JP2019073369A - Outrigger device - Google Patents

Abstract

To provide an outrigger device in which an occupied area of an outrigger cylinder is reduced, so that an occupied area of the outrigger device is reduced when stored.SOLUTION: An outrigger device 9 comprises: a base end side arm 93; a nested tip side arm 95 pivoted to a tip of the base end side arm; a boomerang type link 100 with one end part attached to a horizontal shaft in a freely rotatable manner in a position near the tip of the base end side arm 93; a lateral outrigger cylinder 36 which is arranged inside the tip side arm 95, and of which an end part on a cylinder rod 36b side is supported in a position near a tip of the tip side arm 95, and of which an end part on a cylinder tube 36a side is supported to a horizontal shaft in a freely rotatable manner at the other end part of the boomerang type link 100; and a first prevention member 103 which is disposed on an inner peripheral surface of a base end part of an outer box 96, in order to prevent displacement of the cylinder tube 36a or the like against bending moment caused by reaction force from the boomerang type link 100.SELECTED DRAWING: Figure 6

Description

  The present invention relates to an outrigger apparatus which supports an airframe by projecting laterally from an airframe of a working machine.

  Conventionally, as an outrigger apparatus used for work vehicles, such as a crane, there exists an outrigger apparatus of patent document 1, for example. The outrigger device includes a longitudinal extension link mechanism including a first arm and a first cylinder, and a lateral extension link mechanism including a second arm, an outer box, and a second cylinder. The first arm is pivotally supported at the chassis frame of the work vehicle via the sub-frame and the bracket, and the proximal end of the second arm is pivotally supported at the distal end of the first arm; The proximal end of the outer box is pivotally supported at the distal end of the arm of. Then, the outrigger device projects the horizontal overhang link mechanism by reducing the second cylinder and rotating the second arm from the storage posture state, and extends the first cylinder to expand the first arm. The vertical extension link mechanism is extended by rotating.

JP, 2006-21914, A

However, in the prior art of the above-mentioned patent document 1, the outrigger at the time of storage is caused by the presence of the first cylinder and the second cylinder that generate power when performing the overhang operation of the longitudinal overhang link mechanism and the lateral overhang link mechanism. The area occupied by the device has increased.
Therefore, the present invention has been made in view of such problems, and an outrigger device capable of reducing the exclusive area of the outrigger device at the time of storage by reducing the exclusive area of the cylinder. The task is to provide.

  In order to solve the above problems, an outrigger device according to a first aspect of the present invention is a proximal end arm provided rotatably on a horizontal axis on a base of a working machine, and the proximal end A distal end portion of the arm includes a nested distal end side arm whose proximal end portion is rotatably supported about a first axis parallel to the horizontal axis, and the storage posture during storage and the deployment during operation An outrigger device having an attitude, wherein one end portion is a support shaft at a position near the tip end of the proximal end arm and a second axis parallel to the first axis about the second axis A link member for power transmission that is rotatably attached, and is disposed inside the distal end arm in a posture that is parallel to the longitudinal direction of the distal end arm, and one end thereof is the distal end of the distal end arm Movable end supported at an offset position, the other end being the other end of the link member An outrigger cylinder rotatably mounted on the housing, and the bending moment generated at the other end of the outrigger cylinder due to the application of the extension force of the outrigger cylinder when in the storage posture, A blocking member is provided on the inside of the distal end arm for abutting against the end and blocking displacement of the outrigger cylinder in the bending direction.

  According to the present invention, the outrigger cylinder is incorporated inside the distal end side arm, and the expansion / contraction force is converted into the rotational force of the distal end side arm by the link member for power transmission. By this, it is possible to reduce the occupied area of the outrigger device at the time of storage by an amount corresponding to the outrigger cylinder that generates the rotational force of the distal end side arm. In addition, when the outrigger device is in the storage posture, the blocking member prevents the displacement of the outrigger cylinder in the bending direction with respect to the bending moment generated at the other end by the telescopic operation of the outrigger cylinder. It becomes possible. As a result, for example, when the outrigger cylinder is erroneously extended / contracted in the storage posture, it is possible to avoid the occurrence of a defect in the other end portion of the outrigger cylinder and components in the periphery thereof.

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 vehicle right-hand side. The figure shows a state in which the outrigger device is stored. It is the perspective view which looked at the tower crane concerning a 1st embodiment from the vehicles right-hand side upper part. In the figure, the state which expanded the outrigger apparatus is shown. It is a figure showing an example of the hydraulic circuit concerning a 1st embodiment. It is a block diagram which shows the input-output relationship of the signal of the controller which concerns on 1st Embodiment. It is a side view showing the storing posture of the outrigger device concerning a 1st embodiment. The figure shows a state in which the entire outrigger device is turned approximately 90 ° in the horizontal direction. (A) is a partial top view of the outrigger apparatus which concerns on 1st Embodiment, (b) is the sectional view on the AA line of (a). In the figure (b), the cross section of the proximal end side arm, the center bracket, and the portion of the distal end side arm excluding the float is shown. It is the CC sectional view taken on the line of FIG. (A) is a side view of the outrigger device in the first and second storage postures in which the restraint on the pivotal movement of the distal end arm is released, and (b) is a side view of the distal arm. It is a side view of an outrigger device in the state where it was developed to overhang posture S1 at the time of small. In the figure, the proximal end side arm, the center bracket, and the portion of the distal side arm excluding the float are shown in cross section. It is a side view of an outrigger device in a state where it is developed in the overhanging posture U1 at the maximum time by the rotation operation of the tip end side arm. In the figure, the proximal end side arm, the center bracket, and the portion of the distal side arm excluding the float are shown in cross section. It is a side view of the outrigger device in a state of being deployed in the maximum overhanging posture U2 by the extension operation of the distal end side arm. In the figure, the proximal end side arm, the center bracket, and the portion of the distal side arm excluding the float are shown in cross section. It is a figure for demonstrating the earthing | grounding operation of an outrigger apparatus. In the figure, the proximal end side arm, the center bracket, and the portion of the distal side arm excluding the float are shown in cross section. It is a partial expanded sectional view of an outrigger device for explaining composition of the 1st blocking member. (A) and (b) show the bending moment generated in the cylinder tube of the lateral outrigger cylinder when the lateral outrigger cylinder is extended in a state where the distal end side arm can not rotate in the downward direction and the inner box can not extend. It is a figure for demonstrating. (A) is a figure for demonstrating the relationship of the force in the case of providing a 1st blocking member and supporting a bending moment, (b) is a 1st expansion | deployment attitude | position by the tip end side arm by rotation operation. It is a figure explaining the bending load at the time of extending operation of a horizontal outrigger cylinder in the restrained state. It is a partial top view of the outrigger apparatus which concerns on 2nd Embodiment. (A) is the BB sectional view taken on the line of FIG. 15 for demonstrating the structure of a 2nd blocking member, (b) is a figure which shows a 2nd blocking member. (A) is a fragmentary sectional view for demonstrating the relationship of the force in the case of providing a hook-shaped second blocking member 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 provided 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 between thickness and plane dimensions, ratio, etc. may be different from the actual one, and some parts have different dimensional relationships and ratios among the drawings. There is a case. Moreover, in order to make it easy to understand the positional relationship of each component, there may be a case where a portion which is originally invisible can be perspectively displayed. In addition, the embodiments described below illustrate apparatuses and methods for embodying the technical idea of the present invention, and the technical idea of the present invention includes materials, shapes, structures, and arrangements of component parts. Etc. are not specified in the following embodiment.

First Embodiment
(Constitution)
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 9RF, the right rear outrigger 9RR, the left front outrigger 9LF and the left rear outrigger 9LR, the driver's seat 10, the operation unit 11, the winch 12, the wire rope 13, the hook 14 and the motor And a hook storage bracket 17.

The traveling device 3 is a crawler-type traveling device in which, for example, rubber crawler belts are attached to the left and right, and is provided at a lower portion of the chassis frame 2.
The base 4 is connected and fixed to the upper portion of the chassis frame 2, and the column 5 is rotatably installed on the upper portion of the base 4.
The crane device 6 is pivotally supported at the upper end of the column 5 and is pivotally supported at the distal end of the telescoping boom 7 constituted by a telescopic box type boom and the tip of the hoisting boom 7, And a telescopic folding boom 8 constituted by a telescopic box boom.

At the time of operation, as shown in FIG. 2, the hoisting boom 7 is turned to be in an upright state, and the bending boom 8 is erected with respect to the hoisting boom 7 to turn the front side. Further, by extending the up-and-down boom 7 in the upright state, it is possible to secure a necessary height, and to extend the bending boom 8 to allow the hook 14 to reach a distant load.
Right front, right rear, left front and left rear outrigger devices 9RF, 9RR, 9LF and 9LR are provided on the upper front of the chassis frame 2 at the right front, right rear, left front and left rear, respectively.

Hereinafter, the front right, rear right, front left and rear left outrigger devices 9RF, 9RR, 9LF and 9LR may be abbreviated as “respective outriggers 9RF to 9LR”.
Each of the outrigger devices 9RF to 9LR is provided with a proximal end arm 93 rotatably and inclinably provided on the chassis frame 2, and a telescopic distal end arm 95 provided in the distal end of the proximal end arm 93 in a freely movable manner. Is equipped.

