CN207569009U - Rock drill and its Automatic hydraulic control system - Google Patents
Rock drill and its Automatic hydraulic control system Download PDFInfo
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- CN207569009U CN207569009U CN201721410438.2U CN201721410438U CN207569009U CN 207569009 U CN207569009 U CN 207569009U CN 201721410438 U CN201721410438 U CN 201721410438U CN 207569009 U CN207569009 U CN 207569009U
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Abstract
The utility model discloses a kind of Automatic hydraulic control systems of rock drill, including pilot control oil sources, impact oil sources, turn round oil sources, promote oil sources, percussion mechanism, rotary motor and propelling cylinder, propulsion throttle valve is provided between propelling cylinder rod chamber and propulsion oil sources, the both ends of throttle valve is promoted to be respectively communicated with two hydraulic control hydraulic fluid ports of the first hydraulic control proportional reversing valve, pipeline between the actuator port connection pilot control oil sources and percussion power pilot operated valve device of first hydraulic control proportional reversing valve, first hydraulic control proportional reversing valve can be according to the pressure change switch operating position for promoting throttle valve both ends, to change the on off operating mode of the first hydraulic control proportional reversing valve and fuel tank.It is accurate to obtain geology state by the pressure change of hydraulic oil, and then accurate quickly control device makes corresponding change, realizes automation control by hydraulic control, can prevent to stability and high efficiency card pricker.The invention also discloses a kind of rock drills for including above-mentioned Automatic hydraulic control system.
Description
Technical field
The utility model is related to rock drilling equipment field, more particularly to a kind of Automatic hydraulic control system of rock drill.This
Outside, the utility model further relates to a kind of rock drill for including above-mentioned Automatic hydraulic control system.
Background technology
Hydraulic gate is the important hard rock drilling equipment in modern drill+blast tunnel construction, due to cutting rate
Soon, rock drilling power is big, construction efficiency is high, noise radiation is small and easy the advantages that realizing automation, occupies the master in rock drill market
Lead status.Hydraulic gate is a kind of rotary impact type drilling rock drill, and when carrying out rock drilling operation, rock drill propelling pressure is too
The small sky that will generate is beaten, and not only rock penetration performance reduces, and the service life of rock drill will also shorten；Rock drill propelling pressure is easy when too big
Bore bit is made to deviate target location, while the abrasion that will also accelerate drill bit.In addition, rock drill drives more drilling rods to carry out deep and long hole chisel
Rock operation, rock geology complicated condition is changeable, such as quality unevenness, crack, lava, and the mechanics nonuniformity of rock easily makes drill bit
Deviate drilling target track, cause card pricker phenomenon, meanwhile, the not smooth also easy card pricker of rock quarrel discharge in drilling, therefore, card pricker phenomenon
The randomness of appearance is stronger.To meet the rock drilling operation under the conditions of a variety of rock geologies, rock drill hydraulic control system must have
It is standby that automatic rock drilling and anti-sticking pricker ability are carried out according to geomechanical condition, should especially have pre- in advance to the card pricker situation that will occur
It surveys and handles.
In the prior art using method of controlling switch, due to being digital output modul form, propulsive force cannot be according to revolution
The variation of the moment of resistance and change, anti-sticking pricker is ineffective, particularly in the poor rock stratum of geological conditions during rock drilling bore operation,
Commutation loop is promoted frequently to commutate always, rock penetration performance is low.
Therefore, how to provide it is a kind of can stability and high efficiency to prevent the Automatic hydraulic control system of card pricker be people in the art
The current technical issues that need to address of member.
Utility model content
The purpose of this utility model is to provide a kind of Automatic hydraulic control system of rock drill, can prevent to stability and high efficiency
Card pricker.The another object of the utility model is to provide a kind of rock drill for including above-mentioned Automatic hydraulic control system, can stablize
Efficiently prevent card pricker.
In order to solve the above technical problems, the utility model provides a kind of Automatic hydraulic control system of rock drill, including elder generation
It leads control oil sources, impact oil sources, revolution oil sources, promote oil sources, percussion mechanism, rotary motor and propelling cylinder, the impact oil
Percussion power pilot operated valve device is provided between the oil inlet of the oil outlet in source and the percussion mechanism, the percussion power pilot operated valve device
Hydraulic control mouth connects the pilot control oil sources, and propulsion throttle valve is provided between the propelling cylinder rod chamber and propulsion oil sources,
The both ends for promoting throttle valve are respectively communicated with two hydraulic control hydraulic fluid ports of the first hydraulic control proportional reversing valve, the first hydraulic control ratio
One actuator port of reversal valve connects the pipeline between the pilot control oil sources and the percussion power pilot operated valve device, and described the
Another actuator port connection fuel tank of one hydraulic control proportional reversing valve, the first hydraulic control proportional reversing valve can be pushed away according to described
Into the pressure change switch operating position at throttle valve both ends, to change the break-make shape of the first hydraulic control proportional reversing valve and fuel tank
State.
