WO2005087443A1 - Hydraulic breaking hammer - Google Patents

Hydraulic breaking hammer Download PDF

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Publication number
WO2005087443A1
WO2005087443A1 PCT/SE2005/000325 SE2005000325W WO2005087443A1 WO 2005087443 A1 WO2005087443 A1 WO 2005087443A1 SE 2005000325 W SE2005000325 W SE 2005000325W WO 2005087443 A1 WO2005087443 A1 WO 2005087443A1
Authority
WO
WIPO (PCT)
Prior art keywords
bore
end cover
rear end
cylinder sleeve
hammer
Prior art date
Application number
PCT/SE2005/000325
Other languages
French (fr)
Inventor
Stig Roland Henriksson
Original Assignee
Atlas Copco Construction Tools 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 Atlas Copco Construction Tools Ab filed Critical Atlas Copco Construction Tools Ab
Priority to JP2007502761A priority Critical patent/JP2007528798A/en
Priority to US10/592,600 priority patent/US20070175670A1/en
Priority to DE602005003335T priority patent/DE602005003335T2/en
Priority to EP05711176A priority patent/EP1722931B1/en
Publication of WO2005087443A1 publication Critical patent/WO2005087443A1/en

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/26—Lubricating
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • 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

Definitions

  • the invention relates to a hydraulic breaking hammer of the type having a housing with a longitudinal bore, a cylinder sleeve supported in the bore, a hammer piston sealingly guided in the cylinder sleeve and reciprocated for delivering repeated blows on a working implement inserted through a front opening in the housing, and a rear end cover forming a closure for the bore.
  • the main object of the invention is to create a hydraulic breaking hammer of the above described type having fewer details resulting in reduced manufacturing and assembly costs .
  • Another object of the invention is to create a hydraulic breaking hammer having a simple and robust design with a simplified piston fit.
  • FIG. 1 shows a longitudinal section through a hydraulic breaking hammer according to the invention.
  • Fig. 2 shows on a larger scale a section through the distribution valve of the breaking hammer in Fig. 1.
  • Fig. 3 shows on a larger scale a fractional section through the implement sleeve arrangement of the breaking hammer in Fig. 1.
  • the hydraulic breaking hammer illustrated in the drawing figures comprises a housing 10 formed with a rear mounting shoulder 11 for attachment to a mechanical carrier like an excavator arm.
  • the housing 10 is provided with a longitudinal through bore 12 which in its rear part supports a cylinder sleeve 14 for sealingly guide a hammer piston 15.
  • At the rear end of the housing 10 there is bolted on an end cover 16 which forms an end closure for the bore 12.
  • This end cover 16 is formed as a one piece member with a tube shaped neck portion 17 which extends into the bore 12 and contacts the rear end of the cylinder sleeve 14. The latter is clamped in its proper position in the bore 12 between the end cover neck portion 17 and a shoulder 18 in the bore 12.
  • the neck portion 17 also forms a guide means for the hammer piston 15 and carries a seal ring 19 for co-operation with the rear end of the hammer piston 15.
  • the bore 12 carries a working implement guide sleeve 20 which is intended to receive the rear end of a working implement (not shown) .
  • a working implement guide sleeve 20 For lubricating the sleeve 20 on its inside there is provided a lubricant supply passage 21 in the housing 10 which via radial openings 22 a,b in the guide sleeve 20 communicates with the inside of the guide sleeve 20.
  • the guide sleeve 20 is provided with four O-rings 23 a-d on its outside the purposes of which are two, namely via frictional engagement with the bore 12 retain the sleeve 20 in the bore 12, and to seal off between them two annular compartments 24,25.
  • the radial openings 22 a,b in the guide sleeve 20 are located between the O-rings 23 a,b and 23 c,d, respectively, such that lubricant has to pass through the compartments 24,25 to reach the radial openings 22 a,b and the guide sleeve 20 inside. See Fig. 3. Accordingly, the compartments 24,25 are filled with lubricant (grease), and due to the relative axial extension of the compartments 24,25 lubricant is spread over a substantial part of the outside surface of the guide sleeve 20, thereby, preventing seizure of the guide sleeve 20 relative to the bore 12.
