CN110107220B - Percussion device and rock drilling equipment - Google Patents
Percussion device and rock drilling equipment Download PDFInfo
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- CN110107220B CN110107220B CN201910368803.5A CN201910368803A CN110107220B CN 110107220 B CN110107220 B CN 110107220B CN 201910368803 A CN201910368803 A CN 201910368803A CN 110107220 B CN110107220 B CN 110107220B
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- 238000009527 percussion Methods 0.000 title claims abstract description 113
- 239000011435 rock Substances 0.000 title claims abstract description 18
- 238000005553 drilling Methods 0.000 title claims abstract description 12
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 80
- 230000007246 mechanism Effects 0.000 claims abstract description 50
- 239000003921 oil Substances 0.000 claims abstract description 25
- 230000008859 change Effects 0.000 claims abstract description 13
- 230000009467 reduction Effects 0.000 claims abstract description 13
- 238000007789 sealing Methods 0.000 claims description 9
- 230000006835 compression Effects 0.000 claims description 7
- 238000007906 compression Methods 0.000 claims description 7
- 230000003116 impacting effect Effects 0.000 claims description 5
- 238000000034 method Methods 0.000 description 7
- 238000013016 damping Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000000630 rising effect Effects 0.000 description 3
- 230000001133 acceleration Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 230000036316 preload Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000035945 sensitivity Effects 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 230000001174 ascending effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000005381 potential energy Methods 0.000 description 1
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Classifications
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B1/00—Percussion drilling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
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- Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Mining & Mineral Resources (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Environmental & Geological Engineering (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Earth Drilling (AREA)
- Percussive Tools And Related Accessories (AREA)
Abstract
The invention discloses a percussion device and rock drilling equipment, the percussion device is arranged on a movable carrier, and the percussion device comprises: the hydraulic cylinder mechanism comprises a cylinder body and an impact piston arranged in the cylinder body; a drill rod provided at a lower end of the cylinder block; a cylinder mechanism provided at an upper end of the cylinder block; a hydraulic pump for supplying hydraulic oil to the cylinder block; a direction change valve connected between the cylinder and the hydraulic pump, the hydraulic pump being configured to drive the striking piston to move up and down by switching the direction change valve in a selective manner; and the speed reduction mechanism is used for reducing the speed difference between the actual speed and the rated speed of the impact oil cylinder caused by the flow difference between the actual flow and the rated flow when the actual flow of the hydraulic oil entering the lower cavity of the cylinder body and used for driving the impact piston to move upwards is larger than the rated flow.
Description
Technical Field
The invention relates to a percussion device on rock drilling equipment.
Background
One type of rock drilling apparatus is known to operate by breaking rock or concrete structures by impact forces.
Rock drilling rigs of the above-mentioned type of the prior art generally comprise two parts, namely: moving the carrier and the striking device. The percussion device is mounted on a mobile carrier for controlling the operating position of the percussion device.
A percussion device is a working device of a rock drilling apparatus, which is a main body component for breaking rock and concrete structures, and a prior art percussion device generally includes: the hydraulic cylinder mechanism, the drill rod, the cylinder mechanism, the hydraulic control reversing valve and the hydraulic pump. The hydraulic cylinder mechanism specifically comprises a cylinder body and an impact piston arranged in the cylinder body, a drill rod is arranged below the cylinder body, and the cylinder mechanism is arranged above the cylinder body. Wherein: the hydraulic pump provides hydraulic oil for the cylinder body through the hydraulic control reversing valve so that the impact piston can move up and down, and the moving direction of the impact piston is switched by the hydraulic control reversing valve so that the hydraulic pump can lead the hydraulic oil to the upper cavity and the lower cavity of the cylinder body in a selective mode. When the impact piston is driven to move upwards, the upper end of the impact piston continuously extends into an air cavity of the air cylinder mechanism, so that air is compressed, energy is released when the compressed air moves downwards in an impact movement reversing mode, the impact piston moves downwards quickly to impact the drill rod, and the drill rod impacts a rock and concrete structure body to be broken.
It will be readily appreciated that to brake the upwardly moving percussion piston to reverse to the downwardly moving action, it is necessary to apply a downward pressure to the percussion piston when it has not yet moved to the uppermost position, and as mentioned above, the applied pressure includes at least the hydraulic oil pressure through the upper chamber of the cylinder block by means of the hydraulic pump through the hydraulically controlled directional valve. Specifically, in the prior art, the moving position of the percussion piston is associated with two hydraulic control ports of the hydraulic control directional valve, so that when the ascending percussion piston passes through a preset intermediate position, the pressure of the hydraulic control port 52 changes to actuate the hydraulic control directional valve, so that the pressure built up in the upper chamber of the cylinder body applies downward pressure to the percussion piston, and the percussion piston finally ascends to the preset position and stops.
