CN209308091U - It is equipped on the broken rock device of excavator - Google Patents
It is equipped on the broken rock device of excavator Download PDFInfo
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- CN209308091U CN209308091U CN201822086963.4U CN201822086963U CN209308091U CN 209308091 U CN209308091 U CN 209308091U CN 201822086963 U CN201822086963 U CN 201822086963U CN 209308091 U CN209308091 U CN 209308091U
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- hinged shaft
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- ridge buster
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Abstract
The utility model is a kind of broken rock device for being equipped on excavator, solving existing device large arm, structure is complicated, in the case that be changed without big arm cylinder or big arm cylinder stroke is relatively large can take into account data mining duty, ridge buster often uses operation range distance excavator apart from bigger than normal, cause big arm cylinder lifting difficult or the problem of ridge buster rock breaking capacity difference, one end of large arm and excavator top car body are hinged, the other end is hinged by the 1st hinged shaft with forearm, large arm and the hinged hinge joint of big arm cylinder are the 1st hinged shaft, one end of dipper cylinder is hinged by the 3rd hinged shaft with top in the middle part of large arm, the other end is hinged by the 4th hinged shaft with forearm upper end, the upper end of forearm is hinged by the 5th hinged shaft and ridge buster oil cylinder one end, the ridge buster oil cylinder other end is hinged by the 6th hinged shaft with ridge buster, ridge buster lower end is connect with bucket tooth, the quantity of bucket tooth is one , ridge buster passes through the 7th hinged shaft and forearm lower end is hinged.
Description
Technical field
The utility model is related with the broken rock device of excavator is equipped on.
Background technique
It adopts in construction operation rock stratum is broken, for not being very hard rock stratum, excavator carries the construction method of ridge buster
It is widely adopted since construction effect is good, for the construction method, the prior art has made much large arm, forearm and ridge buster
Optimal improvements, to improve using effect.
The device being made of large arm, forearm, ridge buster and oil cylinder is called broken rock device herein.Existing broken rock device is logical
The increase to the change of forearm torque and large arm, forearm weight is crossed, so that rock breaking capacity is improved, such as patent No.
(zl201220558700.9), oil cylinder of small arm and forearm tie point connect at a distance from large arm tie point with forearm and large arm to forearm
The ratio of distances constant of contact to forearm and ridge buster tie point is 0.4-0.8. and the moment conditions of forearm are power arm and resistance arm
The ratio between be 0.4-0.8, in technology actual use, fill weight in large arm and forearm, increase large arm and the weight of forearm
Add, improve the rock breaking capacity of ridge buster, during advanced optimizing broken rock device, occurs such as the patent No.
The technology of (201310711871.x), the moment conditions of forearm are optimized for the ratio between power arm and resistance arm greater than 0.8, in the technology
In actual use, further increase large arm and forearm weight, promote ridge buster rock breaking capacity further, the technology is existing
It is being widely used.
Occur later application No. is CN2017215292406 and application No. is the patents of CN2018106048515, leads to
The optimization for crossing ridge buster and forearm, further improves rock breaking capacity.
Such as application No. is the patents of CN2016204202011 reduces boom cylinder load by shortening big arm lengths to mention
Rock breaking capacity is risen, the mode for shortening large arm is the length for reducing large arm and forearm hinge joint to big arm cylinder and large arm hinge joint
It realizes, when being changed without big arm cylinder, it is difficult to big arm lengths be made to reach an ideal length.
Theoretically, by reducing big arm cylinder length and increasing big arm cylinder cylinder diameter, big arm lengths and increasing can also be reduced
Add big arm cylinder jacking capacity, but its mining ability for being difficult to take into account excavator, excavator is changed broken rock device and is changed sometimes
Data mining duty may be implemented with arm in excavation, and excavation stroke can be reduced by reducing big arm lengths, and data mining duty effect is made to be deteriorated, and replacement is big
Arm oil cylinder will increase cost.
The big arm cylinder of existing broken rock device due to excavator to be taken into account data mining duty, and retain originally be data mining duty
The big arm cylinder matched, first its stroke range are big, are conducive to excavate, next, which is changed without big arm cylinder, can also save cost, newly
Vehicle factory also in big arm cylinder can match biggish stroke range by data mining duty in order to balance, due to big by conventional excavators
Arm configuration influences, the not no hinge joint common location with large arm and forearm of the hinge joint of big arm cylinder and large arm, in big arm cylinder
A distance is formed between large arm hinge joint to large arm and forearm hinge joint, includes that large arm and forearm are cut with scissors in the distance range
The activity space for connecing the cross section and cross section to be formed, since cross section stress is larger, relative thickness is also larger, separately
Outside, big arm cylinder can also occupy corresponding space with large arm hinge joint, and therefore, large arm and forearm hinge joint are to big arm cylinder and greatly
Arm hinge joint will form a relatively large distance, big arm cylinder and large arm hinge joint to large arm and upper frame hinge joint away from
From in the constant situation of big arm cylinder, in order to guarantee that large arm stroke is reasonable, which cannot make biggish adjustment, in big arm cylinder
In the constant and reasonable situation of large arm stroke, big arm lengths are restricted, and are easy to cause large arm too long.
Secondly, ridge buster stroke cannot be too small, stroke will affect very much efficiency of breaking rock, in order to make ridge buster have biggish row
The stroke of journey, dipper cylinder cannot be too small, in existing broken rock device, in order to which dipper cylinder has relatively large stroke, big arm lengths
Also it is easy to cause too long.
In existing broken rock device use process, the common broken rock range distance excavator of ridge buster is apart from remote, often
The range for entering thrum degree and being relatively suitble to broken rock operation for referring to ridge buster with broken rock range, it is attainable most to be less than ridge buster
Big job area is to be conducive to make the higher job area of efficiency of breaking rock, since excavator center of gravity is within the domain of walk,
Common broken rock range is located at outside the domain of walk due to the design feature of excavator and broken rock device, so common broken rock range
With approach walking be it is best, when main cause is that common broken rock range distance walks closer, identical big arm cylinder lifts identical
Broken rock device it is more laborsaving, lifting speed it is faster, commonly use broken rock range distance walking it is closer when, big arm cylinder lift speed it is constant
In the case where, the weight of broken rock device is bigger, also stronger to the damage capability of rock stratum.
