JP6924669B2 - Outrigger device - Google Patents

Description

The present invention relates to an outrigger device that projects laterally from the machine body of a working machine to support the machine body.

Conventionally, as an outrigger device used for a work vehicle such as a crane, for example, there is an outrigger device described in Patent Document 1. The outrigger device includes a vertical overhang link mechanism including a first arm and a first cylinder, and a horizontal overhang link mechanism including a second arm, an outer box, and a second cylinder. The base end of the first arm is pivotally supported on the chassis frame of the work vehicle via a subframe and a bracket, and the base end of the second arm is pivotally supported on the tip of the first arm. The base end of the outer box is pivotally supported at the tip of the arm. Then, the outrigger device extends the lateral extension link mechanism by reducing the second cylinder and rotating the second arm from the retracted posture, and extends the first cylinder to extend the first arm. The vertical overhang link mechanism is extended by rotating.

Japanese Unexamined Patent Publication No. 2006-21914

However, in the prior art of Patent Document 1, due to the existence of two actuators, a first cylinder and a second cylinder, as actuators for generating power when performing the extension operation of the vertical extension link mechanism and the horizontal extension link mechanism. , Each operation was performed.
Therefore, the present invention has focused on such a problem, and provides an outrigger device capable of covering a plurality of operations necessary for storing and installing the outrigger device with a single actuator. The task is to do.

In order to solve the above problems, the out-trigger device according to the first aspect of the present invention includes a base end side arm rotatably provided on a base of a working machine around a horizontal axis, and the base end side arm. The tip of the device is provided with a nested tip-side arm whose base end is rotatably supported around a first axis parallel to the horizontal axis, and a retracted posture during storage and a deployed posture during work. It is an out-trigger device having and.

In this out-trigger device, the tip-side arm has a plurality of arms in a nested manner and a telescopic actuator is internally provided, and the first end-side arm restrains the rotation of the base-end-side arm and the tip-side arm. The posture holding means and the second posture holding means for restraining the expansion and contraction of the plurality of arms are provided, and the tip side arm is not restrained in rotation by the first posture holding means. When the expansion and contraction is restrained by the second posture holding means, the rotation operation is performed according to the expansion and contraction operation of the actuator, and the rotation is restrained by the first posture holding means and the second. When the expansion / contraction is not restrained by the posture holding means of the above, the expansion / contraction operation of the plurality of arms is performed according to the expansion / contraction operation of the actuator.

According to the present invention, the rotation and expansion / contraction of the distal end side arm and the proximal end side arm are restrained and released by the first posture holding means and the second posture holding means. As a result, it is possible to shift from the retracted posture to the deployed posture by rotating the tip end arm and from the retracted posture to the deployed posture by extending the tip side arm by using one common actuator. .. As a result, it is possible to eliminate the need for an actuator that generates the rotational power of the tip end side arm, so that it is possible to realize cost reduction and weight reduction as compared with the conventional case.

It is a figure which shows the traveling posture of the tower crane which concerns on 1st Embodiment, and is the side view seen from the right-hand side of a vehicle. The figure shows a state in which the outrigger device is stored. It is a perspective view which looked at the tower crane which concerns on 1st Embodiment from the upper right side of a vehicle. The figure shows a state in which the outrigger device is deployed. It is a figure which shows an example of the hydraulic circuit which concerns on 1st Embodiment. It is a block diagram which shows the input / output relation of the signal of the controller which concerns on 1st Embodiment. It is a side view which shows the retracted posture of the outrigger apparatus which concerns on 1st Embodiment. The figure shows a state in which the entire outrigger device is swiveled by approximately 90 ° in the horizontal direction. (A) is a partial top view of the outrigger device according to the first embodiment, and (b) is a sectional view taken along line AA of (a). In FIG. 3B, the cross-sectional view of the base end side arm, the center bracket, and the tip end side arm excluding the float is shown. FIG. 5 is a cross-sectional view taken along the line CC of FIG. (A) is a side view of the outrigger device in a state where the restraint on the rotation operation of the tip side arm is released and the first and second retracted postures are released, and (b) is the most by the rotation operation of the tip side arm. It is a side view of the outrigger device in the state of being deployed in the overhanging posture S1 at the time of small. In the figure, the cross section of the base end side arm, the center bracket, and the tip end side arm excluding the float is shown. It is a side view of the outrigger device in the state of being expanded to the maximum overhanging posture U1 by the rotation operation of the tip side arm. In the figure, the cross section of the base end side arm, the center bracket, and the tip end side arm excluding the float is shown. It is a side view of the outrigger device in the state of being expanded to the maximum overhang posture U2 by the extension operation of the tip side arm. In the figure, the cross section of the base end side arm, the center bracket, and the tip end side arm excluding the float is shown. It is a figure for demonstrating the grounding operation of an outrigger device. In the figure, the cross section of the base end side arm, the center bracket, and the tip end side arm excluding the float is shown. It is a partially enlarged sectional view of the outrigger device for demonstrating the structure of the 1st blocking member. In (a) and (b), the bending moment generated in the cylinder tube of the lateral outrigger cylinder when the lateral outrigger cylinder is extended while the tip end arm cannot rotate in the downward direction and the inner box cannot be extended. It is a figure for demonstrating. (A) is a diagram for explaining the relationship of forces when a first blocking member is provided to support a bending moment, and (b) is a diagram in which the tip end side arm is in a first deployment posture due to a rotational movement. It is a figure explaining the bending load when the lateral outrigger cylinder is extended operation in the restrained state. It is a partial top view of the outrigger device which concerns on 2nd Embodiment. (A) is a partial cross-sectional view taken along the line BB of FIG. 15 for explaining the configuration of the second blocking member, and (b) is a diagram showing the second blocking member. (A) is a partial cross-sectional view for explaining the relationship of forces when a hook-shaped second blocking member is provided to support a bending moment, and (b) is a partially enlarged view of (a). ..

Hereinafter, a tower crane, which is an embodiment of a work vehicle equipped with an outrigger device according to the present invention, will be described with reference to the drawings as appropriate. The drawings are schematic. Therefore, it should be noted that the relationship, ratio, etc. between the thickness and the plane dimension may differ from the actual one, and there are parts where the relationship and ratio of the dimensions are different between the drawings. In some cases. In addition, in order to make it easier to understand the positional relationship of each component, a portion that is originally invisible may be displayed transparently. In addition, the embodiments shown below exemplify devices and methods for embodying the technical idea of the present invention, and the technical idea of the present invention describes the material, shape, structure, and arrangement of constituent parts. Etc. are not specified in the following embodiments.

(First Embodiment)
(composition)
As shown in FIGS. 1 and 2, the tower crane 1 according to the first embodiment of the present invention includes a chassis frame 2, a traveling device 3, a base 4, a column 5, and a crane device 6. In addition, the right front outrigger device 9RF, the right rear outrigger device 9RR, the left front outrigger device 9LF, the left rear outrigger device 9LR, the driver's seat 10, the operation unit 11, the winch 12, the wire rope 13, the hook 14, and the prime mover. A portion 15, a control box 16, and a hook storage bracket 17 are provided.

The traveling device 3 is, for example, a crawler-type traveling device in which rubber tracks are attached to the left and right, and is provided at the lower part of the chassis frame 2.
The base 4 is connected and fixed to the upper part of the chassis frame 2, and the column 5 is erected on the upper part of the base 4 so as to be rotatable.
The crane device 6 is undulatingly pivotally supported at the upper end of the column 5, and is undulatingly pivotally supported by a telescopic undulating boom 7 composed of a nested box-shaped boom and the tip of the undulating boom 7. It is provided with a telescopic folding boom 8 composed of a nested box-shaped boom.

At the time of work, as shown in FIG. 2, the undulating boom 7 is rotated to bring it into an upright state, and the bent boom 8 is raised with respect to the undulating boom 7 to face the front side. Further, the required height can be secured by extending the undulating boom 7 in the upright state, and the hook 14 can reach a distant load by extending the bent boom 8.
Right front, right rear, left front and left rear outrigger devices 9RF, 9RR, 9LF and 9LR are provided on the upper right front, right rear, left front and left rear of the upper part of the chassis frame 2, respectively.

Hereinafter, the right front, right rear, left front and left rear outrigger devices 9RF, 9RR, 9LF and 9LR may be abbreviated as "each outrigger device 9RF to 9LR".
The outrigger devices 9RF to 9LR include a base end side arm 93 that is swiveled and undulated on the chassis frame 2, and a telescopic tip side arm 95 that is undulatingly provided at the tip of the base end side arm 93. It has.

Further, each outrigger device 9RF to 9LR includes right front, right rear, left front and left rear vertical outrigger cylinders 37RF, 37RR, 37LF and 37LR, which are hydraulic actuators for undulating the base end side arm 93. In addition, as shown in FIG. 3, the front right, right rear, left front and left rear lateral outrigger cylinders 36RF, 36RR, 36LF and 36LR, which are hydraulic actuators for undulating and expanding / contracting the tip side arm 95, are provided. There is.

Hereinafter, the right front, right rear, left front and left rear lateral outrigger cylinders 36RF, 36RR, 36LF and 36LR may be abbreviated as "each lateral outrigger cylinders 36RF to 36LR". Further, the right front, right rear, left front and left rear vertical outrigger cylinders 37RF, 37RR, 37LF and 37LR may be abbreviated as "each vertical outrigger cylinder 37RF to 37LR".

Here, as shown in FIG. 4, the tower crane 1 is provided with a remote control device 162 capable of remotely controlling the crane. Although not shown, the remote control device 162 is configured to enable the same operation as the operation lever and operation switch of the operation unit 11 by various operation levers and various operation switches provided on the housing of the remote control device 162. ing. Further, the remote control device 162 is configured to wirelessly transmit a remote control signal Rctr corresponding to the operation of the operation lever and the operation switch.

Each outrigger device 9RF to 9LR is configured to be operable in the retracted posture shown in FIG. 1 and the deployed posture shown in FIG. In the tower crane 1, when the crane device 6 is used, the operator manually rotates each of the outrigger devices 9RF to 9LR in the retracted state in the horizontal direction to rotate the entire outrigger devices 9RF to 9LR in the chassis frame 2. It is positioned at an overhanging position facing the side. Next, the lateral outrigger cylinders 36RF to 36LR are driven by the operation of the operator's operation unit 11 or the remote control device 162 to operate and extend the tip side arm 95 in the starting direction. Further, by driving the vertical outrigger cylinders 37RF to 37LR and operating the base end side arms 93 of the outrigger devices 9RF to 9LR in the prone direction to ground the tip end side arm 95, during work (during suspension). The tower crane 1 is designed to be stable.

The driver's seat 10 is for an operator (driver) to sit on the tower crane 1 during a traveling operation, and is provided so as to project rearward of the tower crane 1 via a link mechanism as shown in FIGS. 1 and 2. ..
The operation unit 11 is provided at the rear end of the tower crane 1, and is an operation panel on which a pair of left and right traveling operation levers and a plurality of operation switches arranged in front of the driver's seat 10 and on the left side of the rear end are arranged. It has (not shown) and a plurality of operation levers (not shown) provided on the right side of the operation panel.