The above-mentioned stopping of the percussion piston at the preset position by means of the reversal of the pilot operated directional control valve is established under the condition that the hydraulic pump provides a normal hydraulic oil flow rate (or a rated range of hydraulic oil flow rate), however, when the hydraulic pump supplies a higher than normal flow rate of hydraulic oil to the lower chamber of the cylinder for uncontrollable reasons or by operator's misoperation, the above-mentioned speed of the percussion piston is increased compared to the normal speed, which leads to the following undesirable results:
the time that the striking piston that moves up at a high speed passes through the intermediate position that can cause the switching-over valve to commutate shortens for the switching-over valve can not in time commutate, and then leads to the epicoele of cylinder body can not in time establish the pressure of restriction striking piston, and this makes the striking piston can not stop at the set position, leads to moving up uncontrollably, and this can make the upper end of striking piston produce the impact to cylinder body upper end and cylinder mechanism's relevant parts, and this kind of impact leads to relevant parts to damage.
Disclosure of Invention
In view of the above-mentioned technical problems in the prior art, embodiments of the present invention provide a percussion device and a rock drilling apparatus.
In order to solve the technical problem, the embodiment of the invention adopts the following technical scheme:
an impact device mounted on a mobile carrier, comprising:
the hydraulic cylinder mechanism comprises a cylinder body and an impact piston arranged in the cylinder body;
a drill rod provided at a lower end of the cylinder block;
a cylinder mechanism provided at an upper end of the cylinder block;
a hydraulic pump for supplying hydraulic oil to the cylinder block;
a direction change valve connected between the cylinder and the hydraulic pump, the hydraulic pump being configured to drive the striking piston to move up and down by switching the direction change valve in a selective manner;
and the speed reduction mechanism is used for reducing the speed difference between the actual speed and the rated speed of the impact oil cylinder caused by the flow difference between the actual flow and the rated flow when the actual flow of the hydraulic oil entering the lower cavity of the cylinder body and used for driving the impact piston to move upwards is larger than the rated flow.
Preferably, the speed reducing mechanism reduces the speed difference of the percussion piston by reducing the amount of hydraulic oil in the lower chamber that contributes to the upward movement of the percussion piston.
Preferably, the speed reduction mechanism reduces the amount of hydraulic oil in the chamber that contributes to the upward movement of the percussion piston in dependence on the actual pressure in the lower chamber.
Preferably, the speed reduction mechanism comprises:
a receiving chamber formed in the percussion piston;
the plug disc is arranged in the accommodating cavity and can vertically move along the accommodating cavity;
a resilient biasing member for urging the plug disc downwardly;
the first flow guide channel is used for communicating the lower cavity with the accommodating cavity below the plug disc;
the second flow guide channel is used for communicating an upper cavity of the cylinder body with the accommodating cavity above the plug disc; wherein:
when the actual pressure in the lower cavity is smaller than the rated pressure, the elastic biasing piece is used for enabling the plug disc to stop at the lower end of the accommodating cavity;
when the actual pressure in the lower cavity is greater than the rated pressure, the hydraulic oil in the lower cavity pushes the plug disc to move upwards through the first flow guide channel, so that the volume of the accommodating cavity below the plug disc is increased, and the hydraulic oil flowing in through the first flow guide channel is accommodated.
Preferably, the speed reduction mechanism comprises:
the accommodating cavity is formed above the air cavity of the air cylinder mechanism, and the lower end of the accommodating cavity is communicated with the air cavity;
the plug disc is arranged in the accommodating cavity and can vertically move along the accommodating cavity;
the elastic biasing piece is arranged in the accommodating cavity and used for pushing the plug disc upwards;
the flow guide pipeline is connected between the upper end of the accommodating cavity and the lower cavity; wherein:
when the actual pressure in the lower cavity is smaller than the rated pressure, the elastic biasing piece is used for enabling the plug disc to stop at the upper end of the accommodating cavity;
when the actual pressure in the lower cavity is greater than the rated pressure, the hydraulic oil in the lower cavity pushes the plug disc to move downwards through the flow guide pipeline, so that the accommodating cavity above the plug disc is enlarged to accommodate the hydraulic oil flowing in through the flow guide pipeline.
Preferably, the percussion piston comprises an upper plug and a lower plug; the lower end of the upper plug column extends into the upper end of the lower plug column to form threaded connection, and is in sealing fit with the upper plug column and tightly pressed against the lower plug column to be locked by virtue of a locking nut sleeved on the upper plug column; wherein:
the containing cavity is formed by the upper plug column and the lower plug column in a limiting mode.
Preferably, the lower plug is provided with a downward stepped surface, and the first flow guide channel extends from the stepped surface to the lower end of the accommodating cavity in an inclined manner; the second flow guide channel extends upwards from the end face of the upper plug column in the axial direction and continues to penetrate to the upper cavity through radial extension.
Preferably, the resilient biasing member is a compression spring.
Preferably, the resilient biasing member is a compression spring.
The invention also discloses a rock drilling device, which comprises a movable carrier and the impacting device, wherein the impacting device is arranged on the movable carrier and is driven by the movable carrier to change the operation position.
Compared with the prior art, the impact device and the rock drilling equipment disclosed by the invention have the beneficial effects that: the speed reduction mechanism is used for reducing the speed of the impact piston caused by flow increase, so that the time for completely reversing the reversing valve can be given when the impact piston moves upwards, and related parts are prevented from being damaged by the movement of the impact piston.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention.
The summary of various implementations or examples of the technology described in this disclosure is not a comprehensive disclosure of the full scope or all features of the disclosed technology.