Preferably, it is provided with revolution throttling between the oil outlet of the revolution oil sources and the oil inlet of the rotary motor
Valve, the both ends of the rotary throttle are respectively communicated with two hydraulic control hydraulic fluid ports of the second hydraulic control proportional reversing valve, second hydraulic control
The oil inlet and oil return opening of proportional reversing valve are respectively communicated with the propulsion oil sources, two works of the second hydraulic control proportional reversing valve
The rod chamber and rodless cavity of the propelling cylinder are respectively communicated with as hydraulic fluid port, the second hydraulic control proportional reversing valve can be according to described
The pressure change switch operating position at rotary throttle both ends, to change the working condition of the propelling cylinder.
Preferably, guide is also disposed between the pilot control oil sources and the percussion power pilot operated valve device and starts electricity
Control reversal valve, the first threeway hydraulic control pressure reducing valve and first throttle valve, the hydraulic control mouth connection institute of the first threeway hydraulic control pressure reducing valve
State the rodless cavity of propelling cylinder, the exit of the first throttle valve is additionally provided with that guide's pressure release of fuel tank is automatically controlled to change for connecting
To valve and it is low wash a mouthful overflow valve open, be additionally provided with low pressure relief valve between the first hydraulic control proportional reversing valve and fuel tank.
Preferably, between the hydraulic control mouth of described second hydraulic control proportional reversing valve one end and one end of the rotary throttle according to
It is secondary to be provided with second throttle, auxiliary hydraulic control proportional reversing valve, the first auxiliary electric control reversal valve, the second hydraulic control ratio commutation
The second threeway hydraulic control pressure reducing valve and are disposed between the hydraulic control mouth of the valve other end and the other end of the rotary throttle
Two auxiliary electric control reversal valves.
Preferably, it is provided with third threeway between the rodless cavity of the propelling cylinder and the second hydraulic control proportional reversing valve
Hydraulic control pressure reducing valve.
Preferably, the percussion mechanism includes impact oil cylinder, impact reversal valve and accumulator.
Preferably, the first hydraulic control proportional reversing valve is specially two-position two-way hydraulic control proportional reversing valve, second liquid
It is specially 3-position 4-way hydraulic control proportional reversing valve to control proportional reversing valve, and it is specially two-position three way that the guide, which starts electric control reversing valve,
Electric control reversing valve, guide's pressure release electric control reversing valve are specially bi-bit bi-pass electric control reversing valve, and the auxiliary hydraulic control ratio is changed
It is specially two-position two-way hydraulic control proportional reversing valve to valve, the first auxiliary electric control reversal valve and second auxiliary electric control commutation
Valve is specially two-position three way electric control reversing valve.
Preferably, the propulsion oil sources also connects the propelling cylinder by automatically controlled proportional reversing valve.
Preferably, the automatically controlled proportional reversing valve is specially the automatically controlled proportional reversing valve of 3-position 4-way.
The utility model also provides a kind of rock drill, including Automatic hydraulic control system, which is characterized in that the hydraulic pressure is certainly
Autocontrol system is specially the Automatic hydraulic control system described in above-mentioned any one.
The utility model provides a kind of Automatic hydraulic control system of rock drill, including pilot control oil sources, impact oil sources,
Turn round oil sources, promote oil sources, percussion mechanism, rotary motor and propelling cylinder, impact oil sources oil outlet and percussion mechanism into
Percussion power pilot operated valve device, the hydraulic control mouth connection pilot control oil sources of percussion power pilot operated valve device, propelling cylinder are provided between hydraulic fluid port
Propulsion throttle valve is provided between rod chamber and propulsion oil sources, the both ends of throttle valve is promoted to be respectively communicated with the commutation of the first hydraulic control ratio
Two hydraulic control hydraulic fluid ports of valve, the actuator port connection pilot control oil sources and percussion power liquid of the first hydraulic control proportional reversing valve
Control the pipeline between valve, another actuator port connection fuel tank of the first hydraulic control proportional reversing valve, the first hydraulic control proportional reversing valve
It can be according to the pressure change switch operating position for promoting throttle valve both ends, to change the logical of the first hydraulic control proportional reversing valve and fuel tank
Disconnected state.
