JPS6033696B2 - Truck crane outrigger - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an outrigger for a truck crane, and particularly to an outrigger for a large truck crane capable of lifting loads of several tens of tons.

In this way, a large truck crane is
Since the load on the vehicle, inside the vehicle, axle load, etc. are restricted by the road traffic regulations of each country, a crane base 29 that supports the telescopic beam 28 in a cantilever manner as shown in FIGS. 9 and 10 is installed. It is rotatably mounted on the rear part of the car body frame, and outriggers 30 that can be extended to both sides are attached to the lower surface of the car body frame before and after the center of rotation of the crane base. , a pair of parallel horizontal beams 31 each having a vertical telescoping support leg (hydraulic cylinder 4) attached to the tip thereof, each having a cylindrical body with a rectangular cross section, is connected and fixed to a pair of horizontal base cylinders 32, each of which can be illuminated. The outrigger unit is constructed on the underside of the vehicle body frame by inserting the bracket into the horizontal base cylinder and fixing the brackets fixed to the tops of both ends of the horizontal base cylinder to the brackets protruding from both sides of the vehicle body frame. It is common practice to measure the drop in the center of gravity of the truck crane.

The outrigger unit shown in Fig. 10 has base cylinders 32, 32 with a length equal to approximately twice the outside diameter of the telescopic support leg 4 subtracted from the inside of the vehicle B, and an end plate that closes the tail end of one of the base cylinders and an end plate that closes the tail end of the base cylinder on the other side. This shows where the base cylinder is joined to reinforce the closing part of the base cylinder. As shown in Japanese Unexamined Patent Publication No. 109654/1980, the lifting performance of such a truck crane is mainly regulated by the boom strength when the boom inclination angle 8 is large, and is mainly regulated by the boom strength while the boom inclination angle 8 is small. Regarding crane stability, the relative position of the center of gravity of the automobile including the outrigger and the center of gravity of the swinging crane including the crane base 29 changes as the crane base turns. The critical moment for overturning is not uniform all around, but as shown in the crane overturning critical moment curve 33 in Fig. 10,
When the telescoping beam 28 is located above or between the ground contact portions of both outriggers at the rear of the vehicle (when suspended from the rear), it is at its maximum or close to it, and when the telescoping beam turns around a position perpendicular to the longitudinal direction of the vehicle. (When suspended from the side) is the smallest except for when suspended from the front (when the telescopic beam turns to the front of the vehicle).

This is because the inside of the car B is regulated by road traffic regulations, so it is not possible to increase the extended length L' of the outriggers on both sides, and the heavy driver's cab 34, engine 35, etc. are installed at the front end of the long car body. According to Noto. The moment curve 33 is a curve in which the length of the radius with the crane base rotation center 0 as the pole is made equal to the crane tipping limit moment when the telescopic boom is positioned on the radius vector. Therefore, when the lifting capacity is regulated by this tipping limit moment and the boom inclination is small (when the working radius is large), the maximum lifting load for side lifting is smaller than that for rear lifting, and the rear lifting The moment curve stored in the crane safety device must be limited to circle 36, which has the crane tipping limit moment during side lifting as the moving seat. I had to.

In order to increase the lifting capacity when the boom inclination is small, the length of the horizontal base cylinder 32 is made to be closer to the length of the inside of the vehicle B minus the outer diameter of the telescopic support leg 4, and the length is adjusted accordingly. Even if the length of the horizontal beam 31 is increased, it is not possible to increase L' during outrigger extension so that the diameter length of the circle 36 approaches the critical moment for tipping over the crane during rear suspension. In order to further increase the inside diameter, the length of the overlapping portion of the overhanging horizontal beam 31 and the horizontal base tube 32 is made shorter than before, which significantly increases the weight of the outrigger, causing the truck crane to be unable to move on the road (while the outrigger is attached). become unable to run.

This is due to the following reason.

