EP0733153B1 - Hydraulischer schlagantrieb - Google Patents

Hydraulischer schlagantrieb Download PDF

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Publication number
EP0733153B1
EP0733153B1 EP95919255A EP95919255A EP0733153B1 EP 0733153 B1 EP0733153 B1 EP 0733153B1 EP 95919255 A EP95919255 A EP 95919255A EP 95919255 A EP95919255 A EP 95919255A EP 0733153 B1 EP0733153 B1 EP 0733153B1
Authority
EP
European Patent Office
Prior art keywords
control
chamber
valve
piston hammer
pressurized
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP95919255A
Other languages
English (en)
French (fr)
Other versions
EP0733153A1 (de
Inventor
Per Gustafsson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
G-DRILL AB
G Drill AB
Original Assignee
G-DRILL AB
G Drill AB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by G-DRILL AB, G Drill AB filed Critical G-DRILL AB
Publication of EP0733153A1 publication Critical patent/EP0733153A1/de
Application granted granted Critical
Publication of EP0733153B1 publication Critical patent/EP0733153B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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

Definitions

  • This invention relates to a hydraulic impact motor of the kind defined in the precharacterizing part of claim 1.
  • it relates to an in-hole rock drilling machine.
  • valve is a spool valve with two control surfaces for shifting the valve between its two stable positions.
  • One of the control surfaces is continuously pressurized during the drilling operation and the other is pressurized and depressurized through a control passage that has ports against the surface of the piston hammer that is in sliding contact with the cylinder.
  • the sliding surface of the piston hammer has a control groove that is axially long, which makes the guided surface of the hammer piston long. A long guided surface is detrimental to the expected life. Further, the leakage from the two cylinder chambers for driving the hammer piston reduces the power efficiency.
  • Figures 1 and 2 are together a side view of an in-hole rock drilling machine in accordance with the invention; Figure 1 shows the rear part of the machine and Figure 2 shows the front part, An intermediate part of the machine is not shown.
  • the in-hole rock drilling machine shown in the Figures has a housing, the main part of which is a cylindrical tube 12 that has an interior shoulder 13 and interior threads in each end.
  • a drill bit 14 is maintained in the housing by means of a sleeve 15 screwed into the tube 12.
  • the sleeve 15 is in splined connection with the drill bit.
  • the drill bit is guided in the housing by the sleeve 15 and a guiding bushing 16 and a stop ring 17 prevents the drill bit from falling out.
  • the drill bit 14 is thus axially movable a limited distance in the housing 12 and it cannot turn relative to the housing.
  • the drill bit 14 has an axial flushing fluid passage that ends in flushing fluid ejecting holes in its front surface.
  • a guide bushing 18 takes support against the shoulder 13 and a distance sleeve 19 takes support against the guide bushing 18.
  • a valve housing 20 with a back head 38 takes support against the distance sleeve 19. and and a tube formed filter support 21 with a filter 21a takes support against the back head 38 of the valve housing 20.
  • a backhead 22 of the machine housing is screwed into the rear end of the tube 12 and it is arranged to axially clamp the parts 18,19,20,38,21 against the shoulder 13. These parts 18,19,20,38,21 act together as a spring and their cumulative lenght is such that they are compressed when the backhead 22 is screwed into place.
  • the overall axial compression is 0.4 - 2 mm.
  • the distance sleeve 19 contributes most to this compression because of its dominating length and its comparatively small steel area in its cross section. It is adapted to be compressed at least 0.3 and preferably 0.8 - 3 pro mille of its length.
  • the filter support 21 may have about the same cross section area of steel as the distance sleeve 19, but it is shorter and its contribution to the spring action is therfore smaller.
  • the back head 38 of the valve housing 20 is thus clamped against the main part of the valve housing 20.
  • the back head 22 of the machine housing is arranged to be screwed to a conventional drill tubing that transmits rotation to the drilling machine and also transmits hydraulic drive fluid in the form of pressure water to the drilling machine.
  • the annular space 58 at the back of the valve housing 20 is thus continuously filled with filtered water under pressure.
  • a tube 23 forms part of the valve housing 20.
  • a piston hammer 24 with a through channel 25 has its front end guided in the guide bushing 18.
  • the rear end 27 of the piston hammer 24 extends into an annular cylinder chamber 26 (drive chamber) that is formed in the valve housing 20 between the sleeve-like front portion 35 of the valve housing and the tube 23 of the valve housing.
