CN211113841U

CN211113841U - Rock breaking device

Info

Publication number: CN211113841U
Application number: CN201921593906.3U
Authority: CN
Inventors: 凌杰
Original assignee: Chengdu Lieshizhe Rock Breaking Technology Co ltd
Current assignee: Sichuan stone Hunter Longyu Technology Co.,Ltd.
Priority date: 2019-09-24
Filing date: 2019-09-24
Publication date: 2020-07-28
Anticipated expiration: 2029-09-24

Abstract

A rock breaking device comprising: big arm, big arm hydro-cylinder and forearm. The large arm comprises a first hinge point, a second hinge point and a third hinge point, wherein the first hinge point is configured to be hinged with the carrier; one end of the big arm oil cylinder is hinged with the big arm at a second hinge point, and the other end of the big arm oil cylinder is configured to be hinged with the carrier; the small arm and the large arm are hinged at a third hinge point, and an included angle between a first plane formed by the axis of the first hinge point and the axis of the second hinge point and a second plane formed by the axis of the third hinge point and the axis of the second hinge point is less than 110 degrees. The rock breaking device can improve the lifting capacity of the large-arm oil cylinder, so that the rock breaking efficiency can be improved.

Description

Rock breaking device

Technical Field

Embodiments of the present disclosure relate to 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, rock breaking can also be performed by using an excavator-mounted ripper in construction and mining. And is widely used due to its high efficiency and convenience.

SUMMERY OF THE UTILITY MODEL

The embodiment of the disclosure provides a rock breaking device. The rock breaking device comprises a large arm, a large arm oil cylinder and a small arm; the large arm comprises a first hinge point, a second hinge point and a third hinge point, wherein the first hinge point is configured to be hinged with the carrier; one end of the big arm oil cylinder is hinged with the big arm at a second hinge point, and the other end of the big arm oil cylinder is configured to be hinged with the carrier; the small arm and the large arm are hinged at a third hinge point, and an included angle between a first plane formed by the axis of the first hinge point and the axis of the second hinge point and a second plane formed by the axis of the third hinge point and the axis of the second hinge point is less than 110 degrees. So set up, under the equal circumstances of the second pin joint of big arm hydro-cylinder and big arm to the first pin joint's of big arm and carrier distance, when the axis of first pin joint and the axis of the axis formation of second pin joint point and the axis of third hinge point are less than 110 degrees between the second plane of axis formation of second pin joint point, the third hinge point of big arm and forearm is shorter to the distance of the first pin joint of big arm and carrier, it is less to lift the required lift force of big arm and forearm this moment, thereby can promote the lift capacity of big arm hydro-cylinder, and then can improve broken rock efficiency.

At least one embodiment of the present disclosure provides a rock breaking device. The rock breaking device comprises a large arm, a first hinge point, a second hinge point and a third hinge point, wherein the first hinge point is configured to be hinged with the carrier; one end of the big arm oil cylinder is hinged with the big arm at the second hinge point, and the other end of the big arm oil cylinder is configured to be hinged with the carrier; and the small arm is hinged with the large arm at the third hinge point, and an included angle between a first plane formed by the axis of the first hinge point and the axis of the second hinge point and a second plane formed by the axis of the third hinge point and the axis of the second hinge point is less than 110 degrees.

For example, in a rock breaking device provided in an embodiment of the present disclosure, the large arm further includes a fourth hinge point, and the small arm includes: fifth pin joint, sixth pin joint and seventh pin joint, broken rock device still includes: one end of the bucket rod oil cylinder is hinged with the large arm at the fourth hinge point, and the other end of the bucket rod 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 with the small arm at the seventh hinge point, and the other end of the ripper oil cylinder is hinged with the ripper at the eighth hinge point.

For example, in the rock breaking device provided by an embodiment of the present disclosure, a ratio of a maximum distance between the axis of the arm cylinder and the third hinge point to a distance between the third hinge point and the sixth hinge point is greater than 0.8.

For example, the rock breaking device that this disclosure an embodiment provided still includes: 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, the lower vehicle body is provided with a traveling device, the upper vehicle body is arranged at a first hinge point and is hinged with a large arm, one end, far away from a second hinge point, of a large arm oil cylinder is hinged with the upper vehicle body, the large arm oil cylinder is in a completely retracted state, the first hinge point and the end, close to the scarifier, of the traveling device form a third plane, the third plane is tangent to the end, close to the scarifier, of the traveling device, the third hinge point is located on one side, close to the carrier, of the third plane, and the second hinge point is located on one side, far away from the carrier, of the third plane.

For example, in a rock breaking device provided in an embodiment of the present disclosure, the first hinge point is located at a first end portion of the large arm, the third hinge point is located at a second end portion of the large arm away from the first end portion, and a cross-sectional area of the large arm gradually increases from the first end portion to the second end portion.

For example, in a rock breaking device provided by an embodiment of the disclosure, the large arm includes an upper cover plate, a lower cover plate and a side plate, the upper cover plate, the lower cover plate and the side plate form a first box-shaped structure, and the cross-sectional area of the first box-shaped structure gradually increases from the first end to the second end.

For example, in the rock breaking device provided by an embodiment of the present disclosure, the boom further includes two first ear plates, the two first ear plates are respectively connected to the two side plates, the upper portion of the connecting member is connected to or integrally disposed with one end of the upper cover plate away from the first hinge point, the lower portion of the connecting member is connected to or integrally disposed with one end of the lower cover plate away from the first hinge point, the thicknesses of the first ear plates are respectively greater than the thicknesses of the upper cover plate, the lower cover plate and the side plates, and the second hinge point and the third hinge point are disposed on the first ear plates.

For example, in the rock breaking device provided in an embodiment of the present disclosure, when the arm cylinder is in a fully retracted state, the connecting member is disposed opposite to the small arm, and a plate surface of the connecting member is substantially parallel to a plate surface of the small arm close to the connecting member.

For example, in a rock breaking device provided in an embodiment of the present disclosure, an included angle between the first lug plate and the plate surface of the lower cover plate is less than 180 degrees to form a recessed space between the first lug plate and the lower cover plate, and an end of the carrier near the small arm may be located in the recessed space.

