FI90277C - drilling - Google Patents

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Publication number
FI90277C
FI90277C FI900834A FI900834A FI90277C FI 90277 C FI90277 C FI 90277C FI 900834 A FI900834 A FI 900834A FI 900834 A FI900834 A FI 900834A FI 90277 C FI90277 C FI 90277C
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FI
Finland
Prior art keywords
valve
feed
throttle valve
pressure
spring
Prior art date
Application number
FI900834A
Other languages
Finnish (fi)
Swedish (sv)
Other versions
FI900834A0 (en
FI90277B (en
Inventor
Guenter Straub
Arno Pascher
Original Assignee
Sig Schweiz Industrieges
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Publication date
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Publication of FI900834A0 publication Critical patent/FI900834A0/en
Application granted granted Critical
Publication of FI90277B publication Critical patent/FI90277B/en
Publication of FI90277C publication Critical patent/FI90277C/en

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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
    • E21B44/00—Automatic control systems specially adapted for drilling operations, i.e. self-operating systems which function to carry out or modify a drilling operation without intervention of a human operator, e.g. computer-controlled drilling systems; Systems specially adapted for monitoring a plurality of drilling variables or conditions
    • E21B44/02—Automatic control of the tool feed
    • E21B44/06—Automatic control of the tool feed in response to the flow or pressure of the motive fluid of the drive
    • 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
    • E21B6/00—Drives for drilling with combined rotary and percussive action
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/20—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors controlling several interacting or sequentially-operating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/782—Concurrent control, e.g. synchronisation of two or more actuators

Landscapes

  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Earth Drilling (AREA)

Description

1 902771 90277

Pora us 1a i te· - Borrapparat.Pora us 1a i te · - Borrapparat.

Keksinto koskee kiviporaa suhteellisen pehmeassa kivi-lajissa tapahtuvaan kaivostyohon ja tunnelinrakennukseen, jos-sa pybrivat iskuporakoneet ovat edullisia ja on kuljettava eri kovuisten alueiden lapi. Tallaisissa laitteissa on pyorinta-koneisto poratangon pyorittåmiseen , iskukoneisto poratangon iskemiseen ja syoton kaytto. Tallaisissa tunnetuissa poraus-laitteissa voidaan tavallisesti saritaa pybrintakoneiston kier -roslukua, iskakoneiston iskutaajuutta ja tehoa seka sydtdn marirria. Asetus perustuu porattavaan kivilajiin ja siita saa-tuihin kokemuksiin. IJsein tapahtuu kuitenkin niin, etta lii-kuttaessa eteenpain porataan eri kivilajien lapi. Asetettavat arvot valitaan talloin kovimraan kivilajin mukaan eivatka ne ole parhaita mahdollisia pehmeammille kerroksille, mika johtaa louhinnan nopeuden pienenemiseen ja tyokalun kulumisen lisaan-tymiseen.The invention relates to a rock drill for mining and tunnel construction in a relatively soft rock type, where swiveling percussion drilling machines are inexpensive and have to be transported through areas of different hardness. Such devices include a rotating mechanism for rotating the drill rod, an impact mechanism for hitting the drill rod and the use of a bait. In such known drilling rigs, the rotational speed of the swinging machine, the stroke frequency and power of the percussion machine, and the heart rate can usually be serialized. The regulation is based on the type of rock to be drilled and the experience gained from it. However, IJsein happens that when moving forward, different types of rock are drilled. The values to be set are then selected according to the hardest rock type and are not the best possible for softer layers, which leads to a reduction in the excavation speed and an increase in tool wear.

