CN103998706A - High frequency fluid driven drill hammer percussion drilling in hard formations - Google Patents
High frequency fluid driven drill hammer percussion drilling in hard formations Download PDFInfo
- Publication number
- CN103998706A CN103998706A CN201280040445.1A CN201280040445A CN103998706A CN 103998706 A CN103998706 A CN 103998706A CN 201280040445 A CN201280040445 A CN 201280040445A CN 103998706 A CN103998706 A CN 103998706A
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- 238000005553 drilling Methods 0.000 title claims abstract description 32
- 239000012530 fluid Substances 0.000 title claims abstract description 25
- 230000015572 biosynthetic process Effects 0.000 title claims abstract description 7
- 238000009527 percussion Methods 0.000 title claims abstract description 5
- 238000005755 formation reaction Methods 0.000 title abstract 2
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 4
- 238000013016 damping Methods 0.000 claims description 10
- 238000000926 separation method Methods 0.000 claims description 2
- 238000002637 fluid replacement therapy Methods 0.000 claims 1
- 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
- 241000209094 Oryza Species 0.000 description 3
- 235000007164 Oryza sativa Nutrition 0.000 description 3
- 230000001133 acceleration Effects 0.000 description 3
- 238000005520 cutting process Methods 0.000 description 3
- 229910052751 metal Inorganic materials 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 235000009566 rice Nutrition 0.000 description 3
- 230000035939 shock Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 230000035515 penetration Effects 0.000 description 2
- 230000001737 promoting effect Effects 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- 229910000639 Spring steel Inorganic materials 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
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000007600 charging Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000013467 fragmentation Methods 0.000 description 1
- 238000006062 fragmentation reaction Methods 0.000 description 1
- 239000010438 granite Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 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
- 239000003209 petroleum derivative Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000004576 sand Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
- UONOETXJSWQNOL-UHFFFAOYSA-N tungsten carbide Chemical compound [W+]#[C-] UONOETXJSWQNOL-UHFFFAOYSA-N 0.000 description 1
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)
- Physics & Mathematics (AREA)
- 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
A fluid pressure driven, high frequency percussion hammer for drilling in hard formations is presented. The hammer piston (20) of the percussion hammer has a relatively large and longitudinally extending bore (41 ) that provides minimal flow resistance for a drilling fluid flowing through the bore (41 ) during the return stroke of the hammer piston (20). The bore (41 ) is closeable in the upstream direction by a valve plug (23) that follows the hammer piston (20) during the stroke. The valve plug (23) is controlled by a relatively long and slender valve stem (49) that is mechanically able to stop the valve plug (23) by approximately 75 % of the full stroke length of the hammer piston (20) and separates the plug (23) from a seat ring (40). Thus the bore (41 ) opens up such that the bore fluid can flow there trough, and the inherent tension spring properties of the valve stem (49) returns the valve plug (23) so rapid that it will be good through flow during return of the hammer piston (20).
Description
Technical field
The present invention relates to a kind of hydraulic-driven, high-frequency percussion hammer for holing at hard formation, wherein this jump bit comprises: housing, one end of this housing is provided with drill bit, this drill bit design is for directly acting on hard formation, this jump bit also comprises: be movably received within the hammer piston in this housing, this hammer piston action is in drill bit, and this hammer piston has the longitudinal extension hole of predetermined amount of flow, and this elongated hole can be closed by valve plug in updrift side, this valve plug is partly followed this hammer piston in the stroke of hammer piston.
Background technology
For the hydraulically actuated impact of holing at rock, hammer business application into shape over 30 years.They use together with attachable drilling rod, and wherein drilling depth is restricted, and are because impact energy dies down at joint, and the weight of this drilling rod becomes overweight and passes to drill bit so that final energy seldom can arrive.