In the actual use of existing broken rock device, it is remote to commonly use broken rock range distance travel distance.
In general, existing oil cylinder of big arm of digger has good matching, the above broken rock on speed and vigor when leaving the factory
Device belongs to a kind of work accessory, and the matching effect that former big arm cylinder is preserved for broken rock device is preferable.
Especially application No. is the broken rock devices of CN2018106048515, since ridge buster weight and volume is filled in broken rock
It is larger to set inner proportion, broken rock installation weight and big arm cylinder it is constant in the case where, the lifting speed of big arm cylinder can be slower.
In addition, the existing big arm configuration of broken rock device is also more complex, it is unfavorable for reducing cost, broken rock device itself is in operation
Large arm stress is larger, to increase fault point, increases manufacture difficulty.
Utility model content
The purpose of the utility model is to provide big arm cylinder lifting speed under a kind of broken rock installation weight and the constant situation of oil cylinder
Faster, power consumption is reduced degree, the broken rock device that efficiency of breaking rock is obviously improved.
The utility model is realized in this way:
A kind of broken rock device being equipped on excavator, including large arm 2, forearm 3, ridge buster 6, dipper cylinder 4, ridge buster oil cylinder
5, bucket tooth 7, the excavator have top car body and lower running device, and car body rotation in top is connected to lower running device,
One end of large arm 2 and excavator top car body are hinged, and the other end and forearm 3 are hinged by the 1st hinged shaft 34, large arm 2 and large arm oil
Cylinder 12 is hinged by the 1st hinged shaft 34, and top is hinged by the 3rd hinged shaft 28 in the middle part of one end of dipper cylinder 4 and large arm, the other end with it is small
3 upper end of arm is hinged by the 4th hinged shaft 42, and the upper end of forearm 3 is hinged by the 5th hinged shaft 55 and 5 one end of ridge buster oil cylinder, ridge buster
5 other end of oil cylinder and ridge buster 6 are hinged by the 6th hinged shaft 56, and ridge buster lower end 72 is connect with bucket tooth 7, and the quantity of bucket tooth 7 is one
Only, ridge buster is hinged by the 7th hinged shaft 63 and 3 lower end of forearm, and the distance of the 4th hinged shaft 42 to the 1st hinged shaft 34 is arrived with the 1st hinged shaft 34
The distance ratio of 7th hinged shaft 63 is greater than 0.8, when the 4th hinged shaft 42, the 1st hinged shaft 34, the 7th hinged shaft 63 separately or concurrently have multiple positions
When, the distance of the 4th hinged shaft 42 to the 1st hinged shaft 34 is subject to longest, and the distance of the 1st hinged shaft 34 to the 7th hinged shaft 63 is subject to most short.
4th hinged shaft 42 is formed by angle H's to the line of the 1st hinged shaft 34 and the line of the 7th hinged shaft 63 to the 1st hinged shaft 34
Angle is within 150 degree.
The free bearing of the oriented ridge buster protrusion in the upper end in forearm towards the face of ridge buster 6, the free bearing of protrusion and the 4th hinged shaft 42 connect
It connects.
Big arm cylinder 12 is located at 34 end of the 1st hinged shaft, large arm 2 and 3 hinge point of forearm be located at big arm cylinder 12 and
Between 1st hinged shaft, 34 hinge point.
One end of ridge buster oil cylinder 5 and forearm 3 are articulated with the 4th hinged shaft 42.
Ridge buster is divided into upper and lower part by the vertical line 73 of the line of the 7th hinged shaft 63 to ridge buster lower end 72, connects bucket tooth
7 be lower part, and connection ridge buster oil cylinder is upper part, and upper partial volume is greater than lower partial volume.
6 volume of ridge buster is greater than 3 volume of forearm, and 6 weight of ridge buster is greater than 3 weight of forearm, and 6 weight of ridge buster is greater than large arm
2 weight.
Counterweight 64 has partially been detachably arranged on ridge buster 6.
1st hinged shaft 34, the 4th hinged shaft 42, the 5th hinged shaft 55, the 6th hinged shaft 56, the 7th hinged shaft 63 separately or concurrently have multiple installations
Position.
Shock excitation device 65 is partially installed on ridge buster 6.
The advantages of the utility model, is as follows:
One, a kind of broken rock device being equipped on excavator, including large arm 2,3 ridge buster 6 of forearm, dipper cylinder 4, ridge buster
Oil cylinder 5, bucket tooth 7, the excavator have top car body and lower running device, and car body rotation in top is connected to lower running dress
It sets, one end of large arm 2 and excavator top car body are hinged, and the other end and forearm 3 are hinged by the 1st hinged shaft 34, large arm 2 and large arm
Oil cylinder 12 is hinged by the 1st hinged shaft 34, and big arm cylinder 12 is located at 34 end of the 1st hinged shaft, large arm 2 and 3 hinge point of forearm
Between 34 hinge point of big arm cylinder 12 and the 1st hinged shaft, top passes through the 3rd hinged shaft in the middle part of one end of dipper cylinder 4 and large arm
28 is hinged, and the other end and 3 upper end of forearm are hinged by the 4th hinged shaft 42, and the upper end of forearm 3 passes through the 5th hinged shaft 55 and ridge buster oil
5 one end of cylinder is hinged, and 5 other end of ridge buster oil cylinder and ridge buster 6 are hinged by the 6th hinged shaft 56, and ridge buster lower end 72 and bucket tooth 7 connect
It connects, the quantity of bucket tooth 7 is one, and ridge buster is hinged by the 7th hinged shaft 63 and 3 lower end of forearm, the 4th hinged shaft 42 to the 1st hinged 34
Distance at a distance from the 1st hinged shaft 34 to the 7th hinged shaft 63 ratio be greater than 0.8, when the 4th hinged shaft 42, the 1st hinged shaft 34, the 7th hinged shaft 63 divide
When not having multiple positions or simultaneously, the distance of the 4th hinged shaft 42 to the 1st hinged shaft 34 is subject to longest, the 1st hinged shaft 34 to the 7th hinged shaft
63 distance is subject to most short.