The plurality of operating levers are the outrigger switching control valve 82 of the control valve 15c, the swivel switching control valve 83, the boom expansion / contraction switching control valve 84, the winch switching control valve 85, and the boom undulating switching control valve shown in FIG. Each spool in 86 is operated directly.
Each of the above operating levers is provided corresponding to each of the various hydraulic actuators, and the hydraulic actuator corresponding to the operating lever can be driven in the direction of tilting from the neutral position.

Specifically, each of the above operating levers includes a lever for operating the left-turning operation and the right-turning operation of the crane device 6, a lever for operating the expansion / contraction operation of the undulating boom 7 and the bending boom 8, a hoisting operation of the hook 14. The lever includes a lever for operating the hoisting operation, and a lever for operating the undulating operation of the undulating boom 7 and the bending boom 8.
The plurality of operation switches are a crane operation-outrigger operation changeover switch, an undulating boom changeover switch, a telescopic boom changeover switch, a hook fixing switch, and an outrigger device for selecting an outrigger device to be operated from the outrigger devices 9RF to 9LR. It includes a device selection switch, an outrigger operation switch for operating the selected outrigger device, and the like.

The crane operation-outrigger operation selector switch is a switch for switching between a crane mode for enabling the operation of the crane device 6 and an outrigger mode for enabling the operation of the outrigger devices 9RF to 9LR.
Further, the undulating boom 7 changeover switch has an undulating boom undulating operation mode for enabling the undulating boom 7 and a bending boom undulating operation mode for enabling the undulating boom 8 in the crane mode. It is a switch for switching.

Further, in the crane mode, the telescopic boom changeover switch switches between an undulating boom telescopic operation mode for enabling the undulating boom 7 to be telescopically operated and a bending boom telescopic operation mode for enabling the undulating boom 8 to be telescopically operated. It is a switch for.
By each of the mode changeover switches, the traveling device 3, the crane device 6, and the outrigger device 9 and the undulating boom 7 and the bending boom 8 in the crane mode are configured so as not to operate at the same time for safety.

The winch 12 projects at a substantially central position on the rear end surface of the undulating boom 7. Then, the tower crane 1 guides the wire rope 13 from the winch 12 to the tip of the bending boom 8 via the first sheave 44 and the second sheave 45. Then, via a third sheave 46 provided at the upper part of the tip portion and a fourth sheave (not shown) provided below the third sheave 46 and inside the tip of the bending boom 8. The hook 14 is suspended from the tip of the bent boom 8 by hanging around the hook 14.

On the other hand, the driving unit 15 has an engine 15a shown in FIG. 3, a pressure oil supply device 15b driven by the engine 15a as a drive source, and pressure oil supplied from the pressure oil supply device 15b inside the housing. It is provided with a control valve 15c for switching and controlling the oil passages of the above.
Further, as shown in FIGS. 1 to 3, the tower crane 1 includes turning of the column 5, expansion and contraction of the undulating boom 7 and the bending boom 8, hoisting and lowering of the winch 12, and undulating boom 7 and the bending boom 8. It is equipped with a hydraulic actuator for undulating.

That is, the tower crane 1 includes a turning hydraulic motor 30, an undulating boom expansion / contraction hydraulic cylinder 31, a bending boom expansion / contraction hydraulic cylinder 32, a winch hydraulic motor 33, an undulation boom undulation hydraulic cylinder 34, and a bending boom undulation hydraulic cylinder. A cylinder 35 is provided.
Furthermore, the tower crane 1 includes a traveling motor 38 as a hydraulic actuator for driving the traveling device 3.

As shown in FIG. 3, the undulating boom undulating hydraulic cylinder 34 is composed of a pair of hydraulic cylinders of a first undulating boom undulating hydraulic cylinder 34R and a second undulating boom undulating hydraulic cylinder 34L.
Further, the bending boom undulating hydraulic cylinder 35 is composed of a pair of hydraulic cylinders of a first bending boom undulating hydraulic cylinder 35R and a second bending boom undulating hydraulic cylinder 35L.

Then, as shown in FIG. 3, these hydraulic actuators 30, 31, 32, 33, 34 and 35 all operate by supplying pressure oil from the pressure oil supply device 15b via the control valve 15c. It is configured in. In addition, each of the horizontal outrigger cylinders 36RF to 36LR and the vertical outrigger cylinders 37RF to 37LR are configured to operate by supplying pressure oil from the pressure oil supply device 15b via the control valve 15c.

On the other hand, as shown in FIG. 3, the pressure oil supply device 15b includes a hydraulic pump 60 driven by the engine 15a as a drive source, a left discharge port 61L, a right discharge port 61R, a main pipeline 62, and a return pipeline 63. And a tank 64.
Further, the control valve 15c includes a crane switching control valve 80, an accelerator cylinder 81, an outrigger device switching control valve 82, a swivel switching control valve 83, a boom expansion / contraction switching control valve 84, and a winch switching control. A valve 85 and a boom undulating switching control valve 86 are provided. Further, a horizontal outrigger cylinder switching valve 87, a vertical outrigger cylinder switching valve 88, a traveling switching control valve 89, a first electromagnetic switching valve 820, a second electromagnetic switching valve 840, and a third electromagnetic switching valve. It is equipped with 860.

The pressure oil discharged from the hydraulic pump 60 is supplied to the traveling switching control valve 89, and the supplied pressure oil passes through the traveling switching control valve 89 when the traveling operation lever is in the neutral state. It flows into the main pipeline 62 and is supplied to the control valve 15c via the main pipeline 62. Further, the pressure oil discharged from the hydraulic pump 60 is returned to the tank 64 via the return pipe 63.

The crane switching control valve 80 includes a main relief valve (unload valve) 180, an unload valve operating solenoid 181 and a hook fixing relief valve 182 provided between the main pipeline 62 and the return pipeline 63. And have.
The unload valve operating solenoid 181 is in either the ON state or the OFF state according to the operation signal Uo from the controller 160. Then, when the ON state is set, the main relief valve 180 is opened so that the main pipe line 62 and the return pipe line 63 communicate with each other. In the example shown in FIG. 3, the pressure oil discharged from the hydraulic pump 60 is passed through the return pipeline 63 without passing through the switching control valve 89 for traveling and the switching control valve 80 for the crane, and the tank 64. It is designed to return to. That is, it is possible to change the operating state of the hydraulic pump 60 to an unloading state (no-load operating state) in which the pressure oil circulates with no load.

The hook fixing relief valve 182 includes a hook relief solenoid 182a and a hook relief valve 182b.
The hook relief solenoid 182a is in either the ON state or the OFF state according to the operation signal Hr from the controller 160 in response to the operation of the hook fixing switch in the operation unit 11 or the remote control device 162 by the manual operation of the operator. It becomes. Then, in the ON state, the pressure oil oil passage from the main pipeline 62 is switched to the oil passage through which the pressure oil flows through the hook relief valve 182b.

Here, the hook relief valve 182b has a low set pressure Ps (Pm> Ps) whose set relief pressure is lower than the main set pressure Pm which is the relief pressure during normal operation. Therefore, by operating the hook relief valve 182b with the hook relief solenoid 182a turned on, it is possible to limit the upper limit of the pressure oil pressure to the low set pressure Ps.
As a result, while the hook fixing switch is ON, the hoisting operating pressure of the hook 14 is limited to a low voltage to prevent damage to the hook storage bracket 17 that fixes the hook 14.

The accelerator cylinder 81 operates the piston rod of the accelerator cylinder 81 in response to the accelerator control signal Vctr from the controller 160 according to the accelerator operation amount of the remote control device 162 or the operation unit 11. The operating position signal of the piston rod is input to the controller 160, and the controller 160 can control the rotation speed of the engine 15a to a desired rotation speed according to the operating position of the accelerator cylinder 81. The amount of pressure oil discharged from the hydraulic pump 60 increases as the rotational speed of the engine 15a is increased by operating the accelerator.

The switching control valve 82 for the outrigger device is operated by the operation lever or the operation signal Actr1 from the controller 160 in response to the operation signal Rctr from the remote control device 162, and the lateral outrigger cylinders 36RF to 36LR of each outrigger device 9RF to 9LR. And each vertical outrigger cylinder 37RF to 37LR is lubricated with pressure oil.
The first electromagnetic switching valve 820 is a control valve that selects either the horizontal outrigger cylinders 36RF to 36LR or the vertical outrigger cylinders 37RF to 37LR of the outrigger devices 9RF to 9LR as the refueling destination of the pressure oil.

The pressure oil flowing out from the outrigger switching control valve 82 first flows into the first electromagnetic switching valve 820. The first electromagnetic switching valve 820 is the lateral outrigger cylinders 36RF to 36LR or each according to the switching control signal Actr2 from the controller 160 by the operation of the outrigger changeover switch (not shown) in the operation unit 11 manually operated by the operator. The oil passage of the pressure oil for the vertical outrigger cylinders 37RF to 37LR is switched.

The lateral outrigger cylinder switching valve 87 is a control valve that selects whether or not to supply pressure oil for each of the lateral outrigger cylinders 36RF to 36LR.
The lateral outrigger cylinder switching valve 87 responds to the operation signals Actr3 to 6 from the controller 160 by the operation of the lateral outrigger cylinder selection switch (not shown) in the operation unit 11 manually operated by the operator, and the lateral outrigger cylinders 36RF to 36LR. Switch the oil passage of the pressure oil to.

The vertical outrigger cylinder switching valve 88 is a control valve that selects whether or not to supply pressure oil for each of the vertical outrigger cylinders 37RF to 37LR.
The vertical outrigger cylinder switching valve 88 is provided with the vertical outrigger cylinders 37RF to 37LR in response to the operation signals Actr7 to 10 from the controller 160 operated by the vertical outrigger cylinder selection switch (not shown) in the operation unit 11 manually operated by the operator. Switch the oil passage of the pressure oil to.

The swivel switching control valve 83 inflows pressure oil into the swivel hydraulic motor 30 according to the operation amount of the operation lever of the operation unit 11 or the operation signal Tctr from the controller 160 in response to the operation of the remote control device 162. do.
The boom expansion / contraction switching control valve 84 responds to the operation signal Bctr1 from the controller 160 in response to the operation of the operation lever of the operation unit 11 or the operation of the remote control device 162, and the undulation boom undulation hydraulic cylinder 34 and the bending boom undulation. Pressure oil is supplied to the hydraulic cylinder 35.