Down-the-hole hammer drill, that is, the hammer drill being installed on directly over drill bit is more effective, and to a great extent for dropping to the dark probing of 200-300 rice.They are by compressed air-driven and have the pressure that can reach about 22bar, and then this restriction drilling depth is to approximately 20 meters, if water enters into well.The hammer drill that water under high pressure drives is commercially available having surpassed 10 years, but these are all limited in size, this means up to approximately 130 millimeters of bore dias.In addition, known they there is the limited life-span and responsive for impurity in water.They are used to mining industry to a great extent, because they hole very effectively and get out very straight hole.They are used to the degree of depth that vertical drilling drops to 1000-1500 rice in limited degree, then, without any direction, control.
It is desirable to, manufacture the fluid-operated hammer drill of downhole drill bit, they can use together with Direction Control Aid, and its production efficiency is high, can make water as drilling fluid, also can use together with having the water-base drilling fluid of additive, and have the economic life-span.Expectation has very large purposes for deepwater drilling geothermal energy and hard recover petroleum and natural gas resource.
In Churn drill, the drill bit of use has the hard metal protuberance (lugs) of insertion, so-called " pressure head ".They are made by tungsten carbide, and typically have a diameter from 8 to 14 millimeters and have the end of spherical or taper.Under ideal situation, each pressure head should have the best impact energy relevant with compressive strength to the hardness of rock and clash into, so that there is little breach or pit on rock.Bit, to hit next time, ideally, forms the new breach being connected with previous breach.The number that the diameter of boring and geometry have determined pressure head.
Optimal impact energy is to be determined by the compressive strength of rock, and it can be holed in the rock higher than 300MPa in compressive strength.The impact energy that surpasses optimised quantity is provided, and overage can be because it be to lose for destroying rock, and Propagation of Energy ripple only.Too little impact energy can not produce breach.When the impact energy of each pressure head is known, and the number of pressure head is while being definite, can obtain the optimal impact energy of drill bit.Pull speed or drilling speed (ROP – penetration speed) then can only by improving frequency of impact, increase.
The amount of the drilling fluids pumping into is to be determined by the minimum necessary recovery rate (return rate) (ring speed) in the annulus between drill string and borehole wall.This at least should surpass 1 meter per second, is preferably 2 meter per seconds, so that the material coming outbreak out, drilling cuttings can be transported to ground.Rock is harder and crisp, and the frequency of impact providing is higher, and drilling cuttings is more in small, broken bits, and slower recovery rate or speed can be accepted.Hard rock and high-frequency will produce the drilling cuttings of dust or fine sand sample.
The hydraulic pressure effect (effect) being applied on hammer drill is multiplied by the unit interval amount of pumping into decision by pressure drop.
Each impact energy of hitting is multiplied by frequency and obtains effect.In the example of a hypothesis, the granite of being drilled has the compressive strength of 260 MPas and uses the bore diameter of 190 millimeters, water is pumped into from earth's surface with 750 liters/min (12.5 liters/second).According to calculating, best impact energy is about 900J.
Hole accordingly but have less diameter, with reference to known data, penetration rate (ROP) is the frequency of impact that 22 ms/h (being rice per hour) should have 60Hz.Here supposition increases frequency of impact to 95 hertz, so ROP is 35 ms/h.Then on drill bit, required net work effect has just become: 0.9 kilojoule x95=86 kilowatt.The mechanical-hydraulic effect that we suppose to hammer into shape at present that structure has is 0.89, then through this hammer, provides 7.7 MPas required Pressure Drop.
This hammer drill is fast 60% by the hammer drill promoting than existing available waterpower so, and saves 60% energy consumption.
Summary of the invention
This realizes by introducing the jump bit of the type, the outstanding feature of this hammer is: the valve rod being connected that valve plug receives slidably in stem sleeve is controlled, this valve rod comprises stop device, it can stop valve plug to hammer the predetermined percentage of the whole length of stroke of piston into shape, and valve plug is separated with the valve base seal on hammer piston, therefore this hole is opened, and allows to flow through fluid in this hole.
Preferably this stop device comprises check plate at the upstream termination of this valve rod, and in described stem sleeve, has crew-served interior stop surface.
In one embodiment, the predetermined percentage of the whole length of stroke of this hammer piston is about 75%.