For example, in a rock breaking device provided in an embodiment of the present disclosure, the ripper includes: the eighth hinge point is located on the ripper body; a scarifier head; a bucket tooth; one end of the scarifier head is detachably fixed on the scarifier body through the fixing device, and the bucket teeth are detachably fixed at one end, far away from the scarifier body, of the scarifier head.

For example, in a rock breaking device provided in an embodiment of the present disclosure, one end of the ripper head near the ripper body includes a ripper head cavity, and the fixing device is configured to be inserted into the ripper head cavity to detachably fix the ripper head and the ripper body.

For example, in a rock breaking device provided by an embodiment of the present disclosure, the fixing device includes an elastic fixing device, one end of the elastic fixing device is in contact with the ripper body, and the other end of the elastic fixing device is in contact with the ripper head.

For example, in a rock breaking device provided by an embodiment of the present disclosure, the weight of the ripper accounts for 50% or more of the total weight of the large arm, the small arm, and the ripper.

For example, in the rock breaking device provided by an embodiment of the present disclosure, a ratio of a distance from the second hinge point to the third hinge point to a distance from the fifth hinge point to the third hinge point is 0.45-0.65.

For example, in the rock breaking device provided by an embodiment of the present disclosure, when the lift angle of the boom cylinder is 45 degrees, the ratio of the vertical distance between the second hinge point and the third hinge point to the distance between the fifth hinge point and the third hinge point is 0.42 to 0.59.

For example, in a rock breaking device provided by an embodiment of the disclosure, the second end of the large arm has a first adjacent surface at a position facing the small arm, the small arm has a second adjacent surface at a position facing the large arm, and the first adjacent surface and the second adjacent surface may be parallel or substantially parallel.

For example, in a rock breaking device provided in an embodiment of the present disclosure, the small arm includes a second box-shaped structure and a second ear plate, the second box-shaped structure is a structural member having a hollow cavity, the fifth hinge point and the seventh hinge point are disposed on the second box-shaped structure, the third hinge point and the sixth hinge point are disposed on the second ear plate, and the third hinge point is disposed on the protruding portion.

For example, in a rock breaking device provided by an embodiment of the present disclosure, the projection is located at a position of the second adjacent face extension portion toward the first 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 structural diagram of a rock breaking device according to an embodiment of the present disclosure;

fig. 2 is a schematic view of another rock breaking device provided in accordance with an embodiment of the present disclosure;

fig. 3 is a schematic diagram of a rock breaking device for lifting according to an embodiment of the present disclosure;

fig. 4 is a schematic structural view of another rock breaking device provided according to an embodiment of the present disclosure;

fig. 5 is a schematic structural view of a boom of a rock breaking device according to an embodiment of the present disclosure;

fig. 6 is a schematic structural view of a boom of another rock breaking device provided according to an embodiment of the present disclosure;

fig. 7 is a schematic view of another rock breaking device provided in accordance with an embodiment of the present disclosure;

FIG. 8 is a schematic structural view of a fixing device according to an embodiment of the present disclosure;

fig. 9 is a schematic structural view of a small arm of a rock breaking device according to an embodiment of the present disclosure; and

fig. 10 is a schematic view illustrating disassembly of a small arm of a rock breaking device 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, and in the embodiments of the present disclosure, the vertical direction is a direction from top to bottom, the vertical direction is a direction of gravity, the horizontal direction is a direction perpendicular to the vertical direction, and the horizontal direction from left to right in the drawings is a direction from front to rear).

When the excavator carries a scarifier to break rocks, in order to save the manufacturing cost, the boom and the boom cylinder can adopt the boom and the cylinder configured for the excavating function of the original excavator. In order to increase the excavation range, the length of the boom and the cylinder, which are configured for the excavation function of the original excavator, is generally increased. However, when the excavator carries a ripper to break rocks, when the boom cylinder is in a fully retracted state, one end of the boom cylinder remote from the excavator may exceed one end of the traveling device of the excavator close to the ripper or approach one end of the traveling device close to the ripper, which may easily cause an excessively large distance between the traveling device and the working range of the ripper, and may cause an excessively large lifting load of the boom cylinder. On the other hand, in order to improve the rock breaking capacity, the weight of the ripper is configured to be large, so that the lifting speed is low under the condition that the lifting oil cylinder is not replaced, and the rock breaking efficiency is low.

In addition, in order to provide the small arm with a lever ratio which is relatively labor-saving, the length from the connection point of the large arm and the small arm to the connection point of the small arm and the ripper is short, and the length of the ripper is limited, resulting in insufficient excavation depth at the time of performing the trenching work and the recessing work.

In order to enable the bucket rod oil cylinder and the scarifier oil cylinder to have a labor-saving lever ratio, the length from a hinge point of the large arm and the small arm to an operating part of the scarifier is relatively short, so that the height from the hinge point of the large arm and the small arm to the rock stratum surface or the upper and lower directions of a horizontal plane is small, the height from the hinge point of the large arm oil cylinder to the hinge point of the large arm and the hinge point of the small arm is close to the height from the hinge point of the large arm and the hinge point of the small arm, so that the lifting angle of the large arm oil cylinder is poor, the length is changed within a certain range in operation, the length comprises the hinge point of the large arm and the small arm to the hinge point of the scarifier and the.

In order to solve the technical problem, the embodiment of the present disclosure provides a rock breaking device. This broken rock device includes: big arm, big arm hydro-cylinder and forearm. The large arm comprises a first hinge point, a second hinge point and a third hinge point, wherein the first hinge point is configured to be hinged with the carrier: one end of the big arm oil cylinder is hinged with the big arm at a second hinge point, and the other end of the big arm oil cylinder is configured to be hinged with the carrier; the small arm and the large arm are hinged at a third hinge point, and an included angle between a first plane formed by the axis of the first hinge point and the axis of the second hinge point and a second plane formed by the axis of the third hinge point and the axis of the second hinge point is less than 110 degrees. So set up, under the equal circumstances of the second pin joint of big arm hydro-cylinder and big arm to the first pin joint's of big arm and carrier distance, when the axis of first pin joint and the axis of the axis formation of second pin joint point and the axis of third hinge point are less than 110 degrees between the second plane of axis formation of second pin joint point, the third hinge point of big arm and forearm is shorter to the distance of the first pin joint of big arm and carrier, it is less to lift the required lift force of big arm and forearm, thereby can promote the lift ability of big arm hydro-cylinder, and then can improve broken rock efficiency.

