CN110565724A

CN110565724A - Big arm and rock breaking device

Info

Publication number: CN110565724A
Application number: CN201910904386.1A
Authority: CN
Inventors: 凌杰
Original assignee: Chengdu Hunters Rock Breaking Technology Co Ltd
Current assignee: Chengdu Hunters Rock Breaking Technology Co Ltd
Priority date: 2019-09-24
Filing date: 2019-09-24
Publication date: 2019-12-13

Abstract

A large arm and a rock breaking device. The large arm includes a large arm main body portion, a counterweight, and a counterweight driver. The large arm main body portion includes a first hinge point, a second hinge point, and a third hinge point. The first hinge point is configured to hinge with the vehicle, the second hinge point is configured to hinge with the functional component, and the third hinge point is configured to hinge with the lift cylinder. The counterweight is detachably arranged on one side of the large arm main body part far away from the third hinge joint point. The counterweight driver is connected with the counterweight. The counterweight is slidably connected to the large arm body portion, and the counterweight driver is configured to drive the counterweight to slide on the large arm body portion. The counterweight is arranged on the large arm and can slide along the large arm, so that the gravity center position of the large arm can be adjusted, and the adaptability of the large arm and the rock breaking device comprising the large arm to different rock strata is improved.

Description

Big arm and rock breaking device

Technical Field

Embodiments of the present disclosure relate to a big arm and a rock breaking device.

Background

work implements carried on excavators typically include a boom, an arm, and a bucket, so that the excavator can excavate and load gravel and earth through the boom, the arm, and the bucket. However, with the development of technology and the increase in the popularity of excavators, the excavator can be equipped with a plurality of different work accessories to perform different work contents. For example, an excavator may carry a rock breaking device so that the excavator may be used to break rock or concrete. Moreover, the rock breaking device has the characteristics of flexibility and high efficiency, so that the rock breaking device is widely applied. For example, the rock breaking device can be applied to engineering projects such as mines, underground foundations, subway tunnels, road construction and the like.

disclosure of Invention

The embodiment of the disclosure provides a big arm and a rock breaking device. The big arm is provided with the counter weight, and the counter weight can slide along the big arm to change the focus of big arm in a flexible way, thereby improve big arm and including the adaptability of this big arm's broken rock device to different terranes.

An embodiment of the present disclosure provides a large arm, including: a main arm portion including a first hinge point configured to hinge with the vehicle, a second hinge point configured to hinge with the functional component, and a third hinge point configured to hinge with the lift cylinder; the counterweight is detachably arranged on one side, far away from the third hinge joint, of the large arm main body part; and a counterweight driver connected with the counterweight, wherein the counterweight is in sliding connection with the large arm body part, and the counterweight driver is configured to drive the counterweight to slide on the large arm body part.

In some examples, a slide rail is arranged on one side of the large arm main body part, which is far away from the third hinge point, the counterweight is connected with the large arm main body part in a sliding manner through the slide rail, a part of the large arm main body part, which is close to the slide rail, comprises a counterweight driving cavity, an opening is arranged between the counterweight driving cavity and the slide rail, and the counterweight driver is arranged in the counterweight driving cavity and connected with the counterweight through the opening so as to drive the counterweight to slide along the slide rail.

In some examples, the counterweight actuator includes a fixed end and a movable end, the movable end is configured to be movable toward or away from the fixed end, the fixed end is connected to one end of the large arm main body portion, the movable end is connected to the counterweight, an extending direction of the counterweight driving chamber is substantially parallel to an extending direction of the slide rail, a connecting line of the fixed end and the movable end is substantially parallel to an extending direction of the counterweight driving chamber, and the movable end is configured to be connected to the counterweight through the opening.

In some examples, the upper arm main body portion further includes a fourth hinge point configured to be connected to the lower arm cylinder, and the fixed end is hinged to the fourth hinge point.

In some examples, the large arm main body portion includes a first end portion close to the first hinge point and a second end portion far from the first hinge point, the second end portion exceeds the second hinge point in a direction from the first end portion to the second end portion, the slide rail extends from the first end portion to the second end portion, and a distance between the first end portion and the second end portion is larger than a distance between the first hinge point and the second hinge point.

in some examples, the counterweight driver is configured to drive the counterweight to slide to the second end and to have an end of the counterweight proximate to the first hinge point a distance from the second end that is less than a distance from an end of the counterweight distal to the first hinge point from the second end.

in some examples, the weight of the counterweight is greater than the weight of the large arm body portion.

In some examples, an angle between a line connecting the first hinge point and the third hinge point and a line connecting the second hinge point and the third hinge point is less than 110 degrees.

in some examples, the counterweight drive includes a ram.

In some examples, the functional component includes a forearm or a ripper.

In some examples, the two counter weights may be respectively located at two sides of the large arm main body portion, the slide rails are respectively located at two sides of the large arm main body portion, and the two counter weights are respectively slidably connected with the two slide rails.

In some examples, the large arm main body portion is provided with an accommodating cavity, a part of the accommodating cavity, which is far away from the first hinge point and the second hinge point, is an opening, and the accommodating cavity is located between the two slide rails.

In some examples, the accommodating cavity is provided with a bottom surface, and the bottom surface and the upper surface of the slide rail form an included angle X, and the included angle X is smaller than 70 degrees.

in some examples, the included angle X ranges from 20 degrees to 45 degrees.

an embodiment of the present disclosure further provides a rock breaking device, including any one of the above-mentioned big arms.

In some examples, the breaking apparatus further comprises: the carrier comprises an upper vehicle body and a lower vehicle body, wherein the upper vehicle body is rotationally connected with the lower vehicle body, and the lower vehicle body is provided with a travelling mechanism; and the lifting oil cylinder, wherein the large arm is hinged with the upper vehicle body at the first hinge point, one end of the lifting oil cylinder is hinged with the upper vehicle body, and the other end of the lifting oil cylinder is hinged with the large arm at the third hinge point.