  • the rear end of the piston hammer 24 is thus guided by the walls of the cylinder chamber 26, that is, by the valve housing 20.
  • the rear end 27 of the piston hammer 24 has a groove 28 with a rear end wall 29 so that the piston hammer 20 has a defined outer guiding surface 30 behind the end wall 29.
  • the piston hammer 24 has also an interior guiding surface 31 of defined length.
  • the outer and inner guiding surfaces 30,31 could have about the same length.
  • the actual length of the guiding surfaces is defined by the guiding surfaces 18 (at the front end of the piston hammer) and 30,31 ⁇ at the rear end of the piston hammer) and it takes up only a minor part of the length of the piston hammer 24.
  • the actual length of guiding is less than 20% of the length of the piston hammer.
  • the major part 32 of the piston hammer 24 is between these guiding surfaces and it has a wide clearance to the distance sleeve 19 of the machine housing 12.
  • the major part 32 of the piston hammer 24 can be radially enlarged as compared with its guided end portions.
  • the guiding surface 33 of the piston hammer sliding against the guide bushing 18 has a smaller diameter than the guiding surface 30 against the valve housing 20 so that the piston hammer will have a differential piston area in the front drive chamber 34 that is formed axially between the guide bushing 18 and the valve housing 20. If the groove 28 and the front guiding surface 33 have the same diameter, then this differential area is represented by the area 36, that is, by the area of the rear wall 29 of the groove 28. This differential area is smaller than the annular piston area 37 in the rear cylinder chamber 26.
  • the valve housing 20 contains a spool valve 40 with three control surfaces A1,A2,A3 that are in three annular control chambers 45,46,47.
  • the effective area of surface A3 is a differential area since the diameter of the sliding surface of the valve 40 close to the surface A1 is greater than the diameter of the sliding surface close to the surface A2.
  • the relation between these areas is A3 ⁇ A1 ⁇ A2+A3.
  • the area A2 is greater than the area A3 and suitably, A1 and A2 can be equal or about equal and about twice as large as A3.
  • the valve 40 has a row of large holes 50 and two small holes 51.
  • a control conduit 52 leads between the annular chamber 46 and the rear cylinder chamber 26 and it has a control port 53 into the rear cylinder chamber 26.
  • Another control condit 54 leads between the annular chamber 45 and the rear drivechamber 26 and it has control ports 55 and 56 to the drive chambers 26 and 34 respectively.
  • a number of parallel channels 57 lead axially through the valve housing 20 and connect the front drive chamber 34 with the continuously pressurized space 58 at the rear of the valve housing 20.
  • a number of channels 59 connect a row of ports 60 into the rear drive chamber 26 with a row of ports 61 into the annular chamber 48.
  • a number of channels connect a row of ports 62 into the annular chamber 47 with the continuously pressurized space 58 at the back of the valve housing 20.
  • valve 40 connects the rear cylinder chamber 26 with the chamber 58 that is continuously under pressure.
  • the control surface A1 of the valve is under pressure during the entire work stroke of the piston hammer 24 since the control port 56 of the control passage 54 is at first open to the continuously pressurized front drive chamber 34 and then, shortly after the closing of the port 56, the control port 55 of the control passage 54 is instead opened to the rear drive chamber 26 which is under pressure.
  • the length of the guide surface 30 of the piston hammer can be such that both ports 56 and 55 are closed during a short period, which, however, will be so short that it will not influence the pressure in the control passage 54.
  • the valve 40 will therefore remain stable in its illustrated forward position because the area A1 overcomes the area A3. The leakage from the annular chamber 46 prevents a pressure build up in the annular chamber 46.
  • the valve 40 is dampened by its nose 65 cutting off a damping chamber so that the valve is retarded before it lands in its rear non-illustrated position and it will therefore not tend to rebounce.
  • the annular chamber 48 is cut off from the annular chamber 47 and is instead coupled to the interior of the valve through the holes 50 in the valve.
  • the rear drive chamber 26 will therefore be depressurized simultaneously with the piston hammer reaching its impacting position, and the continuously pressurized front drive chamber 34 starts to drive the piston hammer rearwardly in its return stroke.
  • control ports 53 and 55 can be varied and the control port 53 need not be axially forwardly of the port 55.
  • the water that flows out of the rear drive chamber 26 during the return stroke of the piston hammer 24 is thus utilized as a flushing fluid for flushing the debris out of the borehole.