  • the housing 10 has a pressure fluid inlet passage 28 for supplying motive pressure fluid to the cylinder sleeve 14 so as to drive the hammer piston 15 in its reciprocating movement for delivering blows to a working implement inserted in the guide sleeve 20.
  • the piston 15 has two oppositely facing drive surfaces 29,30, whereof the lower surface 30 is continuously connected to the pressure fluid source, whereas the upper surface 29 is intermittently pressurised via a pressure fluid distribution valve 31.
  • the distribution valve 31 has a fluid inlet 32 communicating with the pressure fluid inlet passage 28, and a fluid outlet 33 communicating with the upper drive surface 29 of the hammer piston 15.
  • the distribution valve 31 comprises a valve bore 35 and a valve element 34 sealingly guided in the bore 35.
  • the valve element 34 consists of a tubular guide portion 36 guided in the bore 35, and an end wall 37. In the end wall 37 there are through openings 38 for connecting the inside of the guide portion 36 and the fluid inlet 32 with the outer surface of the end wall 37.
  • the end wall 37 is provided with a reduced diameter activation portion 40 which extends co-axially in a direction opposite the guide portion 36 and is received in an intermittently pressurised activation bore 41.
  • the end wall 37 has a slightly larger cross section than the guide portion 36, and since the valve element 34 is open ended the fluid pressure will act constantly both on the surface area formed by the guide portion 36 and via the openings 38 on the outer surface of the end wall 37.
  • the remaining part of the end wall 37 is smaller than the guide portion area resulting in a closing force on the valve element 34.
  • the activation bore 41 is pressurised the total area of the end wall plus activation portion 40 will generate a force that will dominate over the force generated by the pressure acting on the guide portion area. This means that the valve element 34 is shifted to its open position. (Not shown) .
  • the valve element 34 is provided to control the communication between the inlet 32 and the outlet 33, and for that purpose the valve element 34 is formed with a double seal function, namely both a clearance seal and a seat seal.
  • the clearance seal function is obtained by a circumferential surface 44 of the end wall 37 co-operates with the valve bore 35 as illustrated in the closed position of the valve shown in Fig. 1.
  • the seat seal is accomplished by an annular seat 45 at the end of the bore 35 in co-operation with an annular contact surface 46 on the end wall 37.
  • the breaker hammer shown in the drawing also comprises a pressure peak absorbing accumulator 50 which is partly formed by the hammer housing 10 and partly by a cover 51 attached to the housing 10.
  • the accumulator 50 comprises an expansion chamber 52 which in a conventional way is divided by a flexible membrane 53 into a pressure fluid compartment 54 and a gas cushion compartment 55.
  • the expansion chamber 52 is defined by an inner wall 57 and an outer wall 58, wherein the outer wall 58 is formed by the cover 51.
  • a movable membrane support 59 consisting of a stem portion 61 and a membrane engaging head 62.
  • the latter is located inside the pressure fluid compartment 54, whereas the stem portion 61 is displacebly guided in a bore in the inner wall 57.
  • Openings 64 are provided in parallel with the stem portion 61 to communicate pressure fluid into the expansion chamber 52, and the head 62 of the membrane support 59 is arranged to cover these openings 64 at low pressure levels when the membrane 53 is pressed against the inner wall 57.
  • a spring 65 is provided to exert a bias force on the membrane support 59 in the direction of the membrane 53.
  • a stop means in the form of a bulge shaped projection 66 on the outer expansion chamber wall 58.
  • This projection 66 is formed integrally as a one piece member with the cover 51.
  • the end cover arrangement according to the invention means a simpler and less expensive mounting of the cylinder sleeve in the housing, and by forming the piston guide means as a simple two-part arrangement, i.e. cylinder sleeve and end cover with neck portion, there is obtained a substantial cost reduction at manufacturing as well as at maintenance.
  • the embodiments of the invention are not limited to the described example but can be freely varied within the scope of the claims.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Percussive Tools And Related Accessories (AREA)

