JP2003056009A - Swing-out type counterweight construction for motor vehicle - Google Patents

Swing-out type counterweight construction for motor vehicle

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Publication number
JP2003056009A
JP2003056009A JP2001249238A JP2001249238A JP2003056009A JP 2003056009 A JP2003056009 A JP 2003056009A JP 2001249238 A JP2001249238 A JP 2001249238A JP 2001249238 A JP2001249238 A JP 2001249238A JP 2003056009 A JP2003056009 A JP 2003056009A
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JP
Japan
Prior art keywords
counterweight
link
vehicle
shaft
swing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
JP2001249238A
Other languages
Japanese (ja)
Inventor
Masanobu Kawanaka
Makoto Sakai
正信 川中
誠 酒井
Original Assignee
Shin Caterpillar Mitsubishi Ltd
新キャタピラー三菱株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shin Caterpillar Mitsubishi Ltd, 新キャタピラー三菱株式会社 filed Critical Shin Caterpillar Mitsubishi Ltd
Priority to JP2001249238A priority Critical patent/JP2003056009A/en
Publication of JP2003056009A publication Critical patent/JP2003056009A/en
Withdrawn legal-status Critical Current

Links

Abstract

(57) [Summary] [PROBLEMS] To improve the stability of a vehicle body when working on a vehicle such as a crane vehicle or a construction machine vehicle, or when traveling on uneven terrain, with respect to the structure of a vehicle swing-out type counterweight. SOLUTION: The center of gravity G of the counterweight 20 is moved to the rear of the vehicle 1 by rotating the counterweight 20 pivotally attached to the rear part in the front-rear direction of the vehicle 1 to the rear. The weight makes it possible to obtain a balance with respect to the weight of the large increase on the front side. Further, when the counterweight 20 is detached from the vehicle 1, the counterweight 20 is rotated in the direction of the ground surface GF to facilitate the attachment and detachment. In addition, the configuration is such that access to equipment such as an engine, a cooling device, and a hydraulic pump mounted on the vehicle 1 can be facilitated.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a structure of a swing-out type counterweight of a vehicle for improving the stability of the vehicle body when working on a vehicle such as a crane vehicle and a construction machine vehicle or when traveling on an uneven terrain. .

[0002]

2. Description of the Related Art A conventional hydraulic excavator for a construction machine such as the above-mentioned vehicle is disclosed in Japanese Utility Model Laid-Open No. 5-7747. As shown in FIG. 12, the technique described in this publication has a lower traveling body 2 having a shoe 2R and an upper revolving body 4 rotatably mounted on the upper portion of the lower traveling body 2. The upper revolving structure 4 includes a cab 6 which is an operator room, and a bucket 10 for carrying out work such as excavation of sand, loading and leveling in the front part.
The work machine 10 equipped with various work machine attachments is provided in place of the bucket 10a. Further, in order to stabilize the vehicle body during work or traveling on rough terrain, the counterweight 20 is fixed to the rear surface of the vehicle body frame 14 at the rear portion with bolts or the like. The above-mentioned counterweight 20 is usually made of concrete having a high specific gravity, a slag, a slag material or the like filled with a heavy material, or a cast product.

[0003]

However, the counterweight 20 of the prior art described above is mounted by the mounting structure in which the upper surface or the side surface of the rear end of the body frame 14 is fixed by bolts or the like as shown in FIG. The body frame 1 on which the counterweight 20, which is a heavy object, is placed due to a change in the balance of the vehicle body weight during work or traveling, or an impact.
Since an excessive load is applied to the vehicle body 4, it is necessary to strengthen the rigidity of the vehicle body frame 14 and the like, and this impact is propagated to the cab 6 via the vehicle body frame 14 and the riding comfort is deteriorated. Further, the counterweight 20 must be increased or replaced in order to balance the weight by mounting a heavy work attachment in place of the bucket 7.

A working machine 10 arranged in the front part of the vehicle.
With respect to the increase in the weight of the vehicle, the increased amount of the counter weight is detachably attached. However, the increase in the weight of the vehicle as a whole increases the load on each component, which leads to an increase in fuel consumption and a In order to secure the strength, it is necessary to increase the rigidity of the vehicle 1, resulting in a high cost.
Further, the counterweight 20 supported on the rear end of the vehicle body frame 14 includes hydraulic cylinders between the brackets 6 and 7 fixed to the counterweight 20 from the upper left and right rear surfaces of the vehicle body frame 14 near the front intermediate position of the counterweight 20, respectively. 9 are connected to each other by each shaft pin 9a in an inclined shape, and by operating this hydraulic cylinder 9 to expand and contract the piston rod,
The counterweight 20 is tilted in the front-rear direction about the shaft pin 5 of the support portion of the counterweight 20 as shown by the chain double-dashed line in FIG. Further, stopper levers 11 are attached to the rear portion of the vehicle body frame 14 and the left and right side surface portions of the counterweight 20, respectively. The stopper lever 11 has a long hole 11a formed therein. One end of the stopper lever 11 is pivotally supported on the side surface of the vehicle body frame 14 by the shaft pin 12, and the shaft pin 13 attached to the side surface of the counterweight 20 has the long hole 11a. When the shaft pin 13 moves in the elongated hole 11a and comes to the end of the elongated hole 11a as the counterweight 20 tilts back and forth, it is prevented from further tilting.

Therefore, when the vehicle travels on an uneven terrain and when the work is performed, and further, when the attachment of the heavy work attachment causes the unbalance of the vehicle body, the piston rod of the hydraulic cylinder 9 is operated to extend and contract. The counterweight 20 is tilted forward or backward so that the center of gravity (W
By moving 1) to the gravity center position (W2) or the gravity center position (W3), the vehicle body weight imbalance is corrected and stabilized.

According to the technique described in the above publication, as shown in FIG. 13, the stopper lever 11 mounted on the vehicle frame 14a by the shaft pin 12 restricts the shaft pin 13 mounted on the side surface of the counterweight 20 in the long hole 11a. As it has a structure that balances by being moved and moved,
Since it is a substantially horizontal type counterweight, it is difficult to secure the strength of the moving parts.

Further, in the above conventional technique, as shown in FIG. 14, [1] in the equipment arrangement mounted on the vehicle, it can be accessed only from directly above or below the engine. [2] To access the side, it is necessary to go into the engine room from directly below. [3] In addition, when accessing from the top, the handle,
There is a problem that equipment such as steps and anti-slip on the upper surface 4U of the machine body is required, resulting in high cost.