The second electromagnetic switching valve 840 is a control valve that selects either the undulating boom expansion / contraction hydraulic cylinder 31 or the bending boom expansion / contraction hydraulic cylinder 32 as the oil supply destination of the pressure oil.
The pressure oil flowing out from the boom expansion / contraction switching control valve 84 first flows into the second electromagnetic switching valve 840.
The second electromagnetic switching valve 840 is switched from the controller 160 according to the operation of the telescopic boom changeover switch (not shown) in the operation unit 11 manually operated by the operator or according to the operation signal Rctr from the remote control device 162. The oil passage of the pressure oil for the undulating boom expansion / contraction hydraulic cylinder 31 or the bending boom expansion / contraction hydraulic cylinder 32 is switched according to the control signal Bctr3.

The winch switching control valve 85 flows pressure oil into the winch hydraulic motor 33 in response to an operation signal Wctr from the controller 160 in response to the operation of the operation lever of the operation unit 11 or the operation of the remote control device 162. ..
The boom undulation switching control valve 86 includes the undulation boom undulation hydraulic cylinder 34 and the bending boom undulation in response to the operation signal Bctr2 from the controller 160 in response to the operation of the operation lever of the operation unit 11 or the operation of the remote control device 162. Pressure oil is supplied to the hydraulic cylinder 35.

The third electromagnetic switching valve 860 is a control valve that selects either the undulating boom undulating hydraulic cylinder 34 or the bending boom undulating hydraulic cylinder 35 as the oil supply destination of the pressure oil.
The pressure oil flowing out from the boom undulating switching control valve 86 first flows into the third electromagnetic switching valve 860.
The third electromagnetic switching valve 860 is switched from the controller 160 according to the operation of the undulating boom changeover switch (not shown) in the operation unit 11 or the operation signal Rctr from the remote control device 162 by the manual operation of the operator. The oil passage of the pressure oil for the undulating boom undulating hydraulic cylinder 34 or the bending boom undulating hydraulic cylinder 35 is switched according to the control signal Bctr4.

Each of the switching control valves 82 to 86 and the accelerator cylinder 81 is provided with a differential transformer (not shown), and the switching positions L1 to each of the switching control valves 82 to 86 and the accelerator cylinder 81 detected by the respective differential transformers are provided. The detection signal of L6 (hereinafter, may be referred to as “switching position signal”) is input to the controller 160 as shown in FIG. That is, the controller 160 can grasp the operation contents (switching positions) of the switching control valves 82 to 86 and the accelerator cylinder 81 by the switching position signals L1 to L6.

As shown in FIG. 3, the traveling motor 38 includes two traveling motors 38L and 38R corresponding to the left and right tracks of the traveling device 3. Each of the traveling motors 38L and 38R operates independently by individually supplying the pressure oil from the pressure oil supply device 15b via the travel switching control valve 89.
As a result, the tower crane 1 can drive the traveling device 3 and travel in the forward or backward direction by operating the pressure oil supply device 15b and simultaneously moving the pair of left and right traveling operation levers forward or backward. .. Further, when turning right or left, the corresponding left and right tracks can be individually driven by individually moving the pair of left and right traveling operation levers forward or backward, so that the vehicle can simply turn by the speed difference between the left and right.

Returning to FIGS. 1 and 2, the control box 16 includes the controller 160 shown in FIG. 4 inside the control box 16. Although not shown, a receiver 161 is provided above the control box 16.
The receiver 161 is connected to the controller 160 via a signal line (not shown). The receiver 161 receives the remote control signal Rctr wirelessly transmitted from the remote control device 162, and inputs the received remote control signal Rctr to the controller 160 via the signal line.

As shown in FIG. 4, the controller 160 is input with an operation signal Ctr from the operation unit 11, a remote control signal Rctr from the remote control device 162, switching position signals L1 to L6 from various switching control valves, and the like. .. Then, the controller 160 operates and controls various electric devices such as an oil passage switching solenoid valve included in the tower crane 1 in response to these input signals.
Although not shown, the controller 160 includes a CPU (Central Processing Unit) that performs various arithmetic processes based on a predetermined control program, and a ROM (Read Only Memory) that stores various data including the control program. , A RAM (Random Access Memory) for storing data read from a ROM or the like and calculation results required in the calculation process of the CPU, and a timer for time measurement are provided.

The controller 160 further includes an input / output I / F (interface) that mediates data input / output to each device including the receiver 161, the operation unit 11, the remote control device 162, the control valve 15c, and the like described above. , Equipped with various internal and external buses for data transfer. Various internal and external buses are connected to the CPU, ROM, RAM, and timer, and the above devices are connected to this bus via input / output I / F.

Then, when the power is turned on, the system program such as the BIOS stored in the ROM or the like loads various control programs stored in the ROM in advance into the RAM, and the CPU performs according to the instruction described in the program loaded in the RAM. By performing arithmetic processing by making full use of various resources, each function for operating and controlling each of the above devices can be realized on the software.

(Each outrigger device 9RF-9LR)
Hereinafter, each outrigger device 9RF to 9LR will be described in detail. Since each of the outrigger devices 9RF to 9LR has the same configuration, the outrigger devices 9 will be described below without particular distinction. Similarly, the horizontal outrigger cylinders 36RF to 36LR will be referred to as “horizontal outrigger cylinders 36”, and the vertical outrigger cylinders 37RF to 37LR will be referred to as “vertical outrigger cylinders 37” without particular distinction.

As shown in FIG. 5, the outrigger device 9 includes a base bracket 90 mounted on the upper surface of the chassis frame 2. A cylindrical rotation support portion 92 is provided on the base end side of the base bracket 90. The rotation support portion 92 is pivotally supported so as to be rotatable around a vertical axis provided on the upper surface of the chassis frame 2, and the operator manually removes a removable fixing pin (not shown) and manually removes the outrigger device 9. By turning in the horizontal direction, the entire outrigger device 9 can be turned to the overhanging position toward the side of the chassis frame 2.

The overhanging position of the outrigger device 9 is securely fixed by inserting the fixing pin into the overhanging position fixing hole (not shown) at the overhanging position. That is, from the retracted posture shown in FIG. 1, the outrigger devices 9 are positioned so as to project laterally with respect to the chassis frame 2 by manually rotating the four outrigger devices 9 in the horizontal direction. It is configured to be positioned.

In the outrigger device 9, as shown in FIGS. 5, 6 (a) and 6 (b), a plate-shaped bracket portion 91 is formed integrally with the rotation support portion 92 on the base bracket 90. At the lower part of the bracket portion 91, the proximal end portion of the proximal end side arm 93 is rotatably and pivotally supported around the horizontal first rotating shaft 91b. A plate-shaped center bracket 94 is integrally fixed to the tip of the base end side arm 93 with the tip end of the base end side arm 93.

Further, the second mounting arm 94a of the center bracket 94, the first mounting arm 91a provided on the bracket portion 91 of the base bracket 90, and both ends of the vertical outrigger cylinder 37 are respectively the first rotating shaft 91b. It is rotatably pivotally supported around a second rotating shaft 91c and a third rotating shaft 94b that are parallel to each other. By expanding and contracting the vertical outrigger cylinder 37, it is possible to extend the outrigger device 9 when it touches the ground and to accommodate it when it is retracted.

Further, in the outrigger device 9, the tip end side arm 95 is pivotally supported at the tip end portion of the center bracket 94 so that the base end portion thereof can be rotated around a support shaft 94c parallel to the first rotation shaft 91b. ..
As shown in FIGS. 5, 6 (a) and 6 (b), the tip side arm 95 is formed in the square tubular outer box 96 and the outer box 96 so as to be expandable and contractible along the longitudinal direction of the outer box 96. It has a square tubular inner box 97 that is fitted. A float 98 is pivotally supported at the tip of the inner box 97 so as to be rotatable around a horizontal axis. Here, the outer box 96 and the inner box 97 are made of metal (for example, carbon steel for machine structure) and have the rigidity required for an outrigger device.

The outrigger device 9 is further provided with a lateral outrigger cylinder 36 inside the outer box 96 and the inner box 97 in a posture parallel to the longitudinal direction of the outer box 96 and the inner box 97. The outrigger device 9 further includes a pair of plate-shaped boomerang type links 100 (hereinafter, abbreviated as “BM type link 100”) arranged inside the center bracket 94 so as to face each other in the axial direction of the support shaft 94c.

The lateral out-trigger cylinder 36 includes a cylinder tube 36a, a piston (not shown) arranged inside the cylinder tube 36a, a cylinder rod 36b connected to the piston, and a substantially "J-shaped" pressure oil supply in a side view. It has an exhaust pipe 36c and a block 36d having a substantially rectangular shape in a side view.
One end of the pressure oil supply / discharge pipe 36c is connected to the lower end of the block 36d, and a first pressure oil supply / discharge port (not shown) provided in the cylinder cap portion 36aa of the cylinder tube 36a via the block 36d. It is connected to the. On the other hand, the other end of the pressure oil supply / discharge pipe 36c is connected to a second pressure oil supply / discharge port (not shown) provided near the tip of the cylinder tube 36a (close to the end on the rod side). .. The pressure oil discharged from the outrigger switching control valve 82 is supplied into the cylinder tube 36a through the second pressure oil supply / discharge port via the first electromagnetic switching valve 820, thereby reducing the lateral outrigger cylinder 36. On the other hand, the pressure oil in the cylinder tube 36a is poured into the pressure oil supply / discharge pipe 36c through the second pressure oil supply / discharge port and supplied into the cylinder tube 36a through the first pressure oil supply / discharge port. The cylinder 36 is extended.

One end of the BM type link 100 is rotatably and pivotally supported around the first link shaft 100a parallel to the support shaft 94c at a position near the upper end of the base portion of the second mounting arm 94a of the center bracket 94. There is.
Further, the cylinder cap portion 36aa of the cylinder tube 36a is rotatably pivotally supported at the other end of the BM type link 100 around a second link shaft 100b parallel to the first link shaft 100a.

The BM type link 100 has a one-pronged boomerang shape, and has a first wing portion, a second wing portion, and a curved portion connecting them. The BM type link 100 has a shape in which the lengths of the first wing portion on one end side and the second wing portion on the other end side are different so as to sandwich the curved portion. Specifically, the first wing portion is configured to be longer than the second wing portion.
Then, in the BM type link 100, in the retracted state of the outrigger device 9, the first wing portion extends substantially horizontally from the mounting position on the one end side to the tip end side arm 95 side, and the second wing portion sandwiches the curved portion. The portion extends diagonally to the lower right and is arranged in a posture of being connected to the cylinder cap portion 36aa. That is, the BM type link 100 is arranged in a posture of being convex diagonally upward to the right so that the attachment position of the other end portion, which is lower than the attachment position of one end portion, can be reached.

On the other hand, the tip end portion (rod head portion) of the cylinder rod 36b of the lateral outrigger cylinder 36 is fixed at a position closer to the tip end of the inner box 97.
Further, as shown in FIGS. 6A and 6B and FIG. 7, the range from the position near the upper end of the pressure oil supply / discharge pipe 36c to the position in front of the curved portion near the lower end is the outer circumference of the cylinder tube 36a. The surface is covered with a square tubular pipe box 101 integrally formed by welding, for example.