Easily, the internal elasticity spring performance of valve rod is for replying valve plug, and this valve rod is elongated.
Preferably, this jump bit is also provided with inlet valve assembly, it can not be opened and for hammering the operation of piston into shape, until pressure accumulated, arrive approximately 95% complete operating pressure, this inlet valve assembly is suitable for closing main cylinder, and the side neck body in housing can exert pressure to seal this valve plug to hammer piston and the annular space promoting between the housing of this hammer piston at hammer.
Easily, this hammer piston and valve module can, by recoil return motion, wherein be hammered piston energy and valve module into shape and both be provided with the delay that stroke is replied in hydraulic damping control, until stop.
Easily, this hydraulic damping is carried out with annular piston, and this annular piston is pressed in the circular cylinder accordingly with controlled gap, thus the discharge of the fluid that restriction or retardance are held back.
Further, can opening be set at the top of this stem sleeve, the baffle plate of this valve rod can enter this opening, and the radial component of this baffle plate can be with the inner side of relatively narrow this opening of radial clearance seals.
Further, the service valve of annular can be arranged in the cannelure of this opening below, utilizes this service valve can open hole and in stem sleeve, packs liquid by this hole into.
This jump bit housing can be divided into: inlet valve housing, valve chest and hammer housing.
According to hammer drill structure of the present invention for being designated as the type of " straight moving hammer ", that is, this hammer piston has closed valve in the above, can promote piston forward when this valve is in the close position, and when open position, can make to hammer piston into shape and recoil.In hydraulic hammer type in the past, there is valve system, in above-mentioned two kinds of modes, by pressure, promote hammer piston simultaneously.This provides low efficiency, but piston can be controlled more accurately.
The key of high efficiency and high frequency of impact is on valve arrangement.This valve needs high frequency operation, and the flow behavior having had at open position.
Have great advantage simultaneously, the hydraulic-driven hammer that this hammer drill structure also can be installed as surface, is used from boring with drilling rod one, but will its situation as down-hole hammer drill be described in detail herein.
Accompanying drawing explanation
Other and further object of the present invention, feature and advantage are by by the description of the preferred embodiments of the present invention is become obviously, and these preferred embodiments are used for the object of describing, and are described with reference to accompanying drawing, wherein:
Fig. 1 has shown according to the schematic diagram of typical hydraulic pressure hammer drill of the present invention;
Fig. 2 A has shown the elevation of the down-hole hammer drill with drill bit;
Fig. 2 B has shown that the hammer drill of Fig. 2 A rotates the situation of approximately 90 °;
Fig. 2 C has shown the view of arrow A-A direction in Fig. 2 A;
Fig. 2 D has shown the view of arrow B-B direction in Fig. 2 A;
Fig. 3 A has shown the longitudinal sectional view of the hammer drill showing in Fig. 2 A, has wherein shown inside subject part;
Fig. 3 B has shown along the transverse sectional view of the line A-A of Fig. 3 A;
Fig. 3 C has shown along the transverse sectional view of the line B-B of Fig. 3 A;
Fig. 3 D has shown along the transverse sectional view of the line C-C of Fig. 3 A;
Fig. 3 E has shown along the transverse sectional view of the line D-D of Fig. 3 A;
Fig. 3 F has shown the twice zoomed-in view of the part H being lived by frame in Fig. 3 A;
Fig. 3 G has shown the twice zoomed-in view of the part H being lived by frame in Fig. 3 A;
Fig. 3 H has shown five times of zoomed-in views of the part F being lived by frame in Fig. 3 A;
Fig. 3 I has shown five times of zoomed-in views of the part G being lived by frame in Fig. 3 A;
Fig. 4 A shown corresponding to the structure shown in Fig. 3 A, but end in boost phase;
Fig. 4 B has shown the elevation of the valve module of the partial display in Fig. 4 A;
Fig. 4 C has shown along the transverse sectional view of the line B-B of Fig. 4 A;
Fig. 4 D has shown five times of zoomed-in views of the part A being lived by frame in Fig. 4 A;
