CN103998706B - Hydraulic-driven high-frequency percussion hammer for boring in hard formation - Google Patents
Hydraulic-driven high-frequency percussion hammer for boring in hard formation Download PDFInfo
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- CN103998706B CN103998706B CN201280040445.1A CN201280040445A CN103998706B CN 103998706 B CN103998706 B CN 103998706B CN 201280040445 A CN201280040445 A CN 201280040445A CN 103998706 B CN103998706 B CN 103998706B
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- 230000015572 biosynthetic process Effects 0.000 title claims abstract description 7
- 238000009527 percussion Methods 0.000 title claims abstract description 5
- 239000012530 fluid Substances 0.000 claims abstract description 20
- 238000013016 damping Methods 0.000 claims description 10
- 230000033001 locomotion Effects 0.000 claims description 3
- 230000000717 retained effect Effects 0.000 claims description 2
- 238000011144 upstream manufacturing Methods 0.000 claims description 2
- 238000002637 fluid replacement therapy Methods 0.000 claims 1
- 238000005553 drilling Methods 0.000 abstract description 25
- 239000011435 rock Substances 0.000 description 13
- 230000000694 effects Effects 0.000 description 6
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 239000000463 material Substances 0.000 description 4
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- 229910052751 metal Inorganic materials 0.000 description 3
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- 235000009566 rice Nutrition 0.000 description 3
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- 230000008901 benefit Effects 0.000 description 2
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- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 230000035515 penetration Effects 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 208000031481 Pathologic Constriction Diseases 0.000 description 1
- 229910000639 Spring steel Inorganic materials 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 239000000654 additive Substances 0.000 description 1
- 230000000996 additive effect Effects 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000003466 anti-cipated effect Effects 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
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- 238000004891 communication Methods 0.000 description 1
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- 238000013461 design Methods 0.000 description 1
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- 239000000428 dust Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 239000010438 granite Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
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- 238000005461 lubrication Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005065 mining Methods 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
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- UONOETXJSWQNOL-UHFFFAOYSA-N tungsten carbide Chemical compound [W+]#[C-] UONOETXJSWQNOL-UHFFFAOYSA-N 0.000 description 1
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Classifications
-
- 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
- E21B4/00—Drives for drilling, used in the borehole
- E21B4/06—Down-hole impacting means, e.g. hammers
- E21B4/14—Fluid operated hammers
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- Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Mechanical Engineering (AREA)
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- Environmental & Geological Engineering (AREA)
- Fluid Mechanics (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Earth Drilling (AREA)
- Percussive Tools And Related Accessories (AREA)
Abstract
The invention provides a kind of hydraulic-driven high-frequency percussion hammer for holing at hard formation.The hammer piston (20) of this jump bit has the relatively large and hole (41) of longitudinal extension, and this hole (41) provide minimum flow resistance to the drilling fluids flowing through hole (41) during hammer piston (20) backward stroke.Hole (41) can pass through valve plug (23) follow during stroke hammer piston (20) be closed in updrift side.Valve plug (23) is controlled by the valve rod (49) of opposite elongate, and this valve rod (49) can stop valve plug (23) with about the 75% of the whole length of stroke of hammer piston (20) and make valve plug (23) separate from seat ring (40).Therefore hole (41) are open makes hole fluid to flow therethrough, and the internal elasticity spring property of this valve rod (49) makes valve plug (23) return, the speed of this return is fast carries out good flow to during hammer piston (20) backhaul.
Description
Technical field
The present invention relates to a kind of for the hydraulic-driven of boring in hard formation, high-frequency percussion hammer, wherein this jump bit bag
Including: housing, one end of this housing is provided with drill bit, and this drill bit is designed as directly acting on hard formation, and this jump bit also includes: can
The hammer piston being contained in movably in this housing, this hammer piston acts on drill bit, and this hammer piston has the longitudinal direction of predetermined amount of flow
Elongated hole, and this elongated hole can be closed by valve plug in updrift side, and this valve plug partly follows this in the stroke of hammer piston
Hammer piston.
Background technology
Hammer business into shape for the hydraulically actuated impact of boring in rock to apply more than 30 years.They are with attachable brill
Bar is used together, and wherein drilling depth is restricted, and is owing to impact energy dies down at joint, and the weight of this drilling rod becomes
Obtain overweight so that the most little energy can arrive and pass to drill bit.
Down-the-hole hammer drill, i.e. it is more effective for being installed on the hammer drill directly over drill bit, and be used for a great extent dropping to
The probing that 200-300 rice is deep.They are by compressed air-driven and have the pressure up to about 22bar, and then this limits boring deeply
Degree is to about 20 meters, if water enters in well.The hammer drill that water under high pressure drives is the most commercially available more than 10 years, but these are all at chi
Very little limited, it means that to be up to about 130 millimeter opening diameters.Furthermore it is known that they have the limited life-span and in water
Impurity sensitive.They are used for mining industry to a great extent, because they hole highly effective and get out the most straight hole.