[0008] In addition, as a device installation place for special work,
There is no other place than to install it in the space above the engine hood that is installed above the engine. Further, recently, in a model configured to be able to make a small turn to the rear of a hydraulic excavator applied to a building street or a narrow work site, the movement of the counterweight 20 to the rear of the vehicle is reduced, and the work machine 10 on the front side is reduced. It is difficult to balance and stabilize the weight of the counterweight 20 with respect to.

The present invention was devised in view of the above-mentioned problems. The counterweight pivotally attached to the rear portion of the vehicle in the front-rear direction is rotated backward to move the center of gravity of the counterweight to the rear of the vehicle. , The balance is obtained with a smaller weight of the counterweight with respect to the increased weight on the front side, and when the counterweight is attached to or detached from the vehicle, the stopper is removed and the counterweight is rotated toward the ground surface. The engine, the cooling device, mounted on the vehicle to facilitate the attachment / detachment.
It is an object of the present invention to provide a swing-out type counterweight structure for a vehicle that allows easy access to a device such as a hydraulic pump.

[0010]

Therefore, in the swing-out type counterweight structure for a vehicle according to the present invention as defined in claim 1, the working machine is mounted on the front part in the front-rear direction of the vehicle and the counterweight is mounted on the rear part. In a vehicle, a holding portion provided on the rear portion for pivotally supporting the count weight on a vehicle body frame of the vehicle, and a support portion provided on the count weight for rotatably supporting the counter weight on the holding portion, A swing-out mechanism provided in the vehicle for swinging out the counterweight to the rear of the vehicle, and a rotating means arranged in the vehicle for rotating around the holding portion are provided. .

According to a second aspect of the present invention, there is provided a swingout type counterweight structure for a vehicle according to the first aspect, wherein the swingout mechanism is rotated by the holding portion and the supporting portion of the counterweight. It is characterized by being configured as follows. According to a third aspect of the present invention, there is provided the vehicle swing-out type counterweight structure according to the first or second aspect, wherein the counterweight swing-out mechanism has at least one portion between the counterweight and the holding portion. It is characterized in that it is configured to be connected by one link.

A swing-out type counterweight structure for a vehicle according to a fourth aspect of the present invention is the structure according to any one of the first to third aspects, wherein the counterweight is pivotally supported by the counterweight via a link shaft. It is characterized in that the link is provided with a detachable fixing pin which is inserted into the link and the counterweight at a distance from the link shaft.

According to a fifth aspect of the present invention, there is provided the vehicle swing-out type counterweight structure according to the third or fourth aspect, wherein the links are connected by a plurality of links. It has a feature. According to a sixth aspect of the present invention, there is provided a swing-out type counterweight structure for a vehicle according to any one of the first to fifth aspects, wherein a stopper for limiting a swing-out position of the counterweight is provided. It is characterized in that it is provided between the vehicle side and the counterweight side.

According to a seventh aspect of the present invention, there is provided a swing-out type counterweight structure for a vehicle according to the sixth aspect, wherein the stopper is one of a lower portion of the counterweight and a rear portion of the vehicle. Is mounted rotatably or slidably corresponding to the other mounted side. According to the swing-out type counterweight structure for a vehicle of the present invention described in claim 8, in the structure of claim 6, the link and the counterweight pivotally supported via the link shaft provided in the counterweight. A removable fixing pin that is inserted to fix the rotation of the link and abuts the fixing pin on the side of the vehicle corresponding to the rotation position of the counterweight so as to limit the rotation of the counterweight. It is characterized by having the above-mentioned stopper configured.

According to a ninth aspect of the present invention, there is provided a swing-out type counterweight structure for a vehicle according to the fourth or fifth aspect, wherein one end is pivotally supported by the counterweight via the link shaft. And the first link which is connected to the first link at a distance from the link shaft by the removable fixing pin inserted into the counterweight.
The other end and one end of the link are pivotally supported by the other end of the first link via a link shaft pin, and the other end is pivotally supported by the holding part at the rear portion of the vehicle frame via a pivot shaft. Second
There is a space between the link and the link shaft pin, and the first
It is characterized in that it is provided with a detachable inter-link shaft pin that is inserted into the link and the second link, and a detachable fixing pin that is inserted into the second link and the count weight.

According to a tenth aspect of the present invention, there is provided a swing-out type counterweight structure for a vehicle according to the ninth aspect, wherein the other end of the first link and the one end of the second link are connected to each other. The link shaft pin is composed of a first shaft portion and a second shaft portion extending from the first shaft portion, and the first shaft portion pivotally supports the first link and the second link,
The second shaft portion is configured to be inserted into the first link, the second link, and the counterweight.