Fig. 4 E has shown five times of zoomed-in views of the part C being lived by frame in Fig. 4 A;
Fig. 5 A shown corresponding to the structure shown in Fig. 3 A and 4A, but during shock surface in hammer piston impact drill bit;
Fig. 5 B has shown five times of zoomed-in views of the part A being lived by frame in Fig. 5 A;
Fig. 5 C has shown four times of zoomed-in views of the part B being lived by frame in Fig. 5 A;
Fig. 6 A shown corresponding to the structure shown in Fig. 3 A, 4A and 5A, but when hammer piston returns completely;
Fig. 6 B has shown along the part of the line E-E of Fig. 6 C;
Fig. 6 C has shown five times of zoomed-in views of the part A being lived by frame in Fig. 6 A;
Fig. 6 C ' has shown 20 times of zoomed-in views of the part D being lived by frame in Fig. 6 C;
Fig. 6 D has shown 20 times of zoomed-in views of the part C being lived by frame in Fig. 6 E;
Fig. 6 E has shown four times of zoomed-in views of the part B being lived by frame in Fig. 6 A;
Fig. 7 A has shown corresponding to Fig. 3 A, 4A, the structure shown in 5A and 6A, but the decline of this hour hammer piston in falling after rise;
Fig. 7 B has shown 20 times of zoomed-in views of the part B being lived by frame in Fig. 7 C;
Fig. 7 C has shown four times of zoomed-in views of the part A being lived by frame in Fig. 7 A;
Fig. 8 has shown the curve of describing the work period of hammer piston and valve;
Fig. 9 A has shown the curve of description valve with respect to the unexpected closing characteristics of Pressure Drop, and
Fig. 9 B has shown flow and the Pressure Drop when valve-off gradually.
The specific embodiment
Fig. 1 has shown typical in being connected to the hydraulic pressure hammer drill at the top of attachable drilling rod, wherein hammer the inside that structure is positioned at housing 1 into shape, this housing 1 consists of several housing parts, wherein rotation motor 2 makes drilling rod rotation via speed changer 3, these speed changer 3 rotations have the axle of threaded portion 4, and this threaded portion 4 will be screwed onto (not shown) on drilling rod and drill bit.Hammer machine is equipped with fixed head 5 conventionally, for being connected to the feeding mechanism of rig (not shown).Through pipeline and connector 6 sap pressure supply drive fluid, and return by thering are pipeline 6 hydraulic pressure of connector 7.
Fig. 2 A and 2B have shown the down-hole hammer drill with drill bit.These will be for the following description book.Shown housing 1 has the first housing parts 8, and the device of its reception will be described to 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 threaded portion 13 is received drill string (not shown) by hammer.Par 14 is set to torque wrench, hammer be screwed onto to drill string or back out from drill string.Drain hole 15 needs for the inlet valve of explaining after a while, and exists outlet opening 16 to be back to surface for the drilling fluids of the loop configuration between drill hole wall and hammer drill housing (not shown).Hard metal protuberance 17 is for compressing the element of the rock of being holed.Fig. 2 C has shown the view of the direction of arrow A-A in Fig. 2 A, and Fig. 2 D has shown the view of seeing towards drill bit 11 along arrow B-B direction in Fig. 2 A.
Fig. 3 A has shown the longitudinal sectional drawing of hammer drill, and wherein inner critical piece is: inlet valve assembly 18, valve module 19 and hammer piston 20.Drilling fluids is pumped to by entrance 12, by inlet valve in an open position 18, by the hole 21 showing on Fig. 3 B midship section figure 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 is shown as fastening position in the sectional drawing C-C of Fig. 3 D, and valve plug 23 abuts against hammer piston 20 and drives this piston abuts the base section 24 of drill bit.The D-D sectional drawing of Fig. 3 E has shown the lowermost portion of section of rack 25 and the hammer housing 10 of the longitudinal extension in this drill bit 11, transmits torque while moving axially in the acceptable space that they determine by locking circular ring structure 26 at drill bit 11.This is because by hammering the impact of 20 pairs of drill bits 11 of piston into shape, the quality of the parts that are only subjected to displacement or weight are consistent with the intrusion degree that this hard metal protuberance 17 enters rock.This is in order to make, impact energy as much as possible to be transferred in the fragmentation of rock, and reduces as far as possible the mass shift of relatively light drill bit 11.