In some examples, the boom main body further comprises a fourth hinge point, the breaking device further comprising: the small arm and the large arm are hinged at the third hinge point and comprise a fifth hinge point, a sixth hinge point and a seventh hinge point; one end of the small arm oil cylinder is hinged with the large arm at the fourth hinge point, and the other end of the small arm oil cylinder is hinged with the small arm at the fifth hinge point; the scarifier is hinged with the small arm at the sixth hinge point and comprises an eighth hinge point; and one end of the ripper oil cylinder is hinged to the seventh hinged point through the small arm, and the other end of the ripper oil cylinder is hinged to the eighth hinged point through the ripper.

In some examples, the forearm comprises: the two small arm supporting parts are arranged oppositely at intervals, an accommodating space is formed between the two small arm supporting parts, and the fifth hinge point and the sixth hinge point are respectively arranged at the two third end parts of the two small arm supporting parts; and the small arm connecting part is used for connecting two fourth end parts of the two small arm supporting parts, which are far away from the two third end parts, wherein the large arm body part is positioned in the accommodating space.

In some examples, the weight of the counterweight is greater than the combined weight of the large arm body portion and the small arm, and the weight of the counterweight is also greater than the combined weight of the small arm and the ripper.

In some examples, the weight of the counterweight is greater than a total weight of the large arm body portion, the small arm, and the ripper.

in some examples, a boundary line F passing through an axis of the sixth hinge point, a boundary line E passing through an axis of the second hinge point, and a boundary line J passing through an axis of the first hinge point are perpendicular to a line H connecting an axis of the first hinge point and an axis of the second hinge point, respectively, the boundary line J being located within or in front of a range of the weight when the weight is located at the first end portion of the large arm main body portion near the first hinge point, and the boundary line E being located within or behind the range of the weight when the weight is located at the second end portion of the large arm main body portion near the second hinge point.

Drawings

to more clearly illustrate the technical solutions of the embodiments of the present disclosure, the drawings of the embodiments will be briefly introduced below, and it is apparent that the drawings in the following description relate only to some embodiments of the present disclosure and are not limiting to the present disclosure.

FIG. 1 is a schematic plan view of a boom according to an embodiment of the present disclosure;

Fig. 2 is a schematic perspective view of a main body of a large arm according to an embodiment of the present disclosure;

Fig. 3 is a schematic structural diagram of a rock breaking device according to an embodiment of the present disclosure;

Fig. 4 is a schematic top view of a rock breaking device provided according to an embodiment of the present disclosure;

Fig. 5 is a schematic structural view of another rock breaking device provided according to an embodiment of the present disclosure;

Fig. 6 is a schematic perspective view of a forearm according to an embodiment of the disclosure;

Fig. 7 is a schematic structural view of another rock breaking device provided according to an embodiment of the present disclosure;

Fig. 8 is a schematic structural view of another rock breaking device provided in accordance with an embodiment of the present disclosure;

fig. 9 is a schematic diagram of a rock breaking device provided according to an embodiment of the present disclosure;

FIG. 10 is a schematic view of another embodiment of a large arm according to the present disclosure;

FIG. 11 is a schematic structural view of another boom according to an embodiment of the present disclosure

FIG. 12 is a side view of a large arm provided in accordance with an embodiment of the present disclosure; and

Fig. 13 is a schematic structural diagram of a counterweight according to an embodiment of the present disclosure.

Detailed Description

in order to make the objects, technical solutions and advantages of the embodiments of the present disclosure more apparent, the technical solutions of the embodiments of the present disclosure will be described clearly and completely with reference to the drawings of the embodiments of the present disclosure. It is to be understood that the described embodiments are only a few embodiments of the present disclosure, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the described embodiments of the disclosure without any inventive step, are within the scope of protection of the disclosure.

Unless otherwise defined, technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this disclosure belongs. The use of "first," "second," and similar terms in this disclosure is not intended to indicate any order, quantity, or importance, but rather is used to distinguish one element from another. Also, the use of the terms "a," "an," or "the" and similar referents do not denote a limitation of quantity, but rather denote the presence of at least one. The word "comprising" or "comprises", and the like, means that the element or item listed before the word covers the element or item listed after the word and its equivalents. For convenience of description, in some drawings, "up", "down", "front", and "rear" are given, in the embodiments of the present disclosure, a vertical direction is a direction from top to bottom, a vertical direction is a direction of gravity, a horizontal direction is a direction perpendicular to the vertical direction, and a horizontal direction from right to left is a direction from front to rear.

A typical rock breaking device includes a large arm, a small arm, and a ripper. The ripper generates acting force to break rocks by using mechanical power transmitted by the large arm or the small arm and the gravity of the rock breaking device itself. The position of the center of gravity of the rock breaking device can be changed in the operation process of the rock breaking device, and the center of gravity of the existing rock breaking device is positioned at the position of the forearm or behind the forearm in most action states. As can be seen from the force resolution, the ripper of the rock breaking device is difficult to obtain a large downward force by making full use of the gravity of the rock breaking device during operation.

The rock breaking capacity of the rock breaking device can be improved by structurally modifying the rock breaking device, for example, by structurally modifying the boom, the forearm and the ripper to improve the efficiency of the action of force or to change the weight of the rock breaking device. In order to adapt to rock formations of different hardness, one conceivable approach is to increase or decrease the weight of the breaking device by increasing or decreasing the counterweight of the breaking device, so that the breaking device maintains a high efficiency when performing construction operations on rock formations of different hardness. However, in actual operation, the method for increasing and reducing the weight of the rock breaking device is complex in operation and low in efficiency, and is difficult to be widely applied.