Such structure setting is advantageous in that: the hinge joint and large arm of big arm cylinder and large arm and the hinge joint of forearm share
Large arm can be effectively reduced in the case where big arm cylinder is changed without or big arm cylinder stroke is relatively large in one position
Length keeps broken rock device center of gravity closer apart from large arm and upper body hinge joint 60, makes in the case where broken rock installation weight is constant
Big arm cylinder lifts speed and improves, or promotes lifting weight in the case where lifting speed is constant, to promote rock breaking efficiency.
As shown, the maximum range of activities of ridge buster are D, walking end is C, and C is usually located in the range of D, is commonly used
Broken rock range is G, and common broken rock range refers to that ridge buster enters that thrum degree is good, a relatively high working range of efficiency of breaking rock,
Within the scope of D, it is located at outside the domain of walk, does not need too greatly, to be located at row apart from the most peri position F of hinge joint 60 and C minimum range
Broken rock operation can be met outside range by walking, in general, existing excavator upper frame and big arm cylinder will cause big arm cylinder and big
Arm hinge joint and broken rock device hinge joint are easy to keep F distance walking end C minimum range excessive, cause not in same position
Resistance arm is relatively longer, and since broken rock installation weight is relatively large, resistance arm is too long with respect to power arm, can increase big arm cylinder
The decrement of working media hydraulic oil, increases energy loss, and result can show themselves in that, large arm oil equal in broken rock installation weight
Under cylinder and the constant situation of upper frame, resistance arm rationally reduces, and lifting speed can be faster.
In addition, the structure due to large arm is further simplified, keep production cost lower, reliability further increases.
The distance of 4th hinged shaft 42 to the 1st hinged shaft 34 ratio at a distance from the 1st hinged shaft 34 to the 7th hinged shaft 63 is greater than 0.8, favorably
In making forearm have more labour-saving lever ratio.
Two, the 4th hinged shaft 42 is formed by angle to the line of the 1st hinged shaft 34 and the line of the 7th hinged shaft 63 to the 1st hinged shaft 34
Within 150 degree, such structure setting is advantageous in that the angle of H: when big arm lengths
After reduction, it is easy to make the stroke of dipper cylinder too small, thus keep common broken rock range too small and influence efficiency of breaking rock,
Such angle setting is improved, is conducive to keep dipper cylinder stroke bigger, in addition, there have forearm and large arm hinge point to be relatively reasonable
Transverse width keeps forearm intensity more preferable, more reasonable structure.
Three, the free bearing of the oriented ridge buster in the upper end in forearm towards the face of ridge buster 6 protrusion, the free bearing of protrusion and the 4th hinged shaft
42 connections.
Such structure setting is advantageous in that: after big arm lengths shorten, it is easy to cause dipper cylinder stroke too small, so as to cause
Ridge buster stroke is small to have an adverse effect to efficiency of breaking rock, in addition, large arm shorten after in order to guarantee ridge buster excavating depth, forearm
The distance of hinged shaft 34 to hinged shaft 63 needs to increase, and increases the distance that hinged shaft 34 arrives hinged shaft 42 in order to reduce the stress of dipper cylinder,
And then increasing the stroke of dipper cylinder, dipper cylinder 4 has relatively large stroke, and it is bigger to be conducive to ridge buster stroke range, overcomes
Bring adversely affects after large arm shortens, and improves efficiency of breaking rock.
Four, big arm cylinder 12 is located at 34 end of the 1st hinged shaft, and large arm 2 and 3 hinge point of forearm are located at big arm cylinder 12
Between 34 hinge point of the 1st hinged shaft, such structure setting is advantageous in that: oil cylinder of big arm of digger is generally located on large arm two
Side, quantity are generally two, and the distance of two big arm cylinders is easy to be greater than large arm width and forearm width, so using at the same time
Large arm and forearm the hinge point more reasonable structure between two big arm cylinders when 1 hinged shaft 34.
Five, one end of ridge buster oil cylinder 5 and forearm 3 are articulated with the 4th hinged shaft 42, keep forearm structure more simple and reliable, favorably
In reduction cost.
Six, ridge buster is divided into upper and lower part by the line 73 that the line of the 7th hinged shaft 63 to ridge buster lower end 72 is vertical, connection
Bucket tooth 7 is lower part, and connection ridge buster oil cylinder is upper part, and upper partial volume is greater than lower partial volume, 6 volume of ridge buster
Greater than 3 volume of forearm, 6 weight of ridge buster is greater than 3 weight of forearm, and 6 weight of ridge buster is greater than 2 weight of large arm, and such structure is set
Setting is advantageous in that: in the case where there is reasonable broken rock portion, ridge buster weight proportion in broken rock device is larger, favorably
In the momentum transmission capacity for reducing ridge buster oil cylinder, it is further reduced energy loss.
In addition, ridge buster is also made to have more labor-saving lever ratio, is conducive to ridge buster oil cylinder and reduces energy loss.
Seven, counterweight 64, the 1st hinged shaft 34, the 4th hinged shaft 42, the 5th hinged shaft 55, have partially been detachably arranged on ridge buster 6
6 hinged shafts 56, the 7th hinged shaft 63 separately or concurrently have multiple installation sites, and such structure setting is advantageous in that: can be according to difference
Condition of construction adjustment speed and digging force.
Eight, shock excitation device 65 is partially installed on ridge buster 6, such structure setting is advantageous in that: using the dress that impulses
The power that impulses set promotes the rock breaking capacity of ridge buster.