In the detailed cross sectional view of Fig. 3 F, shown inlet valve in the close position 18, this sectional view is selected from the H in Fig. 3 A.When starting hammer function, start the operation that pumps into of drilling fluids in entrance 12.Through hole side or branch 27 of wall of valve chest 8 and bullport 28 hydraulic communication in the installing plate of inlet valve 18.This installing plate 29 is to be fixed in valve chest 8, and comprises pilot valve 30, and this pilot valve 30 remains on open position by spring 31.Drilling fluids flows freely into the guiding of first on the first guiding piston 32 chamber, and diameter and the Area Ratio entrance of this guiding chamber are large.When pressure increases, limited movably valve plug 33 will be forced to close on the valve seat 34 leaning against in housing 8.When the pressure of the inlet valve 18 to closing increases, the pressurized hole 27 through side of circulus 35 between housing 10 and hammer piston 20, it is through 36 pairs, hole entrance 37 chargings of the longitudinal extension in valve chest 9, referring to detailed view F.
Detailed cross sectional view in Fig. 3 H and Fig. 3 I is taken from F and the G of Fig. 3 A, and has shown that hammer piston 20 is against the situation of the inwall of hammer housing 9,10.The diameter of piston 38 is less times greater than the diameter of the second piston 39.By using hammer drill to hole vertically downward, under non-pressurized state, hammer piston 20 is by due to Action of Gravity Field, obviously the striking face in drill bit 11 or shock surface 24 move.In this case, hammer piston 20 between valve plug 23 and valve seat 40 by gapped (seeing detailed view F).Therefore, drilling fluids, by the own valve that flows through stopper 23 places, by the 41He hole, hole 16 (seeing Fig. 2 A) in hammer piston 20, therefore has pressure increase very little to occur for starting this hammer.
Setting in the detailed cross sectional view showing in Fig. 3 F, has the inlet valve 18 of closing and in circulus 35, has pressure accumulatedly, and this will hammer piston 20 into shape and promote to seal valve plug 23.Due to required gap between the surface at piston 38 and the inwall of housing 9, overflow by lubrication channel 42 and hole 43 in the space of drilling fluids from valve plug 23, as shown in arrow in detailed view F.In order to prevent this situation, this leakage rate should provide pressure to gather in the space on valve plug 23, and hole 44 and opening 45 in this valve installing plate 29 allowing by the pilot valve 30 of this position flow out, and further flow out by drain hole 15.90% when above of the operating pressure needing to hammer design when pressure rise, the piston force in the second guiding chamber 46 surpasses the closing force of spring 31, and pilot valve 30 is shifted, as shown in Fig. 3 G.
The first guiding chamber on guiding piston 32 is discharged from (drained) and inlet valve 18 is opened.In the pent while of opening 45, the draining by hole 44 is closed, and this makes can not lose by this hole in operator scheme downforce.Pressure in guiding chamber on hammer piston 20 and closed valve plug 23 makes to have the instant fully work period of effect to start.The time that drains that is arranged to reduce the second guiding chamber 46 of backup valve 47 and nozzle 48, thus realized the relatively slow closure of inlet valve 18.This makes inlet valve 18 keep opening completely, and can be under mode of operation because pressure is subsequently along with collision frequency fluctuation produces interference.