Three first metal sliding pads 120A are predetermined in the longitudinal direction on the box surface 101a facing the outer peripheral surface of the pipe box 101 and the inner peripheral surface of the inner box 97 at the closest positions. It is installed with a gap. Each of these two first sliding pads 120A has a counterbore hole penetrating from the first sliding surface 121A of the first sliding pad 120A to the back surface. Further, a bolt hole penetrating from the front surface to the back surface is provided at the mounting position of the first sliding pad 120A on the box surface 101a of the pipe box 101. Then, the two first sliding pads 120A align their respective counterbore holes with the bolt holes, and the first bolt 122A causes the first sliding surface 121A to be placed on the box surface 101a. It is tightened and fixed in a state where it faces the inner peripheral surface of the inner box 97 with a slight gap.

Here, the seating surface depth of the counterbore is a depth that can accommodate the head of the first bolt 122A, and after tightening the first bolt 122A, the head of the first bolt 122A is counterbored. It fits in the hole and the head of the first bolt 122A does not protrude from the first sliding surface 121A.
Further, metal sliding pads 120B are provided on the front and back ends of the portions of the lateral outrigger cylinder 36 that face each other at the closest positions to the outer peripheral surface of the cylinder tube 36a and the inner peripheral surface of the inner box 97. A first mounting portion 102B and a second mounting portion 102C for mounting are provided. The first mounting portion 102B and the second mounting portion 102C are integrally provided with the cylinder tube 36a by welding in a posture in which the mounting surface faces the inner peripheral surface of the inner box 97. Then, on each of the mounting surfaces of the first and second mounting portions 102B and 102C, the second sliding pad 120B and the third sliding pad 120C are provided with a predetermined gap of three along the longitudinal direction. It is installed. The second sliding pad 120B and the third sliding pad 120C have the same configuration as the first sliding pad 120A. Further, bolt holes penetrating from the front surface to the back surface are provided at the attachment positions of the second sliding pad 120B and the third sliding pad 120C of the first attachment portion 102B and the second attachment portion 102C. .. Then, the three second sliding pads 120B align their respective counterbore holes with the bolt holes, and are placed on the mounting surface of the first mounting portion 102B by the second bolt 122B. The sliding surface 121B of the above is fastened and fixed in a state of facing the inner peripheral surface of the inner box 97 with a slight gap. Similarly, the three third sliding pads 120C align their respective counterbore holes with the bolt holes, and are placed on the mounting surface of the second mounting portion 102C by the third bolt 122C. The sliding surface 121C of No. 3 is tightened and fixed in a state where it faces the inner peripheral surface of the inner box 97 with a slight gap.

The first to third sliding pads 120A to 120C of the present embodiment are made of a metal member whose contact surface with the inner peripheral surface of the inner box 97 has a low friction coefficient.
That is, when the lateral outrigger cylinder 36 of the first embodiment expands and contracts, the inner box 97 has the first to third sliding pads 120A to 120C sandwiched between the inner peripheral surfaces of the inner box 97. It is configured to move within.

Here, since the lateral outrigger cylinder 36 is connected to the BM type link 100 and the direction of rotation is also around the support shaft 94c, the first to third sliding pads 120A to 120C are usually used during expansion and contraction. The force is applied only in the direction in which the cylinder is provided. When the tip end side arm 95 rotates and is in the deployed posture, the inner peripheral surface of the inner box 97 is pressed against the first sliding surface 121A of the first sliding pad 120A by gravity. Become.

Therefore, for example, even when the lateral outrigger cylinder 36 is extended while the inner box 97 is bent, the cylinder tube 36a inside the inner box 97 is inside the inner box 97 by the second and third sliding pads 120B and 120C. Since it does not rub directly against the peripheral surface and the pressure oil supply / discharge pipe 36c is protected by the pipe box 101, it is not crushed. In addition, since the frictional resistance can be reduced by the first to third sliding pads 120A to 120C, smooth movement is possible. This is because one end side of the lateral outrigger cylinder 36 is connected to the BM type link 100 as a free end, and therefore, when the tip end side arm 95 is flipped up to the first unfolded posture, the lateral outrigger cylinder 36 is reduced. The same applies to the operation of the cylinder tube 36a that occurs and the operation of the cylinder tube 36a that occurs when the lateral outrigger cylinder 36 extends to the first retracted posture as a reverse operation.

Further, the outrigger device 9 has a first posture holding pin 190 and a second posture for restraining and releasing the positions corresponding to the deployed posture and the retracted posture on the side surface of the center bracket 94 and the side surface of the outer box 96. A holding pin 191 is provided.
On both sides of the center bracket 94, first posture holding holes are provided at positions corresponding to the retracted posture (hereinafter, may be referred to as "first retracted posture") with respect to the rotation of the tip end side arm 95 in the undulating direction. 94Hh is provided. The first posture holding hole 94Hh penetrates the center bracket 94 coaxially in the width direction (support shaft 94c direction) in a perfect circle. Further, on both sides of the center bracket 94, the second and second positions corresponding to the unfolding posture (hereinafter, may be referred to as "first unfolding posture") due to the rotation of the tip end side arm 95 in the undulating direction. The posture holding holes 94HS and 94HL of No. 3 are provided. The second and third posture holding holes 94HS and 94HL penetrate the center bracket 94 coaxially in the width direction in a perfect circle. The first posture holding holes 94Hh and the second and third posture holding holes 94HS and 94HL are arranged apart from each other on the same circumference centered on the support shaft 94c of the tip end side arm 95 in the circumferential direction. ..

The second and third posture holding holes 94HS and 94HL are formed at positions in which each set corresponds to a plurality of first deployment postures (two postures in this example). That is, in the first embodiment, two postures can be set as the first deployment posture by rotating the tip end side arm 95 with respect to the base end side arm 93.
Of the second and third posture holding holes 94HS and 94HL, the second posture holding hole 94HS formed on the lower side is the minimum overhang shown in FIG. 8B of the two first deployed postures. It is formed at a position corresponding to the posture S1.

Further, of the second and third posture holding holes 94HS and 94HL, the third posture holding hole 94HL formed on the upper side is the maximum overhang posture U1 shown in FIG. 9 among the two first deployed postures. It is formed at the position corresponding to.
On the other hand, as shown in FIGS. 6B, 8 and 9, the outer box 96 has a fourth posture holding hole 96HF forming a perfect circle at a position corresponding to the first storage posture. It is provided along the width direction of. The fourth posture holding hole 96HF is provided at a position coaxial with the first posture holding hole 94Hh at a position corresponding to the first storage posture.

As a result, the fourth posture holding hole 96HF of the outer box 96 is the same as the first posture holding hole 94Hh centered on the support shaft 94c of the outer box 96 and the second and third posture holding holes 94HS and 94HL. It is placed on the circumference.
The first posture holding pin 190 has an outer diameter dimension that can be inserted into the first posture holding hole 94Hh, the second and third posture holding holes 94HS, 94HL with a slight gap, and a center bracket. It has a solid cylindrical shaft portion having a shaft length that can be penetrated over both surfaces of 94.

As a result, the first posture holding pin 190 causes the tip end side arm 95 to undulate at positions corresponding to the first retracted posture and the first deployed posture, and the fourth posture holding hole 96HF holds the first posture. It is inserted and removed when the center of the hole is coaxial with any of the holes 94Hh and the second and third posture holding holes 94HS and 94HL. Then, when the first posture holding pin 190 is inserted into any of the first posture holding holes 94Hh and the second and third posture holding holes 94HS and 94HL, the first retracted posture and the two first postures are inserted. At the position corresponding to the inserted posture holding hole in the deployed posture of, the rotation of the proximal end arm 93 and the distal end arm 95 is restrained, and the relative positions of the proximal end side arm 93 and the distal end side arm 95 are respectively. It is designed to be restrained. On the other hand, when the first posture holding pin 190 is pulled out from the posture holding hole, the restraint of the relative positions of the proximal end side arm 93 and the distal end side arm 95 is released, and the proximal end side arm 93 and the distal end side arm 95 are released from each other. It can be rotated.

Further, at a position near the tip of the tip side arm 95, as shown in FIGS. 5, 6 (b), 8 and 9, the inner box 97 is moved by sliding the inner box 97 with respect to the outer box 96. A second posture holding pin 191 is provided to restrain and release the deployed posture and the retracted posture.
Hereinafter, the unfolding posture of the inner box 97 due to the sliding movement of the inner box 97 may be referred to as a “second unfolding posture”, and the retracting posture of the inner box 97 due to the sliding movement of the inner box 97 may be referred to as a “second retracting posture”. May be described. In addition, when it is simply described as "retracted posture", it is assumed that at least the tip end side arm 95 indicates the state of the first retracted posture and the second retracted posture.

At a position near the tip of the outer box 96, there is a fifth posture holding hole 96H that forms a perfect circle coaxially with the outer box 96 in the width direction, which is common to the second retracted posture and the second deployed posture. It is provided so as to penetrate both sides of the outer box 96.
Further, in the inner box 97, the inner box 97 is coaxially placed in the width direction (support axis 94c direction) at positions corresponding to the second retracted posture and the second deployed posture, and the inner box 97 is made into a perfect circle (or the sliding direction is shortened). The sixth, seventh, and eighth posture holding holes 97HL, 97HM, and 97HS penetrating through the inner box 97 are provided through the inner box 97. The sixth, seventh, and eighth posture holding holes 97HL, 97HM, and 97HS each correspond to a second storage posture and a plurality of second deployment postures (two deployment postures in the first embodiment). It is formed at the position.

Further, the eighth posture holding holes 97HS and the sixth and seventh posture holding holes 97HL and 97HM are arranged apart on the same straight line along the sliding axis of the inner box 97.
That is, in the first embodiment, the position corresponding to the second storage posture (which is also the position corresponding to the overhanging posture S2 at the time of maximum reduction shown in FIG. 8B and FIG. 11) is closer to the tip of the inner box 97. At the position of, an eighth posture holding hole 97HS is provided so as to penetrate in the width direction.

The second posture holding pin 191 has an outer diameter dimension that can be inserted into the eighth posture holding hole 97HS and the sixth and seventh posture holding holes 97HL and 97HM with a slight gap, and an outer. It has a solid cylindrical shaft portion having a shaft length that can be penetrated over both sides of the box 96.
As a result, the second posture holding pin 191 has the eighth posture holding hole 97HS and the sixth and seventh posture holding holes 97HL and 97HM at positions corresponding to the second retracted posture and the second deployed posture. It is inserted and removed from either. Then, when the second posture holding pin 191 is inserted into any of the eighth posture holding holes 97HS and the sixth and seventh posture holding holes 97HL and 97HM, the second retracted posture and the two second postures are inserted. The expansion and contraction of the inner box 97 is restrained by coaxially penetrating the outer box 96 and the inner box 97 at the position corresponding to the inserted posture holding hole in the unfolded posture of the outer box 96 and the inner box 97. The position is constrained. On the other hand, when the second posture holding pin 191 is pulled out from the posture holding hole, the restraint of the relative positions of the outer box 96 and the inner box 97 is released, and the inner box 97 can be expanded and contracted. ..

