FIG. 6, the second piston bodies 24a and 24b are located at the boundary positions of the second cylinder portions 23a and 23b with the first cylinder portion 22, that is, annular step portions 29a and 29b.
It is pressed and held at a stopper function position where it is abutted and locked with b.

As shown in FIGS. 3 to 6, the first piston body 25 has a disk shape having an outer diameter substantially matching the inner diameter of the first cylinder 22. It is vertically movable so as to be allowed to enter the cylinder portions 23a and 23b. The first piston body 25 is operatively connected to the swinging leg 52 via an appropriate connecting means, and the cylinder body 2
1 can be relatively moved up and down. The connecting means is inserted and supported in the end wall 30b of the lower second cylinder portion 23b and the through holes 32 and 33 formed in the center of the second piston body 24b so as to be relatively vertically movable. A piston rod 34 to which the first piston body 25 is fixed, a swing arm 35 fixed to the upper end of the swing leg 52 so as to project rearward, a base end of the piston rod 34 and a tip of the swing arm 35. And a connecting pin 36 for connecting the members in a freely rotatable manner. Connecting means 34, 3
The following relationship is established between the swing displacement of the swing leg 52 interlocked via the gears 5 and 36 and the vertical displacement of the first piston body 25 in the cylinder body 21. That is, the swing leg 52
A position where the distance between the traveling wheel 7 provided on this and the traveling wheel 8 provided on the rigid leg 6 in the rail width direction, that is, the wheel interval coincides with the reference span S of the parallel rails 12 and 13 (positions in FIGS. 1 and 3). When the first piston body 25 is in the first position,
It is located at the center of the cylinder part 22. In this state, when the swinging leg 52 swings in the range of the reference swinging angle θ, when the swinging leg 52 is located at the position farthest from the rigid leg 6 (solid line position in FIG. 4), the first piston Body 2
5 is located at the lower end position of the first cylinder 22, that is, at the position where it abuts on the lower second piston body 24 b located at the stopper function position (solid line in FIG. 9), and the swing leg 52 comes closest to the rigid leg 6 ( When it is located at the position indicated by the dashed line in FIG. 4, the first piston body 25 is located at the upper end position of the first cylinder 22, that is, at a position where it abuts the upper second piston body 24 a located at the stopper function position (FIG. Chain line). In addition, the through hole 3
Each of the ring members 2 and 33 is provided with an annular sealing member (not shown) for sealing the gap between the piston rod 34 and the piston rod 34 while permitting the relative movement of the piston rod 34.

The pressure P of the sealed fluid 26a in the upper second cylinder area 31a is equal to the pressure P of the first piston body 25.
In the swinging direction acting on the swinging leg 52 in a direction in which it is brought closer to the rigid leg 6 in a state where it abuts against the second piston body 24a located at the stopper function position (hereinafter referred to as “leg closing force”). As long as the pressure does not exceed the design load, the pressing force (second pressure) necessary and sufficient to hold the second piston body 24a in the stopper function position so as to prevent the first piston body 25 from moving into the second cylinder portion 23a. The pressure is set according to the design load of the crane machine frame 14 so as to ensure the pressing force of the piston body 24a against the annular step portion 29a. Also,
Filled fluid 26b in lower second cylinder region 31b
Similarly, the pressure P acts on the swing leg 52 in a direction in which the first piston body 25 is separated from the rigid leg 6 in a state where the first piston body 25 is in contact with the second piston body 24b located at the stopper function position. As long as the horizontal force in the swinging direction (hereinafter, referred to as “spreading force”) does not exceed the design load, the first piston 25
Of the second cylinder portion 23b to prevent the
In accordance with the design load of the crane machine frame 14, a necessary and sufficient pressing force (pressing force on the annular step portion 29b of the second piston body 24b) necessary to hold the piston body 24b at the stopper function position can be secured. Is set. In other words, the pressures P, P of the sealed fluids 26a, 26b are such that the holding force at the stopper function position of the second piston bodies 24a, 24b applied by the first piston bodies 25 is lower than the set load by the opening or closing force. Is set to be larger than the pressing force acting on the second piston bodies 24a and 24b via the. Therefore, when the leg opening force or the leg closing force does not exceed the design load, the relative movement range of the first piston body 25 with respect to the cylinder body 21 is limited to the second piston body 2 at the stopper function position.
4a and 24b, the swing range of the swing leg 52 is limited to the range of the reference swing angle θ.
As described above, the second piston bodies 24a and 24b and the sealed fluids 26a and 26b holding the second piston bodies 24a and 24b at the stopper function position are provided.
In the normal state where the horizontal force in the swing direction (spreading force or closing force) exceeding the design load does not act on the swing leg 52, the swing leg 5
2 functions as a stopper that regulates the swing range to the reference swing angle θ.