Drawings
In the drawings, which are not necessarily drawn to scale, like reference numerals may describe similar components in different views. Like reference numerals having letter suffixes or different letter suffixes may represent different instances of similar components. The drawings illustrate various embodiments, by way of example and not by way of limitation, and together with the description and claims, serve to explain the inventive embodiments. The same reference numbers will be used throughout the drawings to refer to the same or like parts, where appropriate. Such embodiments are illustrative, and are not intended to be exhaustive or exclusive embodiments of the present apparatus or method.
Fig. 1 is a schematic structural view of a percussion device provided in embodiment 1 of the present invention (the flow rate of hydraulic oil entering a lower chamber is a rated flow rate).
Fig. 2 is an enlarged view of a portion a of fig. 1.
Fig. 3 is a schematic structural diagram of a percussion device provided in embodiment 1 of the present invention (the flow rate of hydraulic oil entering the lower chamber is greater than the rated flow rate, and the percussion piston is in the first rising stage).
Fig. 4 is an enlarged view of a portion B of fig. 3.
Fig. 5 is a schematic structural diagram of a percussion device provided in embodiment 1 of the present invention (the flow rate of hydraulic oil entering the lower chamber is greater than the rated flow rate, and the percussion piston is in a second ascent stage, in which the reversing valve is in a reversing state at the moment the percussion piston passes through a preset position).
Fig. 6 is an enlarged view of a portion C of fig. 5.
Fig. 7 is a schematic structural diagram of a percussion device provided in embodiment 1 of the present invention (the flow rate of hydraulic oil entering the lower chamber is greater than the rated flow rate, and the percussion piston is in a third rising stage, where the reversing valve completes reversing after the percussion piston passes through a preset position).
Fig. 8 is an enlarged view of a portion D of fig. 7.
Fig. 9 is a schematic structural view of a percussion device provided in embodiment 2 of the present invention (the flow rate of hydraulic oil entering the lower chamber is a rated flow rate).
Fig. 10 is a schematic structural diagram of a percussion device provided in embodiment 2 of the present invention (the flow rate of hydraulic oil entering the lower chamber is greater than the rated flow rate, and the percussion piston is in the first rising stage).
Fig. 11 is an enlarged view of a portion E of fig. 10.
Reference numerals:
10-a hydraulic cylinder mechanism; 11-a cylinder body; 111-lower chamber; 112-an upper chamber; 113-oil return chamber; 12-a percussion piston; 121-lower plug column; 1211-a step surface; 122-upper plug column; 1221-locking nut; 20-a drill rod; 21-a retaining sleeve; 30-a cylinder mechanism; 31-an air cavity; 40-a abatement mechanism; 41-a housing chamber; 42-a resilient biasing member; 43-a first flow guide channel; 44-a second flow directing passage; 45-plug disc; 46-a receiving cavity; 47-a resilient biasing member; 48-plug disc; 50-a diverter valve; 51-a hydraulic control port; 52-hydraulic control port; 60-a hydraulic pump; 70-oil tank; 71-lower joint; 72-oil control joint; 73-oil return connection; 74-upper joint; and 75-a flow guide joint.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the drawings of the embodiments of the present invention. It is to be understood that the embodiments described are only a few embodiments of the present invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the described embodiments of the invention without any inventive step, are within the scope of protection of the invention.
Unless defined otherwise, technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this invention belongs. The use of "first," "second," and similar terms in the present application do not denote any order, quantity, or importance, but rather the terms are used to distinguish one element from another. 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, but does not exclude other elements or items. The terms "connected" or "coupled" and the like are not restricted to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "upper", "lower", "left", "right", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.
To maintain the following description of the embodiments of the present invention clear and concise, a detailed description of known functions and known components of the invention have been omitted.
As shown in fig. 1 to 11, the present invention discloses a striking device which is mounted on a moving carrier and is used to impact rocks, concrete structures, etc. to break them. The percussion device includes: the hydraulic cylinder mechanism 10, the drill rod 20, the cylinder mechanism 30, the hydraulic pump 60, the directional valve 50, the oil tank 70 and the related hydraulic lines.
As shown in fig. 1 and 9, the hydraulic cylinder mechanism 10 includes a cylinder block 11 and a percussion piston 12, the percussion piston 12 being disposed in the cylinder block 11. The area of the cylinder 11 near the upper end is formed with a stepped structure to enclose an upper chamber 112 with the percussion piston 12, the upper chamber 112 forming an axially extending section; the area of the cylinder 11 near the lower end is formed with a stepped structure to enclose a lower cavity 111 with the percussion piston 12, the lower cavity 111 forming a section extending axially; the upper chamber 112 and the lower chamber 111 are adapted to be selectively supplied with hydraulic oil by the hydraulic pump 60 to drive the percussion piston 12 to move up and down. The percussion piston 12 is formed with a stepped structure in its middle portion so that the percussion piston 12 and the cylinder 11 also enclose a return oil chamber 113.
The rod 20 is an actuator for striking the rock or concrete structure, and the striker piston 12 moves down to strike the rod 20, so that the rod 20 strikes the rock or concrete structure to break it.
The cylinder mechanism 30 is installed on the upper end of the cylinder body 11, a closed air cavity 31 is formed in the cylinder mechanism 30, when the percussion piston 12 moves upwards, the upper end of the percussion piston 12 compresses air in the air cavity 31, so that the air in the air cavity 31 is boosted and energy is accumulated, and the compressed air is used for providing power for reversing and downwards moving the percussion piston 12 so as to enable the percussion piston 12 to move downwards at a high speed to strike the drill rod 20.