Further, as shown in FIGS. 5, 6 (b), 8 and 9, the outrigger device 9 is located near the proximal end of the surface of the proximal end side arm 93 facing the distal end side arm 95 in the retracted posture. Is provided with a resin or rubber cushion 99. The cushion 99 has a role as a cushioning material when the outrigger device 9 is stored in the first storage posture.
Furthermore, as shown in FIGS. 6 (a) and 6 (b) and FIG. 12, the outrigger device 9 applies a bending load due to a reaction force from the BM type link 100 to the inner peripheral surface of the base end portion of the outer box 96. A first blocking member 103 is provided to prevent the occurrence of defects such as the cylinder tube 36a.

The first blocking member 103 has a first seat 103a and a second seat 103b.
The first seat 103a is provided on the inner peripheral surface of the first base end portion 96a on the pressure oil supply / discharge pipe 36c side with the lateral outrigger cylinder 36 of the outer box 96 in the retracted posture of the outrigger device 9. .. Further, the first seat 103a is provided so that the first seat surface 130a faces the side surface of the block 36d with a slight gap.

Further, the first seat 103a has a rectangular shape when viewed from above, and has a substantially regular rectangular upper portion and a semi-trapezoidal lower portion when viewed from the side. The upper part of the substantially regular quadrangle is provided with a curved surface at the upper corner on the side facing the block 36d. Further, the lower portion of the semi-trapezoidal shape has a first inclined surface 131a that is inclined obliquely downward toward the inner peripheral surface side of the first base end portion 96a on the first seat surface 130a side. Further, although not shown, two seats 103a have a predetermined gap along the width direction of the outer box 96 on the surface of the first base end portion 96a on the side that comes into contact with the inner peripheral surface. Bolt holes are provided. On the other hand, at the mounting position of the first seat 103a of the first base end portion 96a, two bolt holes are provided at positions corresponding to the bolt holes of the first seat 103a. The first seat 103a is fastened and fixed by two fourth bolts 132 from the outer peripheral surface side of the outer box 96.

The second seat 103b is provided on the inner peripheral surface of the second base end portion 96b on the side opposite to the pressure oil supply / discharge pipe 36c with the lateral outrigger cylinder 36 of the outer box 96 sandwiched between the outrigger devices 9 in the retracted posture. Has been done. Further, the second seat 103b is provided so that the second seat surface 130b is in contact with the outer peripheral surface of the cylinder cap portion 36aa.
Further, the second seat 103b has a regular quadrangular shape in the top view, and has a regular quadrangular upper portion and a semi-trapezoidal lower portion in the side view. The lower portion of the semi-trapezoidal shape has a second inclined surface 131b that is inclined obliquely downward toward the inner peripheral surface side of the second base end portion 96b on the side of the second seat surface 130b.

The details of the role of the first blocking member 103 will be described later.
(Deployment operation from the first storage posture to the first deployment posture)
Next, the deployment operation of the tip end side arm 95 of the outrigger device 9 of the first embodiment from the first retracted posture to the first deployed posture will be described.
In order to shift the tip end arm 95 from the first retracted posture to the first deployed posture, it is first necessary to release the restraint state in the first retracted posture. That is, as shown in FIG. 8A, the first posture holding pin 190 inserted into the first and fourth posture holding holes 94Hh and 96HF is pulled out. On the other hand, in the example of FIG. 8A, the second posture holding pin 191 inserted into the fifth and eighth posture holding holes 96H and 97HS is left as it is. That is, the tip end side arm 95 is made rotatable and the inner box 97 is restrained in a state where the inner box 97 cannot be slidably moved.

In this state, when the operator operates the operation unit 11 or the remote control device 162 to reduce the lateral outrigger cylinder 36, the sliding operation of the inner box 97 is restricted, so that the cylinder tube 36a is placed on the cylinder rod 36b side. A force is generated to attract the cylinder. By this force, as shown in FIG. 8B, the cylinder tube 36a moves toward the cylinder rod 36b, and the lateral outrigger cylinder 36 moves around the second link shaft 100b on the other end side of the BM type link 100. And it rotates counterclockwise. Then, the other end side of the BM type link 100 is pulled inside the outer box 96 and the inner box 97, and the entire tip side arm 95 rotates around the support shaft 94c and counterclockwise. At this time, due to the boomerang shape of the BM type link 100 (curved shape that is convex diagonally upward to the right), the BM type link 100 collides with the base end portion of the outer box 96 with respect to the rotation of the tip side arm 95. It is pulled inward without.

In the state of FIG. 8B, the fourth posture holding hole 96HF just overlaps with the second posture holding hole 94HS. That is, as the first unfolding posture by rotating the tip end side arm 95, the posture is unfolding at a position corresponding to the minimum overhanging posture S1. In the first embodiment, further deployment is possible from this posture, and by continuously reducing the lateral outrigger cylinder 36, as shown in FIG. 9, the entire tip side arm 95 is further rotated counterclockwise. By moving, the fourth posture holding hole 96HF overlaps with the third posture holding hole 94HL. That is, the maximum overhanging posture U1 is set as the first unfolding posture due to the rotation of the tip end side arm 95.
Here, in order to shift from the first retracted posture to the first deployed posture, the lateral outrigger cylinder 36 is in a state of being extended by a predetermined length instead of being in the minimum contracted state in the first retracted posture. .. That is, there is a margin for performing the reduction operation necessary for shifting to the first deployment posture.

(Deployment operation from the second retracted posture to the second unfolded posture)
Next, the deployment operation of the tip end side arm 95 of the outrigger device 9 of the first embodiment from the second retracted posture to the second deployed posture will be described.
In FIG. 9, the tip end side arm 95 is in the first deployed posture, and the inner box 97 is restrained in the fully contracted state, and is in the second retracted posture.

In such a state, in order to shift the tip end arm 95 from the second retracted posture to the second deployed posture, it is first necessary to set the released state in the first deployed posture to the restrained state. That is, in the first deployed posture of FIG. 9, as shown in FIG. 10, the first posture holding pin 190 is inserted into the third and fourth posture holding holes 94HL and 96HF. On the other hand, the second posture holding pin 191 inserted into the fifth and eighth posture holding holes 96H and 97HS is pulled out. As a result, the restrained state of the slide movement of the inner box 97 is released. That is, the tip end side arm 95 is restrained in a state in which it cannot rotate around the support shaft 94c, and the inner box 97 is made in a state in which it can be slidably moved.

In this state, when the operator operates the operation unit 11 or the remote control device 162 to extend the lateral outrigger cylinder 36, the rotation operation of the tip side arm 95 is restricted, so that the cylinder tube 36a is a BM type. It is fixed to the center bracket 94 via the link 100. Therefore, the cylinder rod 36b is extended. Since the tip of the cylinder rod 36b is fixed at a position closer to the tip of the inner box 97, the force applied by the extension of the cylinder rod 36b causes the inner box 97 to move in the extension direction as shown in FIG. Slide to move.

In this way, the transition from the second storage posture to the second deployment posture is made. In the example shown in FIG. 10, the second unfolding posture is the overhanging posture U2 at the time of maximum extension. In this state, by inserting the second posture holding pin 191 into the fifth and eighth posture holding holes 96H and 97HS, it is possible to restrain the state of the overhanging posture U2 at the time of maximum extension.

(Grounding operation of outrigger device 9)
Next, the grounding operation of the outrigger device 9 of the first embodiment will be described.
As shown in FIG. 10, after the maximum overhang position of the tip side arm 95 is set to the second unfolded posture, the second posture holding pin 191 is inserted into the fifth and sixth posture holding holes 96H and 97HL. , Constrain the state of this second deployment posture. That is, the tip end side arm 95 is constrained to the state of the maximum overhanging posture U1 and the overhanging posture U2 at the time of maximum extension.

In this state, when the operator operates the operation unit 11 or the remote control device 162 to extend the vertical outrigger cylinder 37, the vertical outrigger cylinder 37 rotates second on the base bracket 90 side as shown in FIG. It rotates around the shaft 91c and clockwise. Along with this, the base end side arm 93 rotates together with the tip end side arm 95 around the first rotation shaft 91b on the base bracket 90 side and clockwise. Then, as shown by a solid line in FIG. 11, the first unfolded posture and the second unfolded posture are provided at the tip of the inner box 97 in a state of being the maximum overhang posture U1 and the overhang posture U2 at the time of maximum extension. The float 98 touches the ground.

The second unfolded posture of the inner box 97 may be the overhanging posture M at the time of intermediate extension, as shown by the dotted line in FIG. 11, depending on the shape and height of the ground to be grounded. Further, in the first embodiment, the inner box 97 can be grounded even in the state of the second retracted posture (deployed posture S2 at the time of maximum reduction).

(First blocking member 103)
Next, the role of the first blocking member 103 will be described in detail.
Here, for example, as shown in FIG. 13A, the first posture holding pin 190 is pulled out, the lateral outrigger cylinder 36 is extended with the second posture holding pin 191 inserted, and the tip side arm 95 is extended. It is assumed that the outrigger device 9 is placed in the retracted posture by rotating the outer box 96 in the prone direction until it comes into contact with the cushion 99. Then, from this state, when the lateral outrigger cylinder 36 is further extended and operated due to an erroneous operation by the operator or the like, a bending load is applied to the cylinder tube 36a.

This also applies when the lateral outrigger cylinder 36 is extended and operated while the outrigger device 9 is in the retracted posture and the first posture holding pin 190 and the second posture holding pin 191 are inserted. Further, in this state, when the lateral outrigger cylinder 36 is reduced and operated, a bending load is applied to the cylinder tube 36a in the direction opposite to that when the cylinder tube 36a is extended.
Specifically, as shown in FIG. 13B, when the lateral outrigger cylinder 36 is further extended in a situation where the tip end side arm 95 cannot rotate in the down direction, the BM type link 100 with respect to the cylinder extension thrust Fc. The link reaction force Fa received from is generated. Then, the first bending moment MxL, which is the result of multiplying the X-direction component Fxa of the link reaction force Fa by the distance L in FIG. 13B, is applied to the cylinder cap portion 36aa of the cylinder tube 36a. Here, the distance L is defined by the support point Ps on the inner peripheral surface of the inner box 97 that supports the X-direction component Fxa of the link reaction force Fa and the center of the second link shaft 100b on the proximal end side of the cylinder tube 36a. It is the straight line distance between heights (distance between the fulcrum and the force point).