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described below with reference to the drawings. Parts that are substantially the same as those of the conventional structure will be designated by the same reference numerals. FIG. 1 is a schematic explanatory view showing a plane near a counterweight of a hydraulic excavator showing a case where a swing-out type counterweight structure of a vehicle of the present invention is applied to a hydraulic excavator, and FIG. 2 shows a case where the supported counterweight rotates, (A) is a schematic explanatory view showing a side surface of the position of the counterweight during normal work, and (B) is FIG.
FIG. 2A is a schematic explanatory view showing a state in which the counterweight is rotated from the position shown in FIG. 2A to an intermediate horizontal position, and FIG. 2C is from the position of the counterweight shown in FIG. FIG. 3 is a schematic explanatory view showing a state in which the counterweight is rotated and inverted, and FIG. 3 is a modified example of FIG. 2, in which one end is pivotally supported by a holding portion provided on the vehicle body frame and the other end is pivotally supported by the counterweight. In the case of having a link, (A) is a schematic explanatory view showing a state during normal work,
3B is a schematic explanatory view showing a state of the intermediate position in which the counterweight is rotated backward from the position of the counterweight shown in FIG. 3A, and FIG. 3C is a position of the counterweight shown in FIG. 3B. A schematic explanatory view showing a further rotatable and detachable state,
FIG. 4 is an application example of the modified example shown in FIG. 3, showing an operation diagram in the case where a fixing pin for fixing the counterweight and the link is provided, and FIG. Explanatory drawing, (B) is a schematic explanatory view showing a state in which the position of the cowout weight shown in FIG. 4 (A) is rotated to an intermediate position, and (C) is a link with the counterweight shown in FIG. 4 (A). FIG. 5 is a schematic explanatory view showing a state in which the solid weight inserted in and is removed and the counterweight can be detached, and FIG. 5 shows the swing-out type counterweight shown in FIG. (A) is a schematic explanatory view showing a perspective view of a state in which the link rotates integrally with the counterwit by the fixing pin shown in FIG. 4 (A), and (B) shows
The fixing pin shown in FIG. 4 (A) is removed, and a schematic perspective view showing a state in which the link and the counter wit are separately rotated while displacing from the state of FIG. 4 (A) to the state of FIG. 4 (C) 6 and 6 are rotation stoppers which are stoppers for holding the rotated position of the counterweight shown in FIGS. 2 and 4, and (A) is a bottom portion of the counterweight and a shaft of a holding portion of the vehicle body frame. A schematic explanatory view showing a state in which the rotation of the counterweight is restricted by abutting a pivotally supported stopper,
6B is a schematic explanatory diagram showing a state in which the solid line position shown in FIG. 6A has been actuated to a non-actuated position, and FIG. 7 shows a modification of the rotation stopper shown in FIG. In the case where the link shown in FIG. 6 and the fixing pin inserted in the counterweight are also used as stoppers, (A) is a schematic explanatory view showing a state during normal work, and (B) shows the link and the counterweight. A schematic explanatory view showing a state in which when the counterweight comes to an intermediate position at the same time of fixing with a pin, the fixed pin comes into contact with a rotation restraining portion of a holding portion on the vehicle body side and rotation of the counterweight is restricted, C) is shown in FIG.
FIG. 8A is a schematic explanatory view showing a state in which the fixing pin can be detached and rotated from the state of (A) to detach the counterweight. FIG. 8 shows the counterweight in the horizontal state at the intermediate position of the counterweight in each of the above figures. It shows a state where various devices are mounted and used on the upper part, (A) is a schematic explanatory view showing a case where a water tank of a crusher with a dust prevention nozzle is provided,
FIG. 9B is a schematic explanatory view showing a case where a generator such as a lifting magnet is mounted on the upper part of the counterweight in a horizontal state, and FIG. 9 drives the swing-out rotation shown in FIGS. 2 to 4 and 10. It shows an application example of the rotating means to
(A) is a schematic explanatory view showing a state during normal work when a wire and a chain, one end of which is connected to a counterweight and the other end of which is connected to a motor provided on a vehicle side, are applied,
9B is a schematic explanatory view showing a state in which the counterweight shown in FIG. 9A is rotated to an intermediate position, and FIG.
Is configured to be operated by a hydraulic cylinder instead of the motor shown in FIG. 9 (A), and is a schematic explanatory view showing the same state as in FIG. 9 (A), and (D) is shown in FIG. 9 (C). 4 is a schematic explanatory view showing a state in which the position of the counterweight shown in FIG. 4 is rotated to an intermediate position, FIG. 10 is an application example of the embodiment of FIG. 4, and has first and second links, and FIG.
FIG. 4B is a schematic explanatory view showing a state similar to FIG.
4B is a schematic explanatory view showing a state similar to FIG. 4B, and FIG.
FIG. 10D is a schematic explanatory view showing a state similar to that of FIG.
(B) is a schematic explanatory view showing a case where only the second link operates, (E) is a stepped link shaft pin that connects the first link and the second link of FIGS. 10 (A) to 10 (D). 11 shows a modified example of the rotary stopper shown in FIG. 6, (A) is a schematic perspective view showing a locked state showing the structure of the slide stopper, and (B) is a perspective view. FIG. 12 is a schematic perspective explanatory view showing a case where the slide type stopper is in an unlocked state from the locked state of FIG. 11 (A).

As shown in FIG. 1, one embodiment of the present invention has a structure in which a counterweight is provided with a rotary part and the rotary part is rotatable about the rotary part. Further, the vehicle body hood 14 of the upper swing body 4 of the vehicle of the hydraulic excavator 1 has a main frame 14a and a main frame 14a as shown in FIGS.
It is composed of a double-sided revo frame 14b that supports the base of the working machine 10 at the front part fixed to the upper surface of the main frame 14a and extends to the rear end of the main frame 14a. The body frame composed of the main frame 14a and the revo frame 14b. A counterweight 20 is detachably attached to a rear end portion of the counterweight 14, and at the time of attaching the counterweight 20, the counterweight 20 is pivotally supported on a lower front surface of the counterweight 20, a holding portion 3 and a support portion 3A fixed to the rear end surface of the vehicle body frame 14, respectively. The shaft 5 is inserted and rotatably supported.

As shown in FIG. 2, the counterweights 20 supported on the upper rear ends of the upper revolving structures 4 are respectively located from the upper surfaces of the left and right rear portions of the vehicle body to the vicinity of the front intermediate position of the counterweights 20 as shown in FIG. Fixed brackets 6, 7 are provided. Each hydraulic cylinder 9 disposed between the counterweight 20 and the upper part of the upper swing body 4 between the brackets 6 and 7 is tilted and pivotally supported by each shaft pin 29 to operate the hydraulic cylinder 9. By expanding and contracting the counterway 20, the counterway 20 rotates in the front-rear direction of the vehicle body with the pivot shaft 5 of the support portion 3A of the counterweight 20 as the center of rotation.

As shown in FIGS. 1 and 2, the working machine 10 is provided in the front part of the vehicle in the front-rear direction and the counterweight 20 is provided in the rear part of the vehicle. A holding portion 3 for pivotally supporting a counterweight 20 on a portion thereof, a bearing portion 3A for rotatably supporting the holding portion 3, and a hydraulic cylinder 9 as a rotating means. Has a swing-out mechanism K for swinging out. Further, the swing-out mechanism K is provided with a rotating means 9 arranged at the rear portion of the vehicle which rotates via the pivot shaft 5 of the holding portion 3, and in the present embodiment, a hydraulic pressure device which is a pressure response device. It has a cylinder 9.

Further, the above swing-out mechanism K is shown in FIG.
As shown in FIG. 3, the holding portion 3 of the counterweight 20 and the support portion 3A are rotated by the rotating means 9 via the pivot shaft 5. In addition, the hydraulic cylinder 9 which is the rotating means described above.
One end of the piston rod is pivotally supported above the upper revolving structure 4 of the vehicle 1 through a bracket 7, and the other end is pivotally supported above the intermediate portion on the front side of the counterweight 20 through the bracket 6. It is supported. And FIG.
As shown in (A), the pivot shaft 5, which is the center of rotation, is moved outward from the center of gravity G1 of the counterweight 20, so that a rotational force is generated in the clockwise direction with the pivot shaft 5 of the counterweight 20 as the center of rotation. Can be supported and stabilized on the upper swing body 4 side.