  Further, each of the outrigger devices 9RF to 9LR is provided with a right front, a right rear, a left front and a left rear longitudinal outrigger cylinders 37RF, 37RR, 37LF and 37LR which are hydraulic actuators for raising and lowering the proximal arm 93. In addition, as shown in FIG. 3, hydraulic actuators for moving the distal end arm 95 up and down and extending and retracting are provided with right front, right rear, left front and left rear horizontal outrigger cylinders 36RF, 36RR, 36LF and 36LR. There is.

  Hereinafter, the front right, rear right, front left and rear left outrigger cylinders 36RF, 36RR, 36LF, and 36LR may be abbreviated as “respective horizontal outrigger cylinders 36RF to 36LR”. The right front, right rear, left front and left rear vertical outrigger cylinders 37RF, 37RR, 37LF, and 37LR may be abbreviated as “respective vertical outrigger cylinders 37RF to 37LR”.

  Here, as shown in FIG. 4, the tower crane 1 includes a remote control device 162 capable of remotely performing a crane operation. Although not shown, the remote control device 162 is configured to be able to perform the same operation as the control lever and control switch of the operation unit 11 by various control levers and control 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 in accordance with the operation of the control lever and the operation switch.

  Each of the outrigger devices 9RF to 9LR is configured to be operable between the storage attitude shown in FIG. 1 and the deployment attitude shown in FIG. In the tower crane 1, when the crane device 6 is used, the operator manually rotates the outrigger devices 9 RF to 9 LR in the stored state in the horizontal direction, whereby the entire outrigger devices 9 RF to 9 LR are chassis frame 2 It is positioned in the overhanging position directed to the side. Next, the lateral outrigger cylinders 36RF to 36LR are driven by the operation of the operation unit 11 of the operator or the remote control device 162 to operate and extend the distal end side arm 95 in the raising direction. Furthermore, the vertical outrigger cylinders 37RF to 37LR are driven to operate the proximal end arms 93 of the respective outrigger devices 9RF to 9LR in the lowering direction to ground the distal end arm 95, thereby performing work (during suspension). The tower crane 1 is designed to be stable.

The driver's seat 10 is a seat on which an operator (driver) is seated at the time of traveling operation of the tower crane 1, and as shown in FIGS. 1 and 2, provided projecting to the rear of the tower crane 1 via a link mechanism. .
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 travel operation levers and a plurality of operation switches disposed on the front of the driver's seat 10 and on the left side of the rear end. (Not shown) and a plurality of control levers (not shown) provided on the right side of the control panel.

The plurality of control levers shown in FIG. 3 are an outrigger switching control valve 82 of the control valve 15c, a turning switching control valve 83, a boom expansion / contraction switching control valve 84, a winch switching control valve 85, a boom hoisting switching control valve Each spool in 86 is operated directly.
The control levers are provided corresponding to the various hydraulic actuators, and can drive the hydraulic actuators corresponding to the control lever in the direction of tilting from the neutral position.

Specifically, the respective operation levers are a lever for operating the left turning operation and the right turning operation of the crane device 6, a lever for operating the extension boom of the hoisting boom 7 and the bending boom 8, a winding operation of the hook 14 and It includes a lever for operating the lowering operation, a lever for operating the raising and lowering movement of the raising and lowering boom 7 and the bending boom 8.
The plurality of operation switches are a crane operation-autrigger operation switch, a hoisting boom switch, a telescopic boom switch, a hook fixing switch, and an outrigger for selecting an outrigger device to be operated from among the outrigger devices 9RF to 9LR. It includes a device selection switch, an outrigger operating switch for operating the selected outrigger device, and the like.

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

Further, in the crane mode, the telescopic boom changeover switch switches between a telescopic boom telescopic operation mode for enabling telescopic operation of the telescopic boom 7 and a telescopic boom telescopic operation mode for making the telescopic operation of the bending boom 8 possible. It is a switch for
The traveling device 3, the crane device 6 and the outrigger device 9 described above, and the hoisting boom 7 and the bending boom 8 in the crane mode can not be operated at the same time for safety by the respective mode change switches.

  The winch 12 is provided at a substantially central position of the rear end surface of the hoisting 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. The third sheave 46 provided at the top of the tip end portion and the fourth sheave (not shown) provided below the third sheave 46 and inside the tip end of the bending boom 8 The hook 14 is suspended from the tip of the bending boom 8 by being hooked around the hook 14.

On the other hand, the driving unit 15 includes an engine 15a, a pressure oil supply device 15b that drives the engine 15a as a drive source, and a pressure oil supplied from the pressure oil supply device 15b, as shown in FIG. And a control valve 15 c for switching control of the oil passage of
Furthermore, as shown in FIGS. 1 to 3, the tower crane 1 pivots the column 5, extends and retracts the up and down boom 7 and the bending boom 8, rolls up and down the winch 12, and moves up and down the uplift boom 7 and the bending boom 8. A hydraulic actuator for performing the ups and downs of the

That is, the tower crane 1 includes a swing hydraulic motor 30, a hoisting boom telescopic hydraulic cylinder 31, a bending boom telescopic hydraulic cylinder 32, a winch hydraulic motor 33, a hoisting boom hoisting hydraulic cylinder 34, and a bending boom hoisting hydraulic pressure A cylinder 35 is provided.
Furthermore, the tower crane 1 is provided with a traveling motor 38 as a hydraulic actuator for driving the traveling device 3.

The hoisting boom undulating hydraulic cylinder 34, as shown in FIG. 3, is composed of a pair of hydraulic cylinders, a first undulating boom undulating hydraulic cylinder 34R and a second undulating boom undulating hydraulic cylinder 34L.
Further, the folding boom hoisting hydraulic cylinder 35 is constituted by a pair of hydraulic cylinders of a first folding boom hoisting hydraulic cylinder 35R and a second folding boom hoisting hydraulic cylinder 35L.

  These hydraulic actuators 30, 31, 32, 33, 34 and 35 are all operated by supplying pressure oil from the pressure oil supply device 15b via the control valve 15c as shown in FIG. Is configured. In addition, the horizontal outrigger cylinders 36RF to 36LR and the vertical outrigger cylinders 37RF to 37LR are all 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 15 b includes a hydraulic pump 60 driven by the engine 15 a as a drive source, a left discharge port 61 L, a right discharge port 61 R, 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 turning switching control valve 83, a boom expansion / contraction switching control valve 84, and a winch switching control. A valve 85 and a boom relief switching control valve 86 are provided. Furthermore, the horizontal outrigger cylinder switching valve 87, the vertical outrigger cylinder switching valve 88, the travel switching control valve 89, the first electromagnetic switching valve 820, the second electromagnetic switching valve 840, and the third electromagnetic switching valve And an 860.

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

The crane switching control valve 80 is a main relief valve (unload valve) 180, an unloading valve operating solenoid 181, and a hook fixing relief valve 182 provided between the main pipeline 62 and the return pipeline 63. And have.
In response to the operation signal Uo from the controller 160, the unload valve operating solenoid 181 is in either the ON state or the OFF state. When the main relief valve 180 is in the ON state, the main relief valve 180 is opened, and the main conduit 62 and the return conduit 63 are communicated. In the example shown in FIG. 3, the pressure oil discharged from the hydraulic pump 60 is transferred to the tank 64 via the return pipe 63 without passing through the switching control valve 89 for traveling and the switching control valve other than the switching control valve 80 for crane. It is supposed to return to That is, it is possible to make the operating state of the hydraulic pump 60 be an unloading state (no load operating state) in which the pressure oil is circulated without 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 either ON or OFF according to the operation signal Hr from the controller 160 according 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, when in the ON state, the oil passage of the pressure oil from the main conduit 62 is switched to the oil passage through which the pressure oil flows in the hook relief valve 182b.

Here, the hook relief valve 182 b has a low set pressure Ps (Pm> Ps) in which the set relief pressure is lower than the main set pressure Pm which is the relief pressure at the time of normal operation. Therefore, it is possible to limit the pressure upper limit of the pressure oil to the low set pressure Ps by operating the hook relief solenoid 182a in the ON state and operating the hook relief valve 182b.
As a result, while the hook fixing switch is in the ON state, it is possible to limit the lifting operation pressure of the hook 14 to a low pressure 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 an 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 operation position signal of the piston rod is input to the controller 160, and the controller 160 can control the number of rotations of the engine 15a to a desired number of rotations in accordance with the operation position of the accelerator cylinder 81. The discharge amount of the pressure oil from the hydraulic pump 60 increases as the rotational speed of the engine 15a is increased by the accelerator operation.

The outrigger device switching control valve 82 is operated by the operation lever of 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 to each horizontal outrigger cylinder 36RF to 36LR of each outrigger device 9RF to 9LR. And pressure oil is supplied to each vertical outrigger cylinder 37RF to 37LR.
The first electromagnetic switching valve 820 is a control valve that selects any one of the horizontal outrigger cylinders 36RF to 36LR or the vertical outrigger cylinders 37RF to 37LR of the outrigger devices 9RF to 9LR as the oil supply destinations of the pressure oil.