Vaatimuksen 1 johdannon mukainen porauslaite tunnetaan CH-A 657 664 :sta. Tama asiakirja kuvaa iskuporauslaitetta, jossa on py orintakoneisto, iskukoneisto ja syoton kaytto. Po-raustehon parantamiseksi ohjauspaine otetaan ohjausventtiilille syoton kayton syottojohdosta. Iskutaajuuden tietty mukaut-taminen sybttotehoon onnistuu tosin nain, mutta kierrosluvun ja iskutaajuuden optimaalista mukauttamista eri kivilajien ko-vuuksiin ei voida saavuttaa.A drilling rig according to the preamble of claim 1 is known from CH-A 657 664. This document describes an impact drilling rig with a rotating mechanism, an impact mechanism and an inertial drive. In order to improve the drilling power, the control pressure is taken to the control valve from the supply line of the unused drive. Although a certain adjustment of the impact frequency to the sybtt power is possible, the optimal adjustment of the speed and the impact frequency to the hardness of different rock types cannot be achieved.

US-A-4 064 950 :sta on sinansa tunnettua, etta on edullis-ta sovittaa iskutaajuus pybrintakoneiston pydrimisnopeuteen.It is known per se from US-A-4,064,950 that it is advantageous to adjust the stroke frequency to the rate of swirling of the swing mechanism.

Kirjoituksessa ehdotetaan taman vuoksi, etta iskukoneisto ja py orintakoneisto kytketaan sarjaan. Tama ratkaisu ei kuitenkaan ole osoittautunut hyvaksi, silla iskuteho on siina kaantaen riippuvainen pybrintakoneiston tehosta.The paper therefore proposes that the percussion mechanism and the rotating mechanism be connected in series. However, this solution has not proved to be good, as the impact power is, depending on it, dependent on the power of the pinning machine.

US-A- 4 246 973:ssa jaUS-A-4 356 871 :ssa on kuvattu porauslait-teita, joissa iskukoneistoon tuleva paine, pybrintakoneistoon tuleva paine ja syoton kayttobn tuleva paine riippuvat toisis-taan .U.S. Pat. No. 4,246,973 and U.S. Pat. No. 4,356,871 describe drilling devices in which the pressure entering the impact mechanism, the pressure entering the swing mechanism and the pressure entering the feeder depend on each other.

KP-A-203 282 :n ehdotuksessa iskutaajuudesta tehdaan riippuvainen joko pybrintakoneiston vaantomomentista tai syottb- 2 90277 voimasta.The KP-A-203 282 proposal makes the impact frequency dependent on either the oscillation torque of the swing mechanism or the force of the feed.

Ps i11 n olevan keksinnon taustana on teht a ν,ϊ kehittaa alus-samainitun laista porauslaitetta siten, etta eri kivilajeissa voidaan saavuttaa optimaalinen porausteho. Tama tehtava rat-kaistaan vaatimuksen 1 tunnusmerkkien mukaisesti.The invention of Ps i11 n is based on the task of developing a ship-like drilling rig so that optimal drilling performance can be achieved in different rock types. This problem is solved according to the features of claim 1.

Keksinnon yh ta suoritusesimerkkia valaistaan seuraavassa piirustusten avulla, joissa kuvio 1 esittaa kaavion keksinnon mukaisesta poraus-laitteesta , kuvio 2 esittaa leikkauksen saadettavasta kur istimesta , ja kuvio 3 esittaa leikkauksen kuvion 2 mukaisen kuristimen vaihtoehdosta.One embodiment of the invention will now be illustrated by means of drawings, in which Figure 1 shows a diagram of a drilling rig according to the invention, Figure 2 shows a section of an available choke, and Figure 3 shows a section of an alternative to the choke of Figure 2.

Kuvion 1 porauslaitteen toimivat elimet on esitetty vain kaavamaisesti · Niita ovat pydrintakoneisto 1 poratangon 2 pyd-rittamiseen, iskukoneisto 3 poratangon 2 iskemiseen seka syo-ton kaytto 4 porauslaitteen 1, 2, 3 syottamiseen. Laitteessa on lisåksi ohjauslaite 5 pydrintakoneiston 1 py orimisnopeuden ja iskukoneiston 3 iskutaajuuden ja -tehon saStåmiseen seka toinen ohjauslaite 6 syottdvoiman ja -nopeuden saåtåmiseen.The operating members of the drilling rig of Fig. 1 are shown only schematically. The device further comprises a control device 5 for obtaining the rotational speed of the pressure mechanism 1 and the impact frequency and power of the impact mechanism 3, as well as a second control device 6 for obtaining the input force and speed.