In order to solve the technical problem, an embodiment of the present disclosure provides a large arm and a rock breaking device. The large arm includes a large arm main body portion, a counterweight, and a counterweight driver. The large arm main body portion includes a first hinge point, a second hinge point, and a third hinge point. The first hinge point is configured to hinge with the vehicle, the second hinge point is configured to hinge with the functional component, and the third hinge point is configured to hinge with the lift cylinder. The counterweight is detachably arranged on one side of the large arm main body part far away from the third hinge joint point. The counterweight driver is connected with the counterweight. The counterweight is slidably connected to the large arm body portion, and the counterweight driver is configured to drive the counterweight to slide on the large arm body portion. Because the big arm is provided with the counter weight, and the counter weight can slide along the big arm, consequently the focus position of big arm can be adjusted in a flexible way, conveniently to improve big arm and including this big arm broken rock device to the adaptability of different terranes.

the boom and the rock breaking device provided by the embodiment of the disclosure are described in detail below with reference to the accompanying drawings.

fig. 1 is a schematic plan view of a large arm according to an embodiment of the present disclosure. As shown in fig. 1, the large arm 100 includes a large arm body portion 110, a weight 120, and a weight driver 130. The large arm main body portion 110 includes a first hinge point 301, a second hinge point 302, and a third hinge point 303. The first hinge point 301 is used for hinging with a vehicle, which may be an excavator, for example. The rock breaking machine may be a rock breaking machine of application No. CN201822087023.7, which has a vehicle body enclosed therein, and the rock breaking operation area is located in the enclosed area, a bulldozer, or other equipment carrying a rock breaking device.

The second hinge point 302 is used to hinge with a functional component (e.g., ripper, excavator forearm and cutting wheel of a trenching apparatus, etc.), and the third hinge point 303 is used to hinge with the lift cylinder 220 of the boom 100. For example, one end of the lift cylinder 220 may be hinged to the carrier, and the other end of the lift cylinder 220 may be hinged to the boom body 110 at the third hinge point 303, so as to lift the boom 100. The weight 120 is detachably disposed on the side of the large arm main body portion 110 away from the second hinge point 302, for example, as shown in fig. 1, the second hinge point 302 is located at the lower portion of the large arm main body portion 110, and the weight 120 is disposed at the upper portion of the large arm main body portion 110. The counterweight 120 is slidably connected to the boom main body portion 110, and one end of the counterweight actuator 130 is connected to the counterweight 120 and is used to drive the counterweight 120 to slide on the boom main body portion 110. The above-described "slide connection" means that the relative positional relationship between the counterweight and the large arm body portion in the extending direction of the large arm body portion is changeable, and the relative positional relationship between the counterweight and the large arm body portion in the direction perpendicular to the extending direction of the large arm body portion is not changed. In addition, the hinge point refers to a position where two components are connected, and generally includes a hole, a contact surface, a connecting shaft and other components required when the components are connected, and the hole of at least one component rotates relative to the connecting shaft.

In the large arm provided by the embodiment of the disclosure, since the counterweight is slidably connected with the large arm main body portion, and the counterweight driver can drive the counterweight to slide on the large arm main body portion, the gravity center of the large arm can be changed along with the sliding of the counterweight. Therefore, the gravity center of the large arm can be flexibly and conveniently adjusted through the counterweight driver and the counterweight, so that the adaptability of the large arm and the rock breaking device comprising the large arm to different rock strata can be improved. For example, in the case that the functional component is a rock breaking component (e.g., a ripper), when the rock formation hardness is not high, the counterweight driver may drive the counterweight so that the counterweight is closer to the first hinge point at the position of the large arm body portion, that is, the position close to the carrier, and at this time, although the downward shear force obtained by the rock breaking component is relatively small, the lifting speed of the large arm is faster, so that the rock breaking efficiency may be higher; and when the hardness of stratum is higher, the counter weight driver can drive the counter weight antedisplacement for the counter weight leans on more at the position of big arm body portion, is close to the position of broken rock part or is located the position that broken rock part kept away from the carrier, and broken rock part can obtain bigger shear force now, thereby can improve broken rock ability. Therefore, the position of the counterweight on the large arm body part can be adjusted according to concrete conditions such as rock hardness and the like, and therefore the optimal rock breaking effect and the optimal rock breaking efficiency are obtained.

Fig. 2 is a schematic perspective view of a main body of a large arm according to an embodiment of the present disclosure. As shown in fig. 2, the slide rail 118 is disposed on a side of the large arm main body portion 110 away from the second hinge point 302, and the counterweight 120 is slidably connected to the large arm main body portion 110 through the slide rail 118. The portion of the large arm body portion 110 adjacent to the slide rail 118 includes a counterweight drive cavity 119. An opening 117 is provided between the counterweight drive cavity 119 and the slide rail 118, the opening 117 being indicated by a dashed box in fig. 2. A counterweight driver 130 may be disposed within the counterweight drive chamber 119, the counterweight driver 130 being coupled to the counterweight 120 through the opening 117 and driving the counterweight 120 to slide along the slide rails 118 on the boom body portion 110. Therefore, the sliding connection between the balance weight and the large arm main body part is realized through the sliding rail, so that the friction force between the balance weight and the large arm main body part can be reduced, and the stability of the balance weight in sliding on the large arm main body part can be improved. In addition, the opening is arranged, so that when the counterweight slides back and forth along the main body part of the large arm, the connection point of the counterweight driver and the counterweight can pass through the opening without interference, the sliding stroke of the counterweight is prolonged, and the adjustment range of the gravity center of the large arm is enlarged.