The directional control valve 50 is a hydraulic control directional control valve 50, and is a two-position three-way directional control valve 50, specifically, one hydraulic control port 51 of the directional control valve 50 is connected to a main pipeline of the hydraulic pump 60 by a hydraulic pipeline, the other hydraulic control port 52 is connected to an oil control joint 72 by a hydraulic pipeline, and the oil control joint 72 is selectively communicated with the oil return cavity 113; the working port of the directional valve 50 is connected to the upper connector 74 via a hydraulic line, the upper connector 74 is communicated with the upper chamber 112; the lower part of the cylinder 11 is provided with a lower joint 71, the lower joint 71 is communicated with the lower cavity 111, and the lower joint 71 is connected to a main pipeline of the hydraulic pump 60 by a hydraulic pipeline; an oil return joint 73 is provided on the cylinder 11 above the oil control joint 72, the oil return joint 73 being in selective communication with the oil return chamber 113 and being connected to the oil tank 70 by means of a hydraulic line.
When the hydraulic pump 60 is operated normally and the flow rate of the supplied hydraulic oil is the rated flow rate, when the percussion piston 12 is at the lowest position where the drill rod 20 has been struck, the hydraulic oil supplied from the hydraulic pump 60 enters the lower chamber 111 through the direction change valve 50, and the hydraulic oil in the upper chamber 112 flows back to the oil tank 70, so that the percussion piston 12 moves up at the rated speed by the hydraulic oil flowing into the lower chamber 111 at the rated flow rate, and at this time, the pressure applied to the lower end of the percussion piston 12 is the rated pressure corresponding to the rated flow rate.
When the percussion piston 12 moves upward and passes through a predetermined position (the middle position mentioned in the background art) under the action of the hydraulic oil in the lower chamber 111, the oil control joint 72 is communicated with the lower chamber 111, so that the hydraulic oil in the lower chamber 111 enters one of the oil control ports through the hydraulic pipeline to switch the direction of the direction valve 50.
The reversed direction valve 50 allows the hydraulic oil of the hydraulic pump 60 to enter the upper chamber 112 through the upper joint 74, and the hydraulic pump 60 stops supplying the lower chamber 111, at which time the hydraulic pump 60 supplies the upper chamber 112 with the hydraulic oil for decelerating the upwardly moving percussion piston 12 to stop the percussion piston 12 at the set position.
The striking piston 12 can stop moving up at the set position because the flow rate of the hydraulic oil supplied from the hydraulic pump 60 is the rated flow rate during the whole moving up process of the striking piston 12.
When the percussion piston 12 stops moving upwards, the air chamber 31 in the cylinder mechanism 30 is compressed to the maximum extent, at which time the hydraulic pump 60 supplies hydraulic oil to the upper chamber 112, so that the percussion piston 12 moves downwards under the dual action of hydraulic oil and air pressure after stopping, and the percussion piston 12 strikes the drill rod 20 at high speed.
During the downward movement of the percussion piston 12, the oil return connection 73 and the oil control connection 72 are communicated with each other by the oil return cavity 113 for a period of time to allow the direction change valve 50 to change direction again, so that the hydraulic pump 60 supplies oil to the lower cavity 111 again, and the percussion piston 12 moves upward again, and the process is circulated to perform the percussion on the percussion piston 12.
As will be readily appreciated from the background, when the percussion piston 12 is driven upward by the hydraulic pump 60 at a nominal flow rate, the percussion piston 12 will move upward at a nominal speed corresponding to the nominal flow rate, at which point the time taken for the percussion piston 12 to pass through the preset position will allow the reversing valve 50 to complete the full reversing, and thus the percussion piston 12 to stop moving upward at the set position.
It should be noted that: the nominal flow is a flow range, not to be understood as a specific flow value, at which the supply of oil by the hydraulic pump 60 enables the reversing valve 50 to complete the complete reversing, so that the upward movement speed of the percussion piston 12 can be controlled.
Accordingly, it will be readily appreciated that the nominal speed of the percussion piston 12 and the set position of rest described above are ranges and not specific values.
In connection with the description of the background art, when the hydraulic pump 60 supplies the hydraulic oil of more than the rated flow rate (normal flow rate) to the lower chamber 111 of the cylinder 11 due to an uncontrollable reason or an erroneous operation of an operator, the actual speed of the percussion piston 12 exceeds the nominal speed (normal speed), and if the actual speed of the percussion piston 12 is not reduced, the time for the percussion piston 12 to pass a predetermined position (referred to as the intermediate position in the background art) is shortened, so that the reversing valve 50 cannot reverse in time, which in turn results in the upper chamber 112 of the cylinder 11 not being able to build up pressure in time limiting the percussion piston 12, this entails that the percussion piston 12 cannot stop in the set position, which, in general, results in an uncontrolled upward movement of the percussion piston 12, this may cause the upper end of the percussion piston 12 to impact the upper end of the cylinder block 11 and the associated parts of the cylinder mechanism 30, which may cause the associated parts to be damaged.