Pydrintakoneisto 1 koostuu hydraulimoottorista 10 ja sen ulostuloakselista 15, joka on yhdistetty poratankoon 2 pyori-mattomasti. Iskukoneisto 3 koostuu sylinterista 12, jossa isku-mantaa 13 liikutetaan edestakaisin. IskumantS 13 iskee talloin vasten poratangon 2 takapaata, ensi sijassa esittåmatta jate-tyn alasimen valityksella. Pydrintakoneisto 1 ja iskukoneisto 3 on sijoitettu samaan, esittamatta jatettyyn koteloon, joka lisaksi sisaltaa iskukoneistoa 3 ohjaavan kiertoluistin 14. Kiertoluistia 14 kaytetaan akselilla 11 voimansiirtokoneiston 15 valityksella. Taman rakenteen ansiosta iskutaajuus on tark-kaan verrannollinen pyorintakoneiston 1 pyorimisnopeuteen. Tama on osoittautunut erittain edulliseksi pyorimisnopeuden ja iskutaajuuden sovittamisessa eri kivilajikovuuksiin . Poratanko 2 tekee kahden perrikk.aisen iskun valilla ennalta maaratyn kier-tokulman, joka on riippumaton pydrimisnopeudesta. Iskutehon parantamiseksi ja kiertoluistin 14 paineensyottdjohdon 16 ja paluujohdon 17 painesykinniin pitamiseksi pienena naihin joh-toihin on sijoitettu luistin 14 lahelle paineakut 18.The hydrating mechanism 1 consists of a hydraulic motor 10 and its output shaft 15, which is connected to the drill rod 2 without rotation. The percussion mechanism 3 consists of a cylinder 12 in which the percussion mandrel 13 is moved back and forth. The striker 13 strikes the rear end of the drill rod 2, primarily not shown at the appeal of the anvil. The pusher mechanism 1 and the impact mechanism 3 are housed in the same housing, not shown, which further includes a rotating slide 14 controlling the impact mechanism 3. The rotating slide 14 is driven on the shaft 11 by the choice of the transmission mechanism 15. Due to this structure, the impact frequency is exactly proportional to the rotation speed of the rotating mechanism 1. This has proven to be very advantageous in adapting the rotation speed and impact frequency to different rock type hardnesses. The drill rod 2 makes a predetermined rotation angle between two burst strokes, which is independent of the rate of rotation. In order to improve the impact power and to keep the pressure supply line 16 and the return line 17 of the circulating slide 14 small in the pressure pulses, pressure accumulators 18 are placed near the slide 14.

IIII

3 902773 90277

Hydrantimoottorin 10 ja syottojohdon 21 ja paluujohdon 22 valiin on kytketty 4/3-tieventtiili 23, jotta moottoria 10 voi-daan kayttåa myota- ja vastapåivaan. Venttiilin 23 ja moot torin 10 valisi in johtoihin 24, 25 on sijoitettu saadettavan kuristimen 26 ja takaiskuventtiilin 27 muodostamat rinnakkaiskytken-nat. Kuristimet 26 toimivat maåran saatimina, ja niita kayte-taan moot tor in 10 peruskierrosluvun saatnmiseen myota- ja vas-tapaivaan. Moottori 10 pyorii normaalisti vastapaivaan, jolloin johto 24 on kytketty syottojohtoon 21. Tahan johtoon 24 on kytketty rinnan venttiilin 23 ja kuristimen 26 kanssa suhteelli-suussaatoventtiili 28. Venttiili 28 avautuu jousen 29 voimaa vastaan ohjausjohtonsa 30 paineeseen nahden ver rannol lises ti ja paineistaa moottorin 10 ohivirtausjohdon 31 kautta lis.a-oljylla, niin etta moottori pyorii johdon 30 paineeseen n.ahden verrannol1 i sesti nopeammin.A 4/3-way valve 23 is connected between the hydrant motor 10 and the supply line 21 and the return line 22 so that the motor 10 can be operated counterclockwise and counterclockwise. In parallel in the selective lines 24, 25 of the valve 23 and the motor 10, parallel connections formed by the choke 26 and the non-return valve 27 are arranged. The chokes 26 act as ground transmitters and are used to transmit the base speed of the motor tor 10 to the myot and counterparts. The motor 10 normally rotates counterclockwise, the line 24 being connected to the supply line 21. A proportional orifice valve 28 is connected in parallel with the valve 23 and the throttle 26 to the line 24. The valve 28 opens against the force of the spring 29 to the pressure of its control line 30 through the bypass line 31 with additional oil, so that the engine rotates faster than the pressure of the line 30 by about two times.