Further, the rotating means 9 is not limited to the above, and for example, as shown in FIGS. 9A and 9B, one end is connected to the counterweight 20 and the other end is on the upper swing body 4 side. A belt, a cog belt, connected via a pulley attached to the attached motor M, a sprocket, etc.
It is operated by a power transmission member WY such as a wire and a chain. In the case of the present embodiment, it is composed of the wire WY and a motor.

Further, instead of the motor M shown in FIGS. 9 (A) and 9 (B), as shown in FIGS. 9 (C) and 9 (D), the wire WY is passed through the pulley to the upper revolving structure 4 side. It may be configured by a hydraulic cylinder that is a pressure response device provided in the.
Further, when the stability shown in FIG. 2 (B) is maintained, the bottom portion 20L of the counterweight 20 and the rear side surface 4R of the upper swing body are rotated by the operation of the hydraulic cylinder 9 about 90 degrees about the pivot shaft 5. Are in contact with each other to form a stopper for suppressing further downward rotation (counterclockwise rotation) of the counterweight 20, and further rotation is prevented and stabilized. As shown by an arrow Y4 shown in FIG.
The center of gravity G of the counterweight 20 is rotated by 0 degree.
2 is moved to the rear of the hydraulic excavator from the pivot shaft 5, and the counterweight 20 is rotated counterclockwise about the pivot shaft 5 to cause the counterweight 20 to rotate.
The bottom portion 20L of the above can be positively brought into contact with the rear side surface 4R of the upper revolving structure 4, and the above-mentioned stopper action can improve the stability.

Further, as shown in FIG. 2 (C), the hydraulic cylinder 9 is further operated to move the counterweight 20 to the position shown in FIG.
Set the counterweight 20 in the position of the state of (A) to about 1
The counterweight 20 can be easily attached and detached by rotating the counterweight 20 by turning it 80 degrees and inverting it so that the upper portion of the counterweight 20 is grounded. Figure 2 above
In the cases shown in FIGS. 2A and 2B, the side surface of the engine is wide open, which facilitates access to the engine from the ground surface shown in FIG.

Next, the link type of the modified example of the above embodiment
1 will be described with reference to FIG. In this modification, one end is pivotally supported by the pivot shaft 5 of the holding portion 3 and the other end is provided with a link 30 pivotally supported by a link shaft 29 provided on the counterweight 20. Further, when the hydraulic cylinder 9 is operated, the link 30 is rotated from the state shown in FIG. 3A to the state shown in FIG. 3B via the holding portion 3, the support portion 3A, and the pivot shaft 5, and the holding portion 3 is moved. The link 30 is maintained in a substantially horizontal state, and the counterweight 20 rotates about the link shaft 29 as a rotation center to balance the weight of the working machine 10 and perform stable work of the hydraulic excavator. The position of the center of gravity in this state is farthest from the center of rotation, and the stability can be maximized.

The counterweight 20 in this horizontal state
When the hydraulic cylinder 9 is further moved downward, the link 30
Rotates downward about the pivot 5, and the counterweight 2
0 is rotated in the direction of the ground surface GF via the link shaft 29 to be grounded so that the effect as an outrigger can be obtained in a stable state, and the counterweight 20 can be easily attached and detached. A stable state is obtained.

The access for inspection and maintenance of the engine E, the cooling device R, the hydraulic pump P, etc. shown in FIG. 14 as the prior art does not get on the upper surface 4U of the upper revolving structure 4 and the upper revolving structure 4 does not rotate. It can be easily performed from the ground plane position without forcing from below the body 4. next,
An application example of FIG. 3 shown in FIG. 4 will be described. Figure 4
As shown in (A), a link 30 pivotally supported by the counterweight 20 via a link shaft 29 is provided with a fixing pin 32 inserted into the link 30 and the counterweight 20 at a distance from the link shaft 29. I am doing so, so link 30
The link shaft 29 and the fixing pin 32 are the counterweight 20.
The counterweight 20 rotates as an integral part of the link 30 because it is fixed to the integral part.

Therefore, when the hydraulic cylinder 9 is operated as described above, the counterweight 20 is linked with the counterweight 20 as in the state shown in FIG. 4A from the state shown in FIG. As shown in FIG. 4, the fixed pin 32 and the link shaft 29 are integrated with 30.
As shown in (B), via the holding portion 3 and the support portion 3A,
The link 30 rotates about 90 degrees integrally with the counterweight 20 about the pivot shaft 5 as a rotation center, and moves to a posture in which stability in a substantially horizontal state is secured.

When the fixing pin 32 is removed from the counterweight 20 as shown in FIG. 5B in the state of FIG. 4A, the link 30 exerts a function as a link member and the counterweight. 20 is centered around the link shaft 29 and is shown in FIG.
As indicated by an arrow Y1 shown in FIGS. 4A to 4C, the canter weight 20 is rotated in the clockwise direction, and the link 30 is rotated downward about the pivot shaft 5 in the ground surface GF direction. Since the counterweight 20 can be attached and detached by rotating to the ground, the maintenance of the engine E and the equipment in the engine room can be performed on the ground surface G.
It can be easily performed from F.

Next, the case of the two-link type will be described with reference to FIG. The above link 30 is a plurality of links 30.
Is applicable. That is, the first link 30a, one end of which is pivotally supported by the counterweight 20 via the link shaft 29, as in the application example shown in FIG.
It has the above-mentioned first link 30a which is spaced from the link shaft 29 and the above-mentioned detachable fixing pin 32 which is inserted into the counterweight 20. Further, one end of itself is pivotally supported by the other end of the first link 30a via a link shaft pin 39,
The second link 30 whose other end is pivotally supported by the holding portion 3 at the rear portion of the vehicle body frame 14 of the vehicle 1 via a pivot shaft 5.
b.

The link shaft pin 39 is provided with a removable inter-link fixing pin 31 which is inserted into the first link 30a and the second link 30b with a space therebetween, and the link shaft 29 and the link are fixed. The first link 30a and the second link 30 are formed by the pin 31, the fixed pin 32, the link shaft pin 39, and the like.
and b form a link that operates integrally. The link shaft pin 39 connecting the other end of the first link 30a and the one end of the second link 30b has the first shaft portion 39a and the first shaft portion 39a as shown in FIG. 10 (E). The second shaft portion 39b further extends, the first shaft portion 39a pivotally supports the other end of the first link 30a and one end of the second link 30b, and the second shaft portion 39b is connected to the first link 30a. It is configured to be inserted into the other end, the one end of the second link 30b, and the counterweight 20.