When encountering empty geology during rock drilling, propelling cylinder stretches out speed and stretches out speed much larger than normal promote, and pushes away
Become larger into throttle valve pressure at two ends difference, and then the first hydraulic control proportional reversing valve is controlled to open connection fuel tank, make pilot control oil sources
In hydraulic oil flow back to fuel tank, pressure is lower at the hydraulic control mouth of percussion power pilot operated valve device, reduces the fuel feeding to percussion mechanism, reduce
Surge makes rock drill be in tip-tap to convince by patient analysis to poroid state, and the first hydraulic control proportional reversing valve is opened when drill bit bumps against next wall surface
Degree tapers into, and surge increase, rock drill reverts to normal trepanning rock drilling state.
It is accurate to obtain geology state by the pressure change of hydraulic oil, and then accurate quickly control device is made accordingly
Change, automation control is realized by hydraulic control, can prevent to stability and high efficiency card pricker.
The utility model also provides a kind of rock drill for including above-mentioned Automatic hydraulic control system, since above-mentioned hydraulic pressure is automatic
Control system has above-mentioned technique effect, and above-mentioned rock drill should also have same technique effect, no longer be discussed in detail herein.
Description of the drawings
Fig. 1 is a kind of hydraulic principle of specific embodiment of Automatic hydraulic control system provided by the utility model
Figure.
Specific embodiment
The core of the utility model is to provide a kind of Automatic hydraulic control system of rock drill, can prevent to stability and high efficiency
Card pricker.Another core of the utility model is to provide a kind of rock drill for including above-mentioned Automatic hydraulic control system, can stablize
Efficiently prevent card pricker.
In order to which those skilled in the art is made to more fully understand the utility model, below in conjunction with the accompanying drawings and it is embodied
The utility model is described in further detail for mode.
It please refers to Fig.1, Fig. 1 is a kind of specific embodiment of Automatic hydraulic control system provided by the utility model
Hydraulic schematic diagram.
Specific embodiment of the present invention provides a kind of Automatic hydraulic control system of rock drill, including pilot control oil
Source 1, revolution oil sources 3, promotes oil sources 4, percussion mechanism 5, rotary motor 6 and propelling cylinder 7, wherein percussion mechanism at impact oil sources 2
5 include impact oil cylinder, impact reversal valve and accumulator.Total a hydraulic pump and fuel tank can also be used as oil sources.
It impacts between the oil outlet of oil sources 2 and the oil inlet 5c of percussion mechanism 5 and is provided with percussion power pilot operated valve device 8, impact
The hydraulic control mouth 8c connection pilot controls oil sources 1 of power pilot operated valve device 8, is provided between 7 rod chamber of propelling cylinder and propulsion oil sources 4 and pushes away
Into throttle valve 9, the both ends of throttle valve 9 is promoted to be respectively communicated with two hydraulic control hydraulic fluid ports of the first hydraulic control proportional reversing valve 10, the first liquid
The pipeline between the actuator port 10a connection pilot controls oil sources 1 of proportional reversing valve 10 and percussion power pilot operated valve device 8 is controlled,
Another actuator port 10b connection fuel tanks of first hydraulic control proportional reversing valve 10, the first hydraulic control proportional reversing valve 10 being capable of basis
The pressure change switch operating position at 9 both ends of throttle valve is promoted, to change the break-make shape of the first hydraulic control proportional reversing valve 10 and fuel tank
State.
It turns round between the oil outlet of oil sources 3 and the oil inlet 6a of rotary motor 6 and is provided with rotary throttle 11, revolution throttling
The both ends of valve 11 are respectively communicated with two hydraulic control hydraulic fluid ports of the second hydraulic control proportional reversing valve 12, the second hydraulic control proportional reversing valve 12 into
Hydraulic fluid port 12p and oil return opening 12t, which is respectively communicated with, promotes oil sources 4, the actuator port 12a connections of the second hydraulic control proportional reversing valve 12
The rod chamber of propelling cylinder 7, the second hydraulic control proportional reversing valve 12 another actuator port 12b connection propelling cylinder 7 without bar
Chamber, the second hydraulic control proportional reversing valve 12 can be pushed away according to the pressure change switch operating position at 11 both ends of rotary throttle with changing
Into the working condition of oil cylinder 7.