In some examples, the two ends of the sliding rail can be further provided with limiting devices, so that the balance weight can be prevented from sliding off the large arm main body part, and the safety can be improved.

For example, as shown in fig. 2, the length of the opening 117 may be calculated according to actual requirements of the product, which is not specifically limited by the present disclosure. In some examples, as shown in fig. 1 and 2, the weight drive 130 includes a fixed end 131 and a movable end 132. The movable end 132 is configured to move closer to or away from the fixed end 131, the fixed end 131 is connected to one end of the large arm main body 110, the movable end 132 is connected to the counterweight 120, the extension direction of the counterweight driving chamber 119 is substantially parallel to the extension direction of the slide rail 118, the connection line of the fixed end 131 and the movable end 132 is substantially parallel to the extension direction of the counterweight driving chamber 119, and the movable end 132 is configured to be connected to the counterweight 120 through the opening 117. So set up, be favorable to improving the drive efficiency of counter weight driver to the counter weight to be favorable to making the counter weight driver make full use of counter weight drive chamber's inner space, so that big arm compact structure. In addition, the counterweight driving cavity can also play a protection function for the counterweight driver. The term "substantially parallel" includes the case where the extending direction of the counterweight driving chamber is completely parallel to the extending direction of the slide rail or the connecting line between the fixed end and the movable end, and also includes the case where the angle between the extending direction of the counterweight driving chamber and the extending direction of the slide rail or the connecting line between the fixed end and the movable end is less than 5 degrees.

In some examples, the counterweight actuator may be a cylinder, one end of the cylinder being the fixed end and the other end of the cylinder being the movable end. In addition, wires (such as wires, pipelines and the like) connected with the counterweight driver can be arranged in the counterweight driving cavity, so that the smoothness of the large arm and the safety of components in the counterweight driving cavity are improved.

In some examples, the counterweight driver comprises an oil cylinder, a steel rope, a first wheel, a second wheel and a third wheel, one end of the oil cylinder is hinged with the large arm main body part, the other end of the oil cylinder is hinged with the first wheel, the first wheel is in sliding connection with a sliding rail arranged on the large arm main body part, the sliding rail has a limiting effect on the first wheel, the second wheel is hinged with the large arm main body part at a position close to the second end part, the third wheel is hinged with the large arm main body part at a position close to the first end part, the steel rope is wound with the first wheel, the second wheel and the third wheel in a closing way, the steel rope is provided with a counterweight fixing point, the counterweight fixing point is fixedly connected with the counterweight, the first wheel and the second wheel enable the telescopic stroke of the oil cylinder to be amplified through the arrangement of the winding, thereby driving the steel rope to move around the second wheel and the third wheel and driving the balance weight to slide relative to the main body part of the big arm. This structure is similar to the boom extension of a crane, which is also a more common extension in that the opening 117 of fig. 2, as described above, may not be provided in the counterweight drive.

In some examples, the counterweight driver includes a hydraulic motor and a rack, the counterweight is provided with a hydraulic motor fixing position, the hydraulic motor is fixedly connected to the counterweight, a gear is fixedly connected to an end of the hydraulic motor, the structure of the boom main body portion can be shown in fig. 2, the rack is fixedly connected to a sliding rail at the upper portion of the boom main body portion, the gear is meshed with the rack, the hydraulic motor rotates to drive the gear to move relative to the rack, and thus the counterweight slides relative to the boom main body portion, and in such a structure, the opening 117 shown in fig. 2 may not be provided.

in some examples, as shown in fig. 1 and 2, the large arm body portion 110 further includes a fourth hinge point 304, the fourth hinge point 304 is configured to be connected to the small arm cylinder 230, the fixed end 131 of the counterweight actuator 130 has a mounting position 1170 in the counterweight driving chamber 119, and the mounting position 1170 may be located at the same position as the fourth hinge point 304, that is, both the counterweight actuator 130 and the small arm cylinder 230 are hinged at the fourth hinge point 304. Therefore, the hinge point on the large arm body part can be reduced, the installation space is saved, and the related hinge parts such as the hinge shaft can be reduced.

For example, the arm cylinders 230 may be disposed at both sides of the large arm body portion 110, while the counterweight actuator 130 is disposed in the counterweight driving chamber 119 inside the large arm body portion 110, and the arm cylinders 230 and the counterweight actuator 130 are simultaneously hinged at the fourth hinge point 304, e.g., the arm cylinders 230 and the counterweight actuator 130 are simultaneously hinged by hinge shafts disposed at the fourth hinge point. The small arm cylinders 230 provide a sliding space for the counterweight 120 to slide on the large arm body portion 110 when they are located on both sides of the large arm body portion 110.

In some examples, as shown in fig. 1 and 2, the arm cylinder 230 may be hinged not simultaneously with the counterweight actuator 130 through a hinge shaft provided at the fourth hinge point, for example, the arm cylinder 230 is hinged to the arm main body portion 110 at a ninth hinge point 309, and the ninth hinge point 309 is located below the fourth hinge point 304.

In some examples, as shown in fig. 1 and 2, the large arm main body portion 110 includes a first end portion 111 near the first hinge point 301 and a second end portion 112 far from the first hinge point 301. The first end 111 may be a rear end of the boom 100 near the carrier, and the second end 112 may be a front end of the boom 100 far from the carrier. In the direction from the first end 111 to the second end 112, the second end 112 exceeds the second hinge point 302, i.e. the second end 112 is located on the front side of the second hinge point 302. The slide rail 118 extends from the first end 111 to the second end 112, and the distance between the first end 111 and the second end 112 is greater than the distance between the first hinge point 301 and the second hinge point 302. Thereby, the weight 120 can be slid to the first end portion 111 and the second end portion 112, so that the adjustment range of the center of gravity of the boom can be improved. For example, when the weight driver drives the weight such that the weight is located at the second end, the weight may be located farther from the first hinge point, and the center of gravity of the large arm may be located farther from the first hinge point, so that a greater undercut force may be obtained for a functional component, such as a ripper, without changing the weight of the large arm.