Further, a detachable fixing pin 32 for fixing the second link 30b to the counterweight 20.
Are provided for each. Therefore, an integral link is formed by an appropriate combination of the link shaft 29, the inter-link fixing pin 31, the fixing pin 32, and the link shaft pin 39 of the first link 30a and the second link 30b shown in FIG. Since the counterweight 20 is integrated with the counterweight 20, when the counterweight 20 rotates about the pivot shaft 5, the counterweight 20 can rotate to an intermediate position as shown in FIG. 10B.

Further, the two fixing pins 32 are removed from the state shown in FIG. 10 (A), and are pivotally supported by the link shaft 29 and the pivot shaft 5 as shown in FIG. 10 (C). First link 3
0a and the second link 30b are made into a unitary link, so that the bottom portion 20L of the counterweight 20 becomes the ground surface GF.
It is possible to obtain a stable hydraulic excavator by rotating it so that it is grounded.

Further, the inter-link fixing pin 31 and the fixing pin 32 of the second link 30b are removed from the state shown in FIG. 10 (A), and the link shaft 29, the link shaft pin 39 and the first link 30 are removed.
The first link 30a and the counterweight are integrated by at least any two of the fixing pins 32 provided in a, and the link shaft pin 39 is rotated as shown in FIG. It rotates about the moving center via the second link 30b. Then, in this application example, as shown in FIGS. 10A to 10D, the counterweight 20 is moved to the rear of the hydraulic excavator to balance the weight and balance of various working machines mounted on the front side. A stable hydraulic excavator can be obtained by taking it.

Since the above-mentioned application example is constructed as described above, it is constructed so as to connect the first link 30a and the second link 30b, and is arranged so as to be separated from the vehicle body 1 in the rearward direction of the vehicle 1. , The heavy work machine 1 on the front side
When the 0 is attached, the counterweight 20 has a small weight.
It is also possible to ensure the stability that the vehicle weight balance can be achieved. As shown in FIG. 10 (A) to FIG. 10 (D), the counter weight 20 can be rotated to a plurality of positions according to the number of the above-mentioned links. In the case of this application example, since the first and second links 30a and 30b are composed of two links, they can be rotated to two positions. That is, in the case shown in FIG.
First and second links 30a, 30b, link shaft pin 39
In the state of the integrated body, the state becomes the same as that of FIGS. 4B and 4C, and the state can be rotated to the positions of FIGS. 10B to 10C. As described above, the balance of the vehicle 1 can be adjusted by the counterweight 20 having the same weight, depending on the space available behind the hydraulic excavator at the work site.

Next, a rotation stopper for ensuring the stability of the position of the counterweight 20 will be described with reference to FIG. As shown in FIG. 6, the holding portion 3 of the vehicle body frame 14
6A is rotatably supported by a shaft 36 provided in FIG.
6 to move to the position of the solid line from the position of the two-dot chain line shown in FIG.
The head 38U shown in (A) is in contact with the bottom surface 20L of the counterweight 20 in the intermediate position (substantially horizontal position) where the counterweight 20 is rotated by approximately 90 degrees and restricts the rotation of the counterweight 20. The rotation stopper 38 is provided to ensure stability. Then, when the rotation stopper 38 is released as shown by the solid line in FIG. 6 (B), the counterweight 20 can be further rotated about the pivot shaft 5 as the rotation center as described above. Is.

In the case of the above link type shown in FIG. 7,
An end portion of a fixing pin 32, which is inserted into the counterweight 20 and the link 30 to fix the operation, is attached so as to project from the side surface of the counterweight 20, and the counterweight 20 is approximately 90 degrees as shown in FIG. 7B. When rotated to a position in which the intermediate position is substantially horizontal, the fixing pin 32
Of the counterweight 20 corresponding to the increased weight of the working machine 10 by forming a stopper portion 40 for restricting the rotation of the counterweight 20 by abutting a protruding portion of the stopper portion 40 of the holding portion 3 on the body frame 14 side. It is possible to cope with the weight increased by the movement of 20 and ensure the stability of the hydraulic excavator to perform the work. In the above description, the stopper is configured to also serve as the fixing pin 32. However, even if the stopper pin 32 is independently provided as described above, the same effect as the above can be obtained. .

Further, as shown in FIG.
When the fixing pin 32 shown in FIG. 7A is removed and the pivot shaft 5 is rotated as the center of rotation as shown in FIG. 7C, the link 30 and the counterweight 20 operate separately and the counterweight 20 of the counterweight 20 moves. The counterweight 20 is rotated in the direction of the ground surface GF without being restricted by the rotation, and the counterweight 20 is grounded so that the counterweight 20 can be easily attached and detached. As described above, the maintenance of the above-mentioned equipment in the engine room is performed on the ground surface. Alternatively, the steps can be easily performed from the steps provided on the upper surface of the counterweight 20.

Further, as shown in FIG. 6, a rotation stopper 38 for limiting the swing-out position of the counterweight 20 is provided on one of the side surface of the upper swing body 4 and the counterweight 20 side. Since it is provided and disposed between the two, the counterweight 20 is rotated when it is rotated to the intermediate position as shown in FIG. 6A, for example.
The rotation position of can be reliably ensured in a stable state.

Further, the above-mentioned respective embodiments are shown in FIGS.
As described above, when the above embodiments are compared with each other, for example, the embodiment shown in FIG. 4 is more advantageous than the embodiments shown in FIGS. Have a point. [1]: The advantage of FIG. 4 over the embodiment of FIG. In the state shown in FIG. 2C, it is necessary to operate the counterweight 20 upside down. Further, in FIG. 2, the amount of delivery of the piston rod of the hydraulic cylinder 9 becomes long. Moreover, FIG.
When the ground is not flat, the ground cannot be properly grounded, which may make it difficult to attach and detach the counterweight 20. Further, in the embodiment of FIG. 4, there is no possibility that the lower traveling body 2 may come into contact with the lower traveling body 2 when the lower traveling body 2 is longer than the rear end of the counterweight 20 shown in FIG. Is.

[2]: FIG. 4 is advantageous over the embodiment of FIG. In the state of FIG. 3B, the bottom surface 20 of the counterweight 20 is
The gap between L and the ground surface G is small, and there is a risk of contact with ground surface obstacles. Further, in FIG. 3, the counter weight 2
Since 0 is free to rotate around the link shaft 29, the counterweight 20 shakes due to vibration of the machine body and the like, which adversely affects the ensuring of stability, and may cause contact with surrounding obstacles. Advantageously, it does not occur in the embodiment of FIG. In the above case, it may be necessary to ensure stability by urging other members, but it is possible to obtain substantially the same operational effects as the above-described embodiment.