Syoton kaytto 4 kasittaa hydraulisylinterin 35 ja mannan 36 seka mannanvarren 37, joka on yhteydessa pyorinta- ja isku-koneistojen 1, 3 koteloon (jota ei ole esitetty). Sylinterin 35 kamraiot 38, 39 ovat yhteydessa syottojohtoon 41 ja paluu-johtoon 42 4/3-tieventtiililla 40. Venttiilin 40 ja syottokam-mion 39 valiseen johtoon 43 on kytketty kaksinkertaisesti apu-ohjattu, asetettavalla jousivoimalla esikuormitettu paineen-saatoventtiili 44. Venttiilin 44 molemmat ohjauspaineet liit-tyvat kammioihin 38, 39. Poratangon 2 kosketuspaine voidaan syotettaessa nain rajoittaa venttiililla 44 asetettavaan arvoon kammion 38 paineesta riippumatta. Kammioon 38 johtava johto 45 liittyy venttiiliin 40 3/2-tieventtiilin 46 ensimmaisessa kyt-kentaasennossa saadettavisså olevan måaran saatimen 47 valityk-sella. Maaran saadin 47 rajoittaa syottonopeutta. Mannan 36 peraytyessa virtaa oljy ohivirtauksen 48 kautta, joka samalla kytkee venttiilin 46 takaisin ensimmaiseen asentoon ohjaus-kammion 49 avulla.The inoculated drive 4 feeds the hydraulic cylinder 35 and the manna 36 as well as the manna arm 37, which is connected to the housing of the rotating and percussion mechanisms 1, 3 (not shown). The chambers 38, 39 of the cylinder 35 are connected to the supply line 41 and the return line 42 by a 4/3-way valve 40. A double auxiliary, adjustable spring-loaded pressure supply valve 44 is connected to the line 43 between the valve 40 and the supply chamber 39. the control pressures are associated with the chambers 38, 39. The contact pressure of the drill rod 2 can thus be limited to a value to be set by the valve 44, regardless of the pressure in the chamber 38. The line 45 leading to the chamber 38 is connected to the valve 40 by a selection of a mare receiver 47 available in the first switching position of the 3/2-way valve 46. Maaran I got 47 to limit the feed rate. As the manna 36 retracts, the oil flows through the by-pass 48, which at the same time switches the valve 46 back to the first position by means of the control chamber 49.