  The pressure oil that has flowed out of the outrigger switching control valve 82 first flows into the first electromagnetic switching valve 820. The first electromagnetic switching valve 820 is selected from the respective lateral outrigger cylinders 36RF to 36LR or each in response to the switching control signal Actr2 from the controller 160 by the operation of the outrigger switching switch (not shown) in the operation unit 11 by the manual operation of the operator. The hydraulic oil passage for the vertical outrigger cylinders 37RF to 37LR is switched.

The lateral outrigger cylinder switching valve 87 is a control valve that selects whether to supply pressure oil to each of the lateral outrigger cylinders 36RF to 36LR.
The lateral outrigger cylinder switching valve 87 operates in response to the operation signals Actr3 to Actr6 from the controller 160 by the operation of the lateral outrigger cylinder selection switch (not shown) in the operation unit 11 by the manual operation of the operator. Switch the oil path of the pressure oil to.

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

The turning switching control valve 83 flows in pressure oil to the turning hydraulic motor 30 in response to the operation amount of the operation lever of the operation unit 11 or the operation signal Tctr from the controller 160 according to the operation of the remote control device 162. Do.
The boom expansion / contraction switching control valve 84 is configured according 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. The pressure oil is supplied to the hydraulic cylinder 35.

The second electromagnetic switching valve 840 is a control valve that selects one of the up-and-down boom expansion / contraction hydraulic cylinder 31 or the bending boom expansion / contraction hydraulic cylinder 32 as a pressure oil supply destination.
The pressure oil flowing out of 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 in response to the operation of the telescopic boom switching switch (not shown) or in response to the operation signal Rctr from the remote control device 162 in the operation unit 11 manually operated by the operator. In accordance with the control signal Bctr3, the oil path of the pressure oil to the up-and-down boom extension hydraulic cylinder 31 or the bending boom extension hydraulic cylinder 32 is switched.

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

The third electromagnetic switching valve 860 is a control valve that selects one of the rising and lowering boom undulating hydraulic cylinder 34 and the bending boom rising and lowering hydraulic cylinder 35 as a pressure oil supply destination.
The pressure oil flowing out of the boom relief 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 in response to the operation of the hoisting boom switching switch (not shown) in the operating unit 11 or in response to the operation signal Rctr from the remote control device 162 by the manual operation of the operator. In accordance with the control signal Bctr4, the oil path of the pressure oil to the undulating boom undulating hydraulic cylinder 34 or the bending boom undulating hydraulic cylinder 35 is switched.

  Each switching control valve 82 to 86 and the accelerator cylinder 81 each have a differential transformer (not shown), and switching positions L1 to L1 of each switching control valve 82 to 86 detected by each differential transformer and the accelerator cylinder 81 A detection signal of L6 (hereinafter sometimes 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.

The traveling motor 38 is provided with two traveling motors 38L and 38R corresponding to the left and right crawler belts of the traveling device 3, as shown in FIG. Each of the traveling motors 38L and 38R operates independently by separately supplying pressure oil from the pressure oil supply device 15b via the traveling switching control valve 89.
Thus, the tower crane 1 can drive the traveling device 3 to travel in the forward or backward direction by operating the pressure oil supply device 15b and simultaneously advancing or retracting the pair of left and right travel operation levers. . Further, when turning right or left, by individually advancing or retracting the pair of left and right travel operation levers, the corresponding left and right crawler belts can be individually driven, so that turning can be performed simply with a difference in speed between right and left.

Returning to FIG. 1 and FIG. 2, the control box 16 is provided therein with the controller 160 shown in FIG. Although not shown, a receiver 161 is provided at the top of 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 a signal line.

As shown in FIG. 4, the controller 160 receives 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 a solenoid valve for oil path switching provided in the tower crane 1 according to these input signals.
Further, although not shown, the controller 160 includes a central processing unit (CPU) that performs various arithmetic processing based on a predetermined control program, and a read only memory (ROM) that stores various data including the control program. And a RAM (Random Access Memory) for storing data read from a ROM or the like and a calculation result necessary for the calculation process of the CPU, and a timer for measuring time.

  The controller 160 further includes an input / output I / F (interface) for mediating data input / output to each device including the receiver 161, the operation unit 11, the remote control device 162, the control valve 15c, etc. described above. , And various internal and external buses for data transfer. A CPU, a ROM, a RAM, and a timer are connected by various internal and external buses, and the above-described devices are connected to the bus via an input / output I / F.

  Then, when the power is turned on, a system program such as BIOS stored in the ROM etc. loads various control programs stored in advance in the ROM into the RAM, and the CPU follows the instructions described in the program loaded in the RAM. By performing arithmetic processing using various resources, it is possible to realize each function for controlling the operation of each device on software.

(Each outrigger device 9RF to 9LR)
The respective outrigger devices 9RF to 9LR will be described in detail below. Since each of the outrigger devices 9RF to 9LR has the same configuration, it will be described hereinafter as "the outrigger device 9" without particular distinction. Similarly, the horizontal outrigger cylinders 36RF to 36LR will be described as "horizontal outrigger cylinders 36" and the vertical outrigger cylinders 37RF to 37LR will be described as "vertical outrigger cylinders 37" without particular distinction.

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

  The fixing pin is inserted into the overhanging position fixing hole (not shown) at the overhanging position to securely fix the overhanging position of the outrigger device 9. That is, the outrigger device 9 is in the extended position where it is laterally extended with respect to the chassis frame 2 by the operator manually rotating the four outrigger devices 9 horizontally from the storage attitude shown in FIG. It is configured to be positioned.

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

  Furthermore, with respect to the second mounting arm 94a of the center bracket 94 and the first mounting arm 91a provided on the bracket portion 91 of the base bracket 90, both end portions of the longitudinal outrigger cylinder 37 respectively have a first rotation shaft 91b and a first rotation shaft 91b. It is pivotally supported about the parallel second rotation shaft 91c and the third rotation shaft 94b. By expanding and contracting the vertical outrigger cylinder 37, the overhang operation at the time of grounding of the outrigger device 9 and the accommodation operation at the time of storage become possible.

Further, in the outrigger device 9, the distal end arm 95 is pivotally supported by the distal end portion of the center bracket 94 so that its proximal end portion is pivotable about a pivot 94c parallel to the first rotation shaft 91b. .
The distal end side arm 95 is, as shown in FIGS. 5 and 6A and 6B, a rectangular cylindrical outer box 96 and an outer box 96 that can extend and contract along the longitudinal direction of the outer box 96. And a rectangular cylindrical inner box 97 fitted. A float 98 is pivotally supported at the tip of the inner box 97 so as to be rotatable about 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 rigidity required as 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 so as to be 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-like boomerang-type links 100 (hereinafter, abbreviated as “BM type links 100”) disposed in the center bracket 94 so as to be opposed to each other in the axial direction of the support shaft 94c.

The lateral outrigger cylinder 36 includes a cylinder tube 36a, a piston (not shown) disposed 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 substantially rectangular 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 closer to the end of the cylinder tube 36a (closer 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 lateral outrigger is generated by flowing the pressure oil in the cylinder tube 36a into the pressure oil supply / discharge pipe 36c through the second pressure oil supply / discharge port and supplying it into the cylinder tube 36a through the first pressure oil supply / discharge port. The cylinder 36 is extended.

One end portion of the BM type link 100 is rotatably supported on the first link shaft 100a parallel to the support shaft 94c at a position near the upper end of the root portion of the second mounting arm 94a of the center bracket 94 There is.
The cylinder cap portion 36 aa of the cylinder tube 36 a is rotatably supported at the other end of the BM type link 100 about a second link shaft 100 b parallel to the first link shaft 100 a.

The BM type link 100 has a bifurcated boomerang shape, and has a first wing, a second wing, and a curved portion connecting these. The BM type link 100 has a shape in which the lengths of the first wing on one end side and the second wing on the other side are different from each other across the curved portion. Specifically, the first wing is longer than the second wing.
Then, in the BM type link 100, in the stored state of the outrigger device 9, the first wing portion extends substantially horizontally from the mounting position at the one end side to the tip end side arm 95 side, and the second wing sandwiching the curved portion The part extends obliquely in the lower right direction and is disposed in a posture to be connected to the cylinder cap part 36aa. That is, the BM type link 100 is disposed in such a posture that it is convex diagonally to the upper right so as to be able to reach the mounting position of the other end located lower than the mounting position of the one end.

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

  On the box surface 101a facing at the closest position of the outer peripheral surface of the pipe box 101 and the inner peripheral surface of the inner box 97, three metal first sliding pads 120A are provided in the longitudinal direction. It is attached with a gap. In each of the two first sliding pads 120A, a counterbore penetrates from the first sliding surface 121A of the first sliding pad 120A to the back surface. Further, at the mounting position of the first slide pad 120A on the box surface 101a of the pipe box 101, bolt holes penetrating from the front surface to the back surface are provided. Then, the two first sliding pads 120A align the positions of the respective counterbore holes and the bolt holes, and the first sliding surface 121A is formed on the box surface 101a by the first bolts 122A. The inner box 97 is tightened and fixed in such a manner as to face the inner circumferential surface of the inner box 97 with a slight gap therebetween.