Abstract

Hydraulic breaker hammer comprising a housing (10) with a longitudinal bore (12), a cylinder sleeve (14) mounted in the bore (12), a hammer piston (15) sealing guided in the cylinder sleeve (14), a guide sleeve (21) located in the front end portion of the bore (12) for receiving a working implement, and a rear end cover (16) forming a closure for the rear end of the bore (12). The rear end cover (16) comprises a tubular neck portion (17) which is formed integral as a one piece member with the end cover and which extends into the bore (12). The neck portion (17) forms a guide means for the hammer piston (15),and the bore (12) having an axially facing annular shoulder (18), wherein the cylinder sleeve (14) is supported in a correct operating position between the shoulder (18) and the end cover neck portion (17).

Description

Hydraulic breaking hammer.
The invention relates to a hydraulic breaking hammer of the type having a housing with a longitudinal bore, a cylinder sleeve supported in the bore, a hammer piston sealingly guided in the cylinder sleeve and reciprocated for delivering repeated blows on a working implement inserted through a front opening in the housing, and a rear end cover forming a closure for the bore.
Previous breaking hammers of this type, described in for instance US 5,445,232, have been rather complicated in design with many separate details which has resulted in quite high costs regarding manufacturing of the comprised details as well as assembly and service.
The main object of the invention is to create a hydraulic breaking hammer of the above described type having fewer details resulting in reduced manufacturing and assembly costs .
Another object of the invention is to create a hydraulic breaking hammer having a simple and robust design with a simplified piston fit.
Further objects and advantages of the invention will appear from the following specification and claims.
A preferred embodiment of the invention is described below with reference to the accompanying drawing.
In the drawing Fig. 1 shows a longitudinal section through a hydraulic breaking hammer according to the invention. Fig. 2 shows on a larger scale a section through the distribution valve of the breaking hammer in Fig. 1. Fig. 3 shows on a larger scale a fractional section through the implement sleeve arrangement of the breaking hammer in Fig. 1.
The hydraulic breaking hammer illustrated in the drawing figures comprises a housing 10 formed with a rear mounting shoulder 11 for attachment to a mechanical carrier like an excavator arm. The housing 10 is provided with a longitudinal through bore 12 which in its rear part supports a cylinder sleeve 14 for sealingly guide a hammer piston 15. At the rear end of the housing 10 there is bolted on an end cover 16 which forms an end closure for the bore 12. This end cover 16 is formed as a one piece member with a tube shaped neck portion 17 which extends into the bore 12 and contacts the rear end of the cylinder sleeve 14. The latter is clamped in its proper position in the bore 12 between the end cover neck portion 17 and a shoulder 18 in the bore 12. The neck portion 17 also forms a guide means for the hammer piston 15 and carries a seal ring 19 for co-operation with the rear end of the hammer piston 15.
In its front part the bore 12 carries a working implement guide sleeve 20 which is intended to receive the rear end of a working implement (not shown) . For lubricating the sleeve 20 on its inside there is provided a lubricant supply passage 21 in the housing 10 which via radial openings 22 a,b in the guide sleeve 20 communicates with the inside of the guide sleeve 20. Moreover, the guide sleeve 20 is provided with four O-rings 23 a-d on its outside the purposes of which are two, namely via frictional engagement with the bore 12 retain the sleeve 20 in the bore 12, and to seal off between them two annular compartments 24,25. The radial openings 22 a,b in the guide sleeve 20 are located between the O-rings 23 a,b and 23 c,d, respectively, such that lubricant has to pass through the compartments 24,25 to reach the radial openings 22 a,b and the guide sleeve 20 inside. See Fig. 3. Accordingly, the compartments 24,25 are filled with lubricant (grease), and due to the relative axial extension of the compartments 24,25 lubricant is spread over a substantial part of the outside surface of the guide sleeve 20, thereby, preventing seizure of the guide sleeve 20 relative to the bore 12.