Fig. 4 A has shown the situation of hammer drill when boost phase finishes.Hammer piston 20 has now reached maximal rate, is conventionally about 6m/s.This is the result of following condition, and available pressure is for example only lower than 8MPa, the hydraulic pressure region of hammer piston, and for example diameter is 130mm here, and the weight of hammer piston, here 49kg for example.It is closed to the seat opening of hammer piston that valve plug 23 keeps, because the hydraulic pressure region of valve plug 23, here for example diameter is 95mm, and this region is more bigger than the annular region area of hammer piston, approximately large 4%, as shown in Fig. 4 C midship section B-B, is expressed as 23 and 24.This hour hammer piston has covered approximately 75% of its whole strokes, and all stroke is about 9mm.Gap between hammer piston 20 and the scope of attack 24 of drill bit is about 3mm, as amplified as shown in detailed view C in Fig. 4 E.
The movably valve rod 49 with check plate 50 shows on the adjacent surface of the standing valve rod sleeves 51 in housing 9, and stop valve rod 49 to be moved further, as shown in the detailed view A amplifying in Fig. 4 D, after this, valve plug 23 is hammered valve seat 40 separation of piston 20 into shape certainly, thereby is opened.Movably valve module 23,49, and 50 are shown in the elevation of Fig. 4 B.
The kinetic energy of valve plug 23 stops by urgency, slightly elongates relatively elongated valve rod 49, thereby is converted to relatively large spring force, and this spring force accelerates valve rapidly.The elongation slightly of valve rod 49, for example counts about 0.8mm herein, need to be lower than the utilization rate of material, and this material is high-strength spring steel in this case.The quality of valve plug 23 should be as much as possible little, for example made of aluminum here, and in conjunction with the length of valve rod 49, diameter and properties of materials, determined the intrinsic frequency of this valve module.
For practical application, this should minimum be its use frequency 8-10 doubly.This intrinsic frequency is to be determined by following formula:
Quality and spring constant have the most frequently used meaning.The intrinsic frequency of the structure of this demonstration is about 1100-1200Hz, therefore can be used for the situation that operating frequency surpasses 100Hz.
The rebound velocity of the structure shown in this embodiment is 93% of impact or stroke speed.
Fig. 5 A has shown position when hammer piston 20 clashes into the shock in drill bit 11 or adjacent surface and constantly.Valve plug 23 comprises valve rod 49 and baffle plate 50, the speed of this valve plug 23 in returning completely, detailed view A referring to Fig. 5 B, this makes relatively to set up rapidly a large opening between the valve seat 40 on valve plug 23 and hammer piston 20, so that drilling fluids can be crossed the longitudinal hole 41 in hammer piston 20 with relatively little drag stream, as shown in Fig. 5 B is detailed.
The kinetic energy of hammer piston 20 power is partly converted into the spring force on hammer piston 20, because some compression of piston in this knockout process.When the energy waves from impacting is transferred to relative end and back by hammer piston 20, hammer piston 20 is accelerated conversely.Originally return speed is calculated as approximately 3.2 meter per seconds herein, is about 53% of strike or impact velocity, and this is because part energy has been used to the mass shift of drill bit 11, and remaining energy is for making pressure head enter rock.
Fig. 6 A has shown the situation of hammer piston 20 in its complete return speed.Now valve plug 23 is almost back to terminal, and wherein in Fig. 6 C, detailed view A has shown and comprises that the bar 49 of baffle plate 50 enters the open top 52 of stem sleeve 51.
The radial component that detailed view D in Fig. 6 C ' has shown baffle plate 50 seals the private side of opening 52 as how relatively narrow radial clearance.When baffle plate 50, move last 2mm until produce little negative pressure in the chamber below this baffle plate 50 while stopping.Annular service valve 58 is opened and by hole 59 filled with fluid again.Baffle plate 50 volume restriction below or sealing can prevent that valve plug 23 from carrying out recoil and remaining on appropriate location, until next cycle starts.
The service valve 58 of " annular service valve " type, is annular leaf spring in the present embodiment, uses this leaf spring to be because it has little quality and relatively large spring force, therefore can be with high frequency work.