Here, the bearing surface depth of the counterbore is such a depth that the head of the first bolt 122A can be stored, 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.
Furthermore, metal sliding pads 120B are provided at the front and back ends of the portions facing at the closest positions of the outer peripheral surface of the cylinder tube 36a of the horizontal outrigger cylinder 36 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 provided integrally with the cylinder tube 36a by welding in a posture in which the mounting surfaces thereof face 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 spaced a predetermined distance by three along the longitudinal direction. It is attached. The second slide pad 120B and the third slide pad 120C have the same configuration as the first slide pad 120A. Further, bolt holes penetrating from the front surface to the back surface are provided at the attachment positions of the second slide pad 120B and the third slide pad 120C of the first attachment portion 102B and the second attachment portion 102C. . Then, the three second sliding pads 120B align the positions of the respective counterbore holes and the bolt holes, and the second bolt 122B can be used as the second mounting pad 102B on the mounting surface of the first mounting portion 102B. The sliding surface 121 B is tightened and fixed in a state of facing the inner circumferential surface of the inner box 97 with a slight gap. Similarly, the three third sliding pads 120C align the positions of the respective counterbore holes and the bolt holes, and the third bolts 122C move the third sliding pads 120C onto the mounting surface of the second mounting portion 102C. The three sliding surfaces 121C are tightened and fixed in a state of facing the inner circumferential surface of the inner box 97 with a slight gap therebetween.

In the first to third sliding pads 120A to 120C of the present embodiment, the contact surface with the inner peripheral surface of the inner box 97 is formed of a metal member having a low coefficient of friction.
That is, the lateral outrigger cylinder 36 of the first embodiment has the inner box 97 in a state in which the first to third sliding pads 120A to 120C are sandwiched between the inner peripheral surface of the inner box 97 at the time of expansion and contraction. It is configured to move within.

  Here, since the horizontal outrigger cylinder 36 is connected to the BM type link 100 and rotates in the direction around the support shaft 94c, the first to third sliding pads 120A to 120C are normally expanded and contracted. The force is applied only in the provided direction of. When the distal end side arm 95 is pivoted to be in the unfolded posture, the inner circumferential 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 if the lateral outrigger cylinder 36 is extended while the inner box 97 is being bent, the cylinder tube 36a inside the inner box 97 is moved to the inside of the inner box 97 by the second and third sliding pads 120B and 120C. Because the pressure oil supply and discharge pipe 36c is protected by the pipe box 101 without being rubbed directly on the circumferential surface, 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 the 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 distal end arm 95 is flipped up to the first deployed position, the lateral outrigger cylinder 36 shrinks. The same applies to the operation of the generated cylinder tube 36a and the operation of the cylinder tube 36a generated upon the extension of the lateral outrigger cylinder 36 to the first storage position as the reverse operation.

Furthermore, the outrigger device 9 includes a first posture holding pin 190 and a second posture for restraining and releasing a position according to the deployed posture and the stored posture between 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 maintaining holes at positions according to the storage posture (hereinafter sometimes referred to as "first storage posture") with respect to rotation of the distal end side arm 95 in the up and down direction 94Hh is provided. The first posture holding hole 94Hh penetrates the center bracket 94 in a true circle coaxially in the width direction (the direction of the support shaft 94c). Furthermore, on both sides of the center bracket 94, the second and third positions are in positions corresponding to the deployed posture (hereinafter may be referred to as "first deployed posture") due to rotation of the distal end side arm 95 in the up and down direction. Three posture holding holes 94HS and 94HL are provided. The second and third attitude holding holes 94HS and 94HL penetrate the center bracket 94 in a true circle coaxially in the width direction. The first posture holding hole 94Hh and the second and third posture holding holes 94HS and 94HL are circumferentially spaced apart on the same circumference centering on the support shaft 94c of the distal end side arm 95. .

Each of the second and third posture holding holes 94HS and 94HL is formed at a position corresponding to a plurality of first deployed postures (two postures in this example). That is, in the first embodiment, two postures can be set as the first deployed posture by the rotation of the distal end side arm 95 with respect to the proximal end arm 93.
Of the second and third posture holding holes 94HS and 94HL, the second posture holding hole 94HS formed on the lower side has a minimum overhang shown in FIG. 8 (b) 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 has a maximum projecting posture U1 shown in FIG. 9 among two first deployed postures. It is formed in the position according to.
On the other hand, in the outer box 96, as shown in FIG. 6 (b) and FIGS. 8 and 9, a fourth attitude holding hole 96HF which forms a perfect circle at a position corresponding to the first storage attitude is attached to the outer box 96. Provided along the width direction of the The fourth posture holding hole 96HF is provided at a position coaxial with the first posture holding hole 94Hh at a position according to the first storage posture.

Thus, 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 arranged on the circumference.
The first attitude holding pin 190 has an outer diameter dimension that can be inserted with a slight gap to the first attitude holding hole 94Hh, the second and third attitude holding holes 94HS and 94HL, and a center bracket It has a solid cylindrical shaft portion having an axial length which can penetrate through both surfaces of 94.

  Thus, the first attitude holding pin 190 raises and lowers the distal end side arm 95 at a position according to the first storage attitude and the first deployed attitude, and the fourth attitude holding hole 96HF holds the first attitude. When the center of the hole and any of the hole 94Hh and the second and third posture holding holes 94HS and 94HL form a coaxial, the hole is inserted and removed. When the first posture holding pin 190 is inserted into any one of the first posture holding hole 94Hh and the second and third posture holding holes 94HS and 94HL, the first storage posture and the two first The relative position between the proximal end arm 93 and the distal end arm 95 is constrained at a position corresponding to the inserted posture holding hole in the deployed posture. On the other hand, when the first attitude holding pin 190 is pulled out of the attitude holding hole, the restraint of the relative position between the proximal end arm 93 and the distal end arm 95 is released.

Furthermore, as shown in FIG. 5, FIG. 6 (b), FIG. 8 and FIG. 9, the inner box 97 is moved by sliding movement of the inner box 97 with respect to the outer box 96 at a position near the A second posture holding pin 191 is provided to restrain and release the deployed posture and the stored posture.
Hereinafter, the unfolding attitude of the inner box 97 by the sliding movement of the inner box 97 may be referred to as the “second unfolding attitude”, and the storing attitude of the inner box 97 by the sliding movement of the inner box 97 is the “second unfolding attitude”. It may be described as ". In the case where the storage position is simply described, at least the distal end side arm 95 indicates the state of the first storage position and the second storage position.

At a position near the tip of the outer box 96, a fifth attitude holding hole 96H which forms a true circle coaxial with the outer box 96 in the width direction is common to the second storage attitude and the second deployment attitude. It penetrates both sides of outer box 96, and is provided.
Furthermore, in the inner box 97, at a position according to the second storage posture and the second deployment posture, the inner box 97 is concentrically short in the width direction (the direction of the support shaft 94c) (or the slide direction is short). The inner box 97 is provided with sixth, seventh, and eighth posture holding holes 97HL, 97HM, 97HS penetrating in a manner to form an elongated hole). The sixth, seventh, and eighth posture holding holes 97HL, 97HM, and 97HS each correspond to the second storage posture and the plurality of second deployed postures (two deployed postures in the first embodiment). It is formed in position.

Further, the eighth posture holding hole 97HS and the sixth and seventh posture holding holes 97HL and 97HM are arranged apart along the same straight line along the sliding axis of the inner box 97.
That is, in the first embodiment, it is positioned close to the tip of the inner box 97 as a position corresponding to the second storage attitude (also a position according to the overhang attitude S2 at the time of maximum contraction shown in FIG. 8B and FIG. 11). An eighth posture holding hole 97HS is provided in the width direction at the position of.

The second attitude holding pin 191 has an outer diameter dimension that can be inserted with a slight gap from the eighth attitude holding hole 97HS, and the sixth and seventh attitude holding holes 97HL and 97HM, and the outer It has a solid cylindrical shaft with an axial length which can penetrate both sides of the box 96.
Thus, the second posture holding pin 191 is configured to have the eighth posture holding hole 97HS and the sixth and seventh posture holding holes 97HL and 97HM at positions according to the second storage posture and the second deployed posture. It is inserted and removed in either. When the second attitude holding pin 191 is inserted into any of the eighth attitude holding hole 97HS and the sixth and seventh attitude holding holes 97HL and 97HM, the second storage attitude and the two second attitude holding pins The relative position between the outer box 96 and the inner box 97 is restricted by coaxially penetrating the outer box 96 and the inner box 97 at a position corresponding to the inserted posture holding hole among the deployed postures of ing. On the other hand, when the second posture holding pin 191 is pulled out of the posture holding hole, the restraint of the relative position between the outer box 96 and the inner box 97 is released.

Furthermore, as shown in FIGS. 5, 6 (b), 8 and 9, the outrigger device 9 is positioned closer to the proximal end of the surface facing the distal arm 95 of the proximal arm 93 in the storage posture. In addition, a resin or rubber cushion 99 is provided. The cushion 99 has a role as a shock absorbing 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 is applied to the inner peripheral surface of the base end of the outer box 96 against bending load due to reaction force from the BM type link 100. A first blocking member 103 is provided to prevent the occurrence of a defect in the cylinder tube 36a and the like.