In conclusion the utility model shares one by big arm cylinder and large arm hinge joint and large arm and forearm hinge joint
Position do not changing big arm cylinder and keeping under large arm has reasonable travel conditions, make broken rock device center of gravity to hinge joint 60 away from
From reduction, improve big arm cylinder ability in the relatively large broken rock device of lifting weight, due under broken rock device shear force with
Broken rock installation weight is directly proportional, and is the main determining factor of lower shear force, and therefore, the raising of big arm cylinder jacking capacity can be bright
The aobvious lower shear force for promoting broken rock device is overcome after big arm lengths are reduced by the change of forearm structure to dipper cylinder stroke
It influences, compared with the prior art, broken rock device keeps relatively reasonable stroke in the case where having more lower shear force greatly, especially
For ridge buster weight in broken rock installation weight the biggish broken rock device of proportion, since center of gravity is apart from large arm and upper frame
Hinge joint is relatively farther, and effect is more obvious.
Detailed description of the invention
Fig. 1 is that excavator carries broken rock device overall effect figure.
Fig. 2 is the broken rock device figure for having big arm cylinder.
Fig. 3 is in common broken rock range internal conflict tooth pitch from nearest schematic diagram of walking.
Fig. 4 is in common broken rock range internal conflict tooth pitch from farthest schematic diagram of walking.
Fig. 5 is that bucket tooth is attainable apart from the farthest schematic diagram of excavator outside common broken rock range.
Fig. 6 is that bucket tooth is attainable apart from the nearest schematic diagram of excavator outside common broken rock range.
Fig. 7 is broken rock device confined explosion top view.
2, large arm, 3 forearms, 4 dipper cylinders, 5 ridge buster oil cylinders, 6 ridge busters, 7 bucket tooths, 12 big arm cylinders, 28 the 3rd hinged shafts,
29 the 2nd hinged shafts, 34 the 1st hinged shafts, 42 the 4th hinged shafts, 45 walkings, 46 upper frame, 55 the 5th hinged shafts, 56 the 6th hinged shafts, 60 the 8th hinged shafts,
61 the 9th hinged shafts, 63 the 7th hinged shafts, 72 ridge buster lower ends, 73 ridge buster upper and lower part lines of demarcation, 74 forearm extended lines, A bucket tooth
Attainable farthest, B bucket tooth be attainable most nearby, C walking end, D bucket tooth maximum range of activities, E often use broken rock range
Interior bucket tooth farthest, F are often located with bucket tooth within the scope of broken rock recently, G often uses broken rock range.
Specific embodiment
The free bearing of the oriented ridge buster protrusion in the top in forearm towards the face of ridge buster in order to facilitate understanding, embodiment is in Fig. 2
Interior deficiency to have intended an extended line 74, it is a left side towards ridge buster that extended line 74, which is located at forearm towards on the face of ridge buster, towards big
Arm is the right side, and when the free bearing of the oriented ridge buster protrusion in the upper end in forearm towards the face of ridge buster 6, then the 4th hinged shaft can be located at and prolong
Long line 74 is left, and when the free bearing that the upper end in forearm towards the face of ridge buster 6 is not protruded to ridge buster, then the 4th hinged shaft is located at and prolongs
Long line 74 is right.
Embodiment 1:
A kind of broken rock device being equipped on excavator, including large arm 2, forearm 3, ridge buster 6, dipper cylinder 4, ridge buster oil cylinder
5, bucket tooth 7, the excavator have top car body and lower running device, and car body rotation in top is connected to lower running device,
One end of large arm 2 and excavator top car body are hinged, and the other end and forearm 3 are hinged by the 1st hinged shaft 34, large arm 2 and large arm oil
Cylinder 12 is hinged by the 1st hinged shaft 34, and top is hinged by the 3rd hinged shaft 28 in the middle part of one end of dipper cylinder 4 and large arm, the other end with it is small
3 upper end of arm is hinged by the 4th hinged shaft 42, and the upper end of forearm 3 is hinged by the 5th hinged shaft 55 and 5 one end of ridge buster oil cylinder, ridge buster
5 other end of oil cylinder and ridge buster 6 are hinged by the 6th hinged shaft 56, and ridge buster lower end 72 is connect with bucket tooth 7, and the quantity of bucket tooth 7 is one
Only, ridge buster is hinged by the 7th hinged shaft 63 and 3 lower end of forearm, and the distance of the 4th hinged shaft 42 to the 1st hinged shaft 34 is arrived with the 1st hinged shaft 34
The distance ratio of 7th hinged shaft 63 is 0.9.Since the 4th hinged shaft has 2 installation sites, the line of the 4th hinged shaft 42 to the 1st hinged shaft 34 with
The maximum angle that the line of 7th hinged shaft 63 to the 1st hinged shaft 34 is formed by angle H is 147 degree.
Big arm cylinder 12 is located at 34 end of the 1st hinged shaft, large arm 2 and 3 hinge point of forearm be located at big arm cylinder 12 and
Between 1st hinged shaft, 34 hinge point.
One end of ridge buster oil cylinder 5 and forearm 3 are not articulated with the 4th hinged shaft 42.
The free bearing that the upper end in forearm towards the face of ridge buster 6 is not protruded to ridge buster.
Ridge buster is divided into upper and lower part by the vertical line 73 of the line of the 7th hinged shaft 63 to ridge buster lower end 72, connects bucket tooth
7 be lower part, and connection ridge buster oil cylinder is upper part, and upper partial volume is greater than lower partial volume.
6 volume of ridge buster is greater than 3 volume of forearm, and 6 weight of ridge buster is 20 tons, and 3 weight of forearm is 4 tons, and 2 weight of large arm is
4.5 ton.
Partially without counterweight 64 on ridge buster 6.
1st hinged shaft 34 has 1 installation site, and the 4th hinged shaft 42 has 2 installation sites, and the 5th hinged shaft 55 has 1 installation site,
6th hinged shaft 56 has 1 installation site, and the 7th hinged shaft 63 has 1 installation site.
Shock excitation device 65 is partially installed on ridge buster 6.