The speed reducing mechanism 40 of the present invention is used to reduce the speed of the percussion piston 12 in the above situation so that the percussion piston 12, when moving upwards, gives the reversing valve 50 time to completely reverse. Specifically, the method comprises the following steps: when the actual flow rate of the hydraulic oil that enters the lower chamber 111 of the cylinder block 11 for driving the percussion piston 12 upward is greater than the rated flow rate, the speed reducing mechanism 40 is configured to reduce the speed difference between the actual speed and the rated speed of the percussion cylinder caused by the flow rate difference between the actual flow rate and the rated flow rate.
In light of the above-described action of the speed reduction mechanism 40, it should not be understood that: when any large flow difference is encountered, the abatement mechanism 40 is able to abate the actual velocity to the rated velocity, i.e.: reducing the speed difference to zero; but rather should be understood as: the trim mechanism 40 can trim the actual speed to a speed that enables the reversing valve 50 to complete the reversing so as not to cause the slamming piston 12 to cause a severe slam to the associated components.
In some preferred embodiment solutions, the speed reducing mechanism 40 reduces the speed difference of the percussion piston 12 by reducing the amount of hydraulic oil in the lower chamber 111 that contributes to the upward movement of the percussion piston 12.
It should be noted that: in the prior art, the hydraulic oil continuously entering the lower cavity 111 is used for increasing the volume of the lower cavity 111, so that the amount of the entering hydraulic oil is used for pushing the piston to move upwards, and accordingly, when the actual flow rate is larger than the rated flow rate, the actual speed of the impact piston 12 is correspondingly larger than the rated speed. The abatement mechanism 40 provided in the present invention is generally referred to as a abatement mechanism, so that a part of the hydraulic oil entering the lower chamber 111 is not used to increase the volume of the lower chamber 111, especially a part of the hydraulic oil having an actual flow rate higher than a rated flow rate, so that at least a part of the hydraulic oil is not used to increase the volume of the lower chamber 111, thereby reducing the actual speed, or abatement speed difference, of the impact piston 12.
The reducing mechanism 40 having the above-described function may be variously embodied, for example, the reducing mechanism 40 is implemented by a switching valve provided in the lower chamber 111 and a flow meter for taking the flow rate of the hydraulic oil entering the lower chamber 111, and when the flow rate of the hydraulic oil detected by the flow meter is larger than a rated flow rate, the switching valve is made to open to reduce the increase in the speed of the striking piston 12 caused by the increase in the flow rate. However, it is difficult to form a sensitive and closed control such as these in combination with the measurement of the flow rate, which causes the hydraulic oil entering the lower chamber 111 to fluctuate the drive of the percussion piston 12, i.e. it is not possible to increase the volume of the lower chamber 111 steadily.
Two preferred configurations of the striking device will now be described, which are advantageous in the configuration of the reducing mechanism 40.
Example 1
As shown in fig. 1 to 8, the speed reduction mechanism 40 of the impact device according to the present embodiment includes: the receiving cavity 41, the plug disc 45, the elastic biasing member 42, the first flow guide channel 43 and the second flow guide channel 44. The receiving chamber 41 is formed in the striker piston 12 and is axially guided, and a lower end of the receiving chamber 41 is communicated with a lower chamber 111 of the cylinder 11 through a first guide passage 43, and an upper end of the receiving chamber 41 is communicated with an upper chamber 112 of the cylinder 11 through a second guide passage 44. A plug disk 45 is arranged in the receiving chamber 41, which plug disk 45 is brought into sealing engagement with the wall of the receiving chamber 41 by means of a sealing or sealing structure. The resilient biasing member 42 may be embodied as a compression spring, the resilient biasing member 42 being arranged in the receiving cavity 41 above the plug disc 45 for pushing the plug disc 45 downwards.
In this embodiment, the pre-load of the resilient biasing member 42 on the plug disc 45 is configured to: when the actual pressure of the hydraulic oil in the lower cavity 111 of the cylinder 11 is smaller than the rated pressure, the pre-tightening force of the elastic biasing member 42 on the plug disc 45 causes the plug disc 45 to stop at the lower end of the accommodating cavity 41; when the actual pressure of the hydraulic oil in the lower cavity 111 of the cylinder 11 exceeds the rated pressure, the hydraulic oil in the lower cavity 111 can overcome the pre-tightening force of the elastic biasing element 42 on the plug disc 45 to move the plug disc 45 upward.
It should be understood that: the flow rate of the hydraulic oil entering the lower cavity 111 and the pressure of the hydraulic oil in the lower cavity 111 have a certain corresponding relationship, that is, the pressure in the lower cavity 111 can reflect the flow rate entering the lower cavity 111. Therefore, when the actual pressure in the lower chamber 111 is greater than the rated pressure, it is said that the actual flow rate of the hydraulic oil into the lower chamber 111 is also greater than the rated flow rate.
As can be seen from the above description, when the actual pressure reflecting the actual flow rate is greater than the rated pressure, the receiving chamber 41 below the plug 45 is increased (from zero) under the pressure, which causes a portion of the hydraulic oil in the lower chamber 111 of the cylinder 11 to enter the receiving chamber 41 through the first diversion passage 43, so that the portion of the hydraulic oil is not used for increasing the volume of the lower chamber 111 and thus not used for contributing to the speed increase of the percussion piston 12, as shown in fig. 3 and 4. In short, part of the hydraulic oil is allowed to enter the receiving chamber 41 to counteract part of the flow difference (actual flow and rated flow), thereby counteracting the acceleration of the upward movement of the percussion piston 12 (or counteracting the speed difference).