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 proximal end 96a on the side of the pressure oil supply and discharge pipe 36c with the outrigger device 9 in the storage posture, sandwiching the horizontal outrigger cylinder 36 of the outer box 96. . Further, the first seat 103a is provided such that the first seat 130a is opposed to the side face of the block 36d with a slight gap.

  Furthermore, the first seat 103a has a rectangular shape in top view, and has an upper part of a substantially square shape and a lower part of a half trapezoidal shape in side view. The upper part of the substantially square is provided with a curved surface at the upper corner opposite to the block 36d. In addition, the lower half of the semi-trapezoid shape has a first inclined surface 131a that inclines obliquely downward toward the inner peripheral surface side of the first proximal end 96a on the first seat surface 130a side. Furthermore, although not shown in the drawing, the first seat 103a is provided with two predetermined spaces along the width direction of the outer box 96 on the side in contact with the inner peripheral surface of the first proximal end 96a. Bolt holes are provided. On the other hand, at the mounting position of the first seat 103a of the first proximal end 96a, two bolt holes are provided at positions corresponding to the bolt holes of the first seat 103a. The first seat 103 a is fastened and fixed from the outer peripheral surface side of the outer box 96 by two fourth bolts 132.

The second seat 103b is provided on the inner peripheral surface of the second base end 96b opposite to the pressure oil supply and discharge pipe 36c with the outrigger device 9 in the storage posture and sandwiching the horizontal outrigger cylinder 36 of the outer box 96. It is done. The second seat 103b is provided in such a state that the second seat 130b abuts on the outer peripheral surface of the cylinder cap portion 36aa.
Furthermore, the second seat 103b has a square shape in a top view, and has an upper portion of a square shape and a lower portion of a half trapezoidal shape in a side view. The lower half of the half trapezoidal shape has a second inclined surface 131b inclined obliquely downward toward the inner peripheral surface side of the second base end 96b on the second seat 130b side.
The details of the role of the first blocking member 103 will be described later.

(Development operation from the first storage posture to the first deployment posture)
Next, the deployment operation from the first storage orientation of the distal end side arm 95 of the outrigger device 9 of the first embodiment to the first deployment orientation will be described.
In order to shift the distal end side arm 95 from the first storage posture to the first deployed posture, it is necessary to first release the restraint state in the first stored posture. That is, as shown in FIG. 8A, the first attitude holding pin 190 inserted in the first and fourth attitude holding holes 94Hh and 96HF is removed. On the other hand, in the example of FIG. 8A, the second attitude holding pin 191 inserted in the fifth and eighth attitude holding holes 96H and 97HS is left as it is. That is, the distal end side arm 95 is made rotatable, and the inner box 97 is restrained so as not to slide.

  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 movement of the inner box 97 is restrained, so the cylinder tube 36a is on the cylinder rod 36b side. The power to draw to By this force, as shown in FIG. 8B, the cylinder tube 36a moves to the cylinder rod 36b side, and the lateral outrigger cylinder 36 rotates around the second link shaft 100b on the other end side of the BM type link 100. And it turns counterclockwise. Then, the other end side of the BM type link 100 is drawn into the inner side of the outer box 96 and the inner box 97, so that the whole of the tip end side arm 95 pivots around the support shaft 94c counterclockwise. At this time, the BM type link 100 collides with the base end portion of the outer box 96 against the pivoting of the distal end side arm 95 due to the boomerang shape of the BM type link 100 (curved shape which is convex upward to the right). Not drawn inwards.

  In the state of FIG. 8B, the fourth posture holding hole 96HF is just in a state of being overlapped with the second posture holding hole 94HS. That is, as the first unfolded attitude by the rotation of the distal end side arm 95, the attitude is unfolded to the position according to the minimum overhanging attitude S1. In the first embodiment, further deployment is possible from this posture, and by continuing the reduction operation of the lateral outrigger cylinder 36, the entire distal arm 95 is further rotated counterclockwise as shown in FIG. As a result, the fourth posture holding hole 96HF overlaps the third posture holding hole 94HL. That is, as the first unfolded posture by the rotation of the distal end side arm 95, it becomes the maximum overhanging posture U1.

  Here, the lateral outrigger cylinder 36 is in a state of being expanded by a predetermined length in the first storage posture, not in the minimum reduction state, in order to shift from the first storage posture to the first deployment posture. . That is, there is a margin for performing the reduction operation necessary for the transition to the first deployed position.

(Development operation from the second storage posture to the second deployment posture)
Next, the deployment operation from the second storage orientation of the distal end side arm 95 of the outrigger device 9 of the first embodiment to the second deployment orientation will be described.
In FIG. 9, the distal end side arm 95 is in the first deployed position, and the inner box 97 is restrained in the minimum reduction state, and is in the second stored position.

  In order to shift the distal end side arm 95 from the second storage posture to the second deployed posture in such a state, it is necessary to first set the released state in the first deployed posture to the restricted state. That is, as shown in FIG. 10, the first attitude holding pin 190 is inserted into the third and fourth attitude holding holes 94HL and 96HF in the first deployed attitude shown in FIG. On the other hand, the second attitude holding pin 191 inserted in the fifth and eighth attitude holding holes 96H and 97HS is removed. By this, the restriction of the slide movement of the inner box 97 is released. That is, the distal end side arm 95 is restrained in a non-rotatable state around the support shaft 94c, and the inner box 97 is made slideable.

  In this state, when the operator operates the operation unit 11 or the remote control device 162 to extend and operate the horizontal outrigger cylinder 36, the rotational movement of the distal end side arm 95 is restrained, so the cylinder tube 36a is a BM type. It will be in the state fixed to the center bracket 94 via the link 100. Therefore, the cylinder rod 36b is operated to extend. Since the tip of the cylinder rod 36b is fixed at a position near the tip of the inner box 97, the inner box 97 extends in the extension direction as shown in FIG. 10 by the force applied by the extension of the cylinder rod 36b. Slide to move.

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

(Grounding operation of the 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 setting the maximum extension position of the distal end side arm 95 to the second spread 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 distal end side arm 95 is restrained in the state of the maximum overhanging posture U1 and the overhanging posture U2 at the maximum extension time.

  In this state, when the operator operates the operation unit 11 or the remote control device 162 to extend the longitudinal outrigger cylinder 37, as shown in FIG. 11, the longitudinal outrigger cylinder 37 performs a second rotation on the base bracket 90 side. It rotates around the axis 91 c and clockwise. Along with this, the proximal end arm 93 rotates with the distal end arm 95 around the first rotation shaft 91 b on the base bracket 90 side in the clockwise direction. Then, as shown by the solid line in FIG. 11, it is provided at the tip of the inner box 97 in a state in which the first deployed posture and the second deployed posture are the maximum overhanging posture U1 and the overhanging posture U2 at the maximum elongation. Float 98 contacts the ground.

  In addition, according to the shape, height, etc. of the ground to be in contact with the ground, as shown by the dotted line in FIG. Further, in the first embodiment, the inner box 97 can be grounded even in the state of the second storage orientation (the deployment orientation S2 at the time of the maximum contraction).

(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 horizontal outrigger cylinder 36 is extended in a state where the first attitude holding pin 190 is removed and the second attitude holding pin 191 is inserted, and the distal end side arm 95 is It is assumed that the outrigger 9 is placed in the storage posture by pivoting in the downward direction until the outer box 96 abuts against the cushion 99. From this state, when the lateral outrigger cylinder 36 is further extended by the operator's erroneous operation or the like, a bending load is applied to the cylinder tube 36a.

This also applies to the case where the lateral outrigger cylinder 36 is operated to extend in a state in which the outrigger device 9 is in the storage attitude and the first attitude holding pin 190 and the second attitude holding pin 191 are inserted. When the lateral outrigger cylinder 36 is reduced in this state, a bending load is applied in the opposite direction to that when the cylinder tube 36a is extended.
Specifically, as shown in FIG. 13 (b), when the lateral outrigger cylinder 36 is further extended under the condition that the distal end side arm 95 can not turn in the lowering direction, the BM type link 100 is generated against the cylinder extension thrust Fc. The link reaction force Fa received from is generated. Then, a 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 supporting 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 linear distance between the heights (the distance between the fulcrum and the power point).

When a first bending moment MxL is applied to the cylinder cap portion 36aa, for example, as shown in FIG. 13 (b), in particular, 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 it.
On the other hand, although not shown, when the lateral outrigger cylinder 36 is contracted when the outrigger device 9 is restrained in a state in which the distal end side arm 95 can not be rotated or extended in the storage posture, A link reaction force (-Fa) received from the BM type link 100 is generated with respect to Fc). As a result, a second bending moment (-MxL) in the direction opposite to the first bending moment MxL acts on the cylinder cap portion 36aa of the cylinder tube 36a.

Also in this case, if there is no support in the second bending direction (-X direction), a large load may be applied in the second bending direction, and trouble may be generated in the cylinder tube 36a and in the surrounding parts thereof. is there.
Therefore, in the first embodiment, as shown in FIG. 12, the first seat 103a is provided on the inner peripheral surface of the first proximal end 96a of the outer box 96, and the second proximal end 96b of the outer box 96 is provided. The second seat 103 b is provided on the inner circumferential surface of

  Thereby, when the first bending moment MxL is generated, as shown in FIG. 14A, the first seat surface 130a of the first seat 103a abuts on the cylinder cap portion 36aa, and the link reaction force is generated. Support Fa X direction component Fxa. As a result, a reaction force Fxs is generated to reduce the load, and it is possible to avoid the occurrence of a defect in the cylinder tube 36a and hence the parts around it.