They are used for vertical drilling in limited degree and drop to the degree of depth of 1000-1500 rice, then, do not have any direction to control
System.
It is desirable that manufacture the fluid-operated hammer drill of downhole drill bit, they can be used together together with Direction Control Aid, it
Production efficiency high, drilling fluid can be used water as, it is also possible to be used together with the water-base drilling fluid with additive, and have
The economic life-span.Anticipated have the biggest purposes for deepwater drilling geothermal energy resources and hard exploitation oil and natural gas resource.
In impact is bored, the drill bit of use has the hard metal protuberance (lugs) of insertion, so-called " pressure head ".They
It is made up of tungsten carbide, and diameter usually 8 to 14 millimeters and there is the spherical or end of taper.Ideally, each
Pressure head should have the hardness to rock and the relevant optimal impact energy of comprcssive strength is clashed into, so that occurring on rock
Little breach or pit.Bit is to hit next time, ideally, is formed new with what previous breach was connected
Breach.The diameter of boring and geometry determine the number of pressure head.
Optimal impact energy is to be determined by the comprcssive strength of rock, and it can be at the comprcssive strength rock higher than 300MPa
Middle boring.There is provided the impact energy exceeding optimised quantity, then overage can be lost because it is not intended to destruction rock, and
Propagation of Energy ripple.The least impact energy never produces breach.When the impact energy of each pressure head is known, and pressure
Head number determine that time, then can obtain the optimal impact energy of drill bit.Pull speed or drilling speed (ROP penetration speed) right
After can only by improve frequency of impact and increase.
The amount of the drilling fluids pumped into is by the minimum necessary reply speed in the annulus between drill string and borehole wall
Rate (return rate) (ring speed) determines.This at least should be more than 1 meter per second, preferably 2 meter per seconds, so that come outbreak out
Material, drilling cuttings can be transported to ground.Rock is the hardest and crisp, it is provided that frequency of impact the highest, then drilling cuttings is the most in small, broken bits, and slower
Recovery rate or speed then can be accepted.Hard rock and altofrequency will produce dust or the drilling cuttings of fine sand sample.
The hydraulic pressure effect (effect) being applied on hammer drill is multiplied by the unit interval amount of pumping into by pressure drop and determines.
The impact energy every time hit is multiplied by frequency and obtains effect.In one example assumed, the granite tool being drilled
Have the comprcssive strength of 260 MPas and use the bore diameter of 190 millimeters, then by water from earth's surface with 750 liters/min (12.5 liters/
Second) pump into.According to calculating, optimal impact energy is about 900J.
Corresponding boring but there is less diameter, with reference to known data, penetration rate (ROP) be 22 ms/h (i.e.
Rice per hour) then should have the frequency of impact of 60Hz.It is assumed herein that increase frequency of impact to 95 hertz, therefore ROP be 35 meters/little
Time.Then required on drill bit net work effect reforms into: 0.9 kilojoule x 95=86 kilowatt.We assume that hammer structure has at present
Mechanical-hydraulic effect be 0.89, then through this hammer provide 7.7 MPas of required pressure drops.
The hammer drill fast 60% that so this hammer drill will promote than existing available waterpower, and save the energy resource consumption of 60%.
Summary of the invention
This realizes by introducing the jump bit of the type, and the outstanding feature of this hammer is: valve plug can be slided by stem sleeve
The valve rod being connected received controls dynamicly, and this valve rod includes stop device, and it can be with the whole length of stroke of hammer piston
Predetermined percentage stops valve plug, and is separated with the valve base seal on hammer piston by valve plug, and therefore this hole is opened, and allows
Fluid is flow through in this hole.
Preferably this stop device includes check plate at the upstream termination of this valve rod, and has collaborative behaviour in described stem sleeve
The interior stop surface made.
In one embodiment, the predetermined percentage of the whole length of stroke of this hammer piston is of about 75%.
It is expedient to, the internal elasticity spring performance of valve rod is for making valve plug reply, and this valve rod is elongated.
Preferably, this jump bit is additionally provided with inlet valve assembly, and it can not open and be used for hammering into shape the operation of piston, until pressure
Power accumulates the complete operating pressure of about 95%, and this inlet valve assembly is suitable to close main cylinder, and the side neck in hammer housing
Annular space between hammer piston and the housing promoting this hammer piston can be pressed to seal this valve plug by body.
It is expedient to, this hammer piston and valve module can be by recoil return motions, and wherein hammer piston can be with valve module
It is both provided with hydraulic damping and controls to reply the delay of stroke, until stopping.
It is expedient to, this hydraulic damping annular piston is carried out, this annular piston be pressed into have accordingly controlled between
In the circular cylinder of gap, thus limit or block the discharge of the fluid retained.
Further, can arrange opening at the top of this stem sleeve, the baffle plate of this valve rod can enter this opening, and this gear
The radial component of plate can be with the inner side of this opening of radial clearance seals of opposite, narrow.