[0042]

As described in detail above, according to the swing-out type counterweight structure for a vehicle of the first aspect of the present invention, the working machine is provided at the front part of the vehicle in the front-rear direction and the counterweight is provided at the rear part. In the mounted vehicle, a holding portion provided on the rear portion for pivotally supporting the count weight on the vehicle body frame of the vehicle, and a support portion provided on the count weight for rotatably supporting the counter weight on the holding portion. And a swing-out mechanism provided in the vehicle for swinging out the counterweight to the rear of the vehicle, and a rotating means arranged in the vehicle for rotating around the holding portion, Stability can be obtained by rotating the counterweight between the normal working position and the intermediate position by the swing-out mechanism. Furthermore it is possible to rotate easily performed desorption of the counterweight is grounded upper portion of the counterweight on the ground. In the state of the intermediate position and the ground contact position, maintenance of the engine, equipment and the like can be easily performed from the ground surface or the upper part of the counterweight.

According to the swing-out type counterweight structure for a vehicle of the present invention as defined in claim 2, in the structure of claim 1, the swing-out mechanism is rotated by the holding portion and the supporting portion of the counterweight. Since it is configured to move, in addition to the effect of claim 1, stable and reliable rotation of the counterweight can be performed. According to the swing-out type counterweight structure for a vehicle of the third aspect of the present invention, in the configuration of the first or second aspect, the swingout mechanism of the counterweight has a space between the counterweight and the holding portion. Since it is configured to be connected by at least one link, in addition to the effect of claim 1 or 2, the center of gravity of the counterweight is moved to the rear of the vehicle by the rotation of the link and the counterweight. The balance due to the change in the weight of the working machine provided on the side can be easily balanced by one and the same counterweight, and the counterweight can be rotated with a low cost and simple structure.

According to the swing-out type counterweight structure for a vehicle of the present invention as set forth in claim 4, in the structure as set forth in any one of claims 1 to 3, the counterweight is pivotally supported by the counterweight via a link shaft. The link is provided with a detachable fixing pin which is inserted into the link and the counterweight at a distance from the link shaft.
In addition to the effect of any one of to 3, it is possible to easily fix and release the link and the counterweight.

According to the swing-out type counterweight structure for a vehicle of the present invention as defined in claim 5, claim 3 or 4 is provided.
In the configuration described above, since the links are configured to be connected by a plurality of links, in addition to the effect of claim 3 or 4, the position of the center of gravity of the counterweight can be made rearward of the vehicle by the plurality of links. And the balance due to the change in the weight of the working machine provided on the front side can be easily balanced by one and the same counterweight, and the counterweight can be rotated with a low cost and simple structure. You can

According to the swing-out type counterweight structure for a vehicle of the sixth aspect of the present invention, in the configuration according to any one of the first to fifth aspects, the swing-out position of the counterweight is limited. Since the stopper is provided between the vehicle side and the counterweight side, in addition to the effect according to any one of claims 1 to 5, the intermediate position of the counterweight can be reliably held, and the counterweight of the counterweight can be held. The space on the upper surface can be used in a stable state.

According to the swing-out type counterweight structure for a vehicle of the present invention described in claim 7, in the structure of claim 6, the stopper is either one of the lower part of the counterweight and the rear part of the vehicle. while the so in response to the other of the attachment side mounted for rotation possible or slide or, in addition to the effect of claim 5, cost inexpensive with a simple construction, and reliable detachment of the counterweight Can be done.

According to the swing-out type counterweight structure for a vehicle of the present invention described in claim 8, in the structure of claim 6, the link pivotally supported via the link shaft provided in the counterweight, Rotation of the counterweight by abutting the fixing pin, which is inserted into the counterweight and fixes the rotation of the link, on the side of the vehicle corresponding to the rotation position of the counterweight. In addition to the effect of claim 6, since the stopper is configured so as to limit the above, the structure is simple and compact, and the cost is low, in addition to the effect of claim 6. Can be

According to the swing-out type counterweight structure for a vehicle of the present invention described in claim 9, claim 4 or 5 is provided.
In the structure described above, a first link, one end of which is pivotally supported by the counterweight via the link shaft, and the detachable member, which is inserted into the first link and the counterweight at a distance from the link shaft. Other end of the first link connected by a fixed pin, one end of which is pivotally supported by the other end of the first link via a link shaft pin, and the other end of which is the holding portion at the rear portion of the vehicle frame. A second link pivotally supported via a pivot shaft, a removable inter-link shaft pin inserted into the first link and the second link at a distance from the link shaft pin, and Since the second link and the count weight are provided with detachable fixing pins, in addition to the effect of claim 4 or 5, the first link and the second link are configured to be connected to each other. Away from the car body in the above rear direction Arranged so as, when fitted with a large working machine of the weight of the front side, it is also possible to allow secure weight balance of the vehicle is taken stability small weight of the counterweight. The counterweight can be rotated to two rearward maximum rotation positions, and the balance of the vehicle can be adjusted with the counterweight having the same weight in accordance with the space behind the counterweight. It is effective when applied to turning type vehicles.

According to the swing-out type counterweight structure for a vehicle of the present invention described in claim 10, in the structure of claim 9, the other end of the first link and the second
The link shaft pin connecting the one end of the link is the first
It is configured by a shaft portion and a second shaft portion extending from the first shaft portion, the first shaft portion pivotally supports the first link and the second link, and the second shaft portion is the above. Since it is configured to be inserted into the first link, the second link, and the counterweight, in addition to the effect of claim 9, a structure in which the expansion and contraction operation of the first link and the second link is simple Can be done with certainty.

[Brief description of drawings]

FIG. 1 is a schematic explanatory view showing a plane in the vicinity of a counterweight of a hydraulic excavator showing a case where a swing-out type counterweight structure for a vehicle of the present invention is applied to a hydraulic excavator.

2A and 2B show a case in which a counterweight pivotally supported by a holding portion of the vehicle frame in FIG. 1 rotates, and FIG. 2A is a schematic explanatory view showing a side surface of a position of the counterweight during normal work; ) Is a schematic explanatory view showing a state in which the counterweight shown in FIG. 2A is rotated to an intermediate horizontal position, and FIG. 2C is a diagram showing a state in which the counterweight shown in FIG. It is a schematic explanatory drawing which shows the state which turned to the ground surface direction and the counterweight was inverted.