When a second bending moment (-MxL) in the opposite direction is generated, although not shown, the second seat 130b of the second seat 103b is an X-direction component of the link reaction force (-Fa). By supporting (-Fxa), it becomes possible to prevent the occurrence of a failure in the cylinder tube 36a and thus the parts around it.
When the distal end side arm 95 is rotated in the direction from the storage position to the first deployed position, the cylinder cap portion 36 aa of the second seat 103 b is moved by the weight of the outer box 96 and the inner box 97. Is pressed against the seat 130b of the seat. At this time, when there is no second seat 103b, rattling occurs. That is, the second seat 103 b also has a function of preventing rattling when the distal end side arm 95 is rotated.

  On the other hand, as shown in FIG. 14 (b), a state in which the first attitude holding pin 190 and the second attitude holding pin 191 are inserted with the distal end side arm 95 in the first unfolding attitude and the second unfolding attitude. It is assumed that the lateral outrigger cylinder 36 is extended. In this case, the first bending moment MxL becomes small because the angle θ between the extension direction of the lateral outrigger cylinder 36 and the BM type link 100 becomes small, and the problem that may occur when a large load as described above is applied is It does not occur. The same applies to the case where the lateral outrigger cylinder 36 is reduced under the same conditions.

Here, in the first embodiment, the tower crane 1 corresponds to a working machine, and the BM type link 100 corresponds to a link member for power transmission.
In the first embodiment, the first attitude holding pin 190, the first attitude holding hole 94Hh, and the second and third attitude holding holes 94HS and 94HL correspond to the first attitude holding means.
In the first embodiment, the second attitude holding pin 191, the eighth attitude holding hole 97HS, and the sixth and seventh attitude holding holes 97HL and 97HM correspond to the second attitude holding means.

In the first embodiment, the first posture holding hole 94Hh and the second and third posture holding holes 94HS and 94HL correspond to the first posture holding hole, and the eighth posture holding hole 97HS and the The sixth posture holding holes 97HL and 97HM correspond to the second posture holding holes.
In the first embodiment, the outer box 96 and the inner box 97 correspond to the plurality of nested arms, and the first to third sliding pads 120A to 120C correspond to the sliding members.
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. It corresponds.

(Operation and effect of the first embodiment)
The outrigger device 9 according to the first embodiment is provided on the chassis frame 2 of the tower crane 1 so as to be pivotable about a vertical axis and be provided with a proximal end arm 93 which can be raised and lowered around a horizontal first rotation shaft 91b. And the distal end portion of the proximal end arm 93 includes a nested distal end arm 95 rotatably supported about a pivot 94c parallel to the first rotation shaft 91b at the proximal end portion. It has a storage posture at the time and a deployment posture at the time of work. The outrigger device 9 is a support shaft at a position close to the distal end of the proximal end arm 93 at one end portion thereof, and the first link shaft 100a by a first link shaft 100a parallel to the first rotation shaft 91b. The BM-type link 100 rotatably mounted around and the tip end side arm 95 are disposed inside, and the end on the cylinder rod 36b side is supported at a position near the tip end of the tip end side arm 95, the cylinder A lateral outrigger cylinder 36 rotatably mounted around the second link shaft 100b parallel to the first rotation shaft 91b to the other end (movable end) of the BM type link 100 at the end on the tube 36a side and And. Then, the BM type link 100 is configured to convert the stretching force of the lateral outrigger cylinder 36 into the turning force of the distal end side arm 95.

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

In this configuration, when the distal end side arm 95 is pivoted, the base end of the distal end side arm 95 is pivoted along the shape of the BM type link 100, so the lower end portion and the distal end side of the BM type link 100 It is possible to avoid contact with the proximal end of the arm 95. As a result, the BM type link 100 can be arranged compactly.
In addition, the outrigger device 9 according to the first embodiment further includes a nested outer box 96 and an inner box 97 in which the distal end side arm 95 is expanded and contracted by the expansion and contraction force generated by the lateral outrigger cylinder 36. In addition, mutual movement between the proximal arm 93 and the distal arm 95 at positions corresponding to the first storage posture and the first deployment posture, which are the storage posture and the deployment posture for the pivotal movement of the distal arm 95, respectively. The first posture holding means (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 and 94HL) for restraining and releasing the position are used. Prepare. Furthermore, the mutual positions of the outer box 96 and the inner box 97 are restrained and released at positions respectively corresponding to the second storage posture and the second deployment posture, which are the storage posture and the deployment posture for the extension and contraction operation of the distal end side arm 95. The second attitude holding means (in the first embodiment, the second attitude holding pin 191, the eighth attitude holding hole 97HS, and the sixth and seventh attitude holding holes 97HL and 97HM) are provided.

  Then, when the positions of the proximal end arm 93 and the distal end arm 95 are constrained by the first attitude holding means, the rotational force of the BM type link 100 by the expansion and contraction operation of the horizontal outrigger cylinder 36 is Hold posture constrained for transmission. On the other hand, the mutual positions of the proximal arm 93 and the distal arm 95 are not restrained by the first posture holding means, and the mutual positions of the outer box 96 and the inner box 97 are by the second posture holding means. When being restrained, the rotational movement is performed with respect to the transmission of the rotational power through the BM type link 100 by the expansion and contraction operation of the lateral outrigger cylinder 36.

  Also, when the relative position between the outer box 96 and the inner box 97 is constrained by the second posture holding means, the posture held against transmission of the expansion / contraction force by the expansion / contraction operation of the lateral outrigger cylinder 36 is maintained. . On the other hand, the mutual positions of the proximal arm 93 and the distal arm 95 are restrained by the first posture maintaining means, and the mutual positions of the outer box 96 and the inner box 97 are restrained by the second posture maintaining means. When not, the expansion and contraction operation of the inner box 97 is performed with respect to the transmission of the expansion and contraction force by the expansion and contraction operation of the lateral outrigger cylinder 36.

  With this configuration, the first and second storage 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, from the first storage posture to the first deployment posture by the rotation operation of the distal end side arm by the common one horizontal outrigger cylinder 36, and from the second storage posture by the extension operation of the inner box 97 It is possible to shift to the second deployment position. Therefore, it is possible to obtain the power of the up and down movement and the extension and contraction movement of the distal end side arm 95 without adding a new outrigger cylinder and without increasing the occupied area of the outrigger device 9.

  In addition, the outrigger device 9 according to the first embodiment further includes first and second pressure oil supplied into the cylinder tube 36a provided in the cylinder tube 36a, and first and second pressure oil for discharging the pressure oil in the cylinder tube 36a. The pressure oil supply and discharge pipe 36 c is connected to the two pressure oil supply and discharge ports. In addition, an angular tubular pipe box 101 is provided which covers the pressure oil supply and discharge pipe 36c provided on the outer peripheral surface of the cylinder tube 36a. Furthermore, the first to third slide pads 120A to 120C provided between the inner peripheral surface of the inner box 97 of the distal end side arm 95 and the outer peripheral surface of the cylinder tube 36a and the outer peripheral surface of the pipe box 101 Prepare.

With this configuration, direct contact with the inner circumferential surface can be avoided even when a force is applied to press the cylinder tube 36a or the pipe box 101 against the inner circumferential surface of the inner box 97, and a lateral outrigger It is possible to smoothly perform the sliding operation of the inner side 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 where the pivoting operation of the distal end side arm 95 is physically blocked (a state where it abuts on the cushion 99 or a state where it is restrained by a posture holding pin) Against the first bending moment MxL generated at the end (cylinder cap portion 36aa) on the cylinder tube 36a side of the lateral outrigger cylinder 36 by the application of the rotational power by the lateral outrigger cylinder 36 via the BM type link 100. And a first blocking member 103 for blocking displacement of the end in the bending direction.

  Here, in the outrigger device 9 according to the first embodiment, when the lateral outrigger cylinder 36 is in the extension operation, the lateral outrigger is in a state where the pivoting movement of the distal end side arm 95 to the first deployed position is blocked. A first bending moment MxL is generated via the BM type link 100 at the end of the cylinder on the cylinder tube 36a side. As a result, a first bending load is generated which displaces the end of the lateral outrigger cylinder on the side of the cylinder tube 36a in the first bending direction (X direction). On the other hand, when the turning operation of the distal end side arm 95 to the first storage posture is blocked during the reduction operation of the lateral outrigger cylinder 36, the end portion on the cylinder tube 36a side of the lateral outrigger cylinder is A second bending moment (-MxL) is generated through the BM type link 100. As a result, a second bending load is generated which displaces the end of the lateral outrigger cylinder 36 on the cylinder tube 36 a side in a second bending direction (−X direction) opposite to the first bending direction.