The procedure for moving up the percussion piston 12 in the percussion device of the embodiment is described below:
as shown in fig. 1 and fig. 2, when the actual flow rate of the hydraulic oil entering the lower chamber 111 is the rated flow rate, the pressure of the hydraulic oil in the lower chamber 111 is the rated pressure, at this time, the elastic biasing member 42 always makes the plug disc 45 abut against the lower end of the accommodating chamber 41, at this time, the hydraulic oil entering the lower chamber 111 is all used for increasing the volume of the lower chamber 111 to be all used for driving the percussion piston 12 to move up, and during the moving up, the percussion piston 12 is at the rated speed, which enables the reversing valve 50 to obtain sufficient switching time, and the percussion piston 12 can normally operate as in the above case.
As shown in fig. 3 and 4, when the actual flow rate of the hydraulic oil entering the lower chamber 111 is greater than the rated flow rate, the actual pressure of the hydraulic oil in the lower chamber 111 is greater than the rated pressure, and at this time, the hydraulic oil overcomes the pre-tightening force of the elastic biasing element 42 to move the plug disc 45 upward so as to allow a part of the hydraulic oil to enter the accommodating chamber 41, which inevitably reduces the actual speed of the percussion piston 12.
As shown in fig. 5 and 6, when the percussion piston 12 passes the preset position (referred to as the intermediate position in the background art) in the above state, the actual speed of the percussion piston 12 is reduced, so that the time for passing the preset position is sufficient to enable the reversing valve 50 to reverse.
As shown in fig. 7 and 8, when the direction change valve 50 is completely changed, the hydraulic oil supplied from the hydraulic pump 60 is completely supplied to the upper chamber 112, and at this time, the elastic biasing member 42 is restored to make the plug 45 abut against the lower end of the receiving chamber 41 again.
The advantages of this embodiment are:
1. when the actual flow rate is greater than the rated flow rate, the accommodating cavity 41 is used for accommodating part of the hydraulic oil in the lower cavity 111, so that the hydraulic oil entering the lower cavity 111 is not required to be used for driving the piston, the upward movement speed increasing rate of the impact piston 12 is effectively reduced, and the impact piston 12 is controllable.
2. The damping mechanism 40 of the present embodiment determines whether to damp the velocity of the percussion piston 12 by the pressure in the lower chamber 111, and compared with the method of directly measuring the flow rate, the present embodiment has higher sensitivity of damping the velocity of the percussion piston 12, and can effectively reduce the velocity fluctuation of the percussion piston 12.
3. The receiving cavity 41 is formed in the percussion piston 12, so that the whole percussion device is not enlarged compared with the percussion device in the prior art, and the design is ingenious.
Preferably, the percussion piston 12 comprises an upper plug 122 and a lower plug 121; the lower end of the upper plug 122 extends into the upper end of the lower plug 121 to form a threaded connection, and forms a sealing fit, and is locked by a locking nut 1221 sleeved on the upper plug 122 and tightly abutted to the lower plug 121; wherein: the receiving cavity 41 is defined and formed by the upper plug 122 and the lower plug 121; preferably, the lower plug 121 is formed with a downward stepped surface 1211, and the first flow guide channel 43 extends from the stepped surface 1211 to the lower end of the receiving cavity 41; the second flow passage 44 extends axially upward from the end face of the upper plug 122 and continues through to the upper chamber 112 by extending radially.
Example 2
As shown in fig. 9 to 11, the speed reduction mechanism 40 of the impact device according to the present embodiment includes: a receiving cavity 46, a plug disk 48, a resilient biasing member 47 and a flow directing line. A receiving cavity 46 is formed above the air cavity 31 of the cylinder mechanism 30, the lower end of the receiving cavity 46 is communicated with the air cavity 31, the receiving cavity 46 is axially oriented, a diversion pipeline is connected between the upper end of the receiving cavity 46 and the lower cavity 111 of the cylinder body 11 by a diversion connector, a plug disc is arranged in the receiving cavity 46, and the plug disc is in sealing fit with the cavity wall of the receiving cavity 46 through a sealing element or a sealing structure. The resilient biasing member 47 may be embodied as a compression spring, the resilient biasing member 47 being arranged in the receiving cavity 46 below the plug disc for pushing the plug disc upwards.
In an embodiment, the pre-load of the resilient biasing member 47 on the plug disc 48 is configured to: when the actual pressure of the hydraulic oil in the lower cavity 111 of the cylinder 11 is smaller than the rated pressure, the pre-tightening force of the elastic biasing element 47 on the plug disc 48 causes the plug disc 48 to stop at the upper end of the accommodating cavity 46; when the actual pressure of the hydraulic oil in the lower cavity 111 of the cylinder 11 exceeds the rated pressure, the hydraulic oil in the lower cavity 111 can overcome the pre-tightening force of the elastic biasing element 47 on the plug disc 48 through the flow guiding pipeline, so that the plug disc 48 moves downwards.