When carrying out cargo handling work with the outriggers extended, the enormous bending moment in the vertical plane that acts on the horizontal beam 31
The moment is transmitted to the horizontal base cylinder through the contact portions at both ends of the overlapped portion between this and the horizontal base cylinder 32, and the horizontal base cylinder transmits this moment to the vehicle body frame 1. , the extreme pressure that the top surface of the horizontal beam 31 exerts on the tip of the horizontal base tube 32, and the extreme pressure that the bottom surface of the tail end of the horizontal beam exerts on the horizontal base tube all act on the top and bottom plates of the horizontal base tube 32, and this Since the transmission must be transmitted to the entire horizontal base cylinder through its side plates, the thickness of the entire horizontal base cylinder increases at an accelerating rate as the length of the overlapping portion is shortened, and the outrigger weight also increases. This is because it increases significantly.

The present invention makes the length of this overlapping part shorter than the conventional type,
By increasing L' during outrigger extension, the lifting capacity is improved when the boom slope is small, and the outrigger weight is not increased, allowing the truck crane to travel on the road with the outriggers attached. The purpose is to make it possible. In the present invention, a pair of cylindrical horizontal beams each having a rectangular cross section and a vertical bracing at the tip are placed in opposite directions and parallel to each other on the underside of the vehicle body frame in a direction perpendicular to the longitudinal direction of the vehicle body. In order to support the beam in a slidable manner, side plates are provided on both sides of a horizontal bottom plate whose lower end is formed in the guide path at the top of the cylindrical horizontal beam, which are located on substantially the same vertical plane as both side plates of the cylindrical horizontal beam. hollow arm,
Each of the cylindrical horizontal beams is protrudingly fixed to the side surface of the vehicle body frame on the side where the cylindrical horizontal beam extends, and is attached to both side plates of the hollow arm base to enable the cylindrical horizontal beam to slide in cooperation with the bottom plate. The open upper end of the member is fixed for relative rotation in a vertical plane that includes the axis of the hollow arm, and in cooperation with this, each cylindrical horizontal The beam is fixedly connected by a guide member that freely supports the beam between a storage position in the vehicle and a light projecting to the side of the vehicle body, and the tail end of the cylindrical horizontal beam in the projecting position is brushed as described above; The present invention is characterized in that a stopper means is provided to be positioned on the bottom side of the shaped support member.

Hereinafter, in order to make the radial length of the circle 36 very close to the crane tipping limit moment during rear suspension, the length of the horizontal beam including the middle vertical support legs is made equal to the inside of the car B, and the hollow arm is An embodiment of the present invention in which the invention is fully protruded will be described with reference to the drawings.

1 is the body frame of a large truck crane, and the front and rear of the body frame are connected to the ground G via appropriate suspension systems.
Supported by

2 in the figure indicates the rear wheels. Reference numeral 3 denotes a cylindrical horizontal beam with a rectangular cross section. A hydraulic cylinder 4 as a telescopic support leg that expands and contracts by hydraulic pressure is fixed to the tip of the horizontal beam 3, and a ground plate 6 is attached to the lower end of the piston rod 5 of the hydraulic cylinder 4. Can be detachably attached.

A support mechanism in which a set of two horizontal beams 3, 3 are arranged parallel to each other in opposite directions and supported so as to be able to extend to both sides of the underside of the vehicle body frame 1 is constructed by attaching each member of exactly the same configuration in opposite directions to the left and right. Therefore, the support mechanism on the right side of FIG. 1 will be mainly explained below.

Reference numeral 7 denotes a hollow arm whose base is welded to the right side wall of the vehicle body frame 1 in FIG. A partition plate 12 is welded and fixed in the middle of the cylindrical body,
Reinforcing pieces 14 and 15 for guiding the cylindrical horizontal beam 3 are integrally provided at the lower ends of the side plates 10 and 11 beyond the partition plate 12.

Since the illustrated hollow arm 7 protrudes fully into the vehicle, the bottom plate 9 on the distal side of the bulkhead plate 12 has a notch 1 into which a telescopic support leg (hydraulic cylinder 4) protruding from the top surface of the cylindrical horizontal beam is inserted.
There are 3. Also, side plate 1 is installed to reinforce the arm attachment part.
A bracket 16 is welded to the vehicle body frame 1, and a bracket 16 is attached to the mounting portion of the bulkhead plate 12 of 1 and the top plate 8, and a cantilever beam 1 is attached at the tip of the arm 7 to receive the expansion/contraction reaction force of the adjacent horizontal beam.
7 is fixed in a protruding manner. 18 is the cylindrical horizontal beam 3
The upper open portion of the squeegee-shaped support member 18 is pivotally attached to the side plates 10 and 11 at the base of the hollow arm by horizontal pins 19, respectively. A surrounding sleeve 20 provides a reinforcing connection between the side plates 10,11.