The rock breaking device provided by the embodiment of the disclosure is described in detail below with reference to the accompanying drawings.

Fig. 1 is a schematic structural diagram of a rock breaking device according to an embodiment of the present disclosure. Fig. 2 is a schematic view of another rock breaking device provided according to an embodiment of the present disclosure. As shown in fig. 1 and 2, the rock breaking device comprises a large arm 110, a large arm cylinder 120 and a small arm 130. The large arm 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 the vehicle 200 (e.g. excavator).

One end of the boom cylinder 120 is hinged to the boom 110 at the second hinge point 302, and the other end of the boom cylinder 120 is hinged to the vehicle, at this time, the boom 110 can rotate around the first hinge point 301 by the extension and contraction of the boom cylinder 120, so as to lift the boom 110. The small arm 130 is hinged to the large arm 110 at a third hinge point 303. The angle a between a first plane 501 formed by the axis of the first hinge point 301 and the axis of the second hinge point 302 and a second plane 502 formed by the axis of the third hinge point 303 and the axis of the second hinge point 302 is less than 110 degrees.

It should be noted that in practice, the axis of the first hinge point 301 and the axis of the second hinge point 302 may not be absolutely parallel, and the first plane 501 may also be formed such that one axis and a point on the other axis form the first plane 501, and the second plane 502 may also be formed with reference to the first plane 501. In addition, for convenience of description, in some drawings, "up", "down", "front", and "rear" are given, in an embodiment of the present disclosure, a vertical direction is a direction from top to bottom, the vertical direction is a gravity direction, a horizontal direction is a direction perpendicular to the vertical direction, referring to fig. 2, a rotation direction of the excavator is a lateral direction, a first hinge point 301 is a lower direction toward the traveling device 220, the traveling device is an upper direction toward the first hinge point 301, the traveling device 220 is a front direction toward the forearm 130, and the forearm 130 is a rear direction toward the traveling device 220. It should be noted that the hinge point refers to a position where two components are connected, and generally includes a hole, a contact surface, a connection shaft, and other components required when the components are connected, and at least one hole of the components rotates relative to the connection shaft.

In the rock breaking device that this disclosed embodiment provided, under the condition that the distance of second pin joint of big arm hydro-cylinder and big arm to the first pin joint of big arm and carrier equals, when contained angle A between the axis of the first plane that the axis of first pin joint and the axis of second pin joint formed and the second plane that the axis of third hinge joint formed is less than 110 degrees, the distance of the third hinge joint of big arm and forearm to the first pin joint of big arm and carrier is shorter, it is less to lift the required lift force of big arm and forearm, also be favorable to making the direction of lifting of big arm hydro-cylinder towards the top, thereby can promote the lift ability of big arm hydro-cylinder, and then can improve rock breaking efficiency.

In some examples, the rock breaking device is mounted on different vehicles, and now, for example, an excavator is used to analyze a common excavator, and the angle setting of the included angle a between the first plane and the second plane is described as follows:

the excavator 1 of a certain brand model is 50 tons in size, has power of 257 kilowatts, is a model with large remaining quantity, has the crawler lengths of 5455 mm and the crawler widths of 600 mm, has the maximum width of 3900 mm of the two crawlers, is rotatably connected to a lower vehicle body, and is provided with a traveling device. The walking device is composed of two crawler belts, the length direction of the crawler belts is longitudinal, the width direction of the crawler belts is transverse, the longitudinal stability of the excavator is better, the walking is usually carried out along the longitudinal movement, so the rock breaking operation of the excavator is usually carried out along the longitudinal direction, and by combining the figure 3, the explanation is firstly given by taking the example that the scarifier is positioned at the rearmost end of a common rock breaking position J.

At this time, the small arm 130 and the ripper 150 are in the last state of a downward cutting cycle, the downward cutting cycle means that the ripper 150 is located at the front end of the common rock breaking range J and starts downward cutting, at this time, the arm cylinder 140 and the ripper cylinder 160 are in a close closed state, the arm cylinder 140 and the ripper cylinder 160 are extended out, and the large arm cylinder 120 is matched for recovery, the ripper rock breaking portion moves downward and backward, when the rock breaking portion reaches the rearmost end of the common rock breaking range J, the rock entering angle and position of the ripper 150 are not favorable for rock breaking, at this time, the large arm cylinder 120 is extended out, the arm cylinder 140 and the ripper cylinder 160 are simultaneously or respectively recovered, the upper vehicle body 210 is rotated or the traveling device 220 is matched for movement, so that the ripper is located at the next downward cutting point, the next downward cutting point is also the foremost end of the rock breaking range J, and the foremost end position enables the downward cutting angle of the ripper 150 to be favorable, the rock breaking efficiency of the rock entering angle of the rock breaking device is relatively high on the premise of ensuring the maximum common rock breaking range of the scarifier, in actual operation, according to different rock stratums, the common rock breaking range J of the same rock breaking device has a certain difference, the common rock breaking range J is smaller than the range which can be reached by the rock breaking part of the scarifier under the condition of walking immobility, and the undercutting process of the rock breaking part of the scarifier from the most front end to the most rear end of the common rock breaking range J is an undercutting period.

The angle a between the first and second planes is 113 degrees:

the distance from the second hinge point 302 to the third hinge point 303 is 800 mm, the distance from the fifth hinge point 305 to the third hinge point 303 is 1700 mm, the distance from the third hinge point 303 to the sixth hinge point 306 is 1300 mm, the distance from the sixth hinge point 306 to the end of the rock breaking part of the ripper is 1500 mm, the included angle between the plane formed by the axis of the hinge shaft of the fifth hinge point 305 and the axis of the third hinge point 303 and the plane formed by the axis of the hinge shaft of the third hinge point 303 and the axis of the hinge shaft of the sixth hinge point 306 is 105 degrees, the weight of the ripper 150 is 12 tons, the total weight of the rock breaking device is 19 tons, and the rock breaking device comprises a large arm 110, a small arm 130, the ripper 150, a boom cylinder 140, a ripper cylinder 160 and hinge shafts thereof; this data set is a more reasonable arrangement of the rock breaking device, which has a relatively high rock breaking efficiency and a relatively small energy loss.