In some examples, as shown in fig. 1, the weight driver 130 may drive the weight 120 to slide to the second end 112 and may extend a portion of the weight 120 (e.g., portion B in fig. 1) out of the large arm. For example, a distance a between an end of the weight 120 near the first hinge point 301 and the second end 112 is smaller than a distance B between an end of the weight 120 far from the first hinge point 301 and the second end 112. So set up, can be under the limited condition of length of big arm main part for the focus of big arm antedisplacement as far as possible, when the counter weight was located the second tip, the focus of counter weight was located the place ahead of second tip, thereby was favorable to increasing down the cutting force for the broken rock device including this big arm. It should be noted that the forward movement refers to a movement away from the first hinge point or the carrier, and the backward movement refers to a movement toward the first hinge point or the carrier.

For example, in one model of a 50 ton class excavator rock breaking device, the slide rail 118 is 7 meters in length and the first hinge point 301 is 4 meters away from the second hinge point 302.

for example, when the counterweight 120 is slid to the second end 112, in one version of the large arm, the distance A is 0.8 meters and the distance B is 2.5 meters; in another version of the boom, the distance a is 0.8 meters and the distance B is 3.5 meters; in another version of the boom, the distance a is 0.6 meters and the distance B is 2.5 meters; in another version of the boom, the distance a is 0.6 meters and the distance B is 3.5 meters.

In some examples, the weight of the counterweight 120 is greater than the weight of the large arm body portion 110, which may further increase the ability of the counterweight 120 to adjust the center of gravity of the large arm 100. For example, in one model of a 50 ton class excavator rock breaking apparatus, the counterweight 120 weighs 8 tons and the large arm body portion 110 weighs 4 tons. For another example, in another model of a 50 ton class excavator rock breaking device, the weight of the counterweight 120 is 10 tons and the weight of the large arm body portion 110 is 4 tons.

In some examples, as shown in fig. 1, an angle C between a line connecting the first hinge point 301 and the third hinge point 303 and a line connecting the second hinge point 302 and the third hinge point 303 is less than 110 degrees. For example, in one type of large arm, the angle C is 100 degrees; in the other type of big arm, the included angle C is 95 degrees; in another type of big arm, the included angle C is 105 degrees; in another type of large arm, the angle C is 98 degrees. By the arrangement, the upward component force of the acting force of the lifting oil cylinder can be increased, so that the lifting capacity of the lifting oil cylinder of the large arm can be improved.

In some examples, the counterweight drives 130 are cylinders, which belong to the hydraulic drive system. The hydraulic driving system comprises a hydraulic pump, a controller, hydraulic oil, an oil tank, an oil cylinder, a hydraulic motor and the like. When the rock breaking device with the large arm provided by the embodiment is used for rock breaking operation, the oil cylinder is used as a counterweight driver, and working medium hydraulic oil of the oil cylinder has certain compressibility and can play a certain buffering role, so that the shaking of the rock breaking device is reduced. In addition, the oil cylinder has simple and reliable structure and is an ideal counterweight driver. The counterweight driver may also be a pneumatic driving system or an electric driving system, and the disclosure is not limited thereto.

in some examples, the functional component includes a forearm or ripper. The large arm may be connected to the small arm or the ripper via a second hinge point, thereby constituting part of the rock breaking apparatus. Of course, the functional component may also be a component having other functions, such as a cutter, etc., and the disclosure is not limited thereto.

Fig. 3 is a schematic structural diagram of a rock breaking device according to an embodiment of the present disclosure; fig. 4 is a schematic top view of a rock breaking device provided according to an embodiment of the present disclosure; fig. 5 is a schematic structural diagram of another rock breaking device provided according to an embodiment of the present disclosure. As shown in fig. 3-5, the breaking device includes a large arm 100 provided in the above-described embodiment. Thus, since the counterweight is slidably connected to the boom main body portion and the counterweight driver can drive the counterweight to slide on the boom main body portion, the center of gravity of the boom can be changed as the counterweight slides. Therefore, the gravity center of the large arm can be flexibly and conveniently adjusted through the counterweight driver and the counterweight, and the adaptability of the rock breaking device to different rock strata can be improved. For a description of specific beneficial effects, reference may be made to the related description of the embodiment of the large arm, and no further description is given here.

In some examples, as shown in fig. 3-5, the breaking device further includes a carrier 210; the vehicle 210 includes an upper vehicle body 211 and a lower vehicle body 212, the upper vehicle body 211 being rotatably connected to the lower vehicle body 212, and the lower vehicle body 212 being provided with a traveling mechanism 214. The boom 100 is hinged to the upper body 211 at a first hinge point 301, one end of the lift cylinder 220 is hinged to the upper body 211, and the other end of the lift cylinder 220 is hinged to the boom body 110 at a third hinge point 303. The lifting cylinder 220 can drive the big arm 100 to move around the first hinge point 301, so as to lift the big arm 100.

For example, the number of the lift cylinders 220 may be two, and the two lift cylinders are respectively located at the left and right sides of the large arm main body portion 110, and the hinge holes for the lift cylinders to hinge with the large arm main body portion are located at the third hinge point 303. So set up, the hydro-cylinder has two fulcrums to the big arm, makes the lifting action stable.