Detailed view B in Fig. 6 E has shown valve plug 23 in hammer piston 20 and the relatively large opening between valve seat 40, so that drilling fluids herein flows through with minimum resistance.The downside of stem sleeve 51 forms circular cylinder depression (pit) 53, as shown in the detailed view C in Fig. 6 D.The top of valve plug 23 forms annular piston 54, and this annular piston 54 passes through relatively narrow matched in clearance to circular cylinder depression 53.Following this valve and getting back to terminal always, the fluid volume of this restriction is discharged in the mode of controlling, and adds tap 55 discharge by the radial clearance between annular piston 54 and annular canister 53.This controlled discharge is as damping force, and stops the returning so that this valve does not carry out recoil of valve.The damping unit of same type is present on hammer piston 20.On detailed view B, be annular piston 56, be shown on the top of hammer piston 20, except the around shaping drum connected in star 57 of the bottom at valve chest 9.
Fig. 7 A has shown the decline of returning of hammer piston 20.The termination of backward stroke is prevented from a controlled manner, until stop completely when valve seat 40 runs into valve plug 23, is shown in the detailed view A in Fig. 7 C.Detailed view B in Fig. 7 B has shown how fluid volume restriction or airtight in circular cylindrical depression 57 moves through the radial clearance between annular piston 56 and drain hole 60.
Gap between valve seat 40 and valve plug 23 is without complete closure, so that accumulated pressure start the new cycle.Calculating shows, while using the opening of 0.5mm, Pressure Drop is roughly identical with operating pressure.This causes the surface pressing of the contact surface between valve plug 23 and valve seat 40 to diminish, and these assemblies can be used for a long time.
Fig. 8 has shown the curve of describing the work period of hammer piston 20 and valve.Curve A has shown velocity variations, and curve B has shown by the change in location of a work period.For two curves, transverse axis is time shaft, and unit is microsecond.
For curve A, the longitudinal axis represents the speed of Yim/sWei unit, towards the stroke direction of drill bit 11 be+make progress and-, refer to return speed here downwards.
The longitudinal axis of curve B has shown the distance from the YimmWei unit of starting position.Curved portion 61 represents boost phases, and wherein, point 62 is valve stops and it starts to return moment.Point 63 is corresponding to the impact of 20 pairs of drill bits 11 of hammer piston.
Curved portion 64 enters to the displacement in rock for drill bit 11, and 65 is the acceleration of resilience, and 66 for there is no the return speed of damping, and 67 for having the return speed of damping.Curved portion 68 is valve returns to acceleration, and 69 be the acceleration that returns that there is no damping of valve, and 70 is valve slows down the damping stage while returning.
Fig. 9 A has shown curve 71, and this curve has shown the unexpected closure feature for Pressure Drop and the valve plug 23 in hammer piston and the relation between the opening between valve seat 40 of valve.This situation as shown in Figure 9 B.Transverse axis is that unit is the opened gap of mm, the longitudinal axis be unit be bar with nominal rate, pump into drilling fluids time the Pressure Drop that designs, for example this nominal rate is 12.5L/s herein.As shown in the figure, before receiving a sizable pressure drag, closed gap need to be below 1.5mm.
Claims (10)
1. for the hydraulic-driven high-frequency percussion of holing at hard formation, hammer into shape for one kind, described jump bit comprises: housing (8, 9, 10), described housing (8, 9, 10) one end is provided with drill bit (11), described drill bit (11) is designed to directly act on hard formation, described jump bit also comprises: be contained in movably described housing (8, 9, 10) in and act on the hammer piston (20) on drill bit (11), described hammer piston (20) has the hole (41) of the longitudinal extension of predetermined amount of flow volume, and described hole (41) can be closed in the upstream direction by valve plug (23), described valve plug (23) part in the stroke of hammer piston (20) is followed described hammer piston (20), it is characterized in that, the valve rod being associated (49) that described valve plug (23) loads slidably in stem sleeve (51) is controlled, described valve rod (49) comprises stop device (50, 51), described stop device (50, 51) can stop described valve plug (23) with the predetermined percentage of the whole length of stroke of described hammer piston (20), and seat seal (40) separation from hammer piston (20) by described valve plug (23), described hole thereby (41) are opened, and make drilling fluids can flow through described hole (41).