When the first bending moment MxL is applied to the cylinder cap portion 36aa, for example, as shown in FIG. 13B, especially when there is no support in the first bending direction (X direction), the first bending direction. There is a possibility that a large load will be applied to the cylinder tube 36a and thus the parts around the cylinder tube 36a will be defective.
On the other hand, although not shown, when the lateral outrigger cylinder 36 contracts when the front end arm 95 is restrained in a retracted posture in a retracted posture and the front end arm 95 cannot rotate and expand / contract, the cylinder contraction thrust (-). A link reaction force (-Fa) received from the BM type link 100 is generated against Fc). As a result, a second bending moment (−MxL) in the direction opposite to the first bending moment MxL is applied to the cylinder cap portion 36aa of the cylinder tube 36a.

In this case as well, if there is no support in the second bending direction (-X direction), a large load may be applied in the second bending direction, causing a problem in the cylinder tube 36a and the surrounding parts. be.
Therefore, in the first embodiment, as shown in FIG. 12, a first seat 103a is provided on the inner peripheral surface of the first base end portion 96a of the outer box 96, and the second base end portion 96b of the outer box 96 is provided. A second seat 103b was provided on the inner peripheral surface of the.

As a result, when the first bending moment MxL is generated, as shown in FIG. 14A, the first seat surface 130a of the first seat 103a comes into contact with the cylinder cap portion 36aa and the link reaction force. Supports the X-direction component Fxa of Fa. As a result, the reaction force Fxs is generated to reduce the load, and it is possible to avoid the cylinder tube 36a and the peripheral parts from being defective.

Further, when a second bending moment (-MxL) in the opposite direction is generated, although not shown, the second seat surface 130b of the second seat 103b is the X-direction component of the link reaction force (-Fa). By supporting (-Fxa), it is possible to prevent the cylinder tube 36a and the peripheral parts from being defective.
When the tip end side arm 95 is rotated from the retracted posture to the first deployed posture, the cylinder cap portion 36aa becomes the second seat 103b of the second seat 103b due to the weight of the outer box 96 and the inner box 97. It is pressed against the seat surface 130b of. At this time, if there is no second seat 103b, rattling occurs. That is, the second seat 103b also has a function of preventing rattling when the tip end side arm 95 is rotated.

On the other hand, as shown in FIG. 14B, the tip side arm 95 is in the first unfolded posture and the second unfolded posture, and the first posture holding pin 190 and the second posture holding pin 191 are inserted. Then, it is assumed that the lateral outrigger cylinder 36 is extended. In this case, since the angle θ between the extension direction of the lateral outrigger cylinder 36 and the BM type link 100 becomes small, the first bending moment MxL becomes small, and there is a concern that a large load as described above is applied. Does not occur. This also applies when the lateral outrigger cylinder 36 is reduced and operated under the same conditions.

Here, in the first embodiment, the tower crane 1 corresponds to a working machine, the BM type link 100 corresponds to a link member for power transmission, and the lateral outrigger cylinder 36 corresponds to a telescopic actuator.
Further, in the first embodiment, the first posture holding pin 190, the first posture holding hole 94Hh, and the second and third posture holding holes 94HS, 94HL correspond to the first posture holding means.

Further, in the first embodiment, the second posture holding pin 191 and the eighth posture holding hole 97HS, and the sixth and seventh posture holding holes 97HL and 97HM correspond to the second posture holding means.
Further, in the first embodiment, the first posture holding holes 94Hh and the second and third posture holding holes 94HS and 94HL correspond to the first posture holding holes, and the eighth posture holding holes 97HS and the second posture holding holes 97HS. The sixth and seventh posture holding holes 97HL and 97HM correspond to the second posture holding holes.

Further, in the first embodiment, the outer box 96 and the inner box 97 correspond to a plurality of nested arms, and the first to third sliding pads 120A to 120C correspond to the sliding members.
Further, in the first embodiment, the support shaft 94c corresponds to the first rotation shaft, the first link shaft 100a corresponds to the second rotation shaft, and the second link shaft 100b corresponds to the third rotation shaft. handle.

(Action and effect of the first embodiment)
The out-trigger device 9 according to the first embodiment is provided on the chassis frame 2 of the tower crane 1 so as to be rotatable around a vertical axis and undulating around a horizontal first rotating shaft 91b. And, at the tip of the base end side arm 93, a nested tip side arm 95 whose base end portion is rotatably and pivotally supported around a support shaft 94c parallel to the first rotation shaft 91b is provided and stored. It has a storage posture during time and a deployment posture during work. The out-trigger device 9 has a first link shaft 100a at a position where one end is closer to the tip of the base end side arm 93 by a first link shaft 100a which is a support shaft and is parallel to the first rotation shaft 91b. The BM type link 100, which is rotatably attached around the tip, and the end of the cylinder rod 36b side are supported inside the tip side arm 95, and the end portion of the cylinder rod 36b side is supported at a position near the tip of the tip side arm 95. A lateral outrigger cylinder 36 whose end on the tube 36a side is rotatably attached to the other end (movable end) of the BM type link 100 around a second link shaft 100b parallel to the first rotation shaft 91b. , Equipped with. The BM type link 100 is configured to convert the expansion / contraction force of the lateral outrigger cylinder 36 into the rotational power of the tip side arm 95.

With this configuration, the lateral outrigger cylinder 36 is built inside the tip side arm 95, and the expansion and contraction force thereof can be converted into the rotational power of the tip side arm 95 by the BM type link 100. As a result, it is possible to reduce the occupied area of the outrigger device 9 at the time of storage by the amount of the lateral outrigger cylinder 36 that generates the rotational power of the tip end side arm 95.
Further, in the outrigger device 9 according to the first embodiment, in the retracted posture of the BM type link 100, one end on the first link shaft 100a side is the lateral outrigger on the other end on the second link shaft 100b side. It is mounted at a position higher than the mounting position on the cylinder 36 (cylinder cap portion 36aa). Then, after extending in a substantially horizontal direction from the attachment position of one end to the base end side arm 93 toward the tip end side arm 95 side, the shape is bent diagonally downward from the middle toward the attachment position of the other end side ( In the first embodiment, it has an abbreviation-shaped boomerang shape that is convex upward to the right.

With this configuration, when the tip end arm 95 rotates, the base end portion of the tip end side arm 95 rotates along the shape of the BM type link 100, so that the lower end portion and the tip end side of the BM type link 100 are rotated. It is possible to avoid contact with the base end portion of the arm 95. As a result, the BM type link 100 can be arranged compactly.
Further, the outrigger device 9 according to the first embodiment further has a nested outer box 96 and an inner box 97 in which the tip end side arm 95 expands and contracts by the expansion and contraction force generated by the lateral outrigger cylinder 36. In addition, the rotation of the proximal end arm 93 and the distal arm 95 at positions corresponding to the first retracted posture and the first deployed posture, which are the retracted posture and the deployed posture with respect to the rotational movement of the distal arm 95, respectively. (In the first embodiment, the first posture holding pin 190, the first posture holding hole 94Hh, and the second and third posture holding holes 94HS, 94HL) are provided. .. Further, a second posture holding means for restraining and releasing the expansion and contraction of the inner box 97 at positions corresponding to the second retracted posture and the second deployed posture, which are the retracted posture and the deployed posture for the expansion and contraction operation of the tip end side arm 95, respectively. (In the first embodiment, the second posture holding pin 191 and the eighth posture holding hole 97HS, and the sixth and seventh posture holding holes 97HL and 97HM) are provided.

Then, when the rotation of the proximal end side arm 93 and the distal end side arm 95 is restrained by the first posture holding means, the rotational power is transmitted via the BM type link 100 by the expansion and contraction operation of the lateral outrigger cylinder 36. Maintain a restrained posture against. On the other hand, when the rotation of the base end side arm 93 and the tip end side arm 95 is not restrained by the first posture holding means and the expansion and contraction of the inner box 97 is restrained by the second posture holding means. The rotation operation is performed in response to the transmission of the rotational power via the BM type link 100 due to the expansion and contraction operation of the lateral outrigger cylinder 36.

Further, when the expansion and contraction of the inner box 97 is restrained by the second posture holding means, the posture restrained against the transmission of the expansion and contraction force by the expansion and contraction operation of the lateral outrigger cylinder 36 is maintained. On the other hand, when the rotation of the base end side arm 93 and the tip end side arm 95 is restrained by the first posture holding means and the expansion and contraction of the inner box 97 is not restrained by the second posture holding means, the lateral outrigger cylinder The inner box 97 is expanded and contracted in response to the transmission of the expansion and contraction force by the expansion and contraction operation of 36.

With this configuration, the first and second retracted postures and the first and second deployed postures can be restrained and released by the first posture holding means and the second posture holding means. In addition, one common lateral outrigger cylinder 36 shifts from the first retracted posture to the first deployed posture by the rotational movement of the tip end arm, and from the second retracted posture by the extended movement of the inner box 97. It is possible to shift to the second deployment posture. Therefore, it is possible to obtain the power for the undulating operation and the expansion / contraction operation of the tip side arm 95 without adding a new outrigger cylinder and without increasing the occupied area of the outrigger device 9.

Further, the out-trigger device 9 according to the first embodiment further supplies the pressure oil into the cylinder tube 36a provided in the cylinder tube 36a and discharges the pressure oil in the cylinder tube 36a. It has a pressure oil supply / discharge pipe 36c connected to the pressure oil supply / discharge port of 2. In addition, it has a square tubular pipe box 101 that covers the pressure oil supply / discharge pipe 36c provided on the outer peripheral surface of the cylinder tube 36a. Further, first to third sliding pads 120A to 120C provided between the inner peripheral surface of the inner box 97 of the tip side arm 95, the outer peripheral surface of the cylinder tube 36a, and the outer peripheral surface of the pipe box 101 are provided. Be prepared.

With this configuration, even when a force is applied to press the cylinder tube 36a or the pipe box 101 against the inner peripheral surface of the inner box 97, direct contact with the inner peripheral surface can be avoided and the lateral outriggers can be avoided. It is possible to smoothly perform the sliding operation of the inner box 97 of the cylinder 36 and the sliding operation of the inner box 97.
Further, the outrigger device 9 according to the first embodiment is further in a state in which the rotational operation of the tip end side arm 95 is physically blocked (a state in which the outrigger device 9 is in contact with the cushion 99 or a state in which the outrigger device 9 is restrained by the posture holding pin). At this time, with respect to the first bending moment MxL generated at the end portion (cylinder cap portion 36aa) on the cylinder tube 36a side of the lateral outrigger cylinder 36 due to the addition of rotational force via the BM type link 100 by the lateral outrigger cylinder 36. A first blocking member 103 is provided to prevent displacement of the end portion in the bending direction.

Here, in the outrigger device 9 according to the first embodiment, when the lateral outrigger cylinder 36 is extended, the lateral outrigger is prevented from rotating the tip end arm 95 to the first deployed posture. A first bending moment MxL is generated at the end of the cylinder on the cylinder tube 36a side via the BM type link 100. As a result, a first bending load is generated that displaces the end of the lateral outrigger cylinder on the cylinder tube 36a side in the first bending direction (X direction). On the other hand, when the lateral outrigger cylinder 36 is in a state in which the rotational operation of the tip side arm 95 to the first retracted posture is blocked during the contraction operation, the lateral outrigger cylinder is relative to the end portion of the lateral outrigger cylinder on the cylinder tube 36a side. , A second bending moment (-MxL) is generated via the BM type link 100. As a result, a second bending load is generated that displaces the end portion of the lateral outrigger cylinder 36 on the cylinder tube 36a side in the second bending direction (−X direction) in the direction opposite to the first bending direction.