The first blocking member 103 is provided on a first inner circumferential surface, which is an inner circumferential surface on a first bending direction side, across the lateral outrigger cylinder 36 at the proximal end of the distal end side arm 95. A second seat 103b provided on a second inner circumferential surface, which is an inner circumferential surface on the second bending direction side, with the first seat 103a and the lateral outrigger cylinder 36 at the base end of the distal end side arm 95 interposed therebetween. And
The first seat 103a is attached to the end portion of the extended lateral outrigger cylinder 36 on the cylinder tube 36a side when the pivoting operation corresponding to the extending operation of the distal end side arm 95 is in the blocking state. Abuts from the inner peripheral surface side to support a first bending load applied to the end.

In addition, the second seat 103b is a second seat 103b at the end portion on the cylinder tube 36a side of the lateral outrigger cylinder 36, which has been subjected to the contraction operation, when the pivoting operation corresponding to the contraction operation of the distal end side arm 95 is blocked. Abuts from the inner circumferential surface side to support a second bending load applied to the end.
With this configuration, it is possible to support the bending load in the first bending direction by the first bending moment MxL by the first seat 103a, and the second bending by the second bending moment (-MxL) It becomes possible to support the bending load in the direction by the second seat 103b. This makes it possible to avoid the occurrence of a defect in the cylinder tube 36a and hence the parts around it.
The tower crane 1 according to the first embodiment also includes the outrigger device 9 described above.
With this configuration, the same operation and effect as the outrigger device 9 can be obtained.

Second Embodiment
(Constitution)
Next, a second embodiment of the present invention will be described.
The second embodiment differs from the first embodiment in that a bending load is supported by a 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 denoted by the same reference numerals, and the description will be appropriately omitted, and different parts will be described in detail.

As shown in FIG. 15, FIG. 16 (a) and (b), the second outrigger device 9A according to the second embodiment is the first blocking member 103 and the lateral member in 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 a second proximal end 96b of the outer box 96.
The hook main shaft 104a is provided on the inner peripheral surface of the second proximal end 96b, and has a rectangular vertically long upper portion and a semi-trapezoidal lower portion in a side view. The rectangular vertically long upper portion has a first support surface 140 a that abuts on the outer peripheral surface of the second cylinder cap portion 36 ab in the storage posture of the outrigger device 9. In addition, the lower half of the half trapezoidal shape has a third inclined surface 142a that inclines obliquely downward toward the inner peripheral surface side of the second base end 96b on the first support surface 140a side.

The claw portion 104b is provided so as to project upward from the upper end of the hook main shaft 104a beyond the second base end 96b when the outrigger device 9 is in the storage posture. The claw portion 104b extends from the upper end of the hook main shaft 104a toward the block 36d along the curved surface of the upper end of the second cylinder cap 36ab.
Further, the claw portion 104b is located on the block 36d side with respect to the central position of the upper end of the second cylinder cap portion 36ab when the outrigger device 9 is in the storage posture, and the upper end is From the top of the hook main shaft 104a, it extends straight diagonally to the upper right to form an inclined surface, and then extends straight to the tip in a horizontal direction to form a horizontal surface.

Furthermore, the lower end portion of the claw portion 104b has a shape along 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 abuts on the upper end portion of the second cylinder cap portion 36ab when the outrigger device 9 is in the storage posture.
The toe portion 104c is formed so as to project downward from the tip of the claw portion 104b when the outrigger device 9 is in the storage posture. Specifically, the toe portion 104c is a first surface 140c slightly extending vertically downward from the lower end side of the tip end portion of the claw portion 104b and the lower end of the claw portion 104b from the upper end side of the tip portion of the claw portion 104b. And a fourth inclined surface 141c obliquely extending downward and to the right to a height position slightly above the end face. Furthermore, 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. And a fifth inclined surface 143c that obliquely extends to the lowermost position on the cap portion 36ab side. Furthermore, there is provided a third surface 144c connecting the lower end of the fifth inclined surface 143c and the lower end of the second surface 142c horizontally.

  The hook attachment portion 104d extends to a position beyond the second base end portion 96b in a direction opposite to the toe portion 104c side of the claw portion 104b in the storage posture in which the outrigger device 9 extends. It has a connecting portion, and a mounting claw portion 140d extending vertically downward along the outer peripheral surface of the second proximal end 96b from the distal end portion of the connecting portion. Further, the lower end portion 141d is in contact with the upper end surface of the second proximal end portion 96b.

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

The groove portion 360 is formed of a groove having a shape along the shape of a composite surface constituted by the first surface 140c, the fifth inclined surface 143c and the third surface 144c of the toe portion 104c.
The toe portion 104c of the second blocking member 104 has the first surface 140c and the fifth inclined surface on the inner circumferential surface of the groove portion 360 of the second cylinder cap portion 36ab when the outrigger device 9 is in the storage posture. 143c and the third surface 144c are configured to abut.

(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. In addition, about each bending moment and each reaction force which are described below, it becomes the same as what was demonstrated based on FIG.13 (b) in the said 1st Embodiment.

That is, as shown in FIG. 17 (a), when the second horizontal outrigger cylinder 36A is further extended under the condition that the distal end side arm 95 can not turn in the lowering direction, the BM type link against the cylinder extension thrust Fc A link reaction force Fa received from 100 is generated. Then, a 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 as a both-end support beam (a state in which the second lateral outrigger cylinder 36A lies like a beam) Thus, the distance La becomes extremely larger for the distance La from the cylinder rod 36b side to the force point (center of the second link shaft 100b) and for the distance Lb from the cylinder tube side to the force point. 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, particularly when there is no support in the first bending direction (X direction), and the cylinder tube 36a There is a possibility that a fault may occur in the parts around it.
On the other hand, although not shown, when the second lateral outrigger cylinder 36A is contracted when the outrigger device 9 is restrained in a state in which the distal end side arm 95 can not rotate and extend and retract in the storage posture, 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 opposite direction to the first bending moment MxL is applied to the second cylinder cap portion 36ab of the cylinder tube 36a.

Also in this case, if there is no support in the second bending direction (-X direction), a large load may be applied in the second bending direction, and trouble may be generated in the cylinder tube 36a and in the surrounding parts thereof. is there.
Therefore, in the second embodiment, as shown in FIG. 15, FIG. 16A and FIG. 16B, the second base end 96b of the outer box 96 has the upper end of the second cylinder cap 36ab in the storage posture. A hook-shaped second blocking member 104 for holding the portion is provided.

Thereby, 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 surface of the toe portion 104c of the second blocking member 104 are generated. The third surface 144c 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, a reaction force Fxs is generated to reduce the load, and it is possible to avoid the occurrence of a defect in the cylinder tube 36a and hence the parts around it.
Also, when the second bending moment (-MxL) in the reverse direction 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) It is possible to prevent the occurrence of a defect in the cylinder tube 36a and thus in the parts around it.

(Operation and Effect of Second Embodiment)
The second outrigger device 9A according to the second embodiment is a second blocking member 104 and a second lateral member in place of the first blocking member 103 and the lateral outrigger cylinder 36 of the outrigger device 9 according to the first embodiment. 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 of the proximal end portion of the distal end side arm 95 across the second horizontal outrigger cylinder 36A. The end (second cylinder cap portion 36ab) on the cylinder tube 36a side of the second horizontal outrigger cylinder 36A, which has been operated to be contracted, when the rotational operation corresponding to the contraction operation of the distal end side arm 95 is in the blocking state. And a hook main shaft 104a that is in contact with the inner peripheral surface side to support a second bending load applied to the end. In addition, the lower end portion has a shape following 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 storage posture. It comprises the configured claw portion 104b. Furthermore, it extends from the tip of the claw portion 104b toward the side surface portion on the first bending direction (X direction) side of the second cylinder cap portion 36ab of the second horizontal outrigger cylinder 36A, and the side surface in the storage posture The portion includes a toe portion 104c configured to abut on the first bending direction side.

  Specifically, the second cylinder cap portion 36ab has a rounded upper end portion, and a locking portion for hooking the toe portion 104c to the side surface portion on the cylinder tube 36a side of the upper end portion. Groove portion 360 is provided. In addition, the toe portion 104c is a first surface 140c slightly extending vertically downward from the lower end side of the tip end portion of the claw portion 104b, and the lower right side from the lower end of the first surface 140c as compared to the second surface 142c. A fifth inclined surface 143c slightly extending obliquely to the lowermost position on the side of the second cylinder cap portion 36ab, and a third horizontally connecting the lower end of the fifth inclined surface 143c and the lower end of the second surface 142c. And the face 144c.

The groove portion 360 is formed of a groove having a shape conforming to the shape of a composite surface constituted of the first surface 140c, the fifth inclined surface 143c and the third surface 144c of the toe portion 104c. When 9 is in the storage posture, the first surface 140c, the fifth inclined surface 143c and the third surface 144c are in 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 2 in contact with the groove portion 360 of the cylinder cap portion 36ab to support 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). This makes it possible to avoid the occurrence of a defect in the cylinder tube 36a and hence the parts around it.