As can be seen from the above, when the actual pressure reflecting the actual flow rate is greater than the rated pressure, the receiving cavity 46 above the plug 48 is increased under the pressure, which causes a part of the hydraulic oil guiding pipeline in the lower cavity 111 of the cylinder 11 to enter the receiving cavity 46, so that the part of the hydraulic oil is not used for increasing the volume of the lower cavity 111 and further not used for contributing to the speed increase of the percussion piston 12. In short, part of the hydraulic oil is allowed to enter the receiving chamber 46 to counteract part of the flow difference (actual flow and rated flow), thereby counteracting the acceleration of the upward movement of the percussion piston 12 (or counteracting the speed difference).
The advantages of this embodiment are:
1. when the actual flow rate is greater than the rated flow rate, the receiving cavity 46 is used to receive part of the hydraulic oil in the lower cavity 111, so that the hydraulic oil entering the lower cavity 111 is not required to be used for driving the piston, the upward movement speed increase of the impact piston 12 is effectively reduced, and the impact piston 12 is controllable.
2. The damping mechanism 40 of the present embodiment determines whether to damp the velocity of the percussion piston 12 by the pressure in the lower chamber 111, and compared with the method of directly measuring the flow rate, the present embodiment has higher sensitivity of damping the velocity of the percussion piston 12, and can effectively reduce the velocity fluctuation of the percussion piston 12.
3. The particular advantages of this embodiment over embodiment 1 are distinguished by:
the hydraulic oil enters the accommodating cavity 46 above the plug disc 48, so that the accommodating cavity 46 above the plug disc 48 is enlarged, and the downward movement of the plug disc 48 has a compression effect on the gas in the gas cavity 31, so that after the upward movement of the impact piston 12 is stopped, the compression degree of the gas in the gas cavity 31 is larger, and the impact speed of the impact piston 12 is larger.
From the energy conversion perspective, when the actual flow rate provided by the hydraulic pump 60 is greater than the rated flow rate, the energy of the hydraulic oil provided by the hydraulic pump tends to increase, and the increased energy is converted into potential energy of gas by pushing against the plug disc 48 to make the plug disc 48 compress the gas in the gas chamber 31, so that the increased energy is converted into impact energy of the impact piston 12.
The invention also discloses a rock drilling device, which comprises a movable carrier and the impacting device, wherein the impacting device is arranged on the movable carrier and is driven by the movable carrier to change the operation position.
Moreover, although exemplary embodiments have been described herein, the scope of the present invention includes any and all embodiments based on the present invention with equivalent elements, modifications, omissions, combinations (e.g., of various embodiments across), adaptations or alterations. The elements of the claims are to be interpreted broadly based on the language employed in the claims and not limited to examples described in the present specification or during the prosecution of the application, which examples are to be construed as non-exclusive. It is intended, therefore, that the specification and examples be considered as exemplary only, with a true scope and spirit being indicated by the following claims and their full scope of equivalents.
The above description is intended to be illustrative and not restrictive. For example, the above-described examples (or one or more versions thereof) may be used in combination with each other. For example, other embodiments may be used by those of ordinary skill in the art upon reading the above description. In addition, in the above-described embodiments, various features may be grouped together to streamline the disclosure. This should not be interpreted as an intention that a disclosed feature not claimed is essential to any claim. Rather, inventive subject matter may lie in less than all features of a particular disclosed embodiment. Thus, the following claims are hereby incorporated into the detailed description as examples or embodiments, with each claim standing on its own as a separate embodiment, and it is contemplated that these embodiments may be combined with each other in various combinations or permutations. The scope of the invention should be determined with reference to the appended claims, along with the full scope of equivalents to which such claims are entitled.
The above embodiments are only exemplary embodiments of the present invention, and are not intended to limit the present invention, and the scope of the present invention is defined by the claims. Various modifications and equivalents may be made by those skilled in the art within the spirit and scope of the present invention, and such modifications and equivalents should also be considered as falling within the scope of the present invention.
Claims (5)
1. The utility model provides an impacting device installs on removing the carrier, its characterized in that includes:
the hydraulic cylinder mechanism comprises a cylinder body and an impact piston arranged in the cylinder body;
a drill rod provided at a lower end of the cylinder block;
a cylinder mechanism provided at an upper end of the cylinder block;
a hydraulic pump for supplying hydraulic oil to the cylinder block;
a direction change valve connected between the cylinder and the hydraulic pump, the hydraulic pump being configured to drive the striking piston to move up and down by switching the direction change valve in a selective manner;
the speed reduction mechanism is used for reducing the speed difference between the actual speed and the rated speed of the impact oil cylinder caused by the flow difference between the actual flow and the rated flow when the actual flow of the hydraulic oil entering the lower cavity of the cylinder body and used for driving the impact piston to move upwards is larger than the rated flow;
the speed reduction mechanism reduces the speed difference of the percussion piston by reducing the amount of hydraulic oil in the lower chamber that contributes to the upward movement of the percussion piston;
the speed reduction mechanism reducing the amount of hydraulic oil in the chamber to contribute to upward movement of the percussion piston in dependence on the actual pressure in the lower chamber;
the speed reduction mechanism includes:
a receiving chamber formed in the percussion piston;
the plug disc is arranged in the accommodating cavity and can vertically move along the accommodating cavity;
a resilient biasing member for urging the plug disc downwardly;
the first flow guide channel is used for communicating the lower cavity with the accommodating cavity below the plug disc;
the second flow guide channel is used for communicating an upper cavity of the cylinder body with the accommodating cavity above the plug disc; wherein:
when the actual pressure in the lower cavity is smaller than the rated pressure, the elastic biasing piece is used for enabling the plug disc to stop at the lower end of the accommodating cavity;
when the actual pressure in the lower cavity is greater than the rated pressure, the hydraulic oil in the lower cavity pushes the plug disc to move upwards through the first flow guide channel, so that the volume of the accommodating cavity below the plug disc is increased, and the hydraulic oil flowing in through the first flow guide channel is accommodated.
