US3800664A - Impact tools or apparatus - Google Patents

Impact tools or apparatus Download PDF

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Publication number
US3800664A
US3800664A US00218671A US3800664DA US3800664A US 3800664 A US3800664 A US 3800664A US 00218671 A US00218671 A US 00218671A US 3800664D A US3800664D A US 3800664DA US 3800664 A US3800664 A US 3800664A
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US
United States
Prior art keywords
pressure
piston
fluid
chamber
pressure fluid
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
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US00218671A
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English (en)
Inventor
R Phillips
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.)
Joy Global Industries Ltd
Original Assignee
Dobson Park Industries Ltd
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 Dobson Park Industries Ltd filed Critical Dobson Park Industries Ltd
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Publication of US3800664A publication Critical patent/US3800664A/en
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21C—MINING OR QUARRYING
    • E21C37/00—Other methods or devices for dislodging with or without loading
    • E21C37/22—Hand tools or hand-held power-operated tools specially adapted for dislodging minerals
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/06—Means for driving the impulse member
    • B25D9/12—Means for driving the impulse member comprising a built-in liquid motor, i.e. the tool being driven by hydraulic pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/145—Control devices for the reciprocating piston for hydraulically actuated hammers having an accumulator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S173/00—Tool driving or impacting
    • Y10S173/04—Liquid operated