FIG. 3 is a modified example of FIG. 2, showing a case where a holding portion provided on a vehicle body frame has a link whose one end is pivotally supported and the other end is pivotally supported by a counterweight, and FIG. FIG. 3 is a schematic explanatory view showing a state during normal work, FIG.
FIG. 3A is a schematic explanatory view showing a state of the intermediate position rotated backward from the position of the counterweight shown in FIG. 3A, and FIG. 3C is a further rotated state from the position of the counterweight shown in FIG. It is a schematic explanatory drawing which shows a different state.

FIG. 4 is an application example of the modification shown in FIG. 3, showing an operation diagram in the case where a fixing pin for fixing the counterweight and the link is provided, and (A) shows a normal work time. 4B is a schematic explanatory view showing a state in which the cowouter weight shown in FIG. 4A is rotated from the position to the intermediate position, and FIG. 4C is a counterweight shown in FIG. 4A. It is a schematic explanatory drawing which shows the state which can remove | detach the solid weight inserted in the link and the counterweight can be attached or detached.

FIG. 5 is a diagram showing the swing-out type counterweight shown in FIG. 4 being rotated to an intermediate position;
4B is a schematic explanatory view showing a perspective view of a state in which the link rotates integrally with the counterwit by the fixing pin shown in FIG. 4A, and FIG. 4B shows the fixing pin shown in FIG. FIG. 5 is a schematic explanatory view showing a perspective view of a state in which the link and the counterwit which are in the process of being displaced from the state of FIG. 4 (A) to the state of FIG. 4 (C) rotate separately.

FIG. 6 is a rotation stopper which is a stopper for holding the rotated position of the counterweight shown in FIGS. 2 and 4, and (A) is pivotally supported on the shaft of the holding portion of the vehicle body frame at the bottom of the counterweight. Schematic explanatory view showing a state in which the rotation of the counterweight is restricted by abutting the stopped stopper,
FIG. 6B is a schematic explanatory view showing a state in which the solid line position shown in FIG.

FIG. 7 shows a modification of the rotation stopper shown in FIG. 6, showing a case where the link shown in FIG. 5 and the fixing pin inserted in the counterweight are also used as stoppers.
(A) is a schematic explanatory view showing a state during normal work, (B) fixes the link and the counterweight with the fixing pin, and at the same time, when the counterweight reaches an intermediate position, the fixing pin is held on the vehicle body side. FIG. 7C is a schematic explanatory view showing a state in which the rotation of the counterweight is restricted by coming into contact with the rotation inhibiting portion of the section, and FIG. 7C is a state in which the fixing pin is removed from the state shown in FIG. It is a schematic explanatory drawing which shows a possible state.

FIG. 8 shows a state in which various devices are mounted and used on an upper portion of the counterweight which is in a horizontal state at an intermediate position of the counterweight in each of the above figures, and (A) shows a crusher with a dust prevention nozzle. 2B is a schematic explanatory view showing a case where the water tank of FIG. 1 is provided, and FIG. 6B is a schematic explanatory view showing a case where a generator such as a lifting magnet is mounted on the upper part of the horizontal counterweight.

9 shows an application example of a rotating means for driving the rotation of the swing-out shown in FIGS. 2 to 4 and FIG.
(A) is a schematic explanatory view showing a state during normal work when a wire and a chain, one end of which is connected to a counterweight and the other end of which is connected to a motor provided on a vehicle side, are applied,
9B is a schematic explanatory view showing a state in which the counterweight shown in FIG. 9A is rotated to the intermediate position, and FIG. 9C is operated by a hydraulic cylinder instead of the motor shown in FIG. 9A. 9D is a schematic explanatory view showing a state similar to FIG. 9A, and FIG. 9D shows a state in which the position of the counterweight shown in FIG. 9C is rotated to an intermediate position. It is a schematic explanatory drawing.

10A and 10B show a case where the first and second links are applied in an application example of the embodiment of FIG. 4, where FIG. 10A is a schematic explanatory view showing a state similar to FIG. 4A, and FIG. 4B is a schematic explanatory diagram showing a state similar to FIG. 4B, FIG. 4C is a schematic explanatory diagram showing a state similar to FIG. 4C, and FIG. 10D is a case where only the second link of FIG. FIG. 10E is a schematic explanatory view showing FIG.
It is a schematic explanatory drawing which shows the attachment condition of the stepped link shaft pin which connects the 1st link and the 2nd link of (A) -FIG. 10 (D).

FIG. 11 shows a modification of the rotary stopper of FIG. 6, (A) is a schematic perspective view showing the locked state of the structure of the slide type stopper, and (B) is the locked state of FIG. 11 (A). It is a schematic perspective explanatory view showing a case where the slide type stopper is in an unlocked state.

FIG. 12 is a schematic side view showing a conventional hydraulic excavator that is generally used.

13 is a schematic side view showing a side surface of a conventional counterweight mounting structure in which the counterweight mounted on the rear portion of the hydraulic excavator shown in FIG. 12 can be tilted back and forth.

FIG. 14 is a schematic explanatory surface view showing a plan view of arrow 13A of FIG.

[Explanation of symbols]

1 vehicle 2 Undercarriage 2R track 4 Upper rotating body 5 pivots 6 cabs 7 buckets 9 Rotating means (hydraulic cylinder) 9a axis pin 10 working machines 11 Stopper lever 11a long hole 12, 13 axis pin 14 Body frame 20 counterweight 29 Link axis 30 links 30a 1st link 30b Second link 31 Fixing pin between links 32 fixing pin 39 stepped link shaft pin 40 Rotation prevention part E engine K swing-out mechanism P hydraulic pump

Claims (10)