Each of the pressure holding mechanisms 27a and 27b is shown in FIGS.
As shown in FIG. 9, relief passages 40a and 40b for opening the second cylinder regions 31a and 31b are provided in the second cylinder portions 23a and 23b.
a and 40b are provided with relief valves 41a and 41b and a throttle valve 42.
a, 42b. Upper second cylinder part 23
a of the pressure holding mechanism 27a provided in the
When the leg opening force exceeding the design load is applied to the swinging leg 52, the first piston body 25 abuts against and presses the second piston body 24a at the stopper function position, whereby the sealed fluid 26a is sealed. When the pressure is increased beyond the pressure P, the valve is opened and the valve is opened. Further, the relief valve 40b of the pressure holding mechanism 27b provided in the lower second cylinder portion 23b allows the first leg when the closing leg force exceeding the design load acts on the swing leg 52 to act as the first leg.
The piston body 25 is the second piston body 2 in the stopper function position.
4b against and presses against it, thereby enclosing fluid 26
When b rises above the sealing pressure P, this is sensed and the valve opening operation is performed. Therefore,
When a leg opening force or a leg closing force exceeding the design load acts on the swing leg 52, the relief valves 41a and 41b are opened, and the first piston body 25 is moved to the second piston bodies 24a and 24.
b while the second cylinder portions 23a, 23a
3b, and the swing of the swing leg 52 beyond the reference swing angle θ is allowed. At this time, the second cylinder 24
a and 24b are moved toward the non-stopper function limit position by the first piston 25 which abuts on the first and second pistons 25a and 24b.
0b, which is released by the throttle valves 42a, 42a.
The operation is performed at an appropriate speed that is limited by b and can perform a predetermined damper function. That is, each of the pressure holding mechanisms 27a and 27b causes the swing leg 5 to move when the leg opening force or the closing force exceeding the design load acts on the swing leg 52.
(2) A function as a damper that allows a swing displacement in a range exceeding the reference swing angle θ and also reduces a shock due to the swing displacement as much as possible to the swing leg swing range regulating device 20. It is. The maximum swing angle θ ′ of the swing leg 52 in this case is a range in which the first piston body 25 presses and moves the second piston bodies 24a and 24b to the non-stopper function limit position (see FIGS. 5 and 9). ). The maximum swing angle θ ′ is set on condition that the crane does not fall when the swing leg 52 is displaced by a maximum amount (θ ′ / 2) in a direction away from the rigid leg 6 or in a direction approaching the rigid leg 6. It is set as large as possible.