Venttiilin 46 toisessa asennossa johto 45 liittyy yhteys-johdolla 55 såadettavaan kuristimeen 56. Sen poisvirtaus 57 johtaa saadettavan paineensaatoventtiilin 54 kautta sailioon 58. Tamå saatoventtiili 54 pitaa myos kuristimen 56 lapivir-tauksen ollessa pieni ylla suhteellisuussaatoventtiilin 28 , 90277 painetta. Ohjausjohto 30 on kytketty johtoon 55. Kuristin 56 on esitetty leikkauksena kuviossa 2. Pesan 62 lieriomaiseen reikaan 61 on laakeroitu siirtyvaksi uppomanta 63. Manta 63 menee tyontotiukasti teravareunaisen aukon 64 lapi. Aukko 64 erottaa pesassa 62 johtoon 55 liittyvan sisaantulokammion 65 johtoon 57 liittyvasta ulosmenokammiosta 66. Kammiossa 66 jou-si 67 painuu mannan 63 paatya vasten. Jousen esijannitys voi-daan asettaa ruuvilla 68. Manta 63 on lepoasennossa kantta 69 vasten. Mannan 63 pinnalla on sen keskustaan nrihden symmetri-sesti olevat, taaksepain syvenevat aksiaaliset urat 70. tlrien 70 polkkileikkaus suurenee mannan 63 jousen puoleisesta paasta ak siaa1 i se sti poispain mentaessa. Kuristimen poikki-leikkausala suurenee nain olien koko ajan mannan 63 iskun myo-ta, joka puolestaan on verranno 11inen kammioiden 65, 66 paine-eroon. Urien 70 poikkileikkauksen suurenerainen mannan 63 iskun myota on tarkoituksenmukaista mitoittaa siten, etta johtoon 55 syntyva virtauspaine on verrannollinen lMpivirtausmaaraan kuristimessa 56. Kun myos venttiili 28 aukeaa, on hydrauli-moottorin 10 kierrosluvun suureneminen verrannollinen syotto-nopeuteen.In the second position of the valve 46, the line 45 is connected to a throttle 56 provided by the connecting line 55. Its outflow 57 leads to the silo 58 via the pressure relief valve 54. This supply valve 54 also maintains the choke 56 with a low flow above the proportional relief valve 28, 90277. The guide line 30 is connected to the line 55. The choke 56 is shown in section in Figure 2. A recessed socket 63 is mounted to move into the cylindrical hole 61 of the housing 62. The socket 63 passes snugly through the sharp-edged opening 64. The opening 64 separates in the housing 62 the inlet chamber 65 connected to the line 55 from the outlet chamber 66 connected to the line 57. In the chamber 66 the spring 67 presses against the end of the manna 63. The spring preload can be set with the screw 68. The manta 63 is in the rest position against the cover 69. The surface of the semolina 63 has axially grooved, symmetrically retracted axially grooves 70. The pedal section of the mandrels 70 increases from the spring-side end of the semolina 63 as it is displaced. The cross-sectional area of the choke thus increases all the time due to the stroke of the manna 63, which in turn is proportional to the pressure difference of the chambers 65, 66. The large cross-section of the grooves 70 due to the stroke of the manna 63 is expediently dimensioned so that the flow pressure in the line 55 is proportional to the flow rate in the throttle 56. When the valve 28 also opens, the speed of the hydraulic motor 10 increases with the feed rate.

Kokeet ovat osoittaneet, etta pyorintakoneiston 1 pyorimisnopeuden ja iskukoneiston 3 taajuuden lahes suora-viivaisella riippuvuudella syoton kayton 4 nopeudesta voidaan saavuttaa laajalla kivilajien kovuusalueella optimaalinen syottoteho. Tama on yhtapitavaa jo aiemmin havaitun pyorintakoneiston pyorimisnopeuden ja iskukoneiston iskuluvun suoran kytkennan edullisuuden kanssa. Sama edullinen suhde liittyy esilla olevassa keksinnossa kolmanteen muuttujaan.Experiments have shown that with an almost straight line dependence of the rotation speed of the rotating mechanism 1 and the frequency of the impact mechanism 3 on the speed of the feedless drive 4, an optimal feeding power can be achieved over a wide range of rock hardness. This is consistent with the previously observed advantage of direct coupling of the rotational speed of the rotating mechanism and the stroke of the impact mechanism. The same preferred ratio relates to the third variable in the present invention.