Definitions

  • the invention is for an impact tool comprising a pres- [73] Assigneez Dobson Park Industries Limited, sure fluid operating piston and cylinder device in Nottingham, England [22] Filed: Jan. 18, 1972 [21] Appl. No.: 218,671
  • said control means comprises a valve means for controlling the supply of pressure fluid to the cylinder, for the retraction of the piston, and for controlling the exhausting of said pressure fluid from the cylinder, for the advance of the piston, a chamber or chambers connected to the cylinder so that a fluid therein will be subjected to pressure changes by movement of the piston, and means responsive to pressures in said chamber or chambers and operative cyclicly to switch said valve means between a pressure fluid supply position and a pressure fluid exhaust. position.
  • said chamber or chambers is or are connected to the cylinder so that the fluid in said chamber or chambers will be compressed by retraction of the piston.
  • the pressure fluid for the operation of the tool, may be a liquid and the fluid in the chamber or chambers, which is compressible, may be a gas.
  • the pressure fluid, for the operation of the tool may be a compressible liquid and the fluid in the chamber or chambers a similar compressible liquid.
  • an impact tool comprising a pressure fluid operated piston and cylinder device, wherein pressure fluid for the cyclic operation of said device is controlled by means responsive to changes in fluid pressure brought about by relative reciprocatory movement between the piston and cylinder.
  • an impact tool comprising a cylinder, a piston which works in said cylinder, valve means for controlling the supply of pressure fluid to the cylinder, for the retraction of the piston, and for controlling the exhausting of said pressure fluid from the cylinder, for the advance of the piston, a chamber or chambers connected to said cylinder so that a fluid therein will be subjected to pressure changes by movement of the piston, and means responsive to pressures in said chamber or chambers and operative cyclicly to switch said valve means between a pressure fluid supply position and apressure fluid exhaust position.
  • said chamber or chambers is or are connected to the cylinder so that the fluid therein will be compressed by retraction of the piston.
  • an impact tool comprising a cylinder, a piston which works in said cylinder, valve means for controlling the supply of pressure fluid to the cylinder, for the retraction of the piston, and for controlling the exhausting of said pressure fluid from the cylinder, for
  • an impact tool comprising a cylinder, a piston which works in said cylinder, valve means for controlling the supply of pressure fluid to the cylinder for retraction of the piston, and for controlling the exhausting of said pressure fluid from the cylinder, for the advance of the piston, a chamber for a compressible fluid connected to said cylinder so that a compressible fluid within it will be compressed by retraction of the piston and means responsive respectively to high pressure in said chamber and a pressure change created in a part of the cylinder and operative cyclicly to switch said valve'means between a pressure fluid supply position and a pressure fluid exhaust position.
  • F IG. 1 is alongitudinal sectional view of one form of impact tool according to the invention with its associated valves and pressure fluid circuitry shown diagrammatically,
  • FIG. 2 shows in section and in greater detail the valves associated with the tool shown in FIG. 1,
  • FIG. 3 shows in longitudinal section some modifications of and additions to the tool shown in FIG. 1,
  • FIG. 4 shows a further modification of the tool shown in FIG. 1,
  • F IG. 5 shows diagrammatically one form of starting/- stopping arrangement for the tool
  • FIG. 6 shows an alternative starting/stopping arrangement for the tool.
  • the impact tool shown in FIG. 1 comprises a housing 10 having a first cylinder portion 10' in which works a piston 11 having a forward extension 12 of less diameter than the piston 11. At its rear end the housing 10 is provided, behind cylinder portion 10 and the piston 11, with a second cylinder portion 10 including a gas chamber 13.
  • a holder 14 for a chisel or like tool 15 At the forward end of the first cylinder portion 10 there is a holder 14 for a chisel or like tool 15.
  • the chisel has a head 16 adapted to be struck, during operation of the tool, by the forward extension 12 of the piston 1 l.
  • Drains are provided at 17 and 18, in the first cylinder portion 10.
  • a port l9' is provided in the first cylinder portion 10 which communicates with the enlarged part 10a of said first cylinder portion.
  • a passage 20 in the first cylinder portion wall connects the part 10a thereof to the part 10b of smaller diameter.
  • the flow of hydraulic pressure fluid, to and from the first cylinder portion 10' via the port 19, is controlled by a main control valve 21 which includes (see FIG. 2) a spool 22 which is operated by hydraulically driven pilot pistons 23 and 24.
  • the main control valve 21 has a port 25 which is connected to a hydraulic main supply 26 and a port 27 which is connected to a hydraulic return main 28.
  • Operation of the pistons 23 and 24, and thereby movement of the spool 22, ' is controlled by a high pressure pilot valve 29 and a low pressure pilot valve 30.
  • the pilot valves 29 and 30 are connected by pipes 31 to the gas chamber 13 and respond, differentially, to high and low gas pressures therein so that said valves act, in effect, as high and low pressure gas operated switches.
  • a hydraulic pilot start line 32 is connected to a port 33 of the low pressure pilot valve 30.
  • This valve also has a port 34 connected to the cylinder of the pilot piston 24, in the main control valve, and a port 35 connected to a drain pipe 36.
  • the high pressure pilot valve 29 has a port 37 connected to the main supply pipe 26 and a port 38 connected to the return line 28.
  • the high pressure pilot valve 29 also has a port 39 connected, through a spring loaded shuttle valve device 40, to the cylinder of the pilot piston 23 in the main control valve 21.
  • the valve device 40 has a connection to a pilot piston reset line 41.
  • the gas chamber 13 is provided with a gas inflation or charging device 400.
  • the piston 11 is in the forward position and there is no pressure fluid supply to the tool.
  • the pilot pistons 23 and 24 take up the position shown in FIG. 2, if they are not already in that position, due to hydraulic pressure supplied over the pilot reset line 41.