Guide is also disposed in order to realize accurate control, between pilot control oil sources 1 and percussion power pilot operated valve device 8 to open
Dynamic electric control reversing valve 13, the first threeway hydraulic control pressure reducing valve 14 and first throttle valve 15, the hydraulic control of the first threeway hydraulic control pressure reducing valve 14
Mouth 14c connects the rodless cavity of propelling cylinder 7, and the guide for connecting fuel tank is additionally provided at the outlet 15b of first throttle valve 15
Pressure release electric control reversing valve 16 and it is low wash mouthful overflow valve 17 open, be additionally provided with low pressure between the first hydraulic control proportional reversing valve 10 and fuel tank
Overflow valve 18.
It is set gradually between the hydraulic control mouth of 12 one end of the second hydraulic control proportional reversing valve and one end 11b of rotary throttle 11
There are second throttle 19, auxiliary hydraulic control proportional reversing valve 20, the first auxiliary electric control reversal valve 21, the second hydraulic control proportional reversing valve 12
The second threeway hydraulic control pressure reducing valve 22 and are disposed between the hydraulic control mouth of the other end and the other end 11a of rotary throttle 11
Two auxiliary electric control reversal valves 23.Third threeway is provided between the rodless cavity of propelling cylinder 7 and the second hydraulic control proportional reversing valve 12
Hydraulic control pressure reducing valve 24.
Above-mentioned each valve is the function in order to which rock drill is better achieved, and according to circumstances can increase and decrease or change above-mentioned each valve
Door, specifically, the first hydraulic control proportional reversing valve 10 specially two-position two-way hydraulic control proportional reversing valve, the second hydraulic control proportional reversing valve
12 be specially 3-position 4-way hydraulic control proportional reversing valve, and it is specially two-position three way electric control reversing valve that guide, which starts electric control reversing valve 13,
Guide's pressure release electric control reversing valve 16 is specially bi-bit bi-pass electric control reversing valve, and auxiliary hydraulic control proportional reversing valve 20 is specially two
Two-way hydraulic control proportional reversing valve, the first auxiliary electric control reversal valve 21 and the second auxiliary electric control reversal valve 23 are specially two-position three way electricity
Reversal valve is controlled, the type of each valve also can be according to circumstances adjusted, be within the protection scope of the utility model.
On the basis of the Automatic hydraulic control system provided in above-mentioned each specific embodiment, oil sources 4 is promoted also to pass through electricity
It controls proportional reversing valve 25 and connects propelling cylinder 7, body is the automatically controlled proportional reversing valve of 3-position 4-way.
When rock drill is in off working state, guide's startup electric control reversing valve 13 is not charged, the pressure of pilot control oil sources
Oil cannot depressurize the hydraulic control mouth 8c for flowing to percussion power pilot operated valve device 8 through the first threeway hydraulic control pressure reducing valve 14, at this point, guide starts electricity
The actuator port 13a and oil return opening 13t of control reversal valve 13 are connected and oil return box, the hydraulic control mouth 8c pressure of percussion power pilot operated valve device 8
Close to zero, system is in low and rushes state.
When rock drill is in bore state, the pressure oil of pilot control oil sources flows to after guide starts electric control reversing valve 13
First threeway hydraulic control pressure reducing valve 14, the pressure of 7 rodless cavity side of propelling cylinder are fed back to the liquid of the first threeway hydraulic control pressure reducing valve 14
Mouth 14c is controlled, the output pressure of the first threeway hydraulic control pressure reducing valve 14 is determined by the pressure of hydraulic control mouth 14c.Pressure oil is through the first threeway
Hydraulic control pressure reducing valve 14 depressurize after again by flowing to the hydraulic control mouth 8c of percussion power pilot operated valve device 8 after first throttle valve 15.Percussion power
Pilot operated valve device 8 is opened, and the pressure oil of impact oil sources is made to enter percussion mechanism 5, realizes impact operation.
When rock drill is in the tip-tap trepanning stage, surge requires relatively low, 16 band of the electric control reversing valve of guide's pressure release at this time
Electricity, the pressure oil of pilot control oil sources 1 start electric control reversing valve 13, the first threeway hydraulic control pressure reducing valve 14, first throttle through guide
Fuel tank is flowed back to from low mouthful overflow valve 17 of washing open after valve 15 and guide's pressure release electric control reversing valve 16, rock drill is in low and washes guiding open
Poroid state.