The rock breaking device is suitable for selecting 3 representative rock stratums from broken and mined rock stratums to test, the rock stratums are respectively hard, hard and low in hardness, the distance X from the rearmost end of a hard common rock breaking range J to the walking end part is 900 mm, the distance X from the rearmost end of the hard common rock breaking range J to the walking end part is 800 mm, the distance X from the rearmost end of the low-hardness common rock breaking range J to the walking end part is 700 mm, and the distance X is large, so that the gravity center of the rock breaking device is easy to lean forward and is not beneficial to lifting of the large-arm oil cylinder 120; the included angle D is 30 °.

The angle a between the first and second planes is 108 degrees:

the test is carried out on the rock strata with the above 3 hardness, the distance X from the rearmost end of the hard common rock breaking range J to the walking end portion is 800 mm, the distance X from the rearmost end of the hard common rock breaking range J to the walking end portion is 700 mm, the distance X from the rearmost end of the lower common rock breaking range J to the walking end portion is 600 mm, the distance X is slightly larger, and the gravity center of the rock breaking device is slightly forward but has smaller influence; the included angle D is 32 °.

The angle a between the first and second planes is 95 degrees:

the test is carried out on the rock strata with the above 3 hardness, the distance X from the rearmost end of the hard common rock breaking range J to the walking end part is 650 mm, the distance X from the rearmost end of the hard common rock breaking range J to the walking end part is 530 mm, the distance X from the rearmost end of the common rock breaking range J with the lower hardness to the walking end part is 420 mm, the distance X is ideal, the influence of the walking end part on the operation is overcome, and the gravity center of the rock breaking device is enabled to be leaned as far as possible, so that the lifting of the boom cylinder 120 is facilitated; the included angle D is 37 °.

The angle a between the first and second planes is 85 degrees:

the test is carried out on the rock strata with the above 3 hardness, the distance X from the rearmost end of the hard common rock breaking range J to the walking end part is 510 mm, the distance X from the rearmost end of the hard common rock breaking range J to the walking end part is 400 mm, the distance X from the rearmost end of the common rock breaking range J with the lower hardness to the walking end part is 390 mm, the distance X is ideal, the influence of the walking end part on the operation is overcome, and the gravity center of the rock breaking device is enabled to be leaned as far as possible, so that the lifting of the large-arm oil cylinder 120 is facilitated; the included angle D is 41 °.

The angle a between the first and second planes is 73 degrees:

the test is carried out on the rock strata with the above 3 hardness, the distance X from the rearmost end of the hard common rock breaking range J to the walking end part is 390 mm, the distance X from the rearmost end of the hard common rock breaking range J to the walking end part is 270 mm, the distance X from the rearmost end of the lower hardness common rock breaking range J to the walking end part is 110 mm, the distance X is slightly smaller, although the gravity center is closer to the rear, the lifting of the boom cylinder 120 is facilitated, but the walking end part is easy to influence the rock breaking operation; the included angle D is 43 °.

The angle a between the first and second planes is 68 degrees:

the test is carried out on the rock strata with the above 3 hardness, the distance X from the rearmost end of the hard common rock breaking range J to the walking end part is 350 mm, the distance X from the rearmost end of the hard common rock breaking range J to the walking end part is 230 mm, the distance X from the rearmost end of the common rock breaking range J with the lower hardness to the walking end part is 60 mm, the distance is smaller, although the gravity center is closer to the rear, the lifting of the large arm oil cylinder 120 is facilitated, but the walking end part influences the rock breaking operation; the included angle D is 42 °.

The state of the included angle A in different angles can be seen, under the same condition, in the change of 68-113 degrees, the included angle A is smaller and the included angle D is larger, so that the lifting direction of the boom cylinder is enabled to face upwards, the included angle A is smaller in the range of 68-113 degrees, the center of gravity of the rock breaking device is enabled to be more backward, the included angle D is smaller than the included angle A73 degrees when the included angle A is 68 degrees, and the fact that 70-110 degrees are ideal angles is determined.

Through carrying out the analysis to the excavator of other brand models, it is difficult to derive, its condition is the same with above-mentioned experimental example or close, though the factor that influences above experimental data has still included the structure setting of forearm and agitator to and the length setting of the excavator running gear 220 of different brand models is different, but this experimental example can represent most of the circumstances, when to the great condition of difference, refer to the utility model discloses carry out certain adjustment to reach the setting effect of preferred.

According to the rock breaking device mounted on the excavator of the brand model of the experimental example, the length relationship between the distance from the second hinge point 302 to the third hinge point 303 and the distance from the fifth hinge point 305 to the third hinge point 303 is analyzed.

The angle a between the first and second planes was set to 95 degrees, which is a reasonable angle for most excavator models, although other angles do not affect the experimental example.

The distance from the fifth hinge point 305 to the third hinge point 303 is 1700 mm, when the arm cylinder 140 is fully extended, the distance from the fourth hinge point 304 to the fifth hinge point 305 is 3600 mm, and when the arm cylinder 140 is fully retracted, the distance from the fourth hinge point 304 to the fifth hinge point 305 is 2100 mm.

The distance from the second hinge point 302 to the third hinge point 303 is 1100 mm, when the arm cylinder 140 is nearly fully extended, the arm cylinder 140 touches the upper part of the boom 110 and moves backward to the rearmost end through the fourth hinge point 304, if the fourth hinge point 304 is too far backward and easily touches other parts (such as a distribution valve) of the excavator, when the arm cylinder 140 is fully extended, the arm cylinder 140 does not touch the upper part of the boom 110, which is basically the maximum length from the second hinge point 302 to the third hinge point 303.

When the distance from the second hinge point 302 to the third hinge point 303 is 900 mm, when the arm cylinder 140 extends completely, the arm cylinder 140 touches the upper part of the boom 110, and moves backwards to be close to the rearmost end through the fourth hinge point 304, if the fourth hinge point 304 is too far back, when it is easy to touch other parts (such as a distribution valve) of the excavator, when the arm cylinder 140 extends completely, the arm cylinder 140 does not touch the upper part of the boom 110, and the fourth hinge point has a larger setting space in the length.

When the distance from the second hinge point 302 to the third hinge point 303 is 800 mm, and when the arm cylinder 140 extends out completely, the arm cylinder 140 and the upper portion of the large arm 110 are not easy to touch, and the fourth hinge point has a larger setting space in the length.

