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WO1998031509A1 - Marteau hydraulique - Google Patents

Marteau hydraulique Download PDF

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Publication number
WO1998031509A1
WO1998031509A1 PCT/EP1998/000262 EP9800262W WO9831509A1 WO 1998031509 A1 WO1998031509 A1 WO 1998031509A1 EP 9800262 W EP9800262 W EP 9800262W WO 9831509 A1 WO9831509 A1 WO 9831509A1
Authority
WO
WIPO (PCT)
Prior art keywords
casing
piston
pistons
fluid operated
hammer
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.)
Ceased
Application number
PCT/EP1998/000262
Other languages
English (en)
Inventor
Francesco Verardi
Edward Alexander Moss
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to AU59883/98A priority Critical patent/AU5988398A/en
Publication of WO1998031509A1 publication Critical patent/WO1998031509A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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

Definitions

  • This invention relates to a fluid operated hammer and, more specifically, to a fluid operated hammer which may be applied in rock breaking applications and the like.
  • Hammer drills are hydraulically or pneumatically operated and often combine impact with rotational motion of a bit. Such hammer drills are typically hand operated and are used for low energy applications.
  • Impact only hammers may be pneumatically or hydraulically powered and used for both low and high energy per blow applications.
  • a moving piston strikes a tool in contact with a rock or, alternatively, a piston integral with a tool strikes the rock directly, thereby eliminating an intermediate metal-to-metal contact and enabling larger tool impact velocities.
  • a water pulse generator breaks rock by application of large pressure pulses into a hole drilled into a brittle material such as rock.
  • All of the above classes of mechanical device require a means of converting hydraulic or pneumatic input energy into mechanical energy associated with a moving mass which may then be deployed to strike a tool, a rock, or a water column as described above.
  • the above-mentioned hammer drills and hammers require a continuously reciprocating motion whilst the water pulse generator needs to be rapidly loaded and fired and hence a reciprocating mechanism is desirable as several impacts of the water gun may be required to fracture the rock.
  • a fluid operated hammer comprising : a casing; a main piston reciprocatable in the casing; a secondary piston reciprocatable in the casing separately from the main piston; one of the pistons providing a hammer surface; an inlet into the casing for admitting a pressurised fluid; an outlet from the casing separable from the inlet by one of the pistons; an energy storage compartment in communication with a face of one of the pistons; and the pistons being relatively movable between connected and separated positions to allow the pressurised fluid to sequentially supply energy to the storage compartment and release this energy to operatively drive the piston providing the hammer surface.
  • the energy storage compartments to be formed between the closed end of the casing and an end of one of the pistons or for the storage compartment to be a gas accumulator separated from the casing by a flexible diaphragm with the space between the piston and the diaphragm filled with energy transmitting liquid.
  • the invention also provides for the main and secondary pistons to be assembled in line or for the secondary piston to be a sleeve around a major part of the main piston which will have a head in communication with the energy storage compartment.
  • connection 5 means between the two pistons which connection is releasable through contact between one of the pistons and an abutment provided in the casing and for there to be a subsidiary chamber between one of the pistons and the inner wall of the casing to provide a fluid cushion for the piston assembly.
  • Figures 1 to 5 are sectional views of one embodiment of a fluid operated hammer showing various positions of the 5 pistons during operation of the hammer;
  • Figure ⁇ is a sectional representation of an alternative embodiment of a fluid operated hammer.
  • FIG. 7 to 13 illustrate similar views of different embodiments.
  • a fluid operated hammer is indicated generally by reference numeral (1).