The rock drill impact system, the 10-a mouths of solenoid directional control valve 10 are connected to the 17-p mouths of external control pressure reducing valve 17,
The outside control mouth 17-c of external control pressure reducing valve 17 is connected to the rodless cavity oil circuit of propelling cylinder, 17-a mouths and the flow controller 18 of pressure reducing valve 17
The connection of 18-a mouths, the 18-b mouths of flow controller 18 respectively with the 11-a of solenoid directional control valve 11 mouths and hydraulic control proportional direction valve 12
12-a mouthfuls of connections, the 11-b mouths of solenoid directional control valve 11 and the low 4-a mouths connection for rushing overflow valve 4, the 12- of hydraulic control proportional direction valve 12
B mouthfuls connect with the 5-a mouths of low-pressure overflow valve 5, the 10-t mouths of solenoid directional control valve 10 and the 11-t mouths of solenoid directional control valve 11, hydraulic control
The 12-t mouths of proportional direction valve 12 are connected and are connected to fuel tank together.
When bit of rock drilling machine pierces a cavity, since load is small in front of drill bit, drill bit will be quickly propelled until in cavity
Rock wall surface, the usual out-of-flatness of rock wall surface, drill bit is hit will generate a component, structure after empty rock wall surface in radial direction
The relatively low elongate drill rod of rigidity, by flexural deformation, makes drill bit deviate predetermined drilling trace under radial load effect.When drill bit is inclined
Crooked stem deformation will be blocked after creeping into certain depth from desired trajectory, at this point, drilling rod can neither promote, can not be retracted,
Produce card pricker phenomenon.When encountering empty geology, propelling cylinder 7 stretches out speed and stretches out speed much larger than normal promote, this
When promote 9 upstream and downstream pressure differential of throttle valve become larger, upstream and downstream pressure feeds back to 10 both ends of the first hydraulic control proportional reversing valve respectively,
The first hydraulic control proportional reversing valve 10 is driven to be gradually opened, at this point, flowing to the pressure of 8 hydraulic control mouth 8c of percussion power pilot operated valve device originally
Oil flows back to fuel tank through low pressure relief valve 18, and 8 aperture of percussion power pilot operated valve device becomes smaller, and hydraulic oil cannot be introduced into percussion mechanism 5, impact
Pressure is lower, and rock drill is in tip-tap and convinces by patient analysis to poroid state.Load on drill bit is acted on when drill bit bumps against next wall surface again
Revert to it is larger, promote 9 upstream and downstream pressure differential of throttle valve become smaller, driving the first hydraulic control proportional reversing valve 10 progressively close off, impact
Pressure recovery normality at 8 hydraulic control mouth 8c of power pilot operated valve device, surge gradually increase, and rock drill slowly reverts to normal trepanning
Rock drilling state.
The pressure oil that revolution oil sources 3 provides flows to the entrance 6a of rotary motor 6, and pass through back after flowing through rotary throttle 11
Turn the outlet of motor 6 6b and flow directly into fuel tank.6 load of rotary motor is fed back to by the pressure differential before and after rotary throttle 11
Second hydraulic control proportional reversing valve 12 makes the second hydraulic control proportional reversing valve 12 automatically control second according to 6 load of rotary motor
The aperture of hydraulic control proportional reversing valve 12, so as to fulfill propelling cylinder 7 into the control function of flow.
11 one end hydraulic fluid port 11a of rotary throttle is connected with the oil inlet 23p of the second auxiliary electric control reversal valve 23, and second is auxiliary
The oil return opening 23t of electric control reversing valve 23 is helped to be connected to fuel tank, the second auxiliary electric control together with the oil return opening 11t of rotary throttle 11
23 actuator port 23a of reversal valve is connected to the oil inlet of the second threeway hydraulic control pressure reducing valve 22, the second threeway hydraulic control pressure reducing valve 22
Oil return opening is connected to fuel tank, and the actuator port of the second threeway hydraulic control pressure reducing valve 22 is connected to the one of the second hydraulic control proportional reversing valve 12
Hold hydraulic control mouth 12 II.