Further, on the outer peripheral portion of the first piston body 25,
Similarly to the second piston bodies 24a and 24b, an annular seal member (which allows vertical movement (relative movement) in the first cylinder portion 22 and seals between the inner peripheral portion of the first cylinder portion 22 ( (Not shown).
The upper and lower sides of the first piston body 25 in the cylinder portion 22 are formed as first cylinder areas 43, 43 sealed by the first piston 25 and the second piston bodies 24a, 24b located at the stopper function position. And
The two first cylinder regions 43, 43 are communicated with each other by a communication passage 44 formed in the first piston body 25, and the second cylinder regions 31a, 43 are connected to the first cylinder regions 43, 43, respectively.
A fluid lower in pressure than the sealed fluid pressure P of 31b (oil is used in this example) is sealed. The communication passage 44 is provided with a throttle portion, and is configured to impart a certain resistance to fluid movement between the first cylinder regions 43, 43 by the first piston body 25, and acts on the swing leg 52. When the leg opening force or the leg closing force (not exceeding the design load) becomes equal to or less than a predetermined value, the movement of the first piston body 25 is prevented by fluid resistance. That is, when the swing leg 52 swings and displaces in the range of the reference swing angle θ, the swing leg 52 is designed so as not to swing more than necessary from the position where the swing displacement is performed. Even when rocking in which the traveling wheel 7 floats from the rail 12 occurs,
An attempt is made to prevent a situation in which the traveling wheel 7 is disengaged from the rail 12 when the rocking leg 52 is unnecessarily pivotally displaced and returned after locking. Note that the throttle portion of the communication passage 44 is
The communication path 44 may be formed by constricting a part of the communication path 44 to a minute cross-sectional area, or may be formed by forming the entire communication path 44 as a minute hole.

In the bridge type crane constructed as described above, when the horizontal force in the rail width direction relatively acting on the two legs 5 and 6 is equal to or less than the design load, that is, it acts on the swinging leg 52. When the leg opening force or the closing force is equal to or less than the design load, the relative movement of the first piston body 25 with respect to the cylinder body 21 is regulated by the second piston bodies 24a and 24b held at the stopper function position by the sealed fluid pressure P. Swaying legs 5
2 is restricted within the range of the reference swing angle θ. Therefore, even when the rail spans of the parallel rails 12 and 13 change in width within the range of the allowable error ΔS, the rails can follow the change in width and width of the rails, and the horizontal load due to the crane's own weight does not act on the legs 5 and 6. Structural stability. In addition, even when an earthquake occurs in which the crane locks and loses a wheel, both legs 52,
Since the relative distance of 6 does not change more or less than a certain value, the crane does not collapse and the running wheels that have been derailed after the earthquake is calmed down can be returned to the rails, so that the crane can be easily returned to the original operable state. Can be restored and restored. That is, the ground on which the rails are installed (quay 11) or the rails 12 and 13 are not deformed, but can sufficiently cope with an earthquake in which the wheel is lost due to the rocking of the crane. However, there is no possibility that the crane will not collapse and will be damaged or deformed in an irreparable state.

In addition, a strong earthquake such as the Hyogoken-Nanbu Earthquake mentioned at the beginning causes the quay 11 as a ground on which rails are installed.
When the rail itself changes greatly beyond the allowable error ΔS and the leg opening force or the closing force exceeding the design load is applied to the swing leg 52, the first piston by the second pistons 24a and 24b at the stopper function position is deformed. The restriction on the movement of the piston body 25 is released, and the swing of the swing leg 52 beyond the reference swing angle θ is allowed, and as shown in FIG.
The deformation and breakage of the can be prevented.

That is, when the rail span S ₁ ′ greatly exceeds the maximum span S ₁ within the allowable error ΔS due to a crack in the quay wall 11 serving as the rail installation ground, the relief valve 41 b is opened. The first piston body 25 relatively moves to the second cylinder portion 23b while pressing and moving the second piston body 24b in the direction of the non-stopper limit position, and the movement of the swinging leg 52 in the opening direction is allowed. The interval is enlarged according to the rail span S ₁ ′ (FIG. 2).
(A)). Also, the rail span S ₂ ′ is set to the minimum span S _{2 in} the range of the allowable error ΔS due to the rise of the quay 11 or the like.
, The relief valve 41a is opened, and the first piston body 25 relatively moves to the second cylinder portion 23a while pressing and moving the second piston body 24a toward the non-stopper limit position. The swing leg 52 is allowed to move in the closing direction, and the wheel interval is set to the rail span S.
₂ '(FIG. 2B).

Therefore, the rail span has a tolerance ΔS.
When the opening / closing force exceeds the design load on the swinging leg 52, the load exceeding the design load does not act on the sea-side leg 5 or the like including the swinging leg 52. ,
There is no fear that they are deformed or damaged.