In the experiment of carrying the rock breaking device on excavators of other main brands and models, the result is similar to the experimental example.

Of course, the results of the above experimental examples are also influenced by the structure of the small arm 130 and the large arm 110, but the above experimental examples may represent most cases.

As can be understood from the above experimental examples, in the case that the larger the distance from the second hinge point 302 to the third hinge point 303 is, the more the larger the upward direction of the boom cylinder 120 is, the better the ratio of the distance from the second hinge point 302 to the third hinge point 303 to the distance from the fifth hinge point 305 to the third hinge point 303 is 0.45 to 0.65.

With reference to the above experimental example, the perpendicular distance E between the second hinge point 302 and the third hinge point 303 was analyzed:

since the vertical distance E is also affected by the state of the boom, the included angle D is set to 45 degrees, and in the above experimental example, the length of the vertical distance E is 710 mm to 1000 mm, which is a reasonable range, and the lift angle of the boom cylinder 120 is advantageous to be directed upward in the case that the boom cylinder 140 is easily installed, and therefore, it is preferable that the ratio of the vertical distance E to the distance from the fifth hinge point 305 to the third hinge point 303 is 0.42 to 0.59 with the distance from the fifth hinge point 305 to the third hinge point 303 being used as a reference.

It should be noted that the distance of a hinge point to a hinge point refers to the shortest distance of the axis of the shaft of the hinge point to the axis of the shaft of the other hinge point.

In some examples, the angle a between a first plane 501 formed by the axis of the first hinge point 301 and the axis of the second hinge point 302 and a second plane 502 formed by the axis of the third hinge point 303 and the axis of the second hinge point 302 is greater than 70 degrees. In consideration of the working range of the rock breaking device, when the included angle a is greater than 70 degrees, the third hinge point 303 can have a larger moving range, so that the rock breaking device has a larger working range, and the practicability of the rock breaking device is not affected.

It should be noted that the above-mentioned general rock breaking range J refers to a working area formed by the rock breaking device in a rock breaking cycle, and the rock breaking angle of the rock breaking component (e.g., ripper) of the rock breaking device in the working area is favorable for rock breaking. Generally, the above-mentioned common breaking range J is smaller than the range that a breaking component (e.g., ripper) of the breaking device can cover. For example, when the upper vehicle body of the vehicle and the traveling device are parallel, the above-mentioned working range should be kept at a small distance from the end of the traveling device in the front-rear direction, so that the rock breaking member (e.g., ripper) of the rock breaking device and the end of the traveling device are not easily touched while maintaining high working efficiency. The rock breaking period comprises the following steps: step 1: the vehicle is driven to a working position, and a rock breaking component (such as a scarifier) is positioned above a rock layer to be broken; step 2: the traveling device stops, the rock breaking component (such as a ripper) is operated and matched with the upper vehicle body of the carrier to rotate, so that the rock breaking component (such as the ripper) can reach and is favorable for rock stratum breaking in a rock breaking area.

For example, the angle a between a first plane 501 formed by the axis of the first hinge point 301 and the axis of the second hinge point 302 and a second plane 502 formed by the axis of the third hinge point 303 and the axis of the second hinge point 302 may be 85 degrees, 90 degrees or 100 degrees.

In some examples, as shown in fig. 1 and 2, large arm 110 further includes a fourth hinge point 304, and small arm 130 includes a fifth hinge point 305, a sixth hinge point 306, and a seventh hinge point 307. The rock breaking device further comprises a stick cylinder 140, a ripper 150 and a ripper cylinder 160. One end of the arm cylinder 140 is hinged to the upper arm 110 at the fourth hinge point 304, and the other end of the arm cylinder 140 is hinged to the lower arm 130 at the fifth hinge point 305, so that the lower arm 130 can rotate around the third hinge point 303 by the extension and contraction of the arm cylinder 140. The ripper 150 is hinged to the forearm 130 at a sixth hinge point 306. The ripper 150 includes an eighth hinge point 308, one end of the ripper cylinder 160 is hinged with the small arm 130 at the seventh hinge point 307, and the other end of the ripper cylinder 160 is hinged with the ripper 150 at the eighth hinge point 308. At this time, the ripper 150 may be rotated about the sixth hinge point 306 by the extension and contraction of the ripper cylinder 160. Therefore, the large arm, the small arm and the scarifier can move in a coordinated manner through the cooperative driving of the lifting oil cylinder of the large arm, the small arm oil cylinder and the scarifier oil cylinder, so that the rock breaking purpose of the rock breaking device is realized.

In some examples, as shown in fig. 1 and 2, the ratio of the maximum distance of the axis of the arm cylinder 140 from the third hinge point 303 to the distance of the third hinge point 303 from the sixth hinge point 306 is greater than 0.8. When the arm cylinder 140 is in operation, the distance between the axis of the arm cylinder 140 and the third hinge point 303 is changed, and the maximum distance is used as the standard, so that the small arm has a lever ratio which is relatively labor-saving. At this time, the capacity loss of the arm cylinder is also small. The reason is that due to compressibility of working medium hydraulic oil of the oil cylinder, when the pressure applied to the bucket rod oil cylinder is small, the compression amount of the hydraulic oil is small, and when the ratio of the power arm to the resistance arm is large, the capacity loss can be effectively reduced. The axis of the arm cylinder may be an axis of the arm cylinder in the extending and contracting direction.

For example, the maximum distance between the axis of the arm cylinder 140 and the third hinge point 303 is 1.6 meters, and the distance between the third hinge point 303 and the sixth hinge point 306 is 1.6 meters, so that the ratio of the distance between the axis of the arm cylinder 140 and the third hinge point 303 to the distance between the third hinge point 303 and the sixth hinge point 306 is 1.

For example, the maximum distance between the axis of the arm cylinder 140 and the third hinge point 303 is 1.9 m, and the distance between the third hinge point 303 and the sixth hinge point 306 is 1.4 m, so that the ratio of the distance between the axis of the arm cylinder 140 and the third hinge point 303 to the distance between the third hinge point 303 and the sixth hinge point 306 is 1.36, and thus, the small arm has a lever ratio which is relatively labor-saving.