Effect analysis:
It is 0.3 meter that the broken rock device, which often uses broken rock range distance walking minimum range, which has due to different conditions
Difference in certain difference, such as rock stratum condition and the work habit of loosen the soil portion's angle and operator, but the difference one
As be no more than 0.2 meter, the distance of the 8th hinged shaft 60 to the 1st hinged shaft 34 is 3.8 meters, big arm cylinder be it is former excavate Oil cylinder, carry and dig
Dig device after mining ability it is constant, carry the weight broken rock device excavator be 80 tonnes, in the prior art, large arm with it is small
To big arm cylinder and generally 1.3 meters or more of large arm hinge joint distance, common broken rock range distance is walked usually to exist arm hinge joint
1.4 meters or more, this excessive distance be in practice of construction it is useless, the present embodiment resistance arm lengths are usually 3.8 meters, move
Torque arm length is usually at 1 meter, and numerical value is different when broken rock device is in different conditions, but its numerical value change is little, existing
There is technology identical as the utility model in this numerical value change or very close to therefore this numerical value change is disregarded herein, existing
Have in technology, resistance arm is usually at 5 meters or more, and power arm is usually at 1 meter, by removing big arm cylinder and large arm hinge joint to greatly
1.3 meters of length of arm and forearm hinge joint, jacking capacity improve 20% or more, this engineering machine relatively limited in skill upgrading
In tool, obvious technical effects.
In the present embodiment, since big arm cylinder articulated structure not being separately provided in large arm, compared with the prior art, reduce
1.6 ten thousand yuan of cost.
In the present embodiment, since the angle of H is larger, the 4th hinged shaft 42 is located at 3 extended line of forearm, 74 right side, leads to dipper cylinder
Stroke is relatively small, to keep ridge buster stroke relatively small and unfavorable to efficiency of breaking rock.
Ridge buster is not provided with the counterweight of regulating weight, and hinged shaft position is less, relatively to different rock stratum adaptability
Difference.
Ridge buster structure and weight are reasonable, and the rock breaking capacity of ridge buster is stronger, the 8th hinged shaft 60 of broken rock device center of gravity distance away from
From farther out, more demanding to the jacking capacity of big arm cylinder, the present embodiment improves large arm jacking capacity by reducing big arm lengths
Efficiently solve this problem.
Embodiment 2:
A kind of broken rock device being equipped on excavator, including large arm 2, forearm 3, ridge buster 6, dipper cylinder 4, ridge buster oil cylinder
5, bucket tooth 7, the excavator have top car body and lower running device, and car body rotation in top is connected to lower running device,
One end of large arm 2 and excavator top car body are hinged, and the other end and forearm 3 are hinged by the 1st hinged shaft 34, large arm 2 and large arm oil
Cylinder 12 is hinged by the 1st hinged shaft 34, and top is hinged by the 3rd hinged shaft 28 in the middle part of one end of dipper cylinder 4 and large arm, the other end with it is small
3 upper end of arm is hinged by the 4th hinged shaft 42, and the upper end of forearm 3 is hinged by the 5th hinged shaft 55 and 5 one end of ridge buster oil cylinder, ridge buster
5 other end of oil cylinder and ridge buster 6 are hinged by the 6th hinged shaft 56, and ridge buster lower end 72 is connect with bucket tooth 7, and the quantity of bucket tooth 7 is one
Only, ridge buster is hinged by the 7th hinged shaft 63 and 3 lower end of forearm, and the distance of the 4th hinged shaft 42 to the 1st hinged 34 is arrived with the 1st hinged shaft 34
The distance ratio of 7th hinged shaft 63 is 1.4.Since the 7th hinged shaft 63 has 2 installation sites, the line of the 4th hinged shaft 42 to the 1st hinged shaft 34
The maximum angle for being formed by angle H with the line of the 7th hinged shaft 63 to the 1st hinged shaft 34 is 110 degree.
Big arm cylinder 12 is located between 3 hinge point of large arm 2 and forearm.
One end of ridge buster oil cylinder 5 and forearm 3 are articulated with the 4th hinged shaft 42.
The free bearing of the oriented ridge buster protrusion in the upper end in forearm towards the face of ridge buster 6, the free bearing of protrusion and the 4th hinged shaft 42 connect
It connects.
Ridge buster is divided into upper and lower part by the vertical line 73 of the line of the 7th hinged shaft 63 to ridge buster lower end 72, connects bucket tooth
7 be lower part, and connection ridge buster oil cylinder is upper part, and upper partial volume is greater than lower partial volume.
6 volume of ridge buster is greater than 3 volume of forearm, and 6 weight of ridge buster is 20 tons, and 3 weight of forearm is 4 tons, and 2 weight of large arm is
4.5 ton.
6 top of ridge buster, which is set up separately, is equipped with counterweight 64.
1st hinged shaft 34 has 1 installation site, and the 4th hinged shaft 42 has 1 installation site, and the 5th hinged shaft 55 has 1 installation site,
6th hinged shaft 56 has 2 installation sites, and the 7th hinged shaft 63 has 2 installation sites.
Partially without shock excitation device 65 on ridge buster 6.
Effect analysis:
It is 0.3 meter that the broken rock device, which often uses broken rock range distance walking minimum range, which has due to different conditions
Difference in certain difference, such as rock stratum condition and the work habit of loosen the soil portion's angle and operator, but the difference one
As be no more than 0.2 meter, the distance of the 8th hinged shaft 60 to the 1st hinged shaft 34 is 3.8 meters, big arm cylinder be it is former excavate Oil cylinder, carry and dig
Dig device after mining ability it is constant, carry the weight broken rock device excavator be 80 tonnes, in the prior art, large arm with it is small
To big arm cylinder and generally 1.3 meters or more of large arm hinge joint distance, common broken rock range distance is walked usually to exist arm hinge joint
1.4 meters or more, this excessive distance be in practice of construction it is useless, the present embodiment resistance arm lengths are usually 3.8 meters, move
Torque arm length is usually at 1 meter, and numerical value is different when broken rock device is in different conditions, but its numerical value change is little, existing
There is technology identical as the utility model in this numerical value change or very close to therefore this numerical value change is disregarded herein, existing
Have in technology, resistance arm is usually at 5 meters or more, and power arm is usually at 1 meter, by removing big arm cylinder and large arm hinge joint to greatly
1.3 meters of length of arm and forearm hinge joint, jacking capacity improve 20% or more, this engineering machine relatively limited in skill upgrading
In tool, obvious technical effects.