Landscapes

  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
  • Percussive Tools And Related Accessories (AREA)

Claims (4)

  1. Hydraulischer Schlagantrieb, bestehend aus:
    einem Gehäuse (12)
    einem Kolbenhammer (24), der sich in diesem Gehäuse hin- und herbewegen kann und durch den Druck in zwei Druckkammern (26, 34) in einer Hin- und Herbewegung getrieben wird,
    einem Ventil (40) zum abwechselnden Unter-Druck-Setzen und Druck-Ablassen in mindestens einer dieser Druckkammern, um den Kolbenhammer hin- und herzubewegen,
    wobei dieses Ventil in einer ersten Steuerkammer (45) eine erste Steuerfläche (A1) und in einer zweiten Steuerkammer (46) eine zweite Steuerfläche (A2), die entgegengesetzt zu dieser ersten Steuerfläche gerichtet ist, aufweist,
    wobei diese erste und diese zweite Steuerkammer (45, 46) so angeordnet sind, daß sie je nach Position des Kolbenhammers unter Druck gesetzt und drucklos gemacht werden, und zwar durch Steueröffungen (53, 55, 56), die vom Kolbenhammer gesteuert werden, und Steuerleitungen (52, 54),
       dadurch gekennzeichnet, daß eine dritte Steuerfläche (A3) des Ventils in einer ständig unter Druck stehenden Kammer (47) vorgesehen ist, die in der gleichen Richtung wirkt wie die zweite Steuerfläche (A2), wobei diese zweite und diese dritte Steuerfläche (A2, A3) größer sind als diese erste Steuerfläche (A1), und die erste Steuerfläche (A1) größer ist als die dritte Steuerfläche (A3), so daß das Ventil (40) sich in die eine Richtung bewegt, wenn die erste Steuerkammer (45) unter Druck gesetzt wird und die zweite Steuerkammer (46) drucklos gemacht wird, und sich in die andere Richtung bewegt, wenn die erste und die zweite Steuerkammer (45, 46) unter dem gleichen Druck stehen.
  2. Schlagantrieb nach Anspruch 1, dadurch gekennzeichnet, daß diese erste Steuerkammer (45) so angeordnet ist, daß sie von einer dieser Antriebskammern (26) für den Kolbenhammer (24) unter Druck gesetzt wird, um die Bewegung des Ventils (40) in die genannte erste Richtung einzuleiten, und daß die zweite Steuerkammer (46) so angeordnet ist, daß sie von der anderen dieser Antriebskammern (34) unter Druck gesetzt wird, um die Bewegung des Ventils (40) in die andere Richtung einzuleiten.
  3. Schlagantrieb nach einen der vorherigen Ansprüche, dadurch gekennzeichnet, daß der Kolbenhammer (24) an seinem vorderen Ende und an seinem hinteren Ende geführt wird und zwischen diesen nicht geführt wird, daß zwischen einer Fläche (37) in dieser einen Antriebskammer (26), die die hintere Antriebskammer bildet, und einer Fläche (36) in der anderen Antriebskammer (34), die eine ständig unter Druck stehende, vordere Antriebskammer ist, eine hintere Steuerfläche zur Steuerung des Ventils (40) gebildet wird, daß die Steuerleitung (54) zur ersten Steuerkammer (45) eine Öffnung (56) aufweist, die dergestalt angeordnet ist, daß sie sich zu der vorderen Antriebskammer (34) hin öffnet, und eine Öffnung (55) aufweist, die dergestalt angeordnet ist, daß sie sich zu der hinteren Antriebskammer (26) hin öffnet, und daß die Steuerleitung (52) zu dieser anderen Steuerkammer (46) eine Öffnung (53) aufweist, die dergestalt angeordnet ist, daß sie sich zu der hinteren Antriebskammer (26) hin öffnet.
  4. Schlagantrieb nach einen der vorherigen Ansprüche, dadurch gekennzeichnet, daß er eine Loch-Gesteinsbohrmaschine ist und das aus dem Ventil (40) ausgestoßene, verbrauchte Antriebsfluid als Spülfluid durch einen Kanal (25) in dem Kolbenhammer (24) zu dem Bohrmeißel (14) der Bohrmaschine befördert wird.
EP95919255A 1993-12-13 1994-12-13 Hydraulischer schlagantrieb Expired - Lifetime EP0733153B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
SE9304124A SE505171C2 (sv) 1993-12-13 1993-12-13 Ventilslid i ett hydrauliskt slagverk
SE9304124 1993-12-13
PCT/SE1994/001196 WO1995016847A1 (en) 1993-12-13 1994-12-13 A hydraulic impact motor