Further, the service valve of annular may be arranged in the cannelure below this opening, utilizes this service valve to open
Hole also loads liquid by this hole in stem sleeve.
This jump bit housing can be divided into: inlet valve housing, valve chest and hammer housing.
Hammer drill structure according to the present invention is the type being designated as " direct acting hammer ", i.e. this hammer piston has closure valve above,
Piston can be promoted forward when this valve is in the close position, and hammer piston can be made when open position to recoil.Hydraulic pressure in the past
Hammer type there is valve system, promotes hammer piston by pressure with above-mentioned two ways simultaneously.This provides low efficiency, but piston
Can more precise control.
High efficiency and high frequency of impact it is crucial that on valve arrangement.This valve needs high frequency to run, and at open position
The flow behavior having had.
Having great advantage simultaneously, this hammer drill structure is also used as the hydraulic-driven hammer installed on surface, together with drilling rod
For holing, but herein the situation that it is used as down-hole hammer drill is described in detail.
Accompanying drawing explanation
Other and the further purpose of the present invention, feature and advantage are by by the description to the preferred embodiments of the present invention
Becoming obvious, these preferred embodiments for descriptive purposes, and are described with reference to the drawings, wherein:
Fig. 1 shows the schematic diagram of the typical hydraulic pressure hammer drill according to the present invention；
Fig. 2 A shows the front view of the down-hole hammer drill with drill bit；
Fig. 2 B shows that the hammer drill of Fig. 2 A rotates the situation of about 90 °；
Fig. 2 C shows the view in arrow A-A direction in Fig. 2 A；
Fig. 2 D shows the view in arrow B-B direction in Fig. 2 A；
Fig. 3 A shows the longitudinal sectional view of the hammer drill of display in Fig. 2 A, which show inner body portion；
Fig. 3 B shows the transverse sectional view of the line A-A along Fig. 3 A；
Fig. 3 C shows the transverse sectional view of the line B-B along Fig. 3 A；
Fig. 3 D shows the transverse sectional view of the line C-C along Fig. 3 A；
Fig. 3 E shows the transverse sectional view of the line D-D along Fig. 3 A；
Fig. 3 F shows the twice zoomed-in view of part H lived by frame in Fig. 3 A；
Fig. 3 G shows the twice zoomed-in view of part H lived by frame in Fig. 3 A；
Fig. 3 H shows five times of zoomed-in views of part F lived by frame in Fig. 3 A；
Fig. 3 I shows five times of zoomed-in views of part G lived by frame in Fig. 3 A；
Fig. 4 A shows corresponding to the structure shown in Fig. 3 A, but is in the end of boost phase；
Fig. 4 B shows the front view of the valve module that the part in Fig. 4 A shows；
Fig. 4 C shows the transverse sectional view of the line B-B along Fig. 4 A；
Fig. 4 D shows five times of zoomed-in views of part A lived by frame in Fig. 4 A；
Fig. 4 E shows five times of zoomed-in views of part C lived by frame in Fig. 4 A；
Fig. 5 A shows corresponding to the structure shown in Fig. 3 A and 4A, but is in the shock surface of hammer piston impact drill bit
Time；
Fig. 5 B shows five times of zoomed-in views of part A lived by frame in Fig. 5 A；
Fig. 5 C shows four times of zoomed-in views of part B lived by frame in Fig. 5 A；
Fig. 6 A shows corresponding to the structure shown in Fig. 3 A, 4A and 5A, but is in hammer piston when completely returning to；
Fig. 6 B shows the part of the line E-E along Fig. 6 C；
Fig. 6 C shows five times of zoomed-in views of part A lived by frame in Fig. 6 A；
Fig. 6 C ' shows 20 times of zoomed-in views of part D lived by frame in Fig. 6 C；
Fig. 6 D shows 20 times of zoomed-in views of part C lived by frame in Fig. 6 E；
Fig. 6 E shows four times of zoomed-in views of part B lived by frame in Fig. 6 A；
Fig. 7 A shows corresponding to Fig. 3 A, 4A, the structure shown in 5A and 6A, but this hour hammer piston is in the last of falling
Part；
Fig. 7 B shows 20 times of zoomed-in views of part B lived by frame in Fig. 7 C；
Fig. 7 C shows four times of zoomed-in views of part A lived by frame in Fig. 7 A；
Fig. 8 shows the curve of the working cycle describing hammer piston and valve；
Fig. 9 A shows the curve describing valve relative to the unexpected closing characteristics of pressure drop, and
Fig. 9 B shows the flow in time progressively closing off valve and pressure drop.
Detailed description of the invention
Fig. 1 shows the hydraulic pressure hammer drill being typically used for being connected to the top of attachable drilling rod, and wherein hammer structure is positioned at
The inside of housing 1, this housing 1 is made up of several housing portions, and wherein rotation motor 2 makes drilling rod rotate via variator 3, this change
Speed device 3 rotates the axle with threaded portion 4, and this threaded portion 4 will be screwed onto (not shown) on drilling rod and drill bit.Hammer machine is usual
Equipped with fixed plate 5, for being connected to the feeding mechanism of rig (not shown).Hydraulic-driven stream is supplied through pipeline and connector 6
Body, and return by having pipeline 6 hydraulic pressure of connector 7.