[Claims]
1. In a vehicle equipped with a working machine in a front portion of a vehicle in a front-rear direction and a counterweight in a rear portion, a holding portion for pivotally supporting the count weight provided in the rear portion on a vehicle body frame of the vehicle. A support portion provided on the count weight for rotatably supporting the counter weight on the holding portion, a swing-out mechanism provided on the vehicle for swinging out the counter weight behind the vehicle, and the holding portion. A swing-out type counterweight structure for a vehicle, comprising: a rotating means disposed on the vehicle for rotating the vehicle around the center.
2. The swing-out counterweight structure for a vehicle according to claim 1, wherein the swing-out mechanism is configured to rotate by the holding portion and the support portion of the counterweight.
3. The counterweight swing-out mechanism is configured so that the counterweight and the holding portion are connected by at least one link. Swing-out type counterweight structure for vehicles.
4. A detachable fixing pin for inserting a link pivotally supported by the counterweight via a link shaft into the link weight and the counterweight at a distance from the link shaft. The swing-out type counterweight structure for a vehicle according to any one of claims 1 to 3, which is characterized.
5. The swing-out type counterweight structure for a vehicle according to claim 3, wherein the links are configured to be connected by a plurality of links.
6. A stopper for limiting a swing-out position of the counterweight is provided between a vehicle side and the counterweight side, according to any one of claims 1 to 5. Swing-out type counterweight structure for the vehicle described.
7. The stopper is rotatably or slidably attached to either one of a lower portion of the counterweight and a rear portion of the vehicle so as to correspond to an attached side of the other. The swing-out type counterweight structure for a vehicle according to claim 6.
8. A detachable fixing pin that is inserted into the link and the counterweight that are pivotally supported via the link shaft provided in the counterweight and that fixes the rotation of the link, and the fixing pin. 7. The stopper according to claim 6, further comprising the stopper configured to limit rotation of the counterweight by contacting a side of the vehicle corresponding to a rotation position of the counterweight. Vehicle swing-out counterweight structure.
9. A first link, one end of which is pivotally supported by the counterweight through the link shaft, and the detachable member which is inserted into the first link and the counterweight at a distance from the link shaft. First connected with a fixed pin
The other end and one end of the link are pivotally supported by the other end of the first link via a link shaft pin, and the other end is pivotally supported by the holding part at the rear portion of the vehicle frame via a pivot shaft. Second
There is a space between the link and the link shaft pin, and the first
5. A detachable inter-link shaft pin that is inserted into the link and the second link, and a detachable fixing pin that is inserted into the second link and the count weight. 5. A vehicle swing-out counterweight structure according to item 5.
10. The other end of the first link and the second link
The link shaft pin connecting the one end of the link is the first
The first shaft portion is configured to include a shaft portion and a second shaft portion extending from the first shaft portion, the first shaft portion pivotally supports the first link and the second link, and the second shaft portion includes the second shaft portion. 10. The swing-out type counterweight structure for a vehicle according to claim 9, which is configured to be inserted into the first link, the second link and the counterweight.
JP2001249238A 2001-08-20 2001-08-20 Swing-out type counterweight construction for motor vehicle Withdrawn JP2003056009A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2001249238A JP2003056009A (en) 2001-08-20 2001-08-20 Swing-out type counterweight construction for motor vehicle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2001249238A JP2003056009A (en) 2001-08-20 2001-08-20 Swing-out type counterweight construction for motor vehicle

Publications (1)

Publication Number Publication Date
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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100117346A1 (en) * 2008-11-13 2010-05-13 Wolfgang Bauer Agricultural vehicle balancing system
CN102275836A (en) * 2011-06-07 2011-12-14 湖南中联重科专用车有限责任公司 Crane, clump weight loading and unloading mechanism for crane, and clump weight block
CN102718159A (en) * 2012-06-29 2012-10-10 徐工集团工程机械股份有限公司 Folding-arm-type super lifting counter weight amplitude variation device for crawler crane
CN102826465A (en) * 2012-09-11 2012-12-19 三一集团有限公司 Rotary counter weight mechanism and crane
CN102826464A (en) * 2012-08-29 2012-12-19 三一重工股份有限公司 Crawler crane mobile counterweight device and crawler crane
WO2013105282A1 (en) * 2012-01-13 2013-07-18 Fukayo Mitsuharu Construction machine
CN103727176A (en) * 2014-01-15 2014-04-16 徐州市久发工程机械有限责任公司 Movable balance weight
CN103754774A (en) * 2014-01-15 2014-04-30 徐州市久发工程机械有限责任公司 Multifunctional pipe hoisting machine
KR20150058852A (en) * 2013-11-21 2015-05-29 삼성중공업 주식회사 Fixing system of davit and portable davit having the same
JP2016147729A (en) * 2015-02-10 2016-08-18 コベルコクレーン株式会社 Car body weight support device of crawler crane
CN107188052A (en) * 2017-07-19 2017-09-22 广东省特种设备检测研究院东莞检测院 A kind of crane packaged type balanced controls
WO2019050069A1 (en) * 2017-09-08 2019-03-14 Volvo Construction Equipment Ab Construction machine

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8201849B2 (en) * 2008-11-13 2012-06-19 Deere & Company Agricultural vehicle balancing system
US20100117346A1 (en) * 2008-11-13 2010-05-13 Wolfgang Bauer Agricultural vehicle balancing system
CN102275836A (en) * 2011-06-07 2011-12-14 湖南中联重科专用车有限责任公司 Crane, clump weight loading and unloading mechanism for crane, and clump weight block
WO2012167507A1 (en) * 2011-06-07 2012-12-13 长沙中联重工科技发展股份有限公司 Crane and counterweight loading and unloading mechanism for crane, counterweight block
WO2013105282A1 (en) * 2012-01-13 2013-07-18 Fukayo Mitsuharu Construction machine
CN102718159A (en) * 2012-06-29 2012-10-10 徐工集团工程机械股份有限公司 Folding-arm-type super lifting counter weight amplitude variation device for crawler crane
CN102826464A (en) * 2012-08-29 2012-12-19 三一重工股份有限公司 Crawler crane mobile counterweight device and crawler crane
CN102826465A (en) * 2012-09-11 2012-12-19 三一集团有限公司 Rotary counter weight mechanism and crane
KR101581237B1 (en) * 2013-11-21 2015-12-30 삼성중공업 주식회사 Fixing system of davit and portable davit having the same
KR20150058852A (en) * 2013-11-21 2015-05-29 삼성중공업 주식회사 Fixing system of davit and portable davit having the same
CN103754774A (en) * 2014-01-15 2014-04-30 徐州市久发工程机械有限责任公司 Multifunctional pipe hoisting machine
CN103727176A (en) * 2014-01-15 2014-04-16 徐州市久发工程机械有限责任公司 Movable balance weight
JP2016147729A (en) * 2015-02-10 2016-08-18 コベルコクレーン株式会社 Car body weight support device of crawler crane
WO2016129262A1 (en) * 2015-02-10 2016-08-18 コベルコクレーン株式会社 Crawler crane car body weight supporting device
US10618781B2 (en) 2015-02-10 2020-04-14 Kobelco Construction Machinery Co., Ltd. Crawler crane car body weight supporting device
CN107188052A (en) * 2017-07-19 2017-09-22 广东省特种设备检测研究院东莞检测院 A kind of crane packaged type balanced controls
WO2019050069A1 (en) * 2017-09-08 2019-03-14 Volvo Construction Equipment Ab Construction machine

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