The first blocking member 103 is provided on the first inner peripheral surface, which is the inner peripheral surface on the first bending direction side, with the lateral outrigger cylinder 36 at the base end portion of the tip end side arm 95 interposed therebetween. The second seat 103b provided on the second inner peripheral surface, which is the inner peripheral surface on the second bending direction side, sandwiching the seat 103a of 1 and the lateral outrigger cylinder 36 at the base end portion of the tip end side arm 95. And.
The first seat 103a is located at the end of the lateral outrigger cylinder 36 on the cylinder tube 36a side of the lateral outrigger cylinder 36 that has been extended when the rotational operation corresponding to the extension operation of the tip end arm 95 is blocked. It abuts from the inner peripheral surface side to support the first bending load applied to the end portion.

Further, the second seat 103b has a second seat 103b at the end of the lateral outrigger cylinder 36 that has been reduced and operated on the cylinder tube 36a side when the rotation operation corresponding to the reduction operation of the tip side arm 95 is in a blocked state. It abuts from the inner peripheral surface side to support the second bending load applied to the end portion.
With this configuration, the bending load in the first bending direction by the first bending moment MxL can be supported by the first seat 103a, and the second bending by the second bending moment (-MxL). The bending load in the direction can be supported by the second seat 103b. As a result, it is possible to avoid the occurrence of defects in the cylinder tube 36a and the parts around the cylinder tube 36a.
Further, the tower crane 1 according to the first embodiment includes the outrigger device 9.
With this configuration, the same operation and effect as the outrigger device 9 can be obtained.

(Second Embodiment)
(composition)
Next, a second embodiment of the present invention will be described.
The second embodiment is different from the first embodiment in that the bending load is supported by the hook-shaped second blocking member instead of the first blocking member 103 of the first embodiment.

Hereinafter, the same parts as those in the first embodiment are designated by the same reference numerals, description thereof will be omitted as appropriate, and different parts will be described in detail.
As shown in FIGS. 15, 16A and 16B, the second outrigger device 9A according to the second embodiment is the first blocking member 103 and the lateral side of the outrigger device 9 of the first embodiment. Instead of the outrigger cylinder 36, a second blocking member 104 and a second lateral outrigger cylinder 36A are provided.

Further, the second lateral outrigger cylinder 36A is configured to include a second cylinder cap portion 36ab instead of the cylinder cap portion 36aa in the lateral outrigger cylinder 36 of the first embodiment.
The second blocking member 104 includes a hook main shaft 104a, a claw portion 104b, a toe portion 104c, and a hook attachment portion 104d provided at the second base end portion 96b of the outer box 96.

The hook main shaft 104a is provided on the inner peripheral surface of the second base end portion 96b, and has a vertically long rectangular upper portion and a semi-trapezoidal lower portion in a side view. The rectangular vertically long upper portion has a first support surface 140a in which the outrigger device 9 abuts on the outer peripheral surface of the second cylinder cap portion 36ab in the retracted posture. Further, the lower portion of the semi-trapezoidal shape has a third inclined surface 142a that is inclined obliquely downward toward the inner peripheral surface side of the second base end portion 96b on the side of the first support surface 140a.

The claw portion 104b is provided so that the outrigger device 9 projects upward from the upper end of the hook main shaft 104a and above the second base end portion 96b in the retracted posture. The claw portion 104b extends from the upper end of the hook main shaft 104a toward the block 36d side along the curved surface of the upper end portion of the second cylinder cap portion 36ab.
Further, the tip of the hook claw portion 104b is located closer to the block 36d than the center position of the upper end portion of the second cylinder cap portion 36ab in the retracted posture of the outrigger device 9, and the upper end portion thereof is located on the block 36d side. It extends straight from above the hook main shaft 104a diagonally to the upper right to form an inclined surface, and then extends straight in the horizontal direction to the tip portion to form a horizontal plane.

Furthermore, the lower end of the claw portion 104b has a shape that follows the shape of the upper end portion of the second cylinder cap portion 36ab. The claw portion 104b is configured such that the lower end portion thereof comes into contact with the upper end portion of the second cylinder cap portion 36ab when the outrigger device 9 is in the retracted posture.
The toe portion 104c is formed so that the outrigger device 9 projects downward from the tip portion of the claw portion 104b in the retracted posture. Specifically, the toe portion 104c has a first surface 140c that slightly extends vertically downward from the lower end side of the tip portion of the claw portion 104b, and below the crochet portion 104b from the upper end side of the tip portion of the claw portion 104b. It has a fourth inclined surface 141c extending diagonally to the lower right to a height position slightly above the end surface. Further, a second surface 142c extending vertically downward from the lower end of the fourth inclined surface 141c to the lowermost end, and a second cylinder slightly lower than the second surface 142c from the lower end of the first surface 140c to the lower right. It has a fifth inclined surface 143c that extends diagonally to the lowermost position on the cap portion 36ab side. Furthermore, it has a third surface 144c that horizontally connects the lower end of the fifth inclined surface 143c and the lower end of the second surface 142c.

The hook attachment portion 104d has a hook attachment portion 104d with the claw portion 104b, which extends to a position beyond the second base end portion 96b in the direction opposite to the claw tip portion 104c side of the claw portion 104b in the retracted posture of the out trigger device 9. It has a connecting portion and a mounting claw portion 140d extending vertically downward along the outer peripheral surface of the second base end portion 96b from the tip end portion of the connecting portion. Further, a lower end portion 141d that comes into contact with the upper end surface of the second base end portion 96b is provided.

That is, the second blocking member 104 includes the mounting claw portion 140d and the lower end portion 141d of the hook mounting portion 104d, and the second support surface 141a which is a surface opposite to the first support surface 140a of the hook main shaft 104a. The second base end portion 96b is fixedly supported in a groove formed of the above.
The upper end of the second cylinder cap portion 36ab has a rounded shape, and the toe portion 104c of the second blocking member 104 is hooked on the side surface portion of the upper end portion on the cylinder tube 36a side. A groove 360 is provided.

The groove portion 360 is composed of a groove having a shape that follows the shape of a composite surface composed of a first surface 140c, a fifth inclined surface 143c, and a third surface 144c of the toe portion 104c.
Then, when the outrigger device 9 is in the retracted posture, the toe portion 104c of the second blocking member 104 has a first surface 140c and a fifth inclined surface on the inner peripheral surface of the groove portion 360 of the second cylinder cap portion 36ab. The 143c and the third surface 144c are configured to come into contact with each other.

(Second blocking member 104)
Next, the role of the second blocking member 104 of the second embodiment will be described in detail.
The second blocking member 104 has the same role as the first blocking member 103 of the first embodiment. The bending moments and reaction forces described below are the same as those described with reference to FIG. 13B in the first embodiment.

That is, as shown in FIG. 17A, when the second lateral outrigger cylinder 36A is further extended in a situation where the tip end side arm 95 cannot rotate in the downward direction, the BM type link with respect to the cylinder extension thrust Fc. The link reaction force Fa received from 100 is generated. Then, the first bending moment MxL is applied to the second cylinder cap portion 36ab of the cylinder tube 36a.
Here, in the example of FIG. 17A, as shown in the upper part of the figure, the second lateral outrigger cylinder 36A is considered to be a support beam at both ends (a state in which the second lateral outrigger cylinder 36A lies like a beam). Therefore, the distance La from the cylinder rod 36b side to the force point (center of the second link shaft 100b) and the distance Lb from the cylinder tube side to the force point are extremely larger at the distance La. Therefore, the reaction force on the cylinder rod 36b side is omitted.

When the first bending moment MxL is applied to the second cylinder cap portion 36ab, a large load is applied in the first bending direction, especially when there is no support in the first bending direction (X direction), and the cylinder tube. There is a possibility that a defect may occur in 36a and the surrounding parts.
On the other hand, although not shown, when the second lateral outrigger cylinder 36A is contracted when the tip side arm 95 is restrained in a state where it cannot rotate and expand / contract in the retracted posture, the cylinder contracts. A link reaction force (-Fa) received from the BM type link 100 is generated with respect to the thrust (-Fc). As a result, a second bending moment (−MxL) in the direction opposite to the first bending moment MxL is applied to the second cylinder cap portion 36ab of the cylinder tube 36a.

In this case as well, if there is no support in the second bending direction (-X direction), a large load may be applied in the second bending direction, causing a problem in the cylinder tube 36a and the surrounding parts. be.
Therefore, in the second embodiment, as shown in FIGS. 15, 16 (a) and 16 (b), the upper end of the second cylinder cap portion 36ab is attached to the second base end portion 96b of the outer box 96 in the retracted posture. A hook-shaped second blocking member 104 for holding the portion is provided.

As a result, when the first bending moment MxL is generated, as shown in FIG. 17B, the first surface 140c, the fifth inclined surface 143c, and the fifth inclined surface 143c of the toe portion 104c of the second blocking member 104 are generated. The surface 144c of 3 abuts on the groove 360 of the second cylinder cap 36ab to support the X-direction component Fxa of the link reaction force Fa. As a result, the reaction force Fxs is generated to reduce the load, and it is possible to avoid the cylinder tube 36a and the peripheral parts from being defective.

When a second bending moment (-MxL) in the opposite direction is generated, the hook spindle 104a of the second blocking member 104 supports the X-direction component (-Fxa) of the link reaction force (-Fa). , It is possible to avoid the occurrence of a defect in the cylinder tube 36a and the peripheral parts thereof.
Here, in the second embodiment, the second lateral outrigger cylinder 36A corresponds to the telescopic actuator.

(Action and effect of the second embodiment)
The second outrigger device 9A according to the second embodiment replaces the first blocking member 103 and the lateral outrigger cylinder 36 of the outrigger device 9 of the first embodiment with the second blocking member 104 and the second lateral side. An outrigger cylinder 36A is provided. The second blocking member 104 is provided on the inner peripheral surface on the second bending direction (−X direction) side with the second lateral outrigger cylinder 36A at the base end portion of the tip end side arm 95 interposed therebetween. Then, when the rotation operation corresponding to the reduction operation of the tip end side arm 95 is in the blocked state, the end portion (second cylinder cap portion 36ab) of the second lateral outrigger cylinder 36A that has been reduced and operated on the cylinder tube 36a side. Is provided with a hook spindle 104a that comes into contact with the inner peripheral surface side and supports a second bending load applied to the end portion. In addition, the lower end portion has a shape along the outer shape of the upper end portion of the second cylinder cap portion 36ab of the lateral outrigger cylinder 36, and is in contact with the upper end portion of the second cylinder cap portion 36ab in the retracted posture. The configured key claw portion 104b is provided. Further, it extends from the tip of the crochet portion 104b toward the side surface portion of the second cylinder cap portion 36ab of the second lateral outrigger cylinder 36A on the first bending direction (X direction) side, and the side surface portion in the retracted posture. A toe portion 104c configured to abut the portion from the first bending direction side is provided.