Fig. 2 A and 2B shows the down-hole hammer drill with drill bit.In these description that will be used below.Shown housing 1
Having the first housing parts 8, its device received will be described as inlet valve after a while, and the second housing parts 9 comprises valve, and the 3rd
Housing parts 10 comprises hammer piston, and label 11 represents drill bit.Drilling fluids is pumped to by opening main channel (run), and spiral shell
Drill string (not shown) received by hammer by stricture of vagina part 13.Par 14 is arranged to use torque wrench hammer to be screwed onto drill string or from brill
Post is backed out.Osculum 15 is needs for inlet valve explained later on, and there is outlet opening 16 for the wall of a borehole and hammer drill shell
The drilling fluids in loop configuration between body (not shown) is back to surface.Hard metal protuberance 17 is drilled for compression
The element of rock.Fig. 2 C shows the view in the direction of arrow A-A in Fig. 2 A, and Fig. 2 D shows in Fig. 2 A along arrow B-B direction
The view seen towards drill bit 11.
Fig. 3 A shows the longitudinal sectional drawing of hammer drill, and wherein inner main component is: inlet valve assembly 18, valve module 19 He
Hammer piston 20.Drilling fluids is pumped to, by inlet valve 18 in an open position, by Fig. 3 B midship section figure by entrance 12
The hole 21 of the upper display of A-A, then by the hole 22 in Fig. 3 C midship section figure B-B, flow to valve plug 23, this valve plug 23 cuing open at Fig. 3 D
Being shown as closed position in the figure C-C of face, valve plug 23 abuts against hammer piston 20 and drives this piston to abut against the base section of drill bit
24.The D-D profile of Fig. 3 E shows section of rack 25 and the lowermost portion of hammer housing 10 of the longitudinal extension in this drill bit 11,
They transmit torque when moving axially in the acceptable space that drill bit 11 is determined by locking circular ring structure 26.This is because
By by the hammer piston 20 impact to drill bit 11, the quality of the parts being only subjected to displacement or weight and this hard metal protuberance 17
The intrusion degree entering rock is consistent.This is so that transfer to impact energy as much as possible crush rock,
And reduce the mass shift of relatively light drill bit 11 as far as possible.
Showing inlet valve 18 in the close position in the detailed cross sectional view of Fig. 3 F, this sectional view is in Fig. 3 A
H.When starting hammer function, start the drilling fluids in entrance 12 pumps into operation.Through valve chest 8 wall side or point
The hole 27 propped up and bullport 28 hydraulic communication in the installing plate of inlet valve assembly 18.This installing plate 29 is integrally fixed at valve chest 8
In, and include guiding valve 30, this guiding valve 30 is maintained at open position by spring 31.Drilling fluids flows freely into first and draws
The first guiding room on guide piston 32, diameter and the area ratio entrance of this guiding room are big.When pressure increases, limited is removable
Valve plug 33 will be forced to shutdown on the valve seat 34 leaned against in housing 8.When the pressure of the inlet valve 18 to closedown increases, housing 10
And the pressurized hole 27 through side of circulus 35 between hammer piston 20, the hole of its longitudinal extension in valve chest 9
36 pairs of entrances 37 feed, and see Fig. 3 H.
Detailed cross sectional view in Fig. 3 H and Fig. 3 I takes from F and G of Fig. 3 A, and shows that hammer piston 20 is against hammer housing 9,10
The situation of inwall.The diameter of piston 38 is less times greater than the diameter of the second piston 39.By use hammer drill to hole vertically downward,
Under non-pressurized state, hammer piston 20 will obviously face the striking face in drill bit 11 or shock surface 24 moves due to action of gravity
Dynamic.In this case, in hammer piston 20, will have gap (see Fig. 3 H) between valve plug 23 and valve seat 40.Therefore, boring stream
Body by own flowing by the valve at stopper 23, by the hole 41 in hammer piston 20 and hole 16 (see Fig. 2 A), therefore for starting
This hammer has pressure very little to increase generation.
In Fig. 3 F, the setting in the detailed cross sectional view of display, has the inlet valve 18 of closedown and has in circulus 35
Pressure accumulated, hammer piston 20 is promoted to close valve plug 23 by this.Due to required between the inwall of the surface of piston 38 and housing 9
Gap, drilling fluids space from valve plug 23 is overflowed, as shown in arrow in Fig. 3 H by lubrication channel 42 and hole 43.In order to
Preventing this situation, this leakage rate should provide buildup of pressure in the space on valve plug 23, and this is by the guiding valve 30 of this position
Hole 44 and opening 45 in the valve installing plate 29 allowed flow out, and flow out through osculum 15 further.When pressure rises to hammer
When designing more than the 90% of the operating pressure needed, the piston force in room 46 is guided to exceed the closing force of spring 31 second, and
Valve 30 is guided to shift, as shown in Figure 3 G.