For example, the maximum distance between the axis of the arm cylinder 140 and the third hinge point 303 is 1.8 m, and the distance between the third hinge point 303 and the sixth hinge point 306 is 1.3 m, so that the ratio of the distance between the axis of the arm cylinder 140 and the third hinge point 303 to the distance between the third hinge point 303 and the sixth hinge point 306 is 1.38, and thus, the small arm has a lever ratio which is relatively labor-saving.

In some examples, as shown in fig. 1 and 2, when the boom cylinder 120 is in the fully retracted state, it may be that the boom cylinder 120 is not in the fully retracted state, the first hinge point 301 and the end of the carrier 200 close to the ripper 150 form a third plane 503, the third plane 503 is tangent to the end of the carrier 200 close to the ripper 150, the third hinge point 303 may be located on the side of the third plane 503 close to the carrier 200, or below the third plane 503, and the second hinge point 302 may be located on the side of the third plane 503 far from the carrier 200, or above the third plane 503. For example, the third hinge point 303 may be spaced from the third plane 503 by 0.3 meters.

In the operation of the rock breaking device, the boom cylinder 120 is normally fully retracted only when a deep trench or pit is excavated, in which case the rock breaking device is not normally located at both travelling ends of the excavator, in most cases the boom cylinder 120 is not fully retracted, and the third hinge point 303 may also be located at a side of the third plane 503 close to the vehicle 200 or below the third plane 503.

In the rock breaking device provided by the example, when the boom cylinder is in the fully retracted state, since the third hinge point is located on one side of the third plane close to the carrier, namely below the third plane, and the second hinge point is located on one side of the third plane far from the carrier, namely above the third plane, the third hinge point can reach a lower position, thereby being beneficial to improving the digging depth of the ripper. In addition, because the first line of first pin joint and second pin joint and the contained angle of the second line of third hinge joint point and second pin joint are less than 110 degrees, make the second pin joint that is located third hinge joint point top have higher height for third hinge joint point to the angle of lifting that is favorable to the big arm hydro-cylinder has bigger number of degrees at 90 degrees within ranges, is favorable to the big arm hydro-cylinder to have better ascending direction of lifting, thereby is favorable to the ascending lifting of big arm. The height is a height of a working surface on which the rock breaking operation is performed by the rock breaking device.

In some examples, a ratio of a distance of the second hinge point to the third hinge point to a distance of the fifth hinge point to the third hinge point is 0.45-0.65.

In some examples, when the lift angle of the boom cylinder is 45 degrees, the ratio of the vertical distance of the second hinge point and the third hinge point to the distance of the fifth hinge point to the third hinge point is 0.42-0.59. Fig. 3 is a schematic diagram of a rock breaking device provided according to an embodiment of the present disclosure for lifting. As shown in fig. 3, since factors affecting the lift angle of the boom cylinder 120 include the vertical distance of the second hinge point 302 from the work surface, the vertical distance of the second hinge point 302 from the work surface is equal to the sum of the vertical distance F of the third hinge point 303 from the work surface and the vertical distance E of the second hinge point 303 from the third hinge point 303. Therefore, the larger the vertical distance E between the second hinge point 302 and the third hinge point 303 is, the more advantageous the lift angle D of the boom cylinder 120 is. Under the same other conditions, the larger the vertical distance from the second hinge point 302 to the working surface, the larger the lifting angle D of the boom cylinder 120 is, so that the more the lifting angle D of the boom cylinder 120 is favorable to be upward, and the more the boom cylinder 120 is favorable to lift the boom 110.

Regarding the relationship between the vertical distance E and the distance from the second hinge point 302 to the third hinge point 303 and the relationship between the vertical distance E and the distance from the fifth hinge point to the third hinge point, the vertical distance E will change with the state change of the rock breaking device, and the distance E is proportional to the distance from the second hinge point 302 to the third hinge point 303.

In some examples, as shown in fig. 2, the breaking device further comprises a carrier 200. The vehicle 200 includes an upper vehicle body 210 and a traveling device 220, and the upper vehicle body 210 is rotatably connected to the traveling device 220. The upper body 210 is hinged to the arm 110 at a first hinge point 301, and the end of the arm cylinder 120 away from the second hinge point 302 is hinged to the upper body 210. In the fully retracted state of the boom cylinder 120, the third plane 503 passes through the first hinge point 301 and is tangent to the end of the traveling device 220 close to the ripper 150.

For example, the vehicle 200 may be an excavator. Of course, the disclosed embodiments include but are not limited to this, and the vehicle may also be a vehicle dedicated to breaking rock.

For example, the carrier 200 may also be a rock breaker with a laterally retractable car body, which is named as CN201822087022.2, and has a car body formed by enclosing, a rock breaking operation area is located in a hollow area formed by enclosing the car body, a rock breaking device breaks rock in the rock breaking area, when the weight of the rock breaking device is large, the boom cylinder and the hinge point of the rock breaking device are located below the boom and the hinge point of the hinge point, the present invention is also applicable.

In some examples, as shown in fig. 1 and 2, the first hinge point 301 is located at the first end 111 of the large arm 110, the third hinge point 303 is located at the second end 112 of the large arm 110 away from the first end 111, and the cross-sectional area of the large arm 110 gradually increases in a direction from the first end 111 to the second end 112. With the arrangement, the available space on the second end part 112 of the large arm 110 is large, the large arm can be used for being hinged with parts such as a small arm, the structural strength is high, and the stability and the safety of the rock breaking device are improved; while the first end portion 111 of the large arm 110 is required to perform a smaller function, the cross-sectional area of the first end portion 111 can be set smaller. It should be noted that, when the large arm is not a solid structure, the "cross-sectional area" may be the area of the region surrounded by the outer surface of the large arm in one cross-section.

In some examples, as shown in fig. 1 and 2, the large arm 110 includes an upper cover plate 113, a lower cover plate 114, and two side plates 115. The upper deck 113, lower deck 114 and two side panels 115 may form a box-type structure 116. The box-type structure 116 has a cross-sectional area that increases from the first end 111 to the second end 112. So set up, can reduce the cost of big arm under guaranteeing sufficient structural strength. In addition, as mentioned above, when the cross-sectional area of the box-type structure gradually increases from the direction of the first end and the second end, the space available on the second end of the large arm is large, and the large arm can be used for hinging with parts such as a small arm, and the structural strength is high, which is beneficial to improving the stability and the safety of the rock breaking device.