2. A percussion device according to claim 1, in which the percussion piston comprises an upper plug and a lower plug; the lower end of the upper plug column extends into the upper end of the lower plug column to form threaded connection, and is in sealing fit with the upper plug column and tightly pressed against the lower plug column to be locked by virtue of a locking nut sleeved on the upper plug column; wherein:
the containing cavity is formed by the upper plug column and the lower plug column in a limiting mode.
3. The percussion device according to claim 2, wherein the lower plug is formed with a downwardly facing stepped surface, and the first guide passage extends obliquely from the stepped surface to a lower end of the receiving chamber; the second flow guide channel extends upwards from the end face of the upper plug column in the axial direction and continues to penetrate to the upper cavity through radial extension.
4. The percussion device of claim 1, wherein the resilient biasing member is a compression spring.
5. A rock drilling rig comprising a mobile carrier, characterized by a percussion device according to any one of claims 1 to 4 mounted on the mobile carrier and driven by the mobile carrier to change the working position.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910368803.5A CN110107220B (en) | 2019-05-05 | 2019-05-05 | Percussion device and rock drilling equipment |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910368803.5A CN110107220B (en) | 2019-05-05 | 2019-05-05 | Percussion device and rock drilling equipment |
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| CN110107220A CN110107220A (en) | 2019-08-09 |
| CN110107220B true CN110107220B (en) | 2020-12-04 |
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| CN201910368803.5A Active CN110107220B (en) | 2019-05-05 | 2019-05-05 | Percussion device and rock drilling equipment |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5871081A (en) * | 1981-07-10 | 1983-04-27 | エタブリスマン・モンタベル | Impact device operated by pressure fluid |
| SU1028840A1 (en) * | 1980-07-27 | 1983-07-15 | Научно-Исследовательский Горнорудный Институт | Hydraulic percussive mechanism for drilling machines |
| CN2189199Y (en) * | 1994-04-14 | 1995-02-08 | 地质矿产部勘探技术研究所 | Heavy and energy saving hydraulic hammer for drilling |
| CN102410275A (en) * | 2011-09-08 | 2012-04-11 | 常熟理工学院 | Valve-control-free self-flow-distribution gas and liquid combined acting impactor |
| EP2076364A4 (en) * | 2006-10-25 | 2012-11-14 | Atlas Copco Constr Tools Ab | Hydraulic impact device |
| CN203584297U (en) * | 2013-10-24 | 2014-05-07 | 荣成中磊石材有限公司 | Drill rod buffering and positioning device of hydraulic rock drill |
| CN205743690U (en) * | 2016-05-23 | 2016-11-30 | 王向军 | A kind of hydraulic gate |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE528081C2 (en) * | 2004-08-25 | 2006-08-29 | Atlas Copco Constr Tools Ab | Hydraulic impact mechanism |
-
2019
- 2019-05-05 CN CN201910368803.5A patent/CN110107220B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1028840A1 (en) * | 1980-07-27 | 1983-07-15 | Научно-Исследовательский Горнорудный Институт | Hydraulic percussive mechanism for drilling machines |
| JPS5871081A (en) * | 1981-07-10 | 1983-04-27 | エタブリスマン・モンタベル | Impact device operated by pressure fluid |
| CN2189199Y (en) * | 1994-04-14 | 1995-02-08 | 地质矿产部勘探技术研究所 | Heavy and energy saving hydraulic hammer for drilling |
| EP2076364A4 (en) * | 2006-10-25 | 2012-11-14 | Atlas Copco Constr Tools Ab | Hydraulic impact device |
| CN102410275A (en) * | 2011-09-08 | 2012-04-11 | 常熟理工学院 | Valve-control-free self-flow-distribution gas and liquid combined acting impactor |
| CN203584297U (en) * | 2013-10-24 | 2014-05-07 | 荣成中磊石材有限公司 | Drill rod buffering and positioning device of hydraulic rock drill |
| CN205743690U (en) * | 2016-05-23 | 2016-11-30 | 王向军 | A kind of hydraulic gate |
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| Publication number | Publication date |
|---|---|
| CN110107220A (en) | 2019-08-09 |
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Effective date of registration: 20230423 Address after: No. 203-113 Xiaoting Avenue, Xiaoting District, Yichang City, Hubei Province, 443000 Patentee after: Hubei Chunzhijing Ecological Technology Co.,Ltd. Address before: 443002 No. 8, University Road, Yichang, Hubei Patentee before: CHINA THREE GORGES University |