The first guiding room on guiding piston 32 is discharged (drained) and inlet valve 18 is opened.At opening 45 quilt
While closedown, being closed by the draining in hole 44, this makes pressure in an operation mode will not be lost by this hole.At hammer
The pressure in room that guides on the valve plug 23 of piston 20 and Guan Bi makes the working cycle with instant fully effect start.Backup
The setting of valve 47 and nozzle 48 makes it possible to reduce the drain time of the second guiding room 46, it is achieved thereby that inlet valve 18 is relatively slow
Guan Bi.This makes inlet valve 18 keep fully opening, and will not be in the operational mode owing to pressure subsequently is along with collision frequency
Fluctuate and produce interference.
Fig. 4 A shows hammer drill situation at the end of boost phase.Hammer piston 20 now has been maxed out speed, logical
Often it is about 6m/s.This is the result of following condition, and available pressure is such as only below 8MPa, hammers the hydraulic area of piston into shape, here
The most a diameter of 130mm, and the weight of hammer piston, the most such as 49kg.Valve plug 23 keeps the seat opening Guan Bi to hammer piston, because of
For the hydraulic area of valve plug 23, the most a diameter of 95mm, this region is more bigger, the most greatly than the annular region area of hammer piston
4%, as shown in Fig. 4 C midship section B-B, it is expressed as 23 and 24.This hour hammer piston has covered about the 75% of its whole strokes,
All stroke is about 9mm.Gap between hammer piston 20 and the scope of attack 24 of drill bit is about 3mm, as shown in Figure 4 E.
The moveable valve rod 49 with baffle plate 50 is now on the proximal surface of the standing valve rod sleeve 51 in housing 9, and
Stoping valve rod 49 to move further, as shown in Figure 4 D, after this, valve plug 23 separates from the valve seat 40 of hammer piston 20, thus quilt
Open.Movably valve module 23,49,50 is shown in the front view of Fig. 4 B.
The kinetic energy of valve plug 23 passes through jerk, slightly elongates the valve rod 49 of opposite elongate, thus is converted to relatively large spring
Power, valve is accelerated rapidly by this spring force.The slightly elongation of valve rod 49, the most such as, be calculated as about 0.8mm, need the utilization than material
Rate is low, and this material is high-strength spring steel in this case.The quality of valve plug 23 should be the least, the most such as by aluminum
Make, in conjunction with the length of valve rod 49, diameter and properties of materials, determine the natural frequency of this valve module.
Applying for reality, this should its 8-10 times of frequency used minimum.This natural frequency is by below equation
Determine:
Wherein
Quality and spring constant have the most frequently used meaning.The natural frequency of the structure of this display is about 1100-1200Hz,
Therefore can be used for the operating frequency situation more than 100Hz.
The rebound velocity of the structure shown in this embodiment is impact or the 93% of stroke speed.
Fig. 5 A shows position when hammer piston 20 clashes into the shock to drill bit 11 or proximal surface and moment.Valve plug 23 wraps
Including valve rod 49 and baffle plate 50, this valve plug 23 is in the speed completely returned to, and sees Fig. 5 B, and this makes at valve plug 23 and hammer piston 20
On valve seat 40 between relatively quickly set up a big opening, so that drilling fluids can flow through with relatively small resistance
Longitudinal hole 41 in hammer piston 20, as illustrated in detail in Fig. 5 B.
The kinetic energy of hammer piston 20 power is partially converted into the spring force on hammer piston 20, because living in this knockout process
It is plugged with a little compression.When transferring to relative end and back from the energy wave of impact by hammer piston 20, hammer piston 20 is anti-
Come over to be accelerated.The most originally return speed is calculated about 3.2 meter per seconds, is about strike or the 53% of impact velocity, this is because
Part energy has been used for the mass shift of drill bit 11, and remaining energy has been used for making pressure head enter in rock.
Fig. 6 A shows that hammer piston 20 is in its situation completely returning to speed.Now valve plug 23 is almost back to terminal,
Wherein Fig. 6 C shows the open top 52 including that the bar 49 of baffle plate 50 enters stem sleeve 51.
Fig. 6 C ' showing, the private side of opening 52 is entered by the radial clearance of the radial component the most how opposite, narrow of baffle plate 50
Row seals.When baffle plate 50 moves last 2mm until producing little negative pressure in chamber below this baffle plate 50 when stopping.Annular
Service valve 58 is opened and again fills liquid by hole 59.Baffle plate 50 restriction below or the volume closed can prevent valve plug
23 carry out recoil and are held in place by, until next cycle starts.
The service valve 58 of " annular service valve " type, is the leaf spring of annular in the present embodiment, uses this leaf spring to be because
It has little quality and relatively large spring force, therefore, it is possible to high frequency work.