Specifically, the second cylinder cap portion 36ab has a rounded upper end portion, and is for locking to hook the toe portion 104c on the side surface portion of the upper end portion on the cylinder tube 36a side. The groove 360 is provided. Further, the toe portion 104c has a first surface 140c slightly extending vertically downward from the lower end side of the tip end portion of the claw portion 104b, and a lower right side from the lower end of the first surface 140c, more than the second surface 142c. A third that horizontally connects the fifth inclined surface 143c that extends diagonally to the lowermost position on the second cylinder cap portion 36ab side, the lower end of the fifth inclined surface 143c, and the lower end of the second surface 142c. Has a surface 144c.

The groove portion 360 is composed of a groove having a shape along the shape of a composite surface composed of a first surface 140c, a fifth inclined surface 143c, and a third surface 144c of the toe portion 104c, and is an outrigger device. When 9 is in the retracted posture, the first surface 140c, the fifth inclined surface 143c, and the third surface 144c are configured to come into contact with the inner peripheral surface thereof.
With this configuration, when the first bending moment MxL is generated, the first surface 140c, the fifth inclined surface 143c, and the third surface 144c of the toe portion 104c of the second blocking member 104 become the third. It abuts on the groove 360 of the cylinder cap portion 36ab of No. 2 and supports the X-direction component Fxa of the link reaction force Fa. On the other hand, when the second bending moment (-MxL) is generated, the hook main shaft 104a of the second blocking member 104 supports the X-direction component (-Fxa) of the link reaction force (-Fa). As a result, it is possible to avoid the occurrence of defects in the cylinder tube 36a and the parts around the cylinder tube 36a.

(Modification example)
In each of the above embodiments, in order to prevent displacement due to a bending load generated at the end on the cylinder tube side due to the operation of the lateral outrigger cylinder in the retracted posture, in the first embodiment, the base end portion of the tip end side arm 95 is prevented. A first blocking member 103 is provided on the inner peripheral surface on the displacement direction side of the lateral outrigger cylinder, and in the second embodiment, a hook-shaped second blocking member 104 is provided at the base end of the tip end arm 95. Provided. Not limited to these configurations, if it is possible to avoid the occurrence of defects due to bending load, for example, the shape of the seat of the first blocking member 103 can be changed, or the hook of the second blocking member 104 can be changed. Other configurations such as changing the shape and mounting position may be used.

In each of the above embodiments, a boomerang-shaped BM type link 100 has been described as an example of a link member that converts the expansion / contraction force of the lateral outrigger cylinder into the rotational power of the tip end side arm, but the present invention is not limited to this configuration. For example, if the link does not come into contact with the base end portion of the tip end side arm when the tip end side arm 50 rotates and the configuration is such that sufficient rotational power can be transmitted, other configurations such as changing the shape and mounting position are possible. good.

In each of the above embodiments, the hydraulic cylinder has been described as an example of an actuator that generates power for the rotational operation and the expansion / contraction operation of the tip end side arm 95, but the present invention is not limited to this configuration. For example, it may be configured to be powered by another telescopic actuator such as an electric actuator such as a linear stepping motor.
In each of the above embodiments, a tower crane has been described as an example of a working machine equipped with the outrigger device according to the present invention, but the present invention is not limited to this. The present invention is applicable not only to tower cranes but also to other cranes and various work machines other than cranes as long as the work machines to which the outrigger device can be applied.

1 Tower crane (working machine)
2 Chassis frame 3 Traveling device 4 Base 5 Column 6 Crane device 7 Undulating boom 8 Bending boom 9 Winch device 9A Second Winch device 9RF, 9RR, 9LF and 9LR Right front, right rear, left front and left rear out trigger device 10 Driver's seat 11 Operation unit 12 winch 13 Wire rope 14 Hook 15a Engine 15b Pressure oil supply device 15c Control valve 16 Control box 17 Hook storage bracket 30 Swing hydraulic motor 31 Undulating boom expansion / contraction hydraulic cylinder 32 Bending boom expansion / contraction hydraulic cylinder 33 winch Hydraulic motor 34 Undulating boom undulating hydraulic cylinder 34R, 34L 1st and 2nd undulating boom undulating hydraulic cylinder 35 Bending boom undulating hydraulic cylinder 35R, 35L 1st and 2nd undulating boom undulating hydraulic cylinder 36 Horizontal Outrigger cylinder 36A Second horizontal outtrigger cylinder 36a Cylinder tube 36aa Cylinder cap part 36ab Second cylinder cap part 36b Cylinder rod 36c Pressure oil supply / discharge pipe 36d Subplate 36RF, 36RR, 36LF and 36LR Right front, right rear, left front and left Rear Horizontal Winch Cylinder 37 Vertical Winch Cylinder 37RF, 37RR, 37LF and 37LR Right Front, Right Rear, Left Front and Left Rear Vertical Winch Cylinder 44 First Sheave 45 Second Sheave 46 Third Sheave 60 Hydraulic Pump 61L Left Discharge Port 61R Right discharge port 62 Main pipeline 63 Return pipeline 64 Tank 80 Crane switching control valve 81 Accelerator cylinder 82 Out trigger device switching control valve 83 Swing switching control valve 84 Boom expansion / contraction switching control valve 85 Winch switching control valve 86 Boom undulation Switching control valve 87 Horizontal out-trigger cylinder switching valve 88 Vertical out-trigger cylinder switching valve 90 Base bracket 91 Bracket part 91a First mounting arm 91b First rotation shaft 91c Second rotation shaft 92 Rotation support part 93 Base end side arm 94 Center bracket 94a Second mounting arm 94b Third rotation shaft 94c Support shaft 94Hh, 94HS, 94HL 1st, 2nd, 3rd posture holding holes 95 Tip side arm 96 Outer box 96a 1st base end 96b Second base end 96HF 4 posture holding holes 96H 5th posture holding holes 97 inner boxes 97HL, 97HM, 97HS 6th, 7th, 8th posture holding holes 98 float 99 cushion 100 BM type links 100a, 100b 1st and 2nd links Shaft 101 Pipe box 102B First mounting part 102C Second mounting part 103 First blocking member 103a First seat 103b Second seat 104 Second blocking member 104a Hook spindle 104b Key claw part 104c Toe part 104d Hook mounting portions 120A to 120C First to third sliding pads 121A to 121C First to third sliding surfaces 130a First seat surface 131a First inclined surface 130b Second seat surface 131b Second inclined Surface 140a First support surface 140c First surface 140d Mounting claw portion 141a Second support surface 141d Lower end 143c Fifth inclined surface 144c Third surface 160 Controller 161 Receiver 162 Remote control device 180 Main relief valve ( Unload valve)
181 Solenoid for unload valve operation 182 Relief valve for hook fixing 182a Hook relief solenoid 182b Hook relief valve 190,191 1st and 2nd posture holding pins 360 Grooves 820, 840, 860 1st, 2nd and 3rd electromagnetic waves Switching valve

Claims (5)

A base end side arm rotatably provided on the base of the work machine around a horizontal axis, and a first axis around the base end portion of the base end side arm whose base end portion is parallel to the horizontal axis. It is an out-trigger device that is equipped with a tip-side arm that is rotatably and pivotally supported, and has a retracted posture during storage and a deployed posture during work.
The tip side arm has a plurality of arms in a nested manner and has a telescopic actuator built in.
A first posture holding means for restraining the rotation of the base end side arm and the tip end side arm,
A second posture holding means for restraining the expansion and contraction of the plurality of arms is provided.
The tip side arm
When the rotation is not restrained by the first posture holding means and the expansion and contraction is restrained by the second posture holding means, the rotation operation is performed according to the expansion and contraction operation of the actuator.
When the rotation is restrained by the first posture holding means and the expansion and contraction is not restrained by the second posture holding means, the plurality of arms are expanded and contracted according to the expansion and contraction operation of the actuator. An outrigger device characterized by that. One end of the actuator is rotatably attached around the second axis by a second axis parallel to the first axis at a position near the tip of the base end side arm, and the other end thereof is attached. , Supported at a position near the tip of the tip side arm,
The first posture holding means is in a first retracted posture, which is the most prone posture of the tip end arm with respect to the rotation motion, and a first deployment posture, which is a standing posture of the tip end arm with respect to the rotation motion. The rotation of the base end side arm and the tip end side arm is restrained at the corresponding positions, respectively.
The second posture holding means corresponds to a second retracted posture, which is the most contracted posture of the tip end arm with respect to the expansion and contraction motion, and a second deployment posture, which is an extension posture of the tip end arm with respect to the expansion and contraction motion. The outrigger device according to claim 1, wherein the expansion and contraction of the plurality of arms in a nested shape is restrained at a position where the arms are stretched. The first posture holding means is provided with a plurality of postures continuously provided in a fan shape at the tip of the base end side arm and the base end portion of the tip end side arm about the axis of the first shaft. A plurality of first posture holding holes, which are holding pin holes and whose central axes are coaxially penetrated at positions corresponding to the first storage posture and the first deployment posture, and the first posture holding hole. For posture holding, which is inserted into the first posture holding hole at a position corresponding to the retracted posture and the first deployed posture to restrain and release the rotation of the base end side arm and the tip end side arm. It has a first posture holding pin which is a pin,
The second posture holding means is a plurality of posture holding pin holes provided in the plurality of arms, and is a central axis at positions corresponding to the second retracted posture and the second deployed posture, respectively. The plurality of arms are inserted and removed into the plurality of second posture holding holes through which they penetrate coaxially, and the second posture holding holes at positions corresponding to the second retracted posture and the second deployed posture, respectively. The out trigger device according to claim 2, further comprising a second posture holding pin for holding the posture that restrains and releases the expansion and contraction of the above. One end of the actuator is attached to a position closer to the tip of the base end side arm via a link member for power transmission.
One end of the power transmission link member is located near the tip of the base end side arm, around the second axis by a second axis which is a support axis and is parallel to the first axis. It is mounted rotatably and
The outrigger device according to any one of claims 1 to 3, wherein the one end portion of the actuator is rotatably pivotally attached to a movable end portion which is the other end portion of the link member. The actuator is a hydraulic cylinder, and provides a pressure oil supply / discharge pipe connected to a pressure oil supply / discharge port for supplying pressure oil into the tube provided in the tube and discharging the pressure oil in the tube. Have and
A tubular box provided on the outer peripheral surface of the tube and covering the pressure oil supply / discharge pipe,
The outrigger device according to any one of claims 1 to 4, further comprising a sliding member provided between the inner peripheral surface of the tip end side arm, the outer peripheral surface of the tube, and the outer peripheral surface of the box. ..

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