Kaytossa porareika aloitetaan venttiili 46 neutraalissa asennossa. Paineensaatoventtiililla 44 asetetaan porareian ko-vimman odotettavissa olevan kivilajin vaatima optimaalinen kosketuspaine. Myos kuristimen 26 asetus maMraytyy kovimman odotettavissa olevan kivikerroksen mukaan. Alkuporauksen kan-nalta tarkean maarin saatimen 47 asetus sita vastoin tehdaan ensimmaisena porattavana olevan kivilajin optimaalisen syotto-nopeuden mukaan. Kun porareian alku on porattu, venttiilin 46 suunta muutetaan. Jos poran paa sitten porauksen aikana tormari li 5 90277 pehmeampaan kiveen, sybttonopeus kasvaa, koska kosketuspaine pysyy vakiona. Talloin kohoaa virtauspaine kuristimen 56 edes-sa ja samalla myos saatoventtiilin 28 ohjauspaine. Moottoriin 10 ohjautuu talloin lisaå oljya ohivirtausjohdon 31 kautta, niin etta se pybrii nopeammin, jolloin myos iskutaajuus kasvaa voimansiirtokoneiston 15 kautta. Pyorimisnopeus ja iskutaajuus mukautuvat siis automaattisesti optimaalisesti sybttbnopeuteen. Vain voidaan samalla myos minimoida tyokalun kuluminen. Isku-taajuuden kasvaessa yksittåisen iskun energia pienenee, mika pehmeåa kivea porattaessa onkin toivottavaa.In use, the borehole is started with the valve 46 in the neutral position. The pressure relief valve 44 sets the optimum contact pressure required for the hardest expected rock type in the borehole. The setting of the choke 26 also depends on the hardest stone layer to be expected. On the other hand, the setting of the accurate drill 47 for the initial drilling is made according to the optimal feed rate of the first type of rock to be drilled. Once the beginning of the borehole is drilled, the direction of the valve 46 is changed. If the drill then drills into a softer rock during drilling, the firing speed increases because the contact pressure remains constant. In this case, the flow pressure in front of the choke 56 rises and at the same time the control pressure of the supply valve 28 also increases. Additional oil is then directed to the engine 10 via the bypass line 31, so that it rotates faster, whereby the stroke frequency also increases through the transmission mechanism 15. Thus, the rotation speed and the stroke frequency automatically adapt optimally to the sybttb speed. Only at the same time can tool wear be minimized. As the impact frequency increases, the energy of a single impact decreases, which is desirable when drilling soft rock.

Ruuvilla 63 voidaan saataa ohi virtauksen 31 kytkeytymisen alkamista. Jos halutaan, etta myos pyorimisnopeuden riippuvuut-ta voidaan saataa, jousen 67' jousivakiosta voidaan tehda muut-tuva, kuten kuviossa 3. Jousi 67' on siina taivutusjousi. Jousen 67' vapaata pituutta ja nain olien myos sen jousivakiota voidaan siina saataa kengalla 73. Kenkaa 73 voidaan siirtaa asetusruuvilla 74.The screw 63 can be used to delay the start of the switching of the flow 31. If it is desired that the rotation speed dependence can also be obtained, the spring constant of the spring 67 'can be made variable, as in Fig. 3. The spring 67' is the bending spring. The free length of the spring 67 'and thus also its spring constant can be brought there by the shoe 73. The shoe 73 can be moved by the adjusting screw 74.

Claims (9)