Fig. 6 E shows the relatively large opening between valve plug 23 and the valve seat 40 in hammer piston 20, so that herein
Drilling fluids passes through with minimum resistance flowing.The downside of stem sleeve 51 is formed as circular cylinder depression (pit) 53, such as Fig. 6 D
Shown in.The top of valve plug 23 is formed as annular piston 54, and this annular piston 54 is by the matched in clearance of relative narrowness extremely annular gas
In cylinder depression 53.Followed by this valve and return to terminal always, the fluid volume of this restriction is discharged in a controlled fashion, by ring-type work
Radial clearance between plug 54 and annular canister 53 adds tap 55 and discharges.This controlled discharge is as damping force, and stops valve
Return so that this valve does not carry out recoil.The damping unit of same type is present on hammer piston 20.At detailed view 6E
Upper is annular piston 56, is shown on the top of hammer piston 20, except the shaping drum connected in star 57 of the bottom at valve chest 9.
Fig. 7 A shows the decline of the return of hammer piston 20.The termination of backward stroke is prevented from a controlled manner,
Until stopping completely when valve seat 40 runs into valve plug 23, it is shown in Fig. 7 C.Fig. 7 B show in more detail and cave at circular cylindrical
How restriction in 57 or airtight fluid volume is moved through the radial clearance between annular piston 56 and osculum 60.
Gap between valve seat 40 and valve plug 23 is without of completely closed, in order to accumulated pressure also starts the new cycle.Calculate
Showing, when using the opening of 0.5mm, pressure drop is substantially identical with operating pressure.This causes connecing between valve plug 23 and valve seat 40
The surface pressing of contacting surface diminishes, and these assemblies can use for a long time.
Fig. 8 shows the curve of the working cycle describing hammer piston 20 and valve.Curve A shows velocity variations, and curve B shows
Show the change in location by a working cycle.For two curves, transverse axis is time shaft, and unit is microsecond.
For curve A, the longitudinal axis represents the speed in units of m/s, towards the stroke direction of drill bit 11 be+upwards and-to
Under, herein refer to return speed.
The longitudinal axis of curve B shows the distance in units of mm from starting position.Curved portion 61 represents boost phase,
Wherein, 62 for valve stop and its start return moment.Point 63 is corresponding to the hammer piston 20 impact to drill bit 11.
Curved portion 64 is the displacement that drill bit 11 enters in rock, and 65 is the acceleration of resilience, and 66 is not damping
Return speed, and 67 is the return speed with damping.Curved portion 68 is the return acceleration of valve, and 69 is the not damping of valve
Return acceleration, 70 deceleration damping stage when being the return of valve.
Fig. 9 A shows curve 71, this graph illustrates in the unexpected closure feature for pressure drop and the hammer piston of valve
The relation between opening between valve plug 23 and valve seat 40.This situation is as shown in Figure 9 B.Transverse axis is between the opening that unit is mm
Gap, the longitudinal axis be unit be the pressure drop of design when carrying out pumping into drilling fluids with nominal rate of bar, the most such as this nominal speed
Rate is 12.5L/s.Need at below 1.5mm as it can be seen, closed gap before receiving a sizable pressure drag.
Claims (10)
1. the hydraulic-driven high-frequency percussion hammer for boring in hard formation, described jump bit includes: housing, described housing
One end be provided with drill bit (11), described drill bit (11) is designed as directly acting on hard formation, and described jump bit also includes: can move
The hammer piston (20) being contained in described housing dynamicly and act on drill bit (11), described hammer piston (20) has predetermined amount of flow
The hole (41) of the longitudinal extension of volume, and described hole (41) can be closed in the upstream direction by valve plug (23), described valve plug
(23) in the stroke of hammer piston (20), part follows described hammer piston (20), it is characterised in that described valve plug (23) is by valve rod
The valve rod (49) being associated that loads slidably in sleeve (51) controls, and described valve rod (49) includes stop device, described only
Dynamic device can stop suddenly described valve plug (23) with the predetermined percentage of the whole length of stroke of described hammer piston (20), and by institute
State the valve plug (23) seat seal (40) from hammer piston (20) to separate, thus described hole (41) are opened, and make boring
Fluid can flow through described hole (41), and the internal elasticity spring performance of described valve rod (49) utilizes mechanical backlash to make valve plug (23)
With high speed return motion.
Jump bit the most according to claim 1, it is characterised in that described stop device is included in the upper of described valve rod (49)
The baffle plate (50) of trip end, and the stop surfaces of the crew-served inside in described stem sleeve (51).
Jump bit the most according to claim 1, it is characterised in that making a reservation for of the whole length of stroke of described hammer piston (20)
Percentage ratio is 75%.
Jump bit the most according to claim 1, it is characterised in that described valve rod (49) is elongated.