  • the fluid operated hammer (1) includes an elongate casing (2) of circular cross-section having a closed end (3) and having an axial aperture (5) at the opposite end (4) thereof and a main piston (6) which is reciprocatable within the casing with one end (7) of the main piston (6) projecting outwardly through the axial aperture (5).
  • the innermost end of the main piston (6) has a shoulder (15) and a castellated stop formation (16) which abuts against the casing (2) at an inwardly projecting shoulder (17) thereof to limit travel of the main piston into the casing.
  • a secondary piston (8) is located in the casing (2) between the main piston (6) and the closed end (3) of the casing and is reciprocatable in the casing separately from or in unison with the main piston.
  • the variable volume between the secondary piston (8) and the closed end (3) of the casing defines an energy storage compartment which as shown is in the form of a gas accumulator.
  • the casing (2) also includes an inlet (10) for admitting a pressurised fluid therethrough from a power pack (not shown) or other source of liquid under pressure.
  • the pressurised fluid is water.
  • An outlet (11) is located through the wall of the casing and is separated from the inlet (10) by the main piston (6).
  • the interior of the casing (2) is recessed to define a stepped driving cavity (14) spaced from the wall of the main piston.
  • the main piston (6) has two exhaust passages (12a and 12b) extending partway along its length from its innermost end which conforms with the corresponding end of the secondary piston (8).
  • An annular seal (18) separates the exhaust passages (12a and 12b) from the driving cavity (14) when the corresponding ends of the main piston (6) and the secondary piston (8) abut.
  • pressurised fluid is admitted into the driving cavity (14) through the inlet (10).
  • the pressurised fluid acts on the shoulder (15) of the main piston (6) urging the main piston inwardly into the casing (2) in a return direction, thereby effecting a return stroke of the hammer (1).
  • the main piston (6) also urges the secondary piston inwardly towards the closed end (3) of the casing, pressurising the gas in the energy storage compartment (9) to accumulate and store energy.
  • the return stroke of the hammer (1) terminates when the castellated stop formation (16) on the main piston abuts the casing (2) at shoulder (17) to halt its travel.
  • the pressurised fluid in the driving cavity (14) continues to act on the secondary piston (8) through the castellated stop formation (16) and drives it towards the closed end (3) of the casing (2), causing it to separate from the main piston (6).
  • Pressurised fluid now flows from the driving cavity (14) into the volume between the main (6) and secondary (8) pistons as indicated by the arrows in Figure 2.
  • the ingress of pressurised fluid between the main (6) and secondary (8) pistons causes a pressure drop in the driving cavity (14) to create out-of-balance forces on both pistons to cause them to move in a direction opposite to the return direction, a working direction, indicated by the arrows in Figure 3, thereby effecting a working stroke.
  • the pressure in the driving cavity (14) is maintained by the secondary piston (8) which is driven by the pressurised gas in the energy storage compartment (9).
  • the main (6) and secondary (8) pistons continue to separate during the working stroke.
  • the main piston (6) continues to move in the working direction until the shoulder (15) of the main piston (6) co-incides with a further shoulder (19) on the inner periphery of the casing (2).
  • the exhaust passages (12a and 12b) correspond with the outlet (11) to provide a flow path for venting fluid in the driving cavity (14).
  • the co-inciding shoulders (15) and (19) of the main piston (6) and the inner periphery of the casing (2) co-operate to define a subsidiary chamber (21) as shown in Figure 4. Fluid entrapped in the subsidiary chamber (21) is compressed by further motion of the main piston (6) in the working direction during the working stroke.
  • the build up of fluid pressure in the subsidiary chamber (21) absorbs the kinetic energy of the main piston (6) to prevent it from striking and damaging the casing in the event of an incomplete or a null impact of the main piston (6) against a surface.
  • the build up of pressure in the subsidiary chamber (21) is controlled by a leakage path (not shown) between the subsidiary chamber (21) and the driving cavity (14).