  • Pressure fluid from the pilot start line 32 then acts, through the valve 30 which is in the position shown in FIG. 2, on the pilot piston 24 and moves the spool 22 to the left to admit pressure fluid to the first cylinder portion
  • the piston 11, 12 is thus retracted causing the gas pressure in the chamber 13 to rise.
  • the rising gas pressure in the chamber 13 first cancels the pressure pilot signal, by raising the pilot valve 30, and then actuates the pilot valve 29 and pressure fluid then passes through the ports 37 and 39 to restore the spool valve 22, of the main control valve 21, to the position shown in FIG. 2.
  • the piston 11, 12 then commences to make an impact stroke under the influence of the gas pressure in the chamber 13, and strikes the head 16 of the chisel 15.
  • the gas pressure settings of the pressure sensitive rams 29a and 30a of the pilot valves 29, 30 are adjustable by means of adjustably loaded springs associated with said rams. Actual pressure values are chosen to give best impacting. In this connection it may be of advantage to utilise pressure sensitive pilot valves of switching devices 29 and 30 which have an inherent lag characteristic which in other circumstances might be considered a defect.
  • the spool 22 of the main valve is designed to remain stationary in either position until one or other of the pilot pistons 23 or 24 is pressurised.
  • FIG. 3 The modified embodiment of the invention shown in FIG. 3 is similar in many respects to the embodiment already described with reference to FIGS. 1 and 2 and when applicable like reference numerals have been used to designate like parts.
  • a non return air inlet valve device is provided at 4112 to permit an inflow of air to the portion 100 of the first cylinder portion 10' and allow the piston to function as an air pump which tends to keep the front chamber at a higher pressure than the surrounding atmosphere, consequently inhibiting ingress of dirty air from the vicinity of impacting. Clean air can be ducted from a remote region.
  • a chiselbuffer is provided at 44 and the portion 10b of the first cylinder portion 10' is provided with a snubber reliefvalve 42 having a relief-valve damper bleed 43 for removing energy from the piston 11, 12.
  • a chamber 10d of somewhat smaller diameter than the main annulus 10a, is provided in the first cylinder portion l0.
  • the requirement is to switch the main valve spool 22 at the end of the forward stroke of the piston 11. This is done by the creation of a pressure difference in chamber 10d.
  • This pressure difference may act directly on the spool valve via a pipe 46, as shown in FIG. 4, or through a pilot valve 30 connected by a pipe 46a (see FIG. 3) to the portion 10d of the first cylinder portion.
  • the main valve spool 22 is pushed to the left (i.e. the position shown in FIG. 4) by an auxiliary piston or spring arrangement (not shown) to start the cycle in the normal way as above described.
  • the spool 22 is hydrostatically balanced by means of port 48 and 49 connected into the main annulus 10a of the first cylinder portion.
  • Duct 46 and port 48 are made large to minimise energy losses and it is believed that the exhaust pressure to operate the valve will be approximately the same as when exhausting normally.
  • a starting/stopping arrangement for the tool may comprise a full-flow stop valve 52, in the supply line 26, as shown in FIG. 5 or alternatively a stop valve 53 in the hydraulic pilot start line 32 as indicated in FIG. 6.
  • the chamber 13 may be charged with a compressible liquid.
  • the liquid and the liquid for the operation of the tool are similar.
  • An impact tool comprising a housing including a first cylinder portion and a second cylinder portion, a piston working in said first cylinder portion, the first cylinder portion having pressure fluid supply and exhaust means for the retraction and advancement of the piston respectively, a control valve means for said pressure fluid supply and exhaust means, pressure sensitive means operative to actuate said control valve means, means for supporting a tool to be struck by the piston when it is advanced, said second cylinder portion including a chamber positioned to receive the piston when it is retracted, a separate body of fluid permanently disposed in said chamber and compressed therein by retraction of the piston into said chamber, and connecting means between said chamber and said pressure sensitive means whereby said compression of said fluid in the chamber acts on said pressure sensitive means to actuate the control valve means to exhaust the first cylinder portion and allow the piston to advance under the action of said compressed fluid and make a stroke in the impacting direction, and the resultant fall of fluid pressure in the chamber causes said pressure sensitive means to allow the control valve means to actuate to supply pressure fluid.
  • pressure sensitive means is a pressure actuated pilot valve and the control valve means is a spool valve, a supply of pressure fluid to said spool valve for its operation, being controlled by said pilot valve.
  • pressure sensitive means comprises pressure actuated pilot valves and the control valve means is a spool valve, a supply of pressure fluid to said spool valve, for its operation, being controlled by said pilot valves.
  • control valve means comprises a spool valve which is operated from the pressure fluid supply to the pressure fluid exhaust position under the control of a high pressure piston-operated pilot-valve connected for its operation to said chamber, and from the pressure fluid exhaust to the pressure fluid supply position by causing the exhaust fluid to act on said spool valve.
  • control valve means comprises a spool valve which is operated from the pressure fluid supply to the pressure fluid exhaust position under the control of a high pressure piston-operated pilot-valve connected for its operation to said chamber, and from the pressure fluid exhaust to the pressure fluid supply position by causing the exhaust fluid to act on a pilot valve controlling a supply of pressure fluid to the spool valve.
  • An impact tool as claimed in claim 1' wherein means is provided for the charging of said chamber with a compressible fluid.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Geology (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Portable Nailing Machines And Staplers (AREA)
  • Forging (AREA)
US00218671A 1971-02-10 1972-01-18 Impact tools or apparatus Expired - Lifetime US3800664A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB432671A GB1356022A (en) 1971-02-10 1971-02-10 Impact tools or apparatus