In the present embodiment, forearm has relatively labor-saving lever ratio, is conducive to the promotion of broken rock device digging force, but needs
Dipper cylinder stroke is bigger, and since the angle of H is smaller, the 4th hinged shaft 42 is located at 3 extended line of forearm, 74 left side, and dipper cylinder stroke is opposite
It is larger, to keep ridge buster stroke relatively large and advantageous to efficiency of breaking rock.
In the present embodiment, since big arm cylinder articulated structure not being separately provided in large arm, compared with the prior art, reduce
1.6 ten thousand yuan of cost.
The counterweight of regulating weight is arranged in ridge buster, relatively preferable to different rock stratum adaptability.
Big arm cylinder 12 is located between 3 hinge point of large arm 2 and forearm, although not influencing the implementation of this technology,
It is to keep the portion structure larger and be unfavorable for reducing cost and manufacture.
Ridge buster structure and weight are reasonable, and the rock breaking capacity of ridge buster is stronger, the 8th hinged shaft 60 of broken rock device center of gravity distance away from
From farther out, more demanding to the jacking capacity of big arm cylinder, the present embodiment improves large arm jacking capacity by reducing big arm lengths
Efficiently solve this problem.
Embodiment 3:
A kind of broken rock device being equipped on excavator, including large arm 2, forearm 3, ridge buster 6, dipper cylinder 4, ridge buster oil cylinder
5, bucket tooth 7, the excavator have top car body and lower running device, and car body rotation in top is connected to lower running device,
One end of large arm 2 and excavator top car body are hinged, and the other end and forearm 3 are hinged by the 1st hinged shaft 34, large arm 2 and large arm oil
Cylinder 12 is hinged by the 1st hinged shaft 34, and top is hinged by the 3rd hinged shaft 28 in the middle part of one end of dipper cylinder 4 and large arm, the other end with it is small
3 upper end of arm is hinged by the 4th hinged shaft 42, and the upper end of forearm 3 is hinged by the 5th hinged shaft 55 and 5 one end of ridge buster oil cylinder, ridge buster
5 other end of oil cylinder and ridge buster 6 are hinged by the 6th hinged shaft 56, and ridge buster lower end 72 is connect with bucket tooth 7, and the quantity of bucket tooth 7 is one
Only, ridge buster is hinged by the 7th hinged shaft 63 and 3 lower end of forearm, and the distance of the 4th hinged shaft 42 to the 1st hinged 34 is arrived with the 1st hinged shaft 34
The distance ratio of 7th hinged shaft 63 is 1.2.Since the 4th hinged shaft has 2 installation sites, the 1st hinged shaft 34 has 2 installation sites, the 4th hinge
It is 130 that axis 42, which is formed by the maximum angle of angle H to the line of the 1st hinged shaft 34 and the line of the 7th hinged shaft 63 to the 1st hinged shaft 34,
Degree.
The free bearing of the oriented ridge buster protrusion in the upper end in forearm towards the face of ridge buster 6, the free bearing of protrusion and the 4th hinged shaft 42 connect
It connects.
Big arm cylinder 12 is located at 34 end of the 1st hinged shaft, large arm 2 and 3 hinge point of forearm be located at big arm cylinder 12 and
Between 1st hinged shaft, 34 hinge point.
One end of ridge buster oil cylinder 5 and forearm 3 are not articulated with the 4th hinged shaft 42.
Ridge buster is divided into upper and lower part by the vertical line 73 of the line of the 7th hinged shaft 63 to ridge buster lower end 72, connects bucket tooth
7 be lower part, and connection ridge buster oil cylinder is upper part, and upper partial volume is less than lower partial volume.
6 volume of ridge buster is less than 3 volume of forearm, and 6 weight of ridge buster is 2 tons, and 3 weight of forearm is 13 tons, and 2 weight of large arm is
14 tons.
Partially without counterweight 64 on ridge buster 6.
1st hinged shaft 34 has 2 installation sites, and the 4th hinged shaft 42 has 2 installation sites, and the 5th hinged shaft 55 has 1 installation site,
6th hinged shaft 56 has 1 installation site, and the 7th hinged shaft 63 has 1 installation site.
Partially without shock excitation device 65 on ridge buster 6.
Effect analysis:
It is 0.3 meter that the broken rock device, which often uses broken rock range distance walking minimum range, which has due to different conditions
Difference in certain difference, such as rock stratum condition and the work habit of loosen the soil portion's angle and operator, but the difference one
As be no more than 0.2 meter, the distance of the 8th hinged shaft 60 to the 1st hinged shaft 34 is 3.8 meters, big arm cylinder be it is former excavate Oil cylinder, carry and dig
Dig device after mining ability it is constant, carry the weight broken rock device excavator be 80 tonnes, in the prior art, large arm with it is small
To big arm cylinder and generally 1.3 meters or more of large arm hinge joint distance, common broken rock range distance is walked usually to exist arm hinge joint
1.4 meters or more, this excessive distance be in practice of construction it is useless, the present embodiment resistance arm lengths are usually 3.1 meters, move
Torque arm length is usually at 1 meter, and numerical value is different when broken rock device is in different conditions, but its numerical value change is little, existing
There is technology identical as the utility model in this numerical value change or very close to therefore this numerical value change is disregarded herein, existing
Have in technology, usually at 3.8 meters or more, power arm is arrived by removing big arm cylinder with large arm hinge joint resistance arm usually at 1 meter
1.3 meters of length of large arm and forearm hinge joint, jacking capacity improve 14% or more, this engineering relatively limited in skill upgrading
In machinery, technical effect is more significant, and still, the biggish broken rock of proportion fills in broken rock installation weight with ridge buster weight
It sets and compares, effect is relatively weaker.