The other end hydraulic fluid port 11b of rotary throttle 11 is connected to the oil inlet 21p of the first auxiliary electric control reversal valve 21, the
The actuator port 21a of one auxiliary electric control reversal valve 21 is auxiliary with an actuator port 20a of hydraulic control proportional reversing valve 20 is assisted to be connected
Another actuator port 20b connections 19 1 hydraulic fluid port 19a of second throttle of hydraulic control proportional reversing valve 20 are helped, from second throttle
19 19b mouthfuls of another hydraulic fluid port respectively with the other end hydraulic control mouth 12 I of rotary throttle 12 and an actuator port of flow controller
It is connected, another actuator port connection fuel tank of flow controller.Above-mentioned component forms a hydraulic bridge type circuit, plays and stablizes second
The effect of 12 hydraulic control mouth pressure of hydraulic control proportional reversing valve.
When rotary motor 6, which loads, to be reduced, rotary motor speed becomes larger, by the fluid of rotary throttle 11 before it
Generate larger pressure differential afterwards, at this point, the pressure oil at the Upstream Interface 11a of rotary throttle 11 through each valve function in second
II end pilot port of hydraulic control proportional reversing valve 12, value are more than pressure value of the I end pilot port after throttling, and the second hydraulic control ratio is changed
II end on-state is in valve 12, the fluid in circuit is promoted to be flowed by the oil inlet 12p of the second hydraulic control proportional reversing valve 12
The oil inlet 24p of third threeway hydraulic control pressure reducing valve 24 is flowed to after entering by 12b mouthfuls of an actuator port, fluid is after decompression by 24a
Mouth flows to the rodless cavity of propelling cylinder 7, and the fluid of rod chamber flows to the second hydraulic control ratio after flowing through the propulsion throttle valve 9 in oil return line
Another actuator port 12a of example reversal valve 12, and flow back to fuel tank from oil return opening 12t.
When rotary motor 6 loads very big and rotational speed close to zero, the logical oil mass of rotary throttle 11 is smaller to be made
Its front and rear pressure differential is also smaller, at this point, the pressure oil Upstream Interface 11a of rotary throttle 11 at is made after each valve depressurizes
For II end pilot port of the second hydraulic control proportional reversing valve 12, value is less than pressure value of the I end pilot port after throttling, and second
Hydraulic control proportional reversing valve 12 is in I end on-state, promotes the fluid in circuit by the another of the second hydraulic control proportional reversing valve 12
A actuator port 12a mouthfuls of rod chambers for flowing to propelling cylinder 7, the fluid of rodless cavity flow through the list of third threeway hydraulic control pressure reducing valve 24
The 12b mouths of the second hydraulic control proportional reversing valve 12 are flowed back to after valve, and are flowed back to from the oil return opening 12t of the second hydraulic control proportional reversing valve 12
Fuel tank.
And 12 spool design of the second hydraulic control proportional reversing valve into certain degree of overlapping, i.e. it is a bit of to deviate centre position for spool
Inside no fluid passes through.When the fast card pricker of rock drill, propelling cylinder 7 cannot promote further along.But drill bit is also continuous at this time
Ground shock waves rock wall surface, and the rock wall surface before bit of rock drilling machine is rigid, in the continuous impact process of drill bit, rock is not by
Disconnected to peel off, chisel edge will constantly become smaller with rock wall surface contact surface after rock peels off, and rock drill is caused to turn round frictional resistance moment
Constantly become smaller, rock drill rotary motor 6 restores the fast rotation of normal operating conditions again, and therefore, rock drill is not in card pricker
Phenomenon.
Propelling cylinder 7 can also realize expanding-contracting action during to ensure that rock drill rotary motor does not rotate, in circuit is promoted simultaneously
The automatically controlled proportional reversing valve 25 that a Median Function is " O " type is joined, an actuator port 25a of automatically controlled proportional reversing valve 25 connects
The rodless cavity of logical propelling cylinder 7, the rod chamber of another actuator port 25b connection propelling cylinders 7 of automatically controlled proportional reversing valve 25,
When rock drill carries out normal drill operation, automatically controlled proportional reversing valve 25 is in middle position, when having other to need, automatically controlled proportional reversing valve
25 are in other working positions.