Publications (1)

Publication Number Publication Date
US3800664A true US3800664A (en) 1974-04-02

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ID=9775054

Family Applications (1)

Application Number Title Priority Date Filing Date
US00218671A Expired - Lifetime US3800664A (en) 1971-02-10 1972-01-18 Impact tools or apparatus

Country Status (15)

Country Link
US (1) US3800664A (fr)
JP (1) JPS5315001B1 (fr)
AU (1) AU461421B2 (fr)
BE (1) BE778621A (fr)
CA (1) CA937835A (fr)
CS (1) CS178404B2 (fr)
DE (1) DE2147935B2 (fr)
ES (1) ES399577A1 (fr)
FR (1) FR2126776A5 (fr)
GB (1) GB1356022A (fr)
HU (1) HU164405B (fr)
IT (1) IT948390B (fr)
NL (1) NL166636C (fr)
SE (1) SE398720B (fr)
ZA (1) ZA72824B (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3925985A (en) * 1973-01-09 1975-12-16 Rapidex Inc Impact actuator
DE2512690A1 (de) * 1975-03-17 1976-09-30 Linden Alimak Ab Hydraulisch betaetigte vorrichtung zum bohren von gestein
US3995700A (en) * 1975-10-14 1976-12-07 Gardner-Denver Company Hydraulic rock drill system
US4036108A (en) * 1975-09-12 1977-07-19 Dobson Park Industries, Ltd. Pressure fluid operated percussion tools
DE2726046A1 (de) * 1976-06-09 1977-12-15 Mitsui Shipbuilding Eng Hydraulischer hammer
US4344353A (en) * 1979-05-14 1982-08-17 Joy Manufacturing Company Hammer
US4512417A (en) * 1981-11-05 1985-04-23 Ingersoll-Rand Company Hydraulic reciprocating device
US4819542A (en) * 1985-12-23 1989-04-11 Spetsialnoe Konstruktorskoe Bjuro Gidroimpulsnoi Tekhniki Sibirskogo Otdelenia Akademii Nauk Sssr Percussive tool
US11585154B2 (en) * 2017-09-08 2023-02-21 Epiroc Rock Drills Aktiebolag Mining or construction vehicle
US11661797B2 (en) * 2017-09-08 2023-05-30 Epiroc Rock Drills Aktiebolag Mining or construction vehicle and a hydraulic cylinder conduit enclosing a conduit arrangement

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1581441A (en) * 1976-01-29 1980-12-17 Dobson Park Ind Fluid powered impact tools
SE429111B (sv) * 1978-10-19 1983-08-15 Atlas Copco Ab Hydrauliskt drivet slagverk
GB2115886B (en) * 1982-03-02 1985-08-29 Dobson Park Ind Public Limited Impact tools
JPS60153639U (ja) * 1984-03-22 1985-10-14 株式会社荏原製作所 耐水絶縁電線型水中モ−タ
DE4229590C2 (de) * 1992-09-04 1996-06-20 Klemm Guenter Hydraulisches Schlaggerät mit Vorsteuerventil
JP5899071B2 (ja) * 2012-07-06 2016-04-06 古河ロックドリル株式会社 油圧ブレーカ用ガス給気装置およびこれを備えるガス給気装置付油圧ブレーカ
DE102015008339A1 (de) 2015-07-01 2017-01-05 Tracto-Technik Gmbh & Co. Kg "Rammbohrvorrichtung und Verfahren zum Umsteuern einer Rammbohrvorrichtung"
CN113560549A (zh) * 2021-08-06 2021-10-29 四川省柏均机械制造有限责任公司 高锰钢铸件去冒口冲击锤