After the earthquake has subsided and the rail span has been restored to its original state, the swing leg swing range restricting device 20 is repaired (the fluid pressures P, P in the second cylinder regions 31a, 31b are reduced). Or to replace the entire swing leg swing range restricting device 20 with a new one, and return the swing leg 52 to a state where it can swing only at the reference swing angle θ. That is, depending on the earthquake, the second cylinder regions 31a, 3
Only the enclosed fluid pressures P, P of 1b are lost, and no repair is required except for this point, and the bridge crane itself does not need to repair it at all. Therefore, the recovery operation can be performed easily and quickly.

It should be noted that the present invention is not limited to the above-described embodiment, and can be appropriately improved and changed without departing from the basic principle of the present invention. For example, in the crane described above, the land-side leg 6 is
As shown in FIG. 13, similarly to the sea-side leg 5, at the connection point of the horizontal member 9, the upper end portion 61 connected to the girder 1 and the horizontal member 9 and the lower end 63 slidably connected to the upper portion 61. The lower part 62 and the horizontal member 9 are separated from each other.
The rigid leg function canceling device 20 ′ provided between the lower leg portion 62 and the lower leg portion 62 (in the rail width direction (the left-right direction in FIG. ) May be configured to prevent the swing in).

That is, as shown in FIGS. 10 to 13, the rigid leg function release device 20 'is connected to the horizontal member 9 which is a part of the crane machine frame 14, and the first cylinder portion 22'.
And a cylinder body 21 'composed of a pair of second cylinder portions 23'a and 23'b, and a second cylinder portion 23'a,
Second piston bodies 24'a, 24 'arranged at 23'b
b and the inside of the cylinder body 21 (the second cylinder portions 23'a and 23'b are connected to the upper and lower ends of the first cylinder portion 22 'in conjunction with the swing displacement of the lower end portion 62). A first piston body 25 'interlocked with the lower end portion 62 for linear movement, and a respective second cylinder portion 23';
Incompressible fluid 26'a, 26 enclosed in a, 23'b
'B, a pair of pressure holding mechanisms 27'a, 2
7′b, the first cylinder portion 22
The length of the first piston body 25 'is substantially equal to the thickness of the first piston body 25', so that the first piston body 25 'abuts on the annular steps 29'a, 29'b. 2
An annular seal member that can be immovably locked by 4'a and 24'b and that can seal between the outer peripheral portion of the first piston body 25 'and the inner peripheral portion of the first cylinder portion 22'. Are not provided, and the inside of the first cylinder portion 22 'is opened to the atmosphere by the communication hole 22'a,
It has the same structure as the swinging-leg swing range regulating device 20 (the same components as those of the swinging-leg swing range regulating device 20 are shown in FIGS. The detailed description thereof will be omitted by showing the same reference numerals as those of the components of the device 20 by adding dashes. Of course, each second cylinder portion 23 '
Incompressible fluid 26'a, 26 enclosed in a, 23'b
The pressure 'b is also set to be the same as the pressure P of the sealed fluids 26a and 26b in the swinging-leg swing range regulating device 20.

Thus, in the bridge type crane having such a configuration, when the opening force or the closing force acting on the legs 5 and 6 is equal to or less than the design load, the stopper function position ( The first piston body 25 'is fixed by the second piston bodies 24'a and 24'b held at the positions (solid line positions in FIG. 13) abutted and locked by the annular step portions 29'a and 29'b. As a result, the swing of the lower end portion 62 of the land-side leg 6 is prevented. That is, the land-side leg 6 functions as a rigid leg. Therefore, the same function as the bridge-type crane shown in FIG. 1 (such as the ability to follow a wide or narrow change in the rail span within the allowable error ΔS) is exhibited.

On the other hand, when the quay 11 itself as the ground on which the rails are installed is deformed due to the earthquake, the rail span changes greatly beyond the allowable error ΔS, and when the opening or closing force exceeding the design load is applied, the second piston 24a , 24b and 24'a, 24'b, the first piston bodies 25 and 25
′ Is released, the lower end portions 52, 62 of both legs 5, 6 are both swung according to the change of the rail span, and as shown in FIG. Damage is prevented beforehand.