Fig. 4 is a schematic structural diagram of another rock breaking device provided according to an embodiment of the present disclosure. As shown in fig. 4, the second end 112 of the large arm 110 has a first adjacent surface 119 toward the small arm 130, and the small arm 130 has a second adjacent surface 131 toward the large arm 110. The axis of the second hinge point 302 and the third hinge point 303 may form the above-mentioned second plane 502; a fourth plane 504 is tangent to the lower axial end of the second hinge point 302 and is perpendicular to the second plane 502; a fifth plane 505 is tangential to the upper axial end of the third hinge point 303 and perpendicular to the second plane 502; the first adjacent surface 119 and the second adjacent surface 131 are located between the fourth plane 504 and the fifth plane 505, the first adjacent surface 119 and the second adjacent surface 131 are located at a position where the fourth plane 504 faces the third hinge point 303 or is far away from the fifth hinge point 305, the first adjacent surface does not include the projection 134, the second adjacent surface 119 does not include the projection when a connecting structure similar to the projection 134 is provided on the large arm 110, the first adjacent surface 119 and the second adjacent surface 131 are equal in length in the up-down direction, when the arm cylinder 140 is completely retracted, the first adjacent surface 119 and the second adjacent surface 131 may be parallel or substantially parallel, the substantially parallel may be understood as if the first adjacent surface 119 and the second adjacent surface 131 are planes, an included angle formed by the two adjacent surfaces is within 10 degrees, if an arc shape is adopted, the smaller distance of the two adjacent surfaces is better, the two adjacent surfaces are advantageously provided in that, due to the arrangement of the included angle a, and the distance between the second hinge point 302 and the third hinge point 303 needs to be kept at a reasonable length, so that the moving space of the small arm is limited, and the space between the large arm and the small arm is favorably and fully utilized.

Fig. 5 is a schematic structural diagram of a boom of a rock breaking device according to an embodiment of the present disclosure. As shown in FIG. 5, the large arm 110 further includes two first ear plates 117 and a connecting member 1174 of the two first ear plates 117. The two ear plates 117 are respectively connected with the two side plates 115, the upper part of the connecting piece 1174 is connected with or integrally arranged with one end of the upper cover plate 113 far away from the first hinge point 301, the lower part of the connecting piece 1174 is connected with or integrally arranged with one end of the lower cover plate 114 far away from the first hinge point 301, and the thickness of the first ear plate 117 is respectively larger than that of the upper cover plate 113, that of the lower cover plate 114 and that of the side plate 115. A second hinge point 302 and a third hinge point 303 are provided on the first ear plate 117. With such an arrangement, since the thickness of the first ear plate 117 is respectively greater than the thickness of the upper cover plate 113, the thickness of the lower cover plate 114 and the thickness of the side plate 115, the first ear plate 117 can have higher structural strength, and the stability of the rock breaking device can be improved by arranging the second hinge point 302 and the third hinge point 303 on the first ear plate 117. On the other hand, still can realize the structure of buckling through first otic placode to can guarantee that the contained angle of the first line of first pin joint and second pin joint and the second line of third pin joint and second pin joint is less than 110 degrees. In some examples, as shown in fig. 5, connector 1174 may be the front end of large arm 110. When the arm cylinder 140 is in the fully retracted state, the connecting member 1174 is disposed opposite to the arm 130, and the plate surface of the connecting member 1174 is substantially parallel to the plate surface of the arm 130 close to the connecting member 1174. Thus, the space can be fully utilized.

In some examples, as shown in fig. 1, 2, and 5, the angle between the first ear plate 117 and the plate surface of the lower cover plate 114 is less than 180 degrees to form a recessed space between the first ear plate 117 and the lower cover plate 114. In the fully retracted state of boom cylinder 110, the end of carrier 200 near forearm 130 is in the recessed space. When vehicle 200 includes upper body 210 and running gear 220, the end of running gear 220 near forearm 130 may be located in a recessed space. In this way, the carrier 200 or the traveling device 220 does not obstruct the lower portion of the boom 110 and affect the excavation depth.

Fig. 6 is a schematic structural view of a boom of another rock breaking device provided according to an embodiment of the present disclosure. As shown in fig. 6, the first ear plate 117 can also be configured such that the included angle B is an arcuate recess.

In some examples, as shown in FIG. 6, the first ear panel 117 can also be configured such that the included angle C is an arcuate projection.

Fig. 7 is a schematic view of another rock breaking device provided according to an embodiment of the present disclosure. As shown in fig. 7, ripper 150 includes a ripper body 151, a ripper head 152, a tooth 153, and a fixture 154. The eighth hinge point 308 is located on the ripper body 151. One end of the ripper head 152 is detachably fixed to the ripper body 151 by a fixing device 154, and the teeth 153 are detachably fixed to one end of the ripper head 152 remote from the ripper body 151. So set up, can conveniently maintain, change scarifier head and bucket tooth.

In some examples, as shown in fig. 7, one end of ripper head 152 near ripper body 151 has a ripper head cavity 1520, and securing device 154 may be inserted into ripper head cavity 1520 to removably secure ripper head 152 and ripper body 151.

In some examples, as shown in fig. 7, the securing device 154 includes a resilient securing device 158. One end of the elastic fixing device 158 is in contact with the ripper body 151, and the other end is in contact with the ripper head 152.

Fig. 8 is a schematic structural diagram of a fixing device according to an embodiment of the present disclosure. As shown in fig. 8, the elastic fixing device 158 includes two contact portions 1582 and an elastic member 1584 located between the two contact portions 1582, the two contact portions 1582 being in contact with the ripper body 151 and the ripper head 152, respectively.

In some examples, the ripper 150 may weigh more than 50% of the total weight of the big arm, the small arm, and the ripper, such that rock breaking capability may be improved.

For example, the total weight of the big arm, the small arm, and the ripper may be 17 tons, and the weight of the ripper may be 9 tons, so the weight of the ripper 150 accounts for 52% of the total weight of the big arm, the small arm, and the ripper, and thus the rock breaking capability may be improved.