In some examples, as shown in fig. 3 and 4, the breaking device further includes a forearm 240, a forearm cylinder 230, a ripper 250, and a ripper cylinder 260. The small arm 240 is hinged at the second hinge point 302 with the large arm 100, and the small arm 240 includes a fifth hinge point 305, a sixth hinge point 306, and a seventh hinge point 307. One end of the arm cylinder 230 is hinged to the large arm 100 at a fourth hinge point 304, and the other end of the arm cylinder 230 is hinged to the arm 240 at a fifth hinge point 305. Ripper 250 is hinged to forearm 240 at sixth hinge point 306, and ripper 250 includes eighth hinge point 308. One end of the ripper cylinder 260 is hinged to the small arm 240 at a seventh hinge point 307, and the other end of the ripper cylinder 260 is hinged to the ripper 250 at an eighth hinge point 308. Forearm cylinder 230 may drive forearm 240 about second hinge point 302 and ripper cylinder 260 may drive ripper 250 about sixth hinge point 306. In this way, the lifting cylinder 220, the arm cylinder 230 and the ripper cylinder 260 of the boom 100 are cooperatively driven, so that the boom 100, the arm 240 and the ripper 250 can cooperatively move, thereby achieving the purpose of breaking rocks by the rock breaking device.

In some examples, the number of arm cylinders 230 and ripper cylinders 260 is also two, respectively, as is the case with the boom cylinder 220. For example, the two forearm cylinders 230 may be respectively located at the left and right sides of the large arm main body portion 110, so that a sliding space may be provided for the counterweight 120 on the one hand, and stability may be improved on the other hand; two ripper cylinders 260 may also be provided on both sides of the ripper 250 to improve stability.

fig. 6 is a schematic perspective view of a forearm according to an embodiment of the disclosure. As shown in fig. 6, the lower arm 240 includes two lower arm supporting portions 243 and a lower arm connecting portion 244. The two arm support portions 243 are disposed at an interval and form an accommodating space between the two arm support portions 243, and the fifth hinge point 305 and the sixth hinge point 306 are disposed at the third end portions 2433 of the two arm support portions 243, respectively. The small arm connecting part 244 connects the two small arm supporting parts 243 to the two fourth end parts 2434 away from the two third end parts 2433. The large arm body 110 may be partially located in the accommodating space during operation. In some cases, when the small arm cylinder 230 is fully extended, the accommodating space is located at a position close to the lower front, and the large arm body 110 is not located in the accommodating space, so that the large arm body 110 cannot be located in the accommodating space, which should be determined according to specific situations. The width of the accommodating space is larger than that of the counterweight, so that the counterweight can be allowed to pass through the accommodating space. The forearm sets up accommodation space and can make the forearm leave sliding channel for the counter weight when, the cooperation of forearm and big arm, agitator and hydro-cylinder is reasonable, and forearm structural strength is sufficient and the practicality is strong.

in some examples, in the rock breaking device described above, the weight of the counterweight is greater than the total weight of the large arm body portion and the small arm, and the weight of the counterweight is also greater than the total weight of the small arm and the ripper. For example, in one model of a 50 ton class excavator rock breaking device, the counterweight weighs 8 tons, the boom weighs 4 tons, the forearm weighs 3 tons, and the ripper weighs 3 tons. Therefore, the adjustment capability of the counterweight on the gravity center of the rock breaking device can be further increased.

In some examples, in the above-described rock breaking device, the weight of the counterweight is greater than the total weight of the large arm body portion, the small arm, and the ripper. Therefore, the adjustment capability of the counterweight on the gravity center of the rock breaking device can be further increased. For example, in another model of a 50 ton class excavator rock breaking device, the counterweight weighs 10 tons, the boom weighs 4 tons, the forearm weighs 3 tons, and the ripper weighs 2 tons. So the ability of adjusting the gravity center of the rock breaking device by the counterweight can be further increased.

In the rock breaking device provided by the embodiment of the disclosure, the large arm is provided with the slidable counterweight, so that the adaptability of the rock breaking device to different rock strata is improved. For example, when the rock formation hardness is not high and the lifting speed is required to be higher, the counterweight driver drives the counterweight to slide to the position of the large arm close to the carrier, the gravity center of the rock breaking device moves backwards, the lifting speed of the rock breaking device is higher, and therefore the rock breaking efficiency is higher; when the rock stratum hardness is hard and the shearing force needs to be increased, the counterweight driver drives the counterweight to move forwards to a reasonable position, the gravity center of the rock breaking device moves forwards, the shearing force is increased, and therefore the rock breaking capacity can be improved. Moreover, as mentioned above, the gravity center position of the rock breaking device can be conveniently adjusted in the front-back direction, the weight adjustment is accurate, the adjustment effect is better, and the rock breaking capacity of the rock breaking device can be obviously improved. In addition, the broken rock device that this disclosed embodiment provided, counter weight sliding distance is long, and counter weight is big, and the counter weight is strong and operate the facility to broken rock device's focus regulating power. When the counter weight is located big arm second end, broken rock device under most action states, the focus point can be located forearm the place ahead, and broken rock device is rational in infrastructure, compares with general broken rock device, has obviously improved broken rock device's operating capability.

fig. 7 is a schematic structural view of another rock breaking device provided according to an embodiment of the present disclosure; fig. 8 is a schematic structural view of another rock breaking device provided according to an embodiment of the present disclosure. As shown in fig. 7 and 8, the counterweight 120 is located above the second hinge point 302, two counterweights 120 may be provided, two counterweights 120 may be located on two sides of the large arm body portion 110 respectively, the slide rails 118 are located on two sides of the large arm body portion 110 respectively, the two counterweights 120 are slidably connected with the two slide rails 118 respectively, one end of the counterweight driver 130 is connected with the large arm body portion 110, the other end of the counterweight driver 130 is connected with the counterweight 120, and the counterweight driver 130 drives the counterweight 120 to move relative to the large arm body portion 110. Thus, the structure can also conveniently adjust the center of gravity.