By having the function of the rock drill Automatic hydraulic control system of ratio, generated when being throttled using rotary throttle 11
Pressure differential control 12 aperture of the second hydraulic control proportional reversing valve, when revolution load is small, rotary motor 6 rotating speed is high, passes through revolution
The flow of throttle valve 11 is big, and the pressure differential before and after rotary throttle 11 also increases therewith at this time.In 6 oil circuit of rock drill rotary motor
11 front and rear sides pressure of rotary throttle be fed back on the spool of the second hydraulic control proportional reversing valve 12 and with the second hydraulic control ratio
Hookean spring inside example reversal valve 12 reaches dynamic balance, make spool aperture and 11 rear and front end pressure differential of rotary throttle into than
Example relationship；Propelling cylinder 7 controls 7 rodless cavity pressure of propelling cylinder to protect without the third threeway hydraulic control pressure reducing valve 24 in chamber bar side oil circuit
It holds as certain value, pressure is also fixed before the second hydraulic control proportional reversing valve 12, makes the second hydraulic control proportional reversing valve 12
It works with third threeway hydraulic control pressure reducing valve 24 1 and forms a hydraulic control proportional reversing valve with pressure compensation, realize basis
The proportional function of controlling fltting speed of pressure difference before and after rotary throttle 11 in 6 circuit of rotary motor；Effectively to avoid in stratum
Hole region, which exists, causes rock drill to be fast forwarded through in cavity and make drill bit under radially outward force effect bumping against empty wall surface
Deviate target trajectory, card pricker phenomenon occur, be also additionally arranged in the rod chamber lateral line of propelling cylinder 7 and promote throttle valve 9, from pushing away
Into 9 upstream and downstream pressure force feedback of throttle valve to the first hydraulic control proportional reversing valve 10, percussive pressure is continuously controlled according to fltting speed
Power changes, and makes to drill out a pilot hole in empty wall surface during bit of rock drilling machine shock cavity wall surface with low surge, drilling rod passes through
It is crept into behind cavity along pilot hole direction, avoids card pricker phenomenon occur since drill bit deviates target trajectory.The utility model is specifically real
It is standard hydraulic valve to apply all hydraulic valve in mode, there is no special hydraulic valve piece, system structure it is easy to implement, cost compared with
It is low.
In addition to above-mentioned Automatic hydraulic control system, specific embodiment of the present utility model also provides a kind of including above-mentioned liquid
The rock drill of automatic control system is pressed, refer to the prior art for the structure of other each sections of the rock drill, repeats no more herein.
Rock drill provided by the utility model and its Automatic hydraulic control system are described in detail above.Herein
In apply specific case the principle and embodiment of the utility model be expounded, the explanation of above example is only used
Understand the method and its core concept of the utility model in help.It should be pointed out that for those skilled in the art
For, under the premise of the utility model principle is not departed from, can also to the utility model, some improvement and modification can also be carried out, these
Improvement and modification are also fallen into the protection domain of the utility model claims.
Claims (10)
1. a kind of Automatic hydraulic control system of rock drill, including pilot control oil sources (1), impact oil sources (2), revolution oil sources
(3), oil sources (4), percussion mechanism (5), rotary motor (6) and propelling cylinder (7) are promoted, which is characterized in that the impact oil sources
(2) percussion power pilot operated valve device (8), the percussion power are provided between oil outlet and the oil inlet of the percussion mechanism (5)
The hydraulic control mouth of pilot operated valve device (8) connects the pilot control oil sources (1), propelling cylinder (7) rod chamber with promote oil sources (4) it
Between be provided with promote throttle valve (9), it is described promote throttle valve (9) both ends be respectively communicated with the first hydraulic control proportional reversing valve (10)
Two hydraulic control hydraulic fluid ports, an actuator port of the first hydraulic control proportional reversing valve (10) connect the pilot control oil sources (1)
Pipeline between the percussion power pilot operated valve device (8), another actuator port of the first hydraulic control proportional reversing valve (10)
Fuel tank is connected, the first hydraulic control proportional reversing valve (10) can cut according to the pressure change for promoting throttle valve (9) both ends
Change jobs position, to change the on off operating mode of the first hydraulic control proportional reversing valve (10) and fuel tank.
2. Automatic hydraulic control system according to claim 1, which is characterized in that the oil outlet of the revolution oil sources (3)
Rotary throttle (11), the both ends point of the rotary throttle (11) are provided between the oil inlet of the rotary motor (6)
Two hydraulic control hydraulic fluid ports of the second hydraulic control proportional reversing valve (12), the oil inlet of the second hydraulic control proportional reversing valve (12) are not connected
The propulsion oil sources (4), two actuator ports difference of the second hydraulic control proportional reversing valve (12) are respectively communicated with oil return opening
The rod chamber and rodless cavity of the propelling cylinder (7) are connected, the second hydraulic control proportional reversing valve (12) can be according to described time
Turn the pressure change switch operating position at throttle valve (11) both ends, to change the working condition of the propelling cylinder (7).