2. jump bit according to claim 1, it is characterized in that, described stop device (50,51) is included in the baffle plate (50) of the upstream extremity of described valve rod (49), and the stop surfaces of the crew-served inside in described stem sleeve (51).
3. jump bit according to claim 1 and 2, is characterized in that, the predetermined percentage of the whole length of stroke of described hammer piston (20) is about 75%.
4. according to the jump bit described in claim 1,2 or 3, it is characterized in that, described valve rod (49) has the internal elasticity spring performance that makes valve plug (23) return motion, and described valve rod (49) is elongated.
5. according to the jump bit described in any one in claim 1-4, it is characterized in that, this jump bit also has inlet valve assembly (18), described inlet valve assembly (18) is not open until pressure accumulated to being about 95% of whole operating pressures to the operation of hammer piston (20), described inlet valve assembly (18) is suitable for closing main staving (12), and the side staving (27) in described hammer housing to hammer piston (20) and lifting described hammer piston (20) housing (10) between circulus (35) supercharging to seal described valve plug (23).
6. jump bit according to claim 5, it is characterized in that, described hammer piston (20) and valve module (18) be by recoil return motion, wherein said hammer piston (20) and valve module (18) be all provided with hydraulic damping with the delay of controlling reply stroke until stop.
7. jump bit according to claim 6, it is characterized in that, described hydraulic damping occurs by annular piston (54), described annular piston (54) is pushed into corresponding circular cylinder (53), described circular cylinder (53) thus the discharge that there is the restriction of controllable gap or block the fluid of holding back.
8. according to the jump bit described in any one in claim 1-7, it is characterized in that, opening (52) is arranged at the top of described stem sleeve (51), and the baffle plate (50) of described valve rod (49) can enter described opening (52), and the radial component of described baffle plate (50) seals the inner side of described opening (52) with relatively narrow radial clearance.
9. jump bit according to claim 8, it is characterized in that, annular service valve (58) is arranged in the ring-shaped groove of described opening (52) below, and hole (59) can be opened and pass through to described service valve (58) to the middle fluid replacement of stem sleeve (51).
10. according to the jump bit described in any one in claim 1-9, it is characterized in that, described jump bit housing (1) is divided into: 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 true CN103998706A (en) | 2014-08-20 |
| CN103998706B 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 |
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| 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 |
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- 2012-08-17 US US14/239,446 patent/US10385617B2/en active Active
- 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 CN CN201280040445.1A patent/CN103998706B/en active Active
- 2012-08-17 RU RU2014108528A patent/RU2607843C2/en active
- 2012-08-17 ES ES12825336T patent/ES2763384T3/en active Active
- 2012-08-17 CA CA2845789A patent/CA2845789C/en active Active
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| CA1071947A (en) * | 1976-10-08 | 1980-02-19 | Abraham Gien | Pneumatic hammer drill |
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Also Published As
| Publication number | Publication date |
|---|---|
| ES2763384T3 (en) | 2020-05-28 |
| RU2607843C2 (en) | 2017-01-20 |
| NO20111140A1 (en) | 2013-02-20 |
| EP2744966B1 (en) | 2019-10-02 |
| US10385617B2 (en) | 2019-08-20 |
| HUE047284T2 (en) | 2020-04-28 |
| DK2744966T3 (en) | 2019-12-16 |
| US20140174779A1 (en) | 2014-06-26 |
| CA2845789C (en) | 2021-03-09 |
| CN103998706B (en) | 2016-08-17 |
| EP2744966A4 (en) | 2016-07-20 |
| NO334793B1 (en) | 2014-05-26 |
| RU2014108528A (en) | 2015-09-27 |
| WO2013028078A1 (en) | 2013-02-28 |
| CA2845789A1 (en) | 2013-02-28 |
| PL2744966T3 (en) | 2020-05-18 |
| EP2744966A1 (en) | 2014-06-25 |
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