Publications (2)

Publication Number Publication Date
EP0733153A1 EP0733153A1 (de) 1996-09-25
EP0733153B1 true EP0733153B1 (de) 2000-03-15

Family

ID=20392072

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95919255A Expired - Lifetime EP0733153B1 (de) 1993-12-13 1994-12-13 Hydraulischer schlagantrieb

Country Status (8)

Country Link
EP (1) EP0733153B1 (de)
JP (1) JP3393139B2 (de)
KR (1) KR100326485B1 (de)
AU (1) AU685891B2 (de)
DE (1) DE69423511T2 (de)
ES (1) ES2146313T3 (de)
SE (1) SE505171C2 (de)
WO (1) WO1995016847A1 (de)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19625724A1 (de) * 1996-06-27 1998-01-02 Nordmeyer Gmbh & Co Kg Flüssigkeitsbetriebener Bohrhammer für Bohrarbeiten
SE9702547L (sv) * 1997-07-02 1998-06-29 Uniroc Ab Sänkborrmaskin med dubbla drivareor för slagkolvens arbetsslag och returslag
SE515730C2 (sv) * 2000-05-05 2001-10-01 G Drill Ab Borrkroneinfästning
NO313467B1 (no) 2001-01-05 2002-10-07 Bakke Technology As Anordning ved hydraulisk slagverktøy
DE10352747A1 (de) * 2003-11-12 2005-06-16 Rolf Bartholet Tiefloch-Bohrhammer
KR101352302B1 (ko) * 2010-11-22 2014-01-24 주식회사 케이티 수압을 이용한 지하천공용 머드해머
CN102168523B (zh) * 2011-04-27 2013-03-20 兰桥昌 钻机的主传动和变速系统及其操纵机构

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3343565C2 (de) * 1983-12-01 1985-11-14 Ing. Günter Klemm, Spezialunternehmen für Bohrtechnik, 5962 Drolshagen Tieflochhammer
SE500654C2 (sv) * 1987-07-14 1994-08-01 G Drill Ab Hydraulisk sänkborrmaskin

Also Published As

Publication number Publication date
KR960706600A (ko) 1996-12-09
ES2146313T3 (es) 2000-08-01
DE69423511T2 (de) 2000-11-02
DE69423511D1 (de) 2000-04-20
JP3393139B2 (ja) 2003-04-07
EP0733153A1 (de) 1996-09-25
SE505171C2 (sv) 1997-07-07
JPH09506687A (ja) 1997-06-30
WO1995016847A1 (en) 1995-06-22
AU685891B2 (en) 1998-01-29
KR100326485B1 (ko) 2002-06-26
SE9304124D0 (sv) 1993-12-13
AU1286495A (en) 1995-07-03
SE9304124L (sv) 1995-06-14

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