Jump bit the most according to claim 1, it is characterised in that this jump bit also has inlet valve assembly (18), described
Hammer piston (20) operate open until pressure accumulated arriving as the 95% of whole operating pressures by inlet valve assembly (18), described
Inlet valve assembly (18) is suitable to close main staving (12), and the side staving in described housing to hammer piston (20) and promotes described hammer
Circulus (35) supercharging between the hammer housing (10) of piston (20) is to seal described valve plug (23).
Jump bit the most according to claim 5, it is characterised in that described hammer piston (20) and inlet valve assembly (18) pass through
Recoil return motion, wherein said hammer piston (20) and inlet valve assembly (18) are both provided with hydraulic damping to control to reply stroke
Delay until stop.
Jump bit the most according to claim 6, it is characterised in that described hydraulic damping is occurred by annular piston (54),
Described annular piston (54) is pushed into corresponding circular cylinder (53), and described circular cylinder (53) has controllable gap
Thus limit or block the discharge of the fluid retained.
Jump bit the most according to claim 1, it is characterised in that opening (52) is arranged at the top of described stem sleeve (51)
Portion, and the baffle plate (50) of described valve rod (49) can enter described opening (52), the radial component of described baffle plate (50) is with relatively
The inner side of described opening (52) is sealed by narrow radial clearance.
Jump bit the most according to claim 8, it is characterised in that annular service valve (58) is arranged under described opening (52)
In the ring-shaped groove of side, described service valve (58) can open and by hole (59) fluid replacement in stem sleeve (51).
10. according to the jump bit according to any one of claim 1-9, it is characterised in that the described housing of described jump bit divides
Become: inlet valve housing (8), valve chest (9) and hammer housing (10).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| NO20111140A NO334793B1 (en) | 2011-08-19 | 2011-08-19 | High frequency liquid driven drill hammer for percussion drilling in hard formations |
| NO20111140 | 2011-08-19 | ||
| PCT/NO2012/050148 WO2013028078A1 (en) | 2011-08-19 | 2012-08-17 | High frequency fluid driven drill hammer percussion drilling in hard formations |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103998706A CN103998706A (en) | 2014-08-20 |
| CN103998706B true CN103998706B (en) | 2016-08-17 |
Family
ID=47746666
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280040445.1A Active CN103998706B (en) | 2011-08-19 | 2012-08-17 | Hydraulic-driven high-frequency percussion hammer for boring in hard formation |
Country Status (11)
| Country | Link |
|---|---|
| US (1) | US10385617B2 (en) |
| EP (1) | EP2744966B1 (en) |
| CN (1) | CN103998706B (en) |
| CA (1) | CA2845789C (en) |
| DK (1) | DK2744966T3 (en) |
| ES (1) | ES2763384T3 (en) |
| HU (1) | HUE047284T2 (en) |
| NO (1) | NO334793B1 (en) |
| PL (1) | PL2744966T3 (en) |
| RU (1) | RU2607843C2 (en) |
| WO (1) | WO2013028078A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| NO335354B1 (en) | 2013-02-18 | 2014-12-01 | Pav Holding As | High frequency liquid driven drill hammer for percussion drilling in hard formations |
| CN106948753B (en) * | 2017-05-08 | 2018-12-21 | 西南石油大学 | A kind of pulsed drilling fluid hammer |
Family Cites Families (31)
| Publication number | Priority date | Publication date | Assignee | Title |
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| US1096886A (en) * | 1914-01-14 | 1914-05-19 | Ingersoll Rand Co | Fluid-operated percussive tool. |
| US2758817A (en) * | 1950-10-03 | 1956-08-14 | Bassinger Ross | Percussion tools for wells |
| US2774334A (en) * | 1953-05-01 | 1956-12-18 | Hughes Tool Co | Reciprocating prime mover |
| US2873093A (en) * | 1956-09-19 | 1959-02-10 | Jersey Prod Res Co | Combined rotary and percussion drilling apparatus |
| US3130799A (en) | 1961-01-06 | 1964-04-28 | Jersey Prod Res Co | Bounding mass drilling tool |
| US3387671A (en) * | 1965-10-15 | 1968-06-11 | Mission Mfg Co | Percussion tool |
| US3327790A (en) * | 1966-10-24 | 1967-06-27 | Pan American Petroleum Corp | Liquid percussion motor |