That is, when the rail span S ₁ ′ is greatly expanded beyond the maximum span S ₁ within the allowable error ΔS due to a crack in the quay wall 11 serving as the rail installation ground, the relief valves 41 b and 41 ′ b are opened. When the valve is operated, the first piston bodies 25, 25 'are moved to the second piston bodies 24b, 2b.
While pressing and moving the 4′b, the second cylinder portions 23b, 2
3'b (see the solid line in FIG. 8 and the two-dot chain line in FIG. 13), the lower end portions 52, 62 are allowed to move in the leg opening direction, and the wheel interval is determined by the rail span S ₁ ′. (FIG. 11A). Further, when the rail span S ₂ ′ narrows greatly beyond the minimum span S ₂ within the range of the allowable error ΔS due to the uplift of the quay 11, etc., the relief valves 41a and 41′a are opened, and The one piston bodies 25, 25 'move relatively to the second cylinder parts 23a, 23'a while pressing and moving the second piston bodies 24a, 24'a (see the chain lines in FIG. 8 and the dashed line in FIG. 13). The movement of the lower end portions 52, 62 in the closing direction is permitted, and the wheel interval is reduced in accordance with the rail span S ₂ ′ (FIG. 1).
1 (B)).

Therefore, the rail span has an allowable error ΔS
When the leg opening force or the leg closing force acts on the legs 5 and 6, the load exceeding the design load does not act on the legs 5 and 6, and there is no possibility that the legs 5 and 6 may be deformed or damaged. In this case, since both lower end portions 52 and 62 are oscillatingly displaced, even when the amount of oscillating displacement is large, unlike the case where only one lower end side portion 52 is oscillatingly displaced, the crane is inclined. There is almost nothing. Further, the swing amount of each of the lower end portions 52 and 62 is smaller than the case where the swing amount necessary for following the wide and narrow change of the rail span due to the earthquake is secured by the swing of only one lower end portion 52. And each device 2
0, 20 '(especially, the entire length of the cylinder bodies 21, 21) can be reduced in size. After the earthquake has subsided and the rail span has been restored to its original condition, each device 2
Repair the 0,20 'or replace it with a new one.
2 is returned to a state in which it can swing only at the reference swing angle θ, and the land-side leg 6 is returned to a rigid leg configuration in which the swing of the lower end portion 62 is prevented. The state can be easily restored.

In the swing leg swing range regulating device 20 (or the rigid leg function canceling device 20 '), a member to which the cylinder body 21 (or 21') and the first piston body 25 (or 25 ') are connected. The selection is arbitrary, and contrary to the above-described example, the cylinder body 21 (or 21 ′) is connected to the swing leg 52 (or the lower end portion 62), and the first piston body 25 (or 2
5 ') to the connecting means 34, 35, 36 (or 34', 35).
', 36') to the crane machine frame 14 at an appropriate position (the horizontal member 9 or the like).

The swing leg 52 is formed of a leg portion not connected to the rigid leg 6 by the horizontal member 9 as described above, and a leg portion connected to the rigid leg 6 by the horizontal member 9 as described above. It can also be composed of those containing. That is, FIG.
As shown in (A), the upper end of the seaside leg 5 can be swingably connected 53 to a bracket 54 provided on the girder 1, so that the entire seaside leg 5 can be configured as a swing leg 52. in this case,
As shown in FIG. 14A, the cylinder body 21 is pivotally connected 54 to the rigid leg 6 (or the swing leg 5), and the piston rod 34 to which the first piston body 25 is fixed is connected to the swing leg 5 (or the rigid leg 6). ) Is pivotally connected 55 so that the swing leg swing range restricting device 20 functions as the horizontal member 9. Or, without directly connecting the swing leg 5 and the horizontal member 9,
By way of the swing-leg swing range restricting device 20, that is, the cylinder rod 21 is pivotally connected to the swing leg 5 (or the horizontal member 9) and the piston rod 34 to which the first piston body 25 is fixed is connected to the horizontal member 9 (or By pivotally connecting to the rocking leg 5), it is indirectly connected. According to such a configuration,
The entire length of the cylinder body 21 and the piston rod 34 expands and contracts due to the swing of the swing leg 52 accompanying the change in the rail span (see FIG. 14B).