Fig. 9 is a schematic diagram of a rock breaking device provided according to an embodiment of the present disclosure. As shown in fig. 9, the second end portion 112 faces upward relative to the front end of the line connecting the first end portion 111, which facilitates the operation of the rock breaking device. A boundary F passing through the axis of the sixth hinge point 306, a boundary E passing through the axis of the second hinge point 302, and a boundary J passing through the axis of the first hinge point 301 are perpendicular to a connection H of the axis of the first hinge point 301 and the axis of the second hinge point 302, respectively. When the weight 120 is located at the rearmost end of the large arm main body portion 110 (i.e., the end close to the first hinge point), the boundary line J is located within or in front of the weight 120 (i.e., the side of the weight close to the second hinge point), which allows a large adjustment position of the center of gravity of the weight in the rearward direction, and when the weight 120 is located at the foremost end of the large arm main body portion 110 (i.e., the end close to the second hinge point), the boundary line E is located within or behind the weight 120 (i.e., the side of the weight close to the first hinge point), which allows a large adjustment position of the center of gravity of the weight.

It should be noted that, during operation, the position of the sixth hinge point 306 is changed relative to the main body 110, and when the counterweight 120 is located at the foremost end of the main body 110, the boundary line F is located within or behind the counterweight range, which is beneficial for the center of gravity of the counterweight 120 to be located above the undercut point of the ripper 250 during rock breaking, so as to increase the undercut force. FIG. 10 is a schematic view of another embodiment of a large arm according to the present disclosure; fig. 11 is a schematic structural view of another large arm provided according to an embodiment of the present disclosure. As shown in fig. 10 and 11, the accommodating chamber 280 is disposed on the upper front side of the large arm main body portion 110, the accommodating chamber 280 is open towards the front and upward, that is, the portion of the accommodating chamber 280 away from the first hinge point 301 and the second hinge point 302 is open, and the accommodating chamber 280 is located between the two slide rails 118. During operation of the rock breaking device carrying the large arm, the partial position of the small arm 240 or the partial position of the ripper 250 can be located in the accommodating cavity 280, so that the counterweight 120 does not interfere with the small arm 240 and the ripper 250; in some embodiments, ripper 250 may not be located within the receiving cavity when it is relatively small.

FIG. 12 is a side view of a large arm provided in accordance with an embodiment of the present disclosure. As shown in fig. 11 and 12, the receiving cavity 280 is provided with a bottom surface 290, the bottom surface 290 and a plane formed by the slide rail 118 form an included angle X, the included angle X is smaller than 70 degrees, the reason is that the second end 112 or the counterweight 120 is not easy to touch the rock formation, the front part of the bottom surface 290 is lower than the rear part, so that when the forearm cylinder 230 is completely retracted under the condition of a larger stroke, the forearm cylinder 230 is not easy to touch the bottom surface 290, and if the included angle X is larger than 70 degrees, geometric analysis shows that the installation is impossible; it is preferred to use 20 degrees to 45 degrees, when being less than 20 degrees, lead to the broken rock device to have the underarm hydro-cylinder 230 retrieve the stroke to be on the small side under the condition of the great undercut space, or the underarm hydro-cylinder 230 retrieves the stroke under the great condition to be on the small side, when being greater than 45 degrees, the underarm hydro-cylinder 230 retrieves the stroke great, but lead to the slide rail 118 front portion too to the top easily, be unfavorable for on the contrary that the counter weight focus is located more the place ahead under the same slide rail length condition, specific number of degrees should be confirmed according to the concrete setting of broken rock device, different carriers and the setting of different underarm 240 moments and the setting of different big arm 100, its angle that is more ideal can change.

Fig. 13 is a schematic structural diagram of a counterweight according to an embodiment of the present disclosure. As shown in fig. 13, the counterweight 120 includes a sliding portion 420, a driving accommodating cavity 410, and a ninth hinge point 309, the sliding portion 420 is a groove and is engaged with the sliding rail 118, the counterweight 120 is limited and slides on the main body portion 110, and the engagement between the sliding portion 420 and the sliding rail 118 may be surface contact or may be a rolling engagement between the rolling wheel and the sliding rail 118 by disposing a rolling wheel at the position of the sliding portion 420; the ninth hinge point 309 is connected to the movable end of the counterweight actuator 130, the driving accommodating cavity 410 is a space disposed in the counterweight 120, the driving accommodating cavity 410 is used for accommodating the counterweight actuator 130, and the space is a rectangular space; in other embodiments, the shape of the space is determined according to the shape of the weight driver 130, which may be provided in a square, circle, or oval shape, among other shapes; through the arrangement of the balance weight, the structure is compact and reasonable.

The following points need to be explained:

(1) the drawings of the embodiments of the disclosure only relate to the structures related to the embodiments of the disclosure, and other structures can refer to the common design.

(2) Without conflict, embodiments of the present disclosure and features of the embodiments may be combined with each other to arrive at new embodiments.

The above is only a specific embodiment of the present disclosure, but the scope of the present disclosure is not limited thereto, and any person skilled in the art can easily conceive of changes or substitutions within the technical scope of the present disclosure, and shall be covered by the scope of the present disclosure. Therefore, the protection scope of the present disclosure shall be subject to the protection scope of the claims.

Claims

1. An upper arm, comprising:

A main arm portion including a first hinge point configured to hinge with the vehicle, a second hinge point configured to hinge with the functional component, and a third hinge point configured to hinge with the lift cylinder; and

The counterweight is detachably arranged on one side, far away from the second hinge point, of the large arm main body part; and

A counterweight driver connected with the counterweight,

Wherein the counterweight is slidably connected to the large arm body portion, and the counterweight driver is configured to drive the counterweight to slide on the large arm body portion.