In the present embodiment, forearm has relatively labor-saving lever ratio, is conducive to the promotion of broken rock device digging force, but needs
Dipper cylinder stroke is bigger, and since the angle of H is smaller, the 4th hinged shaft 42 is located at 3 extended line of forearm, 74 left side, and dipper cylinder stroke is opposite
It is larger, to keep ridge buster stroke relatively large and advantageous to efficiency of breaking rock.
In the present embodiment, since big arm cylinder articulated structure not being separately provided in large arm, compared with the prior art, reduce
1.6 ten thousand yuan of cost.
The counterweight of regulating weight cannot be arranged in ridge buster, relatively poor to different rock stratum adaptability.
Big arm cylinder 12 is located at 34 end of the 1st hinged shaft, large arm 2 and 3 hinge point of forearm be located at big arm cylinder 12 and
It is compact-sized reasonable between 1st hinged shaft, 34 hinge point.
The rock breaking capacity of ridge buster unreasonable structure and lighter in weight, ridge buster is poor, and broken rock device center of gravity distance the 8th is cut with scissors
Axis 60 is apart from relative close, and relatively lower to the jacking capacity requirement of big arm cylinder, the present embodiment is by reducing big arm lengths
Improve the jacking capacity that big arm cylinder is effectively promoted in large arm jacking capacity.
Embodiment 4:
A kind of broken rock device being equipped on excavator, including large arm 2, forearm 3, ridge buster 6, dipper cylinder 4, ridge buster oil cylinder
5, bucket tooth 7, the excavator have top car body and lower running device, and car body rotation in top is connected to lower running device,
One end of large arm 2 and excavator top car body are hinged, and the other end and forearm 3 are hinged by the 1st hinged shaft 34, large arm 2 and large arm oil
Cylinder 12 is hinged by the 1st hinged shaft 34, and top is hinged by the 3rd hinged shaft 28 in the middle part of one end of dipper cylinder 4 and large arm, the other end with it is small
3 upper end of arm is hinged by the 4th hinged shaft 42, and the upper end of forearm 3 is hinged by the 5th hinged shaft 55 and 5 one end of ridge buster oil cylinder, ridge buster
5 other end of oil cylinder and ridge buster 6 are hinged by the 6th hinged shaft 56, and ridge buster lower end 72 is connect with bucket tooth 7, and the quantity of bucket tooth 7 is one
Only, ridge buster is hinged by the 7th hinged shaft 63 and 3 lower end of forearm, and the distance of the 4th hinged shaft 42 to the 1st hinged 34 is arrived with the 1st hinged shaft 34
The distance ratio of 7th hinged shaft 63 is 1.5.Since the 7th hinged shaft 63 has 2 installation sites, the 1st hinged shaft 34 has 2 installation sites, and the 4th
Hinged shaft 42 has 2 installation sites, the 4th hinged shaft 42 to the line of the 1st hinged shaft 34 and the line institute of the 7th hinged shaft 63 to the 1st hinged shaft 34
The maximum angle of the angle H of formation is 110 degree.
The free bearing of the oriented ridge buster protrusion in the upper end in forearm towards the face of ridge buster 6, the free bearing of protrusion and the 4th hinged shaft 42 connect
It connects.
Big arm cylinder 12 is located at 34 end of the 1st hinged shaft, large arm 2 and 3 hinge point of forearm be located at big arm cylinder 12 and
Between 1st hinged shaft, 34 hinge point.
One end of ridge buster oil cylinder 5 and forearm 3 are articulated with the 4th hinged shaft 42.
Ridge buster is divided into upper and lower part by the vertical line 73 of the line of the 7th hinged shaft 63 to ridge buster lower end 72, connects bucket tooth
7 be lower part, and connection ridge buster oil cylinder is upper part, and upper partial volume is greater than lower partial volume.
6 volume of ridge buster is greater than 3 volume of forearm, and 6 weight of ridge buster is 21 tons, and 3 weight of forearm is 4 tons, and 2 weight of large arm is
4 tons.
6 top of ridge buster, which is set up separately, is equipped with counterweight 64.
1st hinged shaft 34 has 2 installation sites, and the 4th hinged shaft 42 has 2 installation sites, and the 5th hinged shaft 55 has 2 installation sites,
6th hinged shaft 56 has 2 installation sites, and the 7th hinged shaft 63 has 2 installation sites.
6 top of ridge buster, which is set up separately, is equipped with shock excitation device 65.
Effect analysis:
It is 0.3 meter that the broken rock device, which often uses broken rock range distance walking minimum range, which has due to different conditions
Difference in certain difference, such as rock stratum condition and the work habit of loosen the soil portion's angle and operator, but the difference one
As be no more than 0.2 meter, the distance of the 8th hinged shaft 60 to the 1st hinged shaft 34 is 3.8 meters, big arm cylinder be it is former excavate Oil cylinder, carry and dig
Dig device after mining ability it is constant, carry the weight broken rock device excavator be 80 tonnes, in the prior art, large arm with it is small
To big arm cylinder and generally 1.3 meters or more of large arm hinge joint distance, common broken rock range distance is walked usually to exist arm hinge joint
1.4 meters or more, this excessive distance be in practice of construction it is useless, the present embodiment resistance arm lengths are usually 3.8 meters, move
Torque arm length is usually at 1 meter, and numerical value is different when broken rock device is in different conditions, but its numerical value change is little, existing
There is technology identical as the utility model in this numerical value change or very close to therefore this numerical value change is disregarded herein, existing
Have in technology, resistance arm is usually at 5 meters or more, and power arm is usually at 1 meter, by removing big arm cylinder and large arm hinge joint to greatly
1.3 meters of length of arm and forearm hinge joint, jacking capacity improve 20% or more, this engineering machine relatively limited in skill upgrading
In tool, obvious technical effects.