Further, the swinging leg swing range restricting device 20 controls the second swinging motion of the swinging leg 52 exceeding the reference swinging angle θ.
Either a configuration in which the filled fluid pressure P in the cylinder regions 31a and 31b can be recovered (for example, a configuration in which the filled fluid can be refilled and refilled by a hydraulic pump, a manual pump, or the like) or a configuration in which the recovered fluid cannot be recovered may be used. In the latter case, it is necessary to replace the swing leg swing range control device 20 with a new one at the time of recovery work after an earthquake, but the device 20 does not require hydraulic peripheral equipment like a general damper. Therefore, the work and economic burden of replacing with a new one is extremely small. These points are the same for the rigid leg function release device 20 '.

Further, in the swing leg swing range regulating device 20, the first cylinder regions 43, 43 may be communicated with each other by a communication passage 44 arranged outside the cylinder body 21, as shown by a chain line in FIG. Good. In this case, the communication passage 4
4 is provided with a throttle valve 44a as a throttle portion. In the case where the communication passage 44 is formed in the first piston body 25, a minute gap is formed between the outer peripheral portion of the first piston body 25 and the inner peripheral portion of the first cylinder portion 22, and this is formed as a throttle portion. May be made to function as a communication path 44 having Further, as a structure in which the space between the first piston body 25 and the first cylinder portion 22 is not sealed with an annular sealing material, or as a structure in which the inside of the first cylinder portion 22 is opened to the atmosphere,
The first piston body 25 may be configured to be freely movable in the first cylinder portion 22 without receiving the fluid resistance.

In the swing leg swing range restricting device 20, the structure of the pressure holding mechanisms 27a and 27b is optional.
The sealed fluid pressure P in the second cylinder regions 31a and 31b is
The second cylinder region 31 of the first piston body 25 only in a state where the leg opening force or the leg closing force exceeding the set load is not applied.
a, 2nd piston body 2 capable of preventing relative movement to 31b
Any structure can be used as long as it can be maintained at a constant pressure so that the stopper functions of 4a and 24b can be exerted. In addition to the above structure, a structure using an accumulator or the like can be used. As shown in FIG. 15, each of the pressure holding mechanisms 27a and 27b has a relief valve 41a, 41b and a throttle valve 42a, 4b at the end of the second cylinder portion 23a, 23b.
While connecting the first relief passages 40a and 40b having 2b, the intermediate portions of the cylinder portions 23a and 23b
By connecting the second relief passages 140a and 140b having only the relief valves 141a and 141b without the throttle valve, when the rail-installed ground 11 is deformed by the earthquake, the swing of the swing leg 52 due to the wide and narrow change of the rail span. It can be configured so that the dynamic displacement can be performed more smoothly. That is, the relief valves (hereinafter, referred to as “second relief valves”) 141 provided in the second relief paths 140a and 140b.
a, 141b is the first relief passage 40a,
40b, which are set higher than the relief valves (hereinafter referred to as "first relief valves") 41a, 41b,
When the opening or closing force exceeding the set load acts, the swinging leg 52
Swings beyond the reference swing angle θ, the first relief valves 41a and 41b are opened, and the sealed fluids 26a and 26b are opened.
Leaks from the first relief passages 40a and 40b, and the swing displacement of the swing leg 52 is performed while receiving the damper action by the resistance action of the throttle valves 42a and 42b, as in the case shown in FIGS. However, in this case, the opening or closing force (exceeding the design load) is abnormally large, and
2 is extremely high, the second relief valve 1
41a and 141b are opened, and the sealed fluids 26a and 26b leak from the second relief paths 140a and 140b, and the first
The piston body 25 and the second piston bodies 24a, 24b move quickly to the connection point of the second relief paths 140a, 140b without receiving resistance (see the dashed line in FIG. 15). Therefore, since the swinging speed of the swinging leg 52 is extremely high, even in the case shown in FIGS. The swing leg 52 can favorably follow the change in the span, and the wheel does not come off. 6 to 9 when the swing speed of the swing leg 52 decreases or when the second fixie bodies 24a and 24b move beyond the connection between the second relief paths 140a and 140b. Like things,
The filled fluids 26a, 26b are used as first relief paths 40a, 40.
b leaks out, and the damper function is exhibited (see the two-dot chain line in FIG. 15). Therefore, when the deformation of the rail installation ground 11, that is, the change of the rail span due to the earthquake stops, the shock due to the sudden stop of the swing leg 52 does not occur, and the shock may cause the crane to be unexpectedly damaged or deformed. Absent. That is, the swing displacement of the swing leg 52 due to the change in the rail span due to the earthquake is smoothly performed, and there is no fear that the recovery will be hindered thereafter. Such an improvement can be similarly applied to the rigid leg function release device 20 '.