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB784684A (en) * 1954-08-31 1957-10-16 George Stephen Kammer Improvements in reciprocating motors for actuation by a fluid supplied at substantially constant pressure
GB937206A (en) * 1958-11-17 1963-09-18 Friedrich Heinrich Flottmann Control system for a hydraulically operated percussion device
US3225663A (en) * 1963-04-09 1965-12-28 Hispano Suiza Sa Hydraulic control systems including double action receiver apparatus
US3540348A (en) * 1965-05-20 1970-11-17 Hermann Joseph Pennther Fluid operated continuously actuated reciprocating piston drive
US3620126A (en) * 1968-06-19 1971-11-16 Hydrel Ag Maschf Hydraulic reversing system for a reciprocating working member

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB784684A (en) * 1954-08-31 1957-10-16 George Stephen Kammer Improvements in reciprocating motors for actuation by a fluid supplied at substantially constant pressure
GB937206A (en) * 1958-11-17 1963-09-18 Friedrich Heinrich Flottmann Control system for a hydraulically operated percussion device
US3225663A (en) * 1963-04-09 1965-12-28 Hispano Suiza Sa Hydraulic control systems including double action receiver apparatus
US3540348A (en) * 1965-05-20 1970-11-17 Hermann Joseph Pennther Fluid operated continuously actuated reciprocating piston drive
US3620126A (en) * 1968-06-19 1971-11-16 Hydrel Ag Maschf Hydraulic reversing system for a reciprocating working member

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3925985A (en) * 1973-01-09 1975-12-16 Rapidex Inc Impact actuator
DE2512690A1 (de) * 1975-03-17 1976-09-30 Linden Alimak Ab Hydraulisch betaetigte vorrichtung zum bohren von gestein
US4006783A (en) * 1975-03-17 1977-02-08 Linden-Alimak Ab Hydraulic operated rock drilling apparatus
US4036108A (en) * 1975-09-12 1977-07-19 Dobson Park Industries, Ltd. Pressure fluid operated percussion tools
US3995700A (en) * 1975-10-14 1976-12-07 Gardner-Denver Company Hydraulic rock drill system
DE2726046A1 (de) * 1976-06-09 1977-12-15 Mitsui Shipbuilding Eng Hydraulischer hammer
US4344353A (en) * 1979-05-14 1982-08-17 Joy Manufacturing Company Hammer
US4512417A (en) * 1981-11-05 1985-04-23 Ingersoll-Rand Company Hydraulic reciprocating device
US4819542A (en) * 1985-12-23 1989-04-11 Spetsialnoe Konstruktorskoe Bjuro Gidroimpulsnoi Tekhniki Sibirskogo Otdelenia Akademii Nauk Sssr Percussive tool
US11585154B2 (en) * 2017-09-08 2023-02-21 Epiroc Rock Drills Aktiebolag Mining or construction vehicle
US11661797B2 (en) * 2017-09-08 2023-05-30 Epiroc Rock Drills Aktiebolag Mining or construction vehicle and a hydraulic cylinder conduit enclosing a conduit arrangement

Also Published As

Publication number Publication date
DE2147935A1 (de) 1972-10-26
GB1356022A (en) 1974-06-12
IT948390B (it) 1973-05-30
DE2147935B2 (de) 1973-02-22
NL166636C (nl) 1981-09-15
FR2126776A5 (fr) 1972-10-06
AU3822272A (en) 1973-07-26
CA937835A (en) 1973-12-04
BE778621A (fr) 1972-05-16
SE398720B (sv) 1978-01-16
JPS5315001B1 (fr) 1978-05-22
DE2147935C3 (fr) 1973-09-13
NL7201642A (fr) 1972-08-14
ZA72824B (en) 1972-11-29
ES399577A1 (es) 1974-11-01
CS178404B2 (fr) 1977-09-15
HU164405B (fr) 1974-02-28
AU461421B2 (en) 1975-05-29
NL166636B (nl) 1981-04-15

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