As shown in FIGS. 6 to 8, each scraper-shaped support section 18 has a bracket 21 welded and protruded from the horizontal beam projecting side of the vertical beam portions on both sides for guiding the cylindrical horizontal beam.
A guide loaf (guide member) 22 that supports the bottom surface of the cylindrical horizontal beam is pivotally supported at the tip of each of the brackets 21, and at least a small portion of the guide loaf (guide member) 22, which supports the bottom surface of the cylindrical horizontal beam, is supported between the supporting members 18, 18 on both sides of the vehicle body frame. Both ends of a guide member (double guide trough) 23 that guides the bottom of the cylindrical horizontal beam 3 are welded and fixedly connected to each other.

The guide member 23 is made of a thin plate and is light in weight, and simply serves as a steady rest for the skid-shaped support member 18 when the horizontal beam 3 is retracted or extended, as well as for guiding the horizontal beam and for resting the horizontal beam when traveling on the road. Measure. Both sides of a double-acting hydraulic cylinder 25 are pivoted 26 between the inside of the tip of each cylindrical horizontal beam 3 and a bracket 24 fixed to the horizontal beam support arm 7 and the cantilever 17 of the arm 7 on the reaction side. ，
27, so that the horizontal beam 3 can be moved between the retracted position shown in FIG. 1 and the extended position shown in FIG.
It is appropriately provided between the supporting members 18.

According to the configuration of the above-described embodiment, when the truck crane travels on the road, after the telescopic support leg 4 that has escaped the ground platform 6 is retracted as shown in FIG. 1, the horizontal beam 3 is The horizontal beam can be stored in the vehicle by being retracted along the guide members 22 and 23 until the hydraulic cylinder 4 at its tip is inserted into the notch 13 of the arm 7, and the horizontal beam can be stored inside the vehicle. When the hydraulic cylinder 25 is extended so that the horizontal beam is extended so that its tail end is positioned above the bottom of the shaped support member 18, the telescopic support leg 4 to which the grounding plate 6 is attached is extended. The vehicle body frame 1 can be specially supported by the stretchable support legs.

In the present invention, the transmission of the outrigger load between the horizontal beam 3 and the arm 7 when the outriggers are in an extended state is achieved through the contact between the bottom surface of the tail end of the horizontal beam and the bottom of the support member 18. This is done through the extreme pressure generated at the tip of the arm 7 and the top surface of the horizontal beam.
The side plates 10, 11 of the horizontal beam 3 are located on substantially the same vertical plane as the side plates of the horizontal beam 3, and the open upper end portion of the slit-shaped support section 18 is connected to the side plates 10, 11 of the arm base.
Since the arm 7 is pivotally attached to the arm 11 so as to be rotatable in a vertical plane including the arm axis, the extreme pressure acting on the tip of the bottom plate of the arm 7 is mainly directly transmitted to the side plates 10 and 11, and The gutter pressure acting on the bottom side of the scraper-shaped support member 18 is also applied to the side plates 10, 11 through the vertical punch portions on both sides.
transmitted to.

Therefore, the top plate 8 and the bottom plate 9 of the arm 7 mainly perform the function of transmitting the bending moment of the arm 7 caused by the above-mentioned extreme pressures to the vehicle body frame, and even if the bottom plate 9 is provided with a notch 13 as in the illustrated embodiment, it will not interfere at all. There isn't. The illustrated partition plate 12 is provided to prevent the side plates 10 and 11 from buckling. Furthermore, as mentioned above, since the upper end of the support member 18 is pivotally connected to the base of the arm 7 by the horizontal pin 19, even if the arm 7 is moved upward by an outrigger load, the inclination of the elastic line of the arm will not change. There is no risk of the signal being transmitted to the guide member 23 via the support member 18.