| US3403739A (en) * | 1966-11-01 | 1968-10-01 | Bowen Tools Inc | Fluid-actuated impact tool |
| US3410353A (en) * | 1967-08-21 | 1968-11-12 | Leo A. Martini | Percussion tools |
| US3570611A (en) * | 1968-02-09 | 1971-03-16 | Trustul Deforaj Pitesti | Device for freeing seized drill strings |
| CA1071947A (en) * | 1976-10-08 | 1980-02-19 | Abraham Gien | Pneumatic hammer drill |
| AU520087B2 (en) * | 1980-08-01 | 1982-01-14 | Abraham Gien | Piston for pneumatic percussion machine |
| ZA814749B (en) * | 1981-07-13 | 1982-07-28 | Chamber Of Mines Services Ltd | Hydraulic reciprocating machines |
| SE444127B (en) | 1984-06-25 | 1986-03-24 | Atlas Copco Ab | PRESSURE WASHING DRIVE SINGLE DRILLING MACHINE |
| US4606408A (en) * | 1985-02-20 | 1986-08-19 | Halliburton Company | Method and apparatus for gravel-packing a well |
| JPH01502919A (en) * | 1987-02-25 | 1989-10-05 | ザルッギッター マシーネンバウ ゲゼルシャフト ミット ベシュレンクテル ハフツング | Drilling rig for underground drilling with hydraulic percussion generator |
| US4958691A (en) * | 1989-06-16 | 1990-09-25 | James Hipp | Fluid operated vibratory jar with rotating bit |
| US5156223A (en) * | 1989-06-16 | 1992-10-20 | Hipp James E | Fluid operated vibratory jar with rotating bit |
| SU1760067A1 (en) * | 1989-08-29 | 1992-09-07 | Донецкий политехнический институт | Hydraulic percussion unit |
| US5065824A (en) * | 1989-12-28 | 1991-11-19 | Esco Corporation | Hydraulically powered repetitive impact hammer |
| SE502343C2 (en) * | 1991-06-24 | 1995-10-09 | Berema Atlas Copco Ab | Safety device for tools for striking hand-held machines |
| US5566771A (en) * | 1995-08-30 | 1996-10-22 | Ingersoll-Rand Company | Reversible casing for a self-lubricating, fluid-actuated, percussive down-the-hole drill |
| SE9601762L (en) | 1996-05-09 | 1997-08-25 | Sandvik Ab | Impedance and length / time parameter range for hammer device and associated drill bit and piston |
| NO304199B2 (en) * | 1996-10-30 | 1998-11-09 | Weatherford Norge As | Hydraulic impact tool |
| US6062324A (en) * | 1998-02-12 | 2000-05-16 | Baker Hughes Incorporated | Fluid operated vibratory oil well drilling tool |
| GB0112261D0 (en) * | 2001-05-19 | 2001-07-11 | Rotech Holdings Ltd | Downhole tool |
| CN1177126C (en) * | 2002-08-07 | 2004-11-24 | 中国地质科学院勘探技术研究所 | Hydraulic in-the-hole hammer with dual nozzles and combined valve |
| SE526252C2 (en) * | 2003-03-26 | 2005-08-09 | Wassara Ab | Hydraulic drill string device |
| US7353890B2 (en) * | 2006-01-09 | 2008-04-08 | Sandvik Intellectual Property Ab | Down-the-hole hammer and components for a down-the-hole hammer, and a method of assembling a down-the-hole hammer |
| US7422074B2 (en) * | 2006-05-19 | 2008-09-09 | Numa Tool Company | Delayed compression sleeve hammer |
| CA3034320C (en) * | 2015-08-20 | 2023-07-04 | Impulse Downhole Solutions Ltd. | On-bottom downhole bearing assembly |
-
2011
- 2011-08-19 NO NO20111140A patent/NO334793B1/en unknown
-
2012
- 2012-08-17 WO PCT/NO2012/050148 patent/WO2013028078A1/en active Application Filing
- 2012-08-17 DK DK12825336.6T patent/DK2744966T3/en active
- 2012-08-17 US US14/239,446 patent/US10385617B2/en active Active
- 2012-08-17 CA CA2845789A patent/CA2845789C/en active Active
- 2012-08-17 PL PL12825336T patent/PL2744966T3/en unknown
- 2012-08-17 RU RU2014108528A patent/RU2607843C2/en active
- 2012-08-17 HU HUE12825336A patent/HUE047284T2/en unknown
- 2012-08-17 CN CN201280040445.1A patent/CN103998706B/en active Active
- 2012-08-17 ES ES12825336T patent/ES2763384T3/en active Active
- 2012-08-17 EP EP12825336.6A patent/EP2744966B1/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CA2845789A1 (en) | 2013-02-28 |
| US10385617B2 (en) | 2019-08-20 |
| RU2607843C2 (en) | 2017-01-20 |
| NO20111140A1 (en) | 2013-02-20 |
| EP2744966A4 (en) | 2016-07-20 |
| US20140174779A1 (en) | 2014-06-26 |
| CN103998706A (en) | 2014-08-20 |
| EP2744966A1 (en) | 2014-06-25 |
| CA2845789C (en) | 2021-03-09 |
| RU2014108528A (en) | 2015-09-27 |
| EP2744966B1 (en) | 2019-10-02 |
| DK2744966T3 (en) | 2019-12-16 |
| WO2013028078A1 (en) | 2013-02-28 |
| ES2763384T3 (en) | 2020-05-28 |
| HUE047284T2 (en) | 2020-04-28 |
| NO334793B1 (en) | 2014-05-26 |
| PL2744966T3 (en) | 2020-05-18 |
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