  • the pressurised fluid may be a liquid other than water, or a gas.
  • FIGS. 7 to 13 show the secondary piston (22) as a sleeve extending along the major length of the main piston (23).
  • the piston (22) has a head (24) moving in sealing engagement with the casing (25) and means (not shown) are provided to releasably hold the end of secondary piston (22) in sealing engagement with the head (24) during the return stroke.
  • Fig 7 shows the pistons in the fully retracted position of the pistons (22) and (23).
  • the projection (26) on the piston (22) has encountered a shoulder (27) provided in the casing (25) and further movement of the main piston (23) will release the engagement between the pistons and open a flow path for the fluid entering at inlet (28) to exhaust through outlet (29). This relieves the piston head (24) of the inlet fluid pressure and the direction of movement of the pistons can reverse.
  • the working stroke is illustrated in Figure 8. Once the main piston (23) and secondary piston (22) have separated, the pressure decreases in the driving cavity (30) and they start moving in the working direction. The main piston (23) is subject predominately to the pressure acting on the head (24). Thereafter, the area difference between the top bore in the casing (31) and the restricted lower bore indicated at (32) cause further separation between the piston (22) and the piston head (24).
  • the amount by which the piston (22) moves relative to the main piston (23) may be affected by the size of the exhaust ports (33) in the casing: if the exhaust apertures (34) in the piston (22) engage the exhaust ports (33) in the casing early, the movement of the piston (22) relative to the main piston (23) would be restricted, because once they have parted, a portion of the fluid would find a path through the exhaust port, rather than all of it acting to separate the two moving parts (22) and (23) further. Therefore, the system could be arranged to exhaust virtually continuously during the stroke, or to exhaust mainly at the end of the working stroke.
  • Figure 10 illustrates the components during the return stroke. Once the main piston (23) and piston (22) have come to rest, flow into the inlet port (35) pressurizes the driving cavity (36) which forces the two parts back as a unit, and in so doing stores energy in compartment (37A) which resists motion of the main piston (23).
  • Figure 10 shows an intermediate position of the return stroke, prior to the piston (22) again engaging the head (24) of the main piston (23), separating from it, and recommencing the working stroke.
  • a shoulder (37) is provided on the piston (22) for this purpose. A small distance beyond the impact position it engages with and slides inside a similar shoulder (38) in the casing, trapping fluid in the subsidiary chamber (39). The build-up of pressure in the subsidiary chamber (39) is controlled by a leakage path (not shown) between this chamber and the driving cavity (36).
  • FIG. 7 to 11 The particular embodiment depicted in Figures 7 to 11 is one in which the top of the main piston (23) is in contact with liquid in the space (40) which serves mainly as an energy transmission medium between energy storage compartment (37A) and the main piston (23).
  • the main piston (23) retracts on the return stroke, it displaces a given volume of the liquid, resulting in gas in the remotely positioned accumulator (37A) reducing its volume by virtually the same amount, and storing energy commensurately.
  • this arrangement is slightly more complex than the alternative of merely having a pure gas cavity in contact with the top of the main piston (23), it has the potential advantages of (a) virtually eliminating the possibility of gas leakage, and (b) providing flexibility in placement and geometry of the energy storage compartment.
  • the energy storage compartment (37A) is shown separated from the casing (25) by a flexible diaphragm (41) which will be supported in its exhausted condition by a perforated plate (42).
  • Figures 12 and 13 show further embodiments of the invention. In Figure 12 exhaust of inlet pressurised fluid takes place at (43) above the driving cavity (36).
  • the invention therefore provides a general purpose reciprocating driver in which a gas or a liquid may be used as an operating medium and which achieves reciprocating motion without the necessity for a complex valving system.