3. Automatic hydraulic control system according to claim 2, which is characterized in that the pilot control oil sources (1) and institute
It states and guide is also disposed between percussion power pilot operated valve device (8) starts electric control reversing valve (13), the first threeway hydraulic control pressure reducing valve
(14) and first throttle valve (15), the hydraulic control mouth of the first threeway hydraulic control pressure reducing valve (14) connect the propelling cylinder (7)
Rodless cavity, the exit of the first throttle valve (15) are additionally provided with guide's pressure release electric control reversing valve (16) for connecting fuel tank
A mouthful overflow valve (17) is washed open with low, and the first hydraulic control proportional reversing valve (10) is additionally provided with low pressure relief valve between fuel tank
(18)。
4. Automatic hydraulic control system according to claim 3, which is characterized in that the second hydraulic control proportional reversing valve
(12) second throttle (19), auxiliary are disposed between one end of the hydraulic control mouth of one end and the rotary throttle (11)
Hydraulic control proportional reversing valve (20), the first auxiliary electric control reversal valve (21), the second hydraulic control proportional reversing valve (12) other end
The second threeway hydraulic control pressure reducing valve (22) and second are disposed between the other end of hydraulic control mouth and the rotary throttle (11)
Auxiliary electric control reversal valve (23).
5. Automatic hydraulic control system according to claim 4, which is characterized in that the rodless cavity of the propelling cylinder (7)
Third threeway hydraulic control pressure reducing valve (24) is provided between the second hydraulic control proportional reversing valve (12).
6. Automatic hydraulic control system according to claim 5, which is characterized in that the percussion mechanism (5) includes impact
Oil cylinder, impact reversal valve and accumulator.
7. Automatic hydraulic control system according to claim 6, which is characterized in that the first hydraulic control proportional reversing valve
(10) it is specially two-position two-way hydraulic control proportional reversing valve, the second hydraulic control proportional reversing valve (12) is specially 3-position 4-way hydraulic control
Proportional reversing valve, it is specially two-position three way electric control reversing valve that the guide, which starts electric control reversing valve (13), guide's pressure release electricity
It is specially bi-bit bi-pass electric control reversing valve to control reversal valve (16), and the auxiliary hydraulic control proportional reversing valve (20) is specially bi-bit bi-pass
Hydraulic control proportional reversing valve, the first auxiliary electric control reversal valve (21) and the second auxiliary electric control reversal valve (23) are specially two
Position threeway electric control reversing valve.
8. according to the Automatic hydraulic control system described in claim 1 to 7 any one, which is characterized in that the propulsion oil sources
(4) propelling cylinder (7) is also connected by automatically controlled proportional reversing valve (25).
9. Automatic hydraulic control system according to claim 8, which is characterized in that automatically controlled proportional reversing valve (25) tool
Body is the automatically controlled proportional reversing valve of 3-position 4-way.
10. a kind of rock drill, including Automatic hydraulic control system, which is characterized in that the Automatic hydraulic control system is specially
Automatic hydraulic control system described in claim 1 to 9 any one.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201721410438.2U CN207569009U (en) | 2017-10-27 | 2017-10-27 | Rock drill and its Automatic hydraulic control system |
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| CN201721410438.2U CN207569009U (en) | 2017-10-27 | 2017-10-27 | Rock drill and its Automatic hydraulic control system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107620762A (en) * | 2017-10-27 | 2018-01-23 | 中国铁建重工集团有限公司 | Rock drill and its Automatic hydraulic control system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107620762A (en) * | 2017-10-27 | 2018-01-23 | 中国铁建重工集团有限公司 | Rock drill and its Automatic hydraulic control system |
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| GR01 | Patent grant | ||
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| TR01 | Transfer of patent right |
Effective date of registration: 20190516 Address after: 830026 the Xinjiang Uygur Autonomous Region Urumqi economic and Technological Development Zone, 399 South Road. Patentee after: CHINA RAILWAY CONSTRUCTION HEAVY INDUSTRY XINJIANG Co.,Ltd. Address before: 410100 No. 88 Dongqi Road, Changsha Economic and Technological Development Zone, Changsha City, Hunan Province Patentee before: China Railway Construction Heavy Industry Co.,Ltd. |
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Granted publication date: 20180703 Effective date of abandoning: 20230526 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20180703 Effective date of abandoning: 20230526 |
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| AV01 | Patent right actively abandoned |