Further, in the swinging leg swing range regulating device 20, one of the first first and second first swinging devices is actuated by a horizontal force exceeding the design load.
In order to eliminate the inconvenience when the cylinder region 43a (or 43b) becomes negative pressure due to the rapid movement of the first piston body 25 to the other first cylinder region 43b (or 43a), each cylinder region 43a and 43b may be connected to an oil tank. Alternatively, when each of the cylinder regions 43a and 43b has a negative pressure equal to or lower than a predetermined value, an air supply valve that operates to open the cylinder regions 43a and 43b to the atmosphere may be provided.

In the pressure holding mechanisms 27a and 27b of the swinging leg swing range restricting device 20 shown in FIG. 6 or FIG. 15, the first cylinder portion 22 of the first piston 25 caused by the change of the rail span due to the earthquake is shown. In order to smooth the relative movement, at both ends of the first cylinder portion 22,
Third relief paths 240a, 24 having a configuration as shown in FIG.
0b may be connected. That is, the third relief path 240a, 240b is opened when the leg opening force or the leg closing force exceeding the set load acts on the third relief path 240a, 240b.
Relief valves 241a and 241b are provided, and the first piston 25 accompanying the wide and narrow change of the rail span due to the earthquake is provided.
The first cylinder portion 22 may be configured to perform the relative movement quickly.

Further, the swing leg 52 may be constituted by the land-side leg 6 or a part thereof (a portion on the lower end side from the horizontal member 9). Of course, the present invention can be applied to all cranes configured to travel on parallel rails by facing legs, and the scope of application is not limited to bridge-type cranes installed on the quay 11.

[0048]

As can be easily understood from the above description, according to the present invention, the ground on which the rail is installed is not deformed, but the derailment due to the earthquake and the rocking does not occur, but the rail is installed. Ground deformation (rail span greatly changes beyond span tolerance)
In any of such earthquakes, it is possible to reliably prevent the crane from being damaged or deformed to an irreparable state, and to easily perform a recovery operation after the earthquake is calmed down.

[Brief description of the drawings]

FIG. 1 is a side view showing an embodiment of a crane according to the present invention.

FIG. 2 is a side view corresponding to FIG. 1, showing a state where a rail-installed ground (quay) has been deformed by an earthquake.

FIG. 3 is an enlarged detailed view of a main part (a swing leg swing range regulating device) of FIG. 1;

FIG. 4 is a view corresponding to FIG. 3, showing a state in which the swing leg swings within a range of a reference swing angle.

FIG. 5 is a diagram corresponding to FIG. 3, showing a state in which the swing leg swings beyond a reference swing angle.

FIG. 6 is a vertical sectional front view of a main part taken along line VI-VI of FIG. 3;

FIG. 7 is a view corresponding to FIG. 6, showing a state different from FIG. 6;

8 is a diagram corresponding to FIG. 6, showing a state different from FIG. 7;

FIG. 9 is a diagram corresponding to FIG. 6, showing a state different from FIG. 8;

FIG. 10 is a side view showing a modified example of the crane according to the present invention.

FIG. 11 is a side view corresponding to FIG. 10 showing a state where a rail-installed ground (quay) has been deformed by an earthquake.