Fig. 9 is a schematic structural view of a small arm in a rock breaking device according to an embodiment of the present disclosure. Fig. 10 is a schematic view illustrating disassembly of a small arm of a rock breaking device according to an embodiment of the present disclosure. As shown in fig. 9 and 10, the small arm 130 includes a second box-shaped structure 133 and a second ear plate 132, the second box-shaped structure 133 is a structural member having a hollow cavity, a fifth hinge point 305 and a seventh hinge point 307 are disposed on the second box-shaped structure 133, the second ear plate 132 is a single metal plate and is formed by cutting a larger metal plate, a third hinge 303 and a sixth hinge point 306 are disposed on the second ear plate 132, the second ear plate 132 is welded to the second box-shaped structure 133, the third hinge point 303 is disposed on the protruding portion 134, and the protruding portion 134 is located in a direction toward the first hinge point 301 of the extension portion of the second adjacent surface 131, so that it is advantageous to fully utilize the space between the large arm and the small arm, and the strength of the small arm 130 is better under the condition that the structure between the third hinge point 303 and the sixth hinge point 306 is simpler.

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. A rock breaking device, comprising:

a large arm comprising a first hinge point, a second hinge point, and a third hinge point, the first hinge point configured to hinge with a vehicle;

one end of the big arm oil cylinder is hinged with the big arm at the second hinge point, and the other end of the big arm oil cylinder is configured to be hinged with the carrier; and

a small arm hinged to the large arm at the third hinge point,

wherein an included angle between a first plane formed by the axis of the first hinge point and the axis of the second hinge point and a second plane formed by the axis of the third hinge point and the axis of the second hinge point is less than 110 degrees.

2. The rock breaking device of claim 1, wherein the large arm further comprises a fourth hinge point, and the small arm comprises: fifth pin joint, sixth pin joint and seventh pin joint, broken rock device still includes:

one end of the bucket rod oil cylinder is hinged with the large arm at the fourth hinge point, and the other end of the bucket rod 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 with the small arm at the seventh hinge point, and the other end of the ripper oil cylinder is hinged with the ripper at the eighth hinge point.

3. The rock breaking device of claim 2, wherein a ratio of a maximum distance between the axis of the arm cylinder and the third hinge point to a distance between the third hinge point and the sixth hinge point is greater than 0.8.

4. A rock breaking device according to claim 2, further comprising:

the carrier comprises an upper vehicle body and a lower vehicle body, the upper vehicle body is rotationally connected with the lower vehicle body, the lower vehicle body is provided with a walking device,

the upper vehicle body is hinged to the large arm at the first hinge point, one end, far away from the second hinge point, of the large arm cylinder is hinged to the upper vehicle body, the first hinge point and the end, close to the ripper, of the traveling device form a third plane, the third plane is tangent to the end, close to the ripper, of the traveling device, the third hinge point can be located on one side, close to the carrier, of the third plane, and the second hinge point can be located on one side, far away from the carrier, of the third plane.

5. A rock breaking device according to any one of claims 2 to 4, wherein the first hinge point is located at a first end of the large arm and the third hinge point is located at a second end of the large arm remote from the first end, the cross-sectional area of the large arm increasing in a direction from the first end to the second end.

6. A rock breaking device according to claim 5, wherein the boom includes an upper deck, a lower deck and side panels, the upper deck, the lower deck and the side panels forming a first box-type structure having a cross-sectional area that increases progressively in a direction from the first end to the second end.

7. The rock breaking device of claim 6, wherein the boom further comprises two first ear plates and a connecting piece of the two first ear plates, the two first ear plates are respectively connected with the two side plates, the upper portion of the connecting piece is connected with or integrally arranged at one end of the upper cover plate far away from the first hinge point, the lower portion of the connecting piece is connected with or integrally arranged at one end of the lower cover plate far away from the first hinge point, the thickness of the first ear plates is respectively larger than that of the upper cover plate, that of the lower cover plate and that of the side plates, and the second hinge point and the third hinge point are arranged on the first ear plates.

8. The rock breaking device of claim 7, wherein the connection piece is disposed opposite the small arm when the arm cylinder is in a fully retracted state, and a plate surface of the connection piece is substantially parallel to a plate surface of the small arm adjacent to the connection piece.

9. A rock breaking device according to claim 7, wherein the angle between the first lug and the face of the lower deck is less than 180 degrees to form a recessed space between the first lug and the lower deck in which the end of the carrier near the forearm is locatable.

10. A rock breaking device according to any one of claims 2-4, wherein the ripper includes:

the eighth hinge point is located on the ripper body;

a scarifier head;

a bucket tooth; and

a fixing device is arranged on the base plate,

one end of the scarifier head is detachably fixed on the scarifier body through the fixing device, and the bucket teeth are detachably fixed at one end, far away from the scarifier body, of the scarifier head.

11. The rock breaking device of claim 10, wherein an end of the ripper head proximate the ripper body includes a ripper head cavity, the securing device configured to be inserted into the ripper head cavity to removably secure the ripper head and the ripper body.

12. The rock breaking device of claim 10, wherein the securing device comprises an elastic securing device, one end of the elastic securing device being in contact with the ripper body and the other end of the elastic securing device being in contact with the ripper head.

13. The rock breaking device of any one of claims 2-4, wherein the ripper has a weight that is greater than 50% of a total weight of the large arm, the small arm, and the ripper.

14. A rock breaking device according to any one of claims 2-4, wherein the ratio of the distance of the second hinge point to the third hinge point to the distance of the fifth hinge point to the third hinge point is 0.45-0.65.

15. The rock breaking device according to any one of claims 2 to 4, wherein when the lift angle of the boom cylinder is 45 degrees, the ratio of the vertical distance of the second hinge point and the third hinge point to the distance of the fifth hinge point and the third hinge point is 0.42 to 0.59.

16. A rock breaking device according to claim 5, wherein the second end of the large arm has a first adjacent face towards the small arm and the small arm has a second adjacent face towards the large arm, the first and second adjacent faces being parallel or substantially parallel.

17. A rock breaking device according to claim 16, wherein the forearm comprises a second box-like structure and a second ear plate, the second box-like structure being a structural member having a hollow cavity, the fifth and seventh hinge points being provided at the second box-like structure, the third and sixth hinge points being provided at the second ear plate, the third hinge point being provided at a projection.

18. A rock breaking device according to claim 17 wherein the projection is located towards the first hinge point of the second adjacent face extension.