1. Borrapparat, i vilken firms ett rotationsmaskineri (1) for att vrida runt borrstången (2), ett stotverk (3) for att ge derma stotverkan, anvåndning av matning (4) for att mata rotationsmaskineriet (1), stotverket (3) och borrstången (2), en styrinråttning (5) for att stal la in rotationsmaskineriets (1) varvtal och stotverkets (3) slagfrekvens samt en andra styrinråttning (6) for att stålla in matningen, kannetecknad darav, att den ena styrinråttningen (6) innehåller ett måtningsorgan (56) for att mata matningshastigheten, och att måtningsorganet (56) år i forbindelse med styrinråttningen (5), sålunda att rotationsmaskineriets (1) varvtal och stotverkets (3) stotfrekvens våxer når matningshastigheten tilltar.A drilling apparatus in which there is a rotary machinery (1) for rotating the drill rod (2), a thrust unit (3) for providing this thrust action, use of feed (4) for feeding the rotary machinery (1), the thrust unit (3). and the drill rod (2), a guide device (5) for adjusting the rotational machinery (1) speed and thrust frequency (3) stroke frequency, and a second guide device (6) for setting the feed, characterized therefrom, that one guide device (6) contains a measuring means (56) for feeding the feed rate, and the measuring means (56) is in connection with the control device (5), so that the rotational speed of the rotary machine (1) and the throttle frequency (3) increase as the feed rate increases. 2. Borrapparat enligt patentkrav 1, kannetecknad dårav, att stotverket (3) omf attar en cylinder (12) med slagkolv (13) som styrs av en slid (14) och rotationsmaskineriet (1), en hydraulikmotor (10) vårs utkommande axel (11) år kopplad till sliden (14) med ett kraftoverforingsverk (15).2. Drilling apparatus according to claim 1, characterized in that the thrust unit (3) comprises a cylinder (12) with impact piston (13) which is guided by a slide (14) and the rotary machinery (1), a hydraulic motor (10) coming out of the spring ( 11) years connected to the slide (14) with a power transmission plant (15). 3. Apparat enligt patentkrav 2, kannetecknad dårav, att anvåndningen av matning (4) omfattar ett dubbelverkande hydraulikcylinderaggregat (35,36) och att matningsorganet (56) under tiden for hydraulikaggregatets (35,36) matning år en vattenforingsmåtare (56) som firms i den till returstromningen kopplade forstå cylinderkammarens (38) retur ledning.3. Apparatus according to claim 2, characterized in that the use of feed (4) comprises a double-acting hydraulic cylinder assembly (35,36) and that the feed means (56) during the feeding of the hydraulic unit (35,36) is a water-feeding meter (56) provided in the return flow connected to the return flow understand the return line of the cylinder chamber (38). 4. Apparat enligt patentkrav 3, kannetecknad dårav, att i den andra cylinderkammarens (39) ledning (43) som firms mittemot cylinderkammaren (38) skall placeras entryckregleringsventil (44) som styrs av tryckski1lnaden mellan cylinderkamrama (38,39) och varmed man ståller in matningskraften som år oberoende av matningshastigheten.4. Apparatus according to claim 3, characterized in that in the conduit (43) of the second cylinder chamber (39) which is opposite the cylinder chamber (38), an entry control valve (44) is controlled, which is controlled by the pressure difference between the cylinder chambers (38,39) and in feed power which is independent of feed rate. 5. Apparat enligt patentkrav 3 eller 4, kannetecknad darav, att vattenforings-måtaren år en reglerbar strypventil (56) som ger ett s tromn ings tryck som år beroende av vattenstromningen och att detta stromningstryck år kopplat till stymingskvantiteten hos styrningsinråttningens (5) regler ingsventil (28) varvid reglcringsventilen (28) oppnar sig då strdmningstrycket våxer.5. Apparatus according to claim 3 or 4, characterized in that the water liner meter is an adjustable throttle valve (56) which gives a drum pressure which is dependent on the water flow and that this flow pressure is coupled to the control quantity of the control device (5) control valve. (28) wherein the control valve (28) opens as the flow pressure increases. 6. Apparat enligt patentkrav 5, kannetecknad dårav, att i våtskemotoms (10) matningsledning (21,24) år placerad en koppiingsventi1 (23) och en stållbar II 9 90277 strypventil (26) och att regleringsventilen (28) år placerad i kopplingsventi-lens (23) och den stallbara strypventilens (26) forbistromning (31).6. Apparatus according to claim 5, characterized in that in the supply line (21,24) of the liquid engine (10) a coupling valve (23) and an adjustable throttle valve (26) are placed and that the control valve (28) is placed in the coupling valve. lens (23) and bypass flow (31) of the adjustable throttle valve (26). 7. Apparat enligt patentkrav 5 och 6, kannetecknad darav, att den ena styr-ningssinråttningen (6) innehåller en kopplingsventil (46) som leder till cylinderkammarens (38) returstromning (45) antingen via den stallbara strypven-tilen (47) eller den reglerbara strypventilen (56).Apparatus according to claims 5 and 6, characterized in that one of the control devices (6) contains a switching valve (46) which leads to the return flow (45) of the cylinder chamber (38) either via the stowable throttle valve (47) or the adjustable throttle valve (56). 8. Apparat enligt något av patentkraven 5-7, kannetecknad darav, att den reglerbara strypventilen (56) innehåller en fjåderbelastad plungerkolv (63) som reagerar for tryckskillnaden mellan strypventilens (56) ingångs- och utgångs-tryck (65,66) och som går genom en oppning (64) och att åtminstone en i kolvaxelns riktning gående fåra (70) har inarbetats i kolvens (63) yta.Apparatus according to any of claims 5-7, characterized in that the adjustable throttle valve (56) contains a spring-loaded plunger piston (63) which responds to the pressure difference between the input and output pressure (65,66) of the throttle valve (56) and which passes through an aperture (64) and at least one groove (70) extending in the direction of the piston shaft has been incorporated into the surface of the piston (63). 9. Apparat enligt patentkrav 8, kannetecknad darav, att forspånningen och/eller fjåderkonstanten hos fjådem (67) som belastar kolven (63) kan stallas in.9. Apparatus according to claim 8, characterized in that the bias and / or spring constant of the spring (67) loading the piston (63) can be adjusted.
FI900834A 1989-02-23 1990-02-20 drilling FI90277C (en)