Therefore, even if the support members 18, 18 on both sides are firmly connected by the guide member 23, the outrigger load hardly acts on the guide member 23, so that the guide member can be thin and light in weight. According to the present invention, when the outriggers are extended, the cylindrical horizontal beam and the hollow arms with grooved support parts directly transmit extreme pressure between the side plates having high resistance to extreme pressure. Even if the extreme pressure increases by making the length of the overlap between the hollow arm and the cylindrical horizontal beam shorter than before, it can sufficiently withstand it, and therefore L' during outrigger extension can be increased compared to before, and the hollow arm Not only are the strength members such as the support members short and small, but the weight of the guide members 23 and 22 is also light as described above, so the weight increase due to reinforcement of the cylindrical horizontal beam is taken into account. However, the weight of the outrigger including the hollow arm can be prevented from increasing compared to the conventional outrigger. For example, the vehicle length L is 14.08, so the vehicle length is 12 inches, the vehicle interior B is 2.75, the vehicle height is 3.9, and the maximum lifting load is 60.
When installing an outrigger with a horizontal beam with a length of 2.75mm and a height of 0.43mm on a ton truck crane, in the conventional method, the length of the overlapping part of the horizontal beam and horizontal base tube when the outrigger is extended is 0.8 skin or more is required, and the weight of each front and rear outrigger unit is about 3 tons, but according to the present invention, a cylindrical horizontal beam, a sag, and a hollow arm with a shaped support member (length 0 .85m)
reducing the length of the overlapped portion of to 0.634;
Moreover, the weight of each outrigger unit including the hollow arm could be reduced to about 2.3 tons, and the total weight of the truck crane could be suppressed to about 51.5 tons.

[Brief explanation of the drawing]

Figure 1 is a longitudinal sectional front view when the outriggers are retracted (
Figure 2 is a plan view, Figure 3 is an enlarged Y-Y cross-sectional view of Figure 1, Figure 4 is a vertical front view when the outriggers are extended, and Figure 5 is an enlarged view. 4, FIGS. 6 and 7 are a front view and a plan view of the shading, support member, and guide member assembly, respectively, and FIG.
-W sectional view, FIGS. 9 and 10 are a side view and a plan view, respectively, of a conventional truck crane. 1...Vehicle frame, 2...Rear wheel,
3... Cylindrical horizontal beam, 4... Telescopic support leg, 6... Ground plate, 7... Hollow arm, 8... Top plate, 9... ...Bottom plate, 10, 11...
...Side plate, 13...Notch, 18...
Scraping, shaped support member, 19...Horizontal pin, 2
2, 23... Guide member, 25... Hydraulic cylinder. Na 1 figure square 2 figure figure 3 figure figure 4 figure S figure figure A figure 8 figure fang 10 figure figure 7 figure figure? figure

Claims (1)

[Scope of Claims] 1. A pair of cylindrical horizontal beams each having a rectangular cross-section and each having a vertical telescopic support leg attached to its tip are arranged opposite to each other and placed under the vehicle body frame at right angles to the longitudinal direction of the vehicle body. In order to support the horizontal beam so that it can slide in any direction, side plates are installed on both sides of a horizontal bottom plate whose lower end is formed in the guide path at the top of the horizontal cylindrical beam, and which are located on substantially the same vertical plane as the side plates on both sides of the horizontal cylindrical beam. A hollow arm provided with a cylindrical horizontal beam is protruded and fixed to the side surface of the vehicle body frame on the side where the cylindrical horizontal beam extends, and the cylindrical horizontal beam is slidably supported on both side plates of the base of the hollow arm in cooperation with the bottom plate thereof. The upper end open portion of the straddle-shaped support member is pivotally connected so as to be relatively rotatable in a vertical plane including the axis of the hollow arm, and the straddle-shaped support members on both sides of the vehicle body frame are jointly connected. Each cylindrical horizontal beam is fixedly connected by a guide member that supports the cylindrical horizontal beam in a slidable manner between a storage position within the vehicle width and an extended position toward the side of the vehicle body, and the tail end of the cylindrical horizontal beam at the extended position is An outrigger for a truck crane, characterized in that it is provided with a stopper means located on the bottom side of a support member. 2. The outrigger for a truck crane according to claim 1, wherein the length of the cylindrical horizontal beam including the telescopic support legs is approximately equal to the width of the vehicle.