In the present embodiment, forearm has relatively labor-saving lever ratio, is conducive to the promotion of broken rock device digging force, but needs
Dipper cylinder stroke is bigger, and since the angle of H is smaller, the 4th hinged shaft 42 is located at 3 extended line of forearm, 74 left side, and dipper cylinder stroke is opposite
It is larger, to keep ridge buster stroke relatively large and advantageous to efficiency of breaking rock.
In the present embodiment, since big arm cylinder articulated structure not being separately provided in large arm, compared with the prior art, reduce
1.6 ten thousand yuan of cost.
The counterweight of regulating weight is arranged in ridge buster, relatively preferable to different rock stratum adaptability.
Big arm cylinder 12 is located at 34 end of the 1st hinged shaft, large arm 2 and 3 hinge point of forearm be located at big arm cylinder 12 and
It is compact-sized reasonable between 1st hinged shaft, 34 hinge point.
6 top of ridge buster, which is set up separately, is equipped with shock excitation device 65, passes through rock breaking capacity by the power that impulses of shock excitation device.
The present embodiment ridge buster structure and weight are reasonable, and the rock breaking capacity of ridge buster is stronger, broken rock device center of gravity distance the 8th
Hinged shaft 60 is apart from farther out, and more demanding to the jacking capacity of big arm cylinder, the present embodiment improves large arm by reducing big arm lengths
Jacking capacity efficiently solves this problem.
In conclusion rock breaking capacity is obviously improved the present embodiment compared with the existing technology.
Claims (10)
1. a kind of broken rock device for being equipped on excavator, including large arm (2), forearm (3) ridge buster (6), dipper cylinder (4), loosen the soil
Device oil cylinder (5), bucket tooth (7), the excavator have top car body and lower running device, and car body rotation in top is connected to lower part
Running gear, which is characterized in that one end of large arm (2) and excavator top car body are hinged, and the other end and forearm (3) pass through the 1st
Hingedly, large arm (2) and big arm cylinder (12) pass through the 1st hinged shaft (34) hingedly to hinged shaft (34), in one end and large arm of dipper cylinder (4)
Portion top by the 3rd hinged shaft (28) hingedly, the other end and forearm (3) upper end by the 4th hinged shaft (42) hingedly, forearm (3) it is upper
End is hinged by the 5th hinged shaft (55) and ridge buster oil cylinder (5) one end, and ridge buster oil cylinder (5) other end and ridge buster (6) pass through the
Hingedly, ridge buster lower end (72) are connect 6 hinged shafts (56) with bucket tooth (7), and the quantity of bucket tooth (7) is one, and ridge buster passes through the 7th hinge
Axis (63) and forearm (3) lower end are hinged, the distance and the 1st hinged shaft (34) to the 7th hinged shaft of the 4th hinged shaft (42) to the 1st hinged shaft (34)
(63) distance ratio is greater than 0.8, when the 4th hinged shaft (42), the 1st hinged shaft (34), the 7th hinged shaft (63) separately or concurrently have multiple positions
When, the distance of the 4th hinged shaft (42) to the 1st hinged shaft (34) is subject to longest, the distance of the 1st hinged shaft (34) to the 7th hinged shaft (63) with
Subject to most short.
2. broken rock device according to claim 1, which is characterized in that the line of the 4th hinged shaft (42) to the 1st hinged shaft (34) with
The line of 7th hinged shaft (63) to the 1st hinged shaft (34) is formed by the angle of angle H within 150 degree.
3. broken rock device according to claim 2, which is characterized in that the upper end in forearm towards the face of ridge buster (6) is oriented
The free bearing of ridge buster protrusion, the free bearing of protrusion are connect with the 4th hinged shaft (42).
4. broken rock device according to claim 2, which is characterized in that big arm cylinder (12) is located at the 1st hinged shaft (34)
End, large arm (2) and forearm (3) hinge point are located between big arm cylinder (12) and the 1st hinged shaft (34) hinge point.
5. broken rock device according to claim 2, which is characterized in that one end and forearm (3) of ridge buster oil cylinder (5) are hinged
In the 4th hinged shaft (42).
6. broken rock device according to claim 1, which is characterized in that the 7th hinged shaft (63) arrives the company of ridge buster lower end (72)
Ridge buster is divided into upper and lower part by the vertical line of line (73), and connection bucket tooth (7) is lower part, and connection ridge buster oil cylinder is
Upper part, upper partial volume are greater than lower partial volume.
7. broken rock device according to claim 6, which is characterized in that ridge buster (6) volume is greater than forearm (3) volume, pine
Earthenware (6) weight is greater than forearm (3) weight, and ridge buster (6) weight is greater than large arm (2) weight.
8. broken rock device according to claim 6, which is characterized in that be partially detachably arranged and matched on ridge buster (6)
Weight (64).
9. broken rock device according to claim 6, which is characterized in that the 1st hinged shaft (34), the 4th hinged shaft (42), the 5th hinged shaft
(55), the 6th hinged shaft (56), the 7th hinged shaft (63) separately or concurrently have multiple installation sites.
10. broken rock device according to claim 7, which is characterized in that ridge buster is partially equipped with shock excitation device on (6)
(65).
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| CN201822086963.4U CN209308091U (en) | 2018-12-13 | 2018-12-13 | It is equipped on the broken rock device of excavator |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109356217A (en) * | 2018-12-13 | 2019-02-19 | 成都市猎石者破岩科技有限责任公司 | It is equipped on the broken rock device of excavator |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109356217A (en) * | 2018-12-13 | 2019-02-19 | 成都市猎石者破岩科技有限责任公司 | It is equipped on the broken rock device of excavator |
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Effective date of registration: 20200617 Address after: No. 1303, floor 13, unit 1, building 1, No. 888, middle section of Taodu Avenue, Longquan street, Longquanyi District, Chengdu City, Sichuan Province Patentee after: Sichuan stone Hunter Longyu Technology Co.,Ltd. Address before: 610000 402 4, 4 4 Tongji Avenue, Qingbaijiang District, Chengdu, Sichuan. Patentee before: CHENGDU LIESHIZHE ROCK BREAKING TECHNOLOGY Co.,Ltd. |
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