12 is an enlarged detailed view of a main part (a swing leg swing range regulating device) of FIG. 10;

FIG. 13 is a longitudinal sectional rear view of a main part along the line XIII-XIII in FIG. 12;

FIG. 14 is a side view showing another modified example of the crane according to the present invention.

FIG. 15 is a longitudinal sectional front view corresponding to FIG. 6 and showing a modification of the swing leg swing range regulating device.

FIG. 16 is a longitudinal sectional front view corresponding to FIG. 6, showing another modified example of the swing leg swing range regulating device.

FIG. 17 is a side view showing a general bridge type crane.

FIG. 18 is a schematic diagram showing a swinging form of a swinging leg in a range of a reference swing angle.

FIG. 19 is a cross-sectional view showing an engaged state between a traveling wheel and a rail.

[Explanation of symbols]

5: Sea-side leg, 6: Land-side leg (rigid leg), 7, 8: Running wheel, 9: Horizontal material, 10: Diagonal material, 11: Quay (rail installation ground), 12, 13: Parallel rail , 15 ... flange, 20 ... rocking swing range control device, 21 ... cylinder body, 22 ... first cylinder part, 23a, 23b ... second cylinder part, 24
a, 24b ... second piston body, 25 ... first piston body,
26a, 26b ... incompressible fluid (oil), 27a, 27b
... pressure holding mechanism, 31a, 31b ... second cylinder area,
34 ... Piston rod, 40a, 40b, 140a, 1
40b ... relief road, 41a, 41b, 141a, 14
1b relief valve, 42a, 42b throttle valve, 43 first cylinder region, 44 communication path, 44a throttle section (throttle valve).

Claims (3)

[Claims] 1. A crane comprising a swinging leg slidably connected to a crane machine frame having a rigid structure and configured to run on parallel rails, wherein between a swinging leg and the crane machine frame. A swing-leg swing range regulating device for regulating the swing range of the swing leg is interposed. The swing-leg swing range regulating device is a cylinder body connected to one of the swing leg and the crane machine frame. A first cylinder portion and a pair of second cylinder portions communicating with both ends of the first cylinder portion connected in series with each other; A first piston body connected to the other of the swinging leg and the crane machine frame so that the first piston body can move relative to the first cylinder body; The body is first
A second piston body that is pressed and moved by the first piston body when relatively moved from the cylinder portion to the second cylinder portion; and a rear side area of the second piston body in each second cylinder portion, the A non-compressible seal filled in the second cylinder region sealed by the two piston body so as to press and hold the second piston body at a stopper function position which is a boundary position between the second cylinder part and the first cylinder part. The fluid and the incompressible fluid provided in each second cylinder portion and sealed in the second cylinder region of the second cylinder portion are subjected to a horizontal force in the swing direction exceeding the design load acting on the swing leg. Only the first piston body can be relatively moved from the first cylinder portion to the second cylinder portion while the first piston body abuts on the second piston body. And a pressure holding mechanism capable of leaking with the relative movement thereof, wherein the swing displacement of the swing leg is normally reduced when a swing direction horizontal force exceeding the design load does not act on the swing leg. In the case where the first piston body is restricted to a range in which the first piston body relatively moves within the first cylinder portion, and a swinging horizontal force exceeding the design load acts on the swing leg, the first piston body is moved from the first cylinder portion to the other side. Wherein the relative movement to the second cylinder portion is allowed, and the swing leg is swingably displaced beyond the above range. 2. The pressure holding mechanism according to claim 1, wherein a relief passage for opening the second cylinder region is provided in the second cylinder portion, and a relief valve and a throttle valve are provided in the relief passage. The crane according to claim 1, wherein 3. Both side regions of the first piston body in the first cylinder portion are formed as first cylinder regions sealed by the first piston body and both second piston bodies, so that both first and second piston bodies are closed.
The cylinder region is communicated by a communication passage having a throttle portion, and the first cylinder region is filled with a fluid having a lower pressure than the incompressible fluid of each second cylinder region. Or the crane according to claim 2.