(Modification)
In each of the above embodiments, the base end of the distal end side arm 95 is used in the first embodiment in order to prevent the displacement due to the bending load generated at the end portion on the cylinder tube side by the operation of the lateral outrigger cylinder in the storage posture. The first blocking member 103 is provided on the inner circumferential surface on the displacement direction side across the lateral outrigger cylinder, and in the second embodiment, the hook shaped second blocking member 104 is provided at the base end of the distal end side arm 95. Provided. Not limited to these configurations, for example, the configuration of the seat of the first blocking member 103 may be changed or the hook of the second blocking member 104, as long as the configuration is capable of avoiding the occurrence of a defect due to a bending load. Other configurations, such as changing the shape and the mounting position, may be used.

  In each of the above embodiments, the boomerang-shaped BM type link 100 has been described as an example of the link member for converting the expansion and contraction force of the lateral outrigger cylinder into the turning force of the distal end side arm. For example, as long as the distal end side arm 50 is configured such that the link does not contact the base end portion of the distal end side arm and sufficient rotational power can be transmitted, the configuration or mounting position may be changed. Good.

  In each of the above-described 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 various cranes and various work machines other than cranes as long as it is a work machine to which the outrigger device can be applied.

1 Tower crane (working machine)
Reference Signs List 2 chassis frame 3 traveling device 4 base 5 column 6 crane device 7 relief boom 8 bending boom 9 outrigger device 9A second outrigger device 9RF, 9RR, 9LF and 9LR right front, right rear, left front and left rear outrigger device 10 driver's seat 11 operation part 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 hydraulic motor for turning 31 up and down boom telescopic hydraulic cylinder 32 folding boom telescopic hydraulic cylinder 33 for winch Hydraulic motor 34 Unfolding 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 bending boom undulating Hydraulic cylinder 36 Horizontal outrigger cylinder 36A Second horizontal outrigger cylinder 36a Cylinder tube 36aa Cylinder cap 36ab Second cylinder cap 36b Cylinder rod 36c Pressure oil supply and discharge pipe 36d Sub plate 36RF, 36RR, 36LF and 36LR Right front, right rear Left front and left rear horizontal outrigger cylinders 37 Vertical outrigger cylinders 37RF, 37RR, 37LF and 37LR Right front, right rear, left front and left rear vertical outrigger cylinders 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 Outrigger device switching control valve 83 Swing control switching valve 84 Boom telescopic Switching control valve 85 Switching control valve for winch 86 Switching control valve for boom relief 87 Horizontal outrigger cylinder switching valve 88 Vertical outrigger cylinder switching valve 90 Base bracket 91 Bracket part 91a 1st mounting arm 91b 1st rotating shaft 91c 2nd Rotary shaft 92 Rotary support 93 Base end arm 94 Center bracket 94a Second mounting arm 94b Third rotary shaft 94c Support shaft 94Hh, 94HS, 94HL 1st, 2nd, 3rd posture holding holes 95 Tip side Arm 96 outer box 96a first proximal end 96b second proximal end 96HF fourth attitude holding hole 96H fifth attitude holding hole 97 inner box 97HL, 97HM, 97HS sixth, seventh, eighth attitude Retaining hole 98 Float 99 Cushion 100 BM type link 100a, 100b 1st, 2nd re K-shaft 101 pipe box 102B first mounting portion 102C second mounting portion 103 first blocking member 103a first seat 103b second seat 104 second blocking member 104a hook main shaft 104b claw portion 104c toe portion 104d Hook mounting portion 120A to 120C first to third sliding pads 121A to 121C first to third sliding surfaces 130a first seating surface 131a first inclined surface 130b second seating surface 131b second Inclined surface 140a first support surface 140c first surface 140d mounting claw portion 141a second support surface 141d lower end portion 143c fifth inclined surface 144c third surface 160 controller 161 receiver 162 remote control device 180 main relief valve (Unload valve)
181 Solenoid for unloading valve operation 182 Relief valve for hook fixation 182a Hook relief solenoid 182b Hook relief valve 190, 191 1st, 2nd attitude holding pin 360 Groove part 820, 840, 860 1st, 2nd, 3rd electromagnetic Switching valve

Claims (7)

A proximal arm provided rotatably on a horizontal axis on a base of a working machine, and a distal end of the proximal arm, a first axis whose proximal end is parallel to the horizontal axis An outrigger device comprising: a nested distal end arm pivotally supported so as to freely rotate around, and having a storage posture when stored and a deployment posture when working;
A power transmission rotatably mounted at a position close to the distal end of the proximal end arm by a second shaft parallel to the first shaft, the second shaft being parallel to the first shaft. Link member,
It is disposed inside the distal end arm in a posture parallel to the longitudinal direction of the distal end arm, and one end is supported at a position near the tip of the distal end arm, and the other end is the link member An outrigger cylinder rotatably journalled at the movable end which is the other portion of
The bending moment generated at the other end of the outrigger cylinder due to the application of the extension force of the outrigger cylinder when in the storage posture is abutted against the other end and displacement of the outrigger cylinder in the bending direction An outrigger device comprising a blocking member for blocking the inner side of the distal arm. In the outrigger device in the storage posture,
The bending moment generated by the extension operation of the outrigger cylinder when the pivoting movement of the tip end arm in the rotation direction corresponding to the extension operation of the outrigger cylinder is physically prevented is taken as a first bending moment ,
Opposite to the first bending moment caused by the reduction operation of the outrigger cylinder when the pivotal movement of the distal side arm in the rotation direction corresponding to the reduction operation of the outrigger cylinder is physically blocked. Let the bending moment in the direction be the second bending moment
The blocking member is
A first blocking portion for supporting a displacement of the outrigger cylinder caused by applying a first bending load generated from the first bending moment to the other end of the outrigger cylinder;
The second blocking portion for supporting the displacement of the outrigger cylinder caused by applying a second bending load generated from the second bending moment to the other end portion of the outrigger cylinder. Outrigger device. In the outrigger device in the storage posture,
The operation of the outrigger cylinder is performed when the pivotal movement of the distal end arm in the rotation direction corresponding to the operation content of one of the expansion operation and the contraction operation of the outrigger cylinder is physically blocked. Let the bending moment generated by operating at be the first bending moment,
The outrigger cylinder operates with the other operation content when the pivoting movement of the outrigger cylinder corresponding to the other operation content of the extension operation or the reduction operation is physically blocked. A bending moment in the opposite direction to the first bending moment generated by
The blocking member is
A hook main shaft supporting a displacement caused by applying a first bending load generated from the first bending moment to the other end of the outrigger cylinder;
The outrigger device according to claim 1, further comprising: a claw portion that supports displacement caused by applying a second bending load generated from the second bending moment to the other end of the outrigger cylinder. The proximal end arm at a position corresponding respectively to a first storage posture as the storage posture with respect to the pivotal movement of the distal end arm and a first deployment posture as the deployable posture with respect to the pivotal movement of the distal end arm First attitude holding means for restraining the mutual position of the arm and the distal end arm,
The distal arm is
When the relative position between the proximal end arm and the distal end arm is restrained by the first posture holding means, the transmission of the rotational force via the link member by the expansion and contraction operation of the outrigger cylinder is performed. Hold a position that is constrained against
When the relative position between the proximal end arm and the distal end arm is not restricted by the first posture holding means, the transmission of the rotational power via the link member by the expansion and contraction operation of the outrigger cylinder The outrigger device according to any one of claims 1 to 3, wherein the pivoting motion is performed. The distal end arm includes a plurality of nested arms that are telescopically operated by the telescopic force generated by the telescopic operation of the outrigger cylinder,
The plurality of nested arms at positions respectively corresponding to a second storage posture, which is the storage posture for the expansion and contraction movement of the distal end side arm, and a second deployment posture, which is the expansion posture for the expansion and contraction movement of the distal end side arm A second posture holding means for restraining the mutual position of
The distal arm is
The second posture holding means holds the posture restricted with respect to the transmission of the expansion / contraction force by the expansion / contraction operation of the outrigger cylinder when the mutual positions of the plurality of arms are restrained by the second posture holding means;
When the relative positions of the proximal end arm and the distal end arm are restrained by the first posture holding means and the mutual positions of the plurality of arms are not restrained by the second posture holding means The outrigger device according to claim 4, wherein the plurality of arms extend and retract in response to the transmission of the expansion and contraction force by the expansion and contraction operation of the outrigger cylinder. The first posture holding means is provided at the distal end portion of the proximal end arm and at the proximal end portion of the distal end arm at positions respectively corresponding to the first storage posture and the first deployed posture. A plurality of first attitude holding holes formed when a plurality of attitude holding pin holes are coaxially penetrated continuously, and positions corresponding to the first storage attitude and the first deployed attitude, respectively A first attitude holding pin which is an attitude holding pin which is inserted into and removed from the first attitude holding hole to restrain and release the relative position of the proximal arm and the distal end arm;
In the second posture holding means, a plurality of posture holding pin holes provided in the plurality of arms are continuously coaxial at positions respectively corresponding to the second storage posture and the second deployed posture. The plurality of second posture holding holes formed when penetrating and the second posture holding holes at positions respectively corresponding to the second storage posture and the second deployed posture are inserted and removed. The outrigger device according to claim 5, further comprising a second attitude holding pin for attitude holding which restrains and releases the mutual position of the arms.   The outrigger device according to any one of claims 1 to 6, wherein the link member has a shape in which a central portion of a rectangular plate is bent and formed into a substantially V shape.

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