Landscapes

  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Abstract

Marteau hydraulique (1) comportant un carter (2, 25), un piston principal (6, 23) conçu pour effectuer un déplacement alternatif dans le carter, un deuxième piston (8, 22) conçu pour effectuer un déplacement alternatif dans le carter séparément du piston principal, une entrée (10, 28) dans le carter servant à admettre un liquide sous pression à travers le carter, ainsi qu'une sortie (11, 33) depuis ledit carter pouvant être séparée de l'entrée par un des pistons. Un compartiment d'accumulation d'énergie (9, 37a) est en communication avec une face d'un des pistons; les pistons étant relativement mobiles entre des positions d'accouplement et de séparation afin de permettre au liquide sous pression d'alimenter séquentiellement en énergie le compartiment d'accumulation d'énergie et de relâcher cette énergie afin d'entraîner le piston constituant la surface du marteau.
PCT/EP1998/000262 1997-01-20 1998-01-19 Marteau hydraulique Ceased WO1998031509A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU59883/98A AU5988398A (en) 1997-01-20 1998-01-19 Fluid operated hammer

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ZA97421 1997-01-20
ZA97/0421 1997-01-20

Publications (1)

Publication Number Publication Date
WO1998031509A1 true WO1998031509A1 (fr) 1998-07-23

Family

ID=25586151

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1998/000262 Ceased WO1998031509A1 (fr) 1997-01-20 1998-01-19 Marteau hydraulique

Country Status (3)

Country Link
AU (1) AU5988398A (fr)
WO (1) WO1998031509A1 (fr)
ZA (1) ZA98431B (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1157787A1 (fr) * 2000-05-18 2001-11-28 Günter Prof. Dr.-Ing. Klemm Procédé pour travailler le sol et des pierres et outil de percussion hydraulique
JPWO2017010400A1 (ja) * 2015-07-13 2017-12-28 古河ロックドリル株式会社 液圧式打撃装置
WO2018131689A1 (fr) * 2017-01-12 2018-07-19 古河ロックドリル株式会社 Dispositif de percussion hydraulique

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1124526A (en) * 1966-05-19 1968-08-21 Sonomotive Engineers Ltd Improvements in or relating to percussive tools and machines
GB2010714A (en) * 1977-12-05 1979-07-04 Fujitake T Hydraulic power hammer
EP0099097A2 (fr) * 1982-07-15 1984-01-25 Horst Dipl.-Ing. Knäbel Dispositif pour produire une force de travail, en pariculier pour moutons, presses ou similaires
DE3229309A1 (de) * 1982-08-05 1984-02-16 Institut avtomatiki Akademii Nauk Kirgizskoj SSR, Frunze Schlagmechanismus

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1124526A (en) * 1966-05-19 1968-08-21 Sonomotive Engineers Ltd Improvements in or relating to percussive tools and machines
GB2010714A (en) * 1977-12-05 1979-07-04 Fujitake T Hydraulic power hammer
EP0099097A2 (fr) * 1982-07-15 1984-01-25 Horst Dipl.-Ing. Knäbel Dispositif pour produire une force de travail, en pariculier pour moutons, presses ou similaires
DE3229309A1 (de) * 1982-08-05 1984-02-16 Institut avtomatiki Akademii Nauk Kirgizskoj SSR, Frunze Schlagmechanismus

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1157787A1 (fr) * 2000-05-18 2001-11-28 Günter Prof. Dr.-Ing. Klemm Procédé pour travailler le sol et des pierres et outil de percussion hydraulique
JPWO2017010400A1 (ja) * 2015-07-13 2017-12-28 古河ロックドリル株式会社 液圧式打撃装置
US11052524B2 (en) 2015-07-13 2021-07-06 Furukawa Rock Drill Co., Ltd. Hydraulic hammering device
WO2018131689A1 (fr) * 2017-01-12 2018-07-19 古河ロックドリル株式会社 Dispositif de percussion hydraulique
CN110177658A (zh) * 2017-01-12 2019-08-27 古河凿岩机械有限公司 液压式冲击装置
JPWO2018131689A1 (ja) * 2017-01-12 2019-11-07 古河ロックドリル株式会社 液圧式打撃装置
EP3569362A4 (fr) * 2017-01-12 2020-01-15 Furukawa Rock Drill Co., Ltd. Dispositif de percussion hydraulique
US11207769B2 (en) 2017-01-12 2021-12-28 Furukawa Rock Drill Co., Ltd. Hydraulic hammering device

Also Published As

Publication number Publication date
AU5988398A (en) 1998-08-07
ZA98431B (en) 1998-07-28

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