2. The large arm according to claim 1, wherein a slide rail is provided on a side of the large arm main body portion away from the second hinge point, the counterweight is slidably connected with the large arm main body portion through the slide rail,

The part of the large arm main body part close to the sliding rail comprises a counterweight driving cavity, an opening is formed between the counterweight driving cavity and the sliding rail, and the counterweight driver is arranged in the counterweight driving cavity and is connected with the counterweight through the opening to drive the counterweight to slide along the sliding rail.

3. The large arm according to claim 2, wherein the weight actuator includes a fixed end and a movable end, the movable end being configured to be movable toward and away from the fixed end, the fixed end being connected to one end of the large arm main body portion, the movable end being connected to the weight,

The extending direction of the counterweight driving cavity is approximately parallel to the extending direction of the slide rail, the connecting line of the fixed end and the movable end is approximately parallel to the extending direction of the counterweight driving cavity, and the movable end is configured to be connected with the counterweight through the opening.

4. The large arm according to claim 3, wherein the large arm main body portion further includes a fourth hinge point configured to be connected to a small arm cylinder, the fixed end being hinged to the fourth hinge point.

5. The large arm according to claim 2, wherein the large arm main body portion includes a first end portion close to the first hinge point and a second end portion distant from the first hinge point, the second end portion exceeding the second hinge point in a direction from the first end portion to the second end portion, the slide rail extending from the first end portion to the second end portion, a distance between the first end portion and the second end portion being larger than a distance between the first hinge point and the second hinge point.

6. the large arm according to claim 4, wherein the counterweight driver is configured to drive the counterweight to slide to the second end and to have a distance between an end of the counterweight close to the first hinge point and the second end smaller than a distance between an end of the counterweight far from the first hinge point and the second end.

7. A large arm according to any of claims 1-6, wherein the weight of the counterweight is greater than the weight of the large arm body portion.

8. The large arm according to any of claims 1-6, wherein an angle between a line connecting the first hinge point and the third hinge point and a line connecting the second hinge point and the third hinge point is less than 110 degrees.

9. the boom of any of claims 1-6, wherein the counterweight drive comprises a ram.

10. The large arm according to any one of claims 1-6, wherein the functional component comprises a small arm or ripper.

11. the rock breaking device according to any one of claims 2 to 6, wherein the balance weight is provided in two, two balance weights can be respectively located on two sides of the large arm main body part, the slide rails are respectively located on two sides of the large arm main body part, and the two balance weights are respectively in sliding connection with the two slide rails.

12. The rock breaking device according to claim 11, wherein a containing cavity is arranged on the large arm main body part, the part of the containing cavity, which is far away from the first hinge point and the second hinge point, is an opening, and the containing cavity is positioned between the two slide rails.

13. The rock breaking device of claim 12, wherein the receiving cavity is provided with a bottom surface that forms an included angle X with an upper surface of the slide rail, the included angle X being less than 70 degrees.

14. a rock breaking device according to claim 13, wherein the included angle X is in the range 20-45 degrees.

15. A rock breaking device comprising a large arm according to any one of claims 1-14.

16. The rock breaking device of claim 15, further comprising:

The carrier comprises an upper vehicle body and a lower vehicle body, wherein the upper vehicle body is rotationally connected with the lower vehicle body, and the lower vehicle body is provided with a travelling mechanism; and

A lifting oil cylinder is arranged on the base,

The large arm is hinged with the upper vehicle body at the first hinge point, one end of the lifting oil cylinder is hinged with the upper vehicle body, and the other end of the lifting oil cylinder is hinged with the large arm at the third hinge point.

17. The rock breaking device of claim 16, wherein the boom body portion further comprises a fourth hinge point, the rock breaking device further comprising:

The small arm and the large arm are hinged at the third hinge point and comprise a fifth hinge point, a sixth hinge point and a seventh hinge point;

One end of the small arm oil cylinder is hinged with the large arm at the fourth hinge point, and the other end of the small arm oil cylinder is hinged with the small arm at the fifth hinge point;

The scarifier is hinged with the small arm at the sixth hinge point and comprises an eighth hinge point; and

and one end of the ripper oil cylinder is hinged to the seventh hinged point through the small arm, and the other end of the ripper oil cylinder is hinged to the eighth hinged point through the ripper.

18. The rock breaking device of claim 17, wherein the small arm comprises:

The two small arm supporting parts are arranged oppositely at intervals, an accommodating space is formed between the two small arm supporting parts, and the fifth hinge point and the sixth hinge point are respectively arranged at the two third end parts of the two small arm supporting parts; and

A small arm connecting part connecting two fourth end parts of the two small arm supporting parts far away from the two third end parts,

the large arm body part can be partially positioned in the accommodating space during operation.

19. The rock breaking device of claim 17 or 18, wherein the weight of the counterweight is greater than the total weight of the large arm body portion and the small arm, and the weight of the counterweight is also greater than the total weight of the small arm and the ripper.

20. The rock breaking device of claim 19, wherein the weight of the counterweight is greater than the total weight of the large arm body portion, the small arm, and the ripper.

21. The rock breaking device according to claim 17 or 18, wherein a boundary line F passing through an axis of the sixth hinge point, a boundary line E passing through an axis of the second hinge point, and a boundary line J passing through an axis of the first hinge point are perpendicular to a connection line H between the axis of the first hinge point and the axis of the second hinge point, respectively, the boundary line J being located within or in front of the counterweight when the counterweight is located at the first end portion of the large arm main body portion near the first hinge point, and the boundary line E being located within or behind the counterweight when the counterweight is located at the second end portion of the large arm main body portion near the second hinge point.