Applications Claiming Priority (2)

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CH66089 1989-02-23
CH66089 1989-02-23

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FI90277C true FI90277C (en) 1994-01-10

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FI115552B (en) 2002-11-05 2005-05-31 Sandvik Tamrock Oy Arrangement for controlling rock drilling
SE532483C2 (en) 2007-04-11 2010-02-02 Atlas Copco Rock Drills Ab Method, apparatus and rock drilling rig for controlling at least one drilling parameter
CN102536141B (en) * 2012-01-20 2013-11-06 中船重工中南装备有限责任公司 Automatic drill-rod-replacing control system for rock-drilling drill carriage
CN103758802B (en) * 2014-01-24 2016-01-13 长沙金阳机械设备科技开发有限公司 Automatic drill feed liquor pressure control system and operating vehicle
DE102015107194A1 (en) * 2015-05-08 2016-11-10 TERRA AG für Tiefbautechnik Drilling rig for generating or expanding a ground hole in the ground and method for controlling a feed drive of such a rig
CN106351900B (en) * 2016-09-27 2018-12-18 桂林航天工业学院 A kind of anti-deflection rock drilling control system
CN111101859A (en) * 2019-11-08 2020-05-05 四川诺克钻探机械有限公司 Drilling pressure adjusting method of coring drilling machine for railway engineering exploration

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US4064950A (en) * 1976-07-19 1977-12-27 Pekka Salmi Hydraulic drilling machine
US4271914A (en) * 1976-12-02 1981-06-09 The United States Of America As Represented By The Secretary Of The Interior Automatic feed and rotational speed control system of a hydraulic motor operated drill
US4246973A (en) * 1978-01-23 1981-01-27 Cooper Industries, Inc. Controls for hydraulic percussion drill
US4440236A (en) * 1979-09-20 1984-04-03 Toyo Kogyo Co. Ltd. Hydraulic control system for a rock drill
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DE3518892C1 (en) * 1985-05-25 1987-02-26 Klemm Bohrtech Hydraulic hammer drill

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FI900834A0 (en) 1990-02-20
DE59000150D1 (en) 1992-07-16
AU4917490A (en) 1990-08-30
AU630914B2 (en) 1992-11-12
FI90277B (en) 1993-09-30
EP0384888A1 (en) 1990-08-29
EP0384888B1 (en) 1992-06-10

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