The housing 10 has a pressure fluid inlet passage 28 for supplying motive pressure fluid to the cylinder sleeve 14 so as to drive the hammer piston 15 in its reciprocating movement for delivering blows to a working implement inserted in the guide sleeve 20. The piston 15 has two oppositely facing drive surfaces 29,30, whereof the lower surface 30 is continuously connected to the pressure fluid source, whereas the upper surface 29 is intermittently pressurised via a pressure fluid distribution valve 31. The distribution valve 31 has a fluid inlet 32 communicating with the pressure fluid inlet passage 28, and a fluid outlet 33 communicating with the upper drive surface 29 of the hammer piston 15. Moreover, the distribution valve 31 comprises a valve bore 35 and a valve element 34 sealingly guided in the bore 35. The valve element 34 consists of a tubular guide portion 36 guided in the bore 35, and an end wall 37. In the end wall 37 there are through openings 38 for connecting the inside of the guide portion 36 and the fluid inlet 32 with the outer surface of the end wall 37. The end wall 37 is provided with a reduced diameter activation portion 40 which extends co-axially in a direction opposite the guide portion 36 and is received in an intermittently pressurised activation bore 41.
The end wall 37 has a slightly larger cross section than the guide portion 36, and since the valve element 34 is open ended the fluid pressure will act constantly both on the surface area formed by the guide portion 36 and via the openings 38 on the outer surface of the end wall 37. In the position where the activation bore 41 is connected to tank, i.e. no pressure acting on the activation portion 40, the remaining part of the end wall 37 is smaller than the guide portion area resulting in a closing force on the valve element 34. When instead the activation bore 41 is pressurised the total area of the end wall plus activation portion 40 will generate a force that will dominate over the force generated by the pressure acting on the guide portion area. This means that the valve element 34 is shifted to its open position. (Not shown) .
The valve element 34 is provided to control the communication between the inlet 32 and the outlet 33, and for that purpose the valve element 34 is formed with a double seal function, namely both a clearance seal and a seat seal. The clearance seal function is obtained by a circumferential surface 44 of the end wall 37 co-operates with the valve bore 35 as illustrated in the closed position of the valve shown in Fig. 1. The seat seal is accomplished by an annular seat 45 at the end of the bore 35 in co-operation with an annular contact surface 46 on the end wall 37. By a combined clearance seal and seat seal as described above there is obtained a high degree of valve tightness and, hence, a high efficiency of the hammer.
The breaker hammer shown in the drawing also comprises a pressure peak absorbing accumulator 50 which is partly formed by the hammer housing 10 and partly by a cover 51 attached to the housing 10. The accumulator 50 comprises an expansion chamber 52 which in a conventional way is divided by a flexible membrane 53 into a pressure fluid compartment 54 and a gas cushion compartment 55. The expansion chamber 52 is defined by an inner wall 57 and an outer wall 58, wherein the outer wall 58 is formed by the cover 51.
There is also provided a movable membrane support 59 consisting of a stem portion 61 and a membrane engaging head 62. The latter is located inside the pressure fluid compartment 54, whereas the stem portion 61 is displacebly guided in a bore in the inner wall 57. Openings 64 are provided in parallel with the stem portion 61 to communicate pressure fluid into the expansion chamber 52, and the head 62 of the membrane support 59 is arranged to cover these openings 64 at low pressure levels when the membrane 53 is pressed against the inner wall 57. A spring 65 is provided to exert a bias force on the membrane support 59 in the direction of the membrane 53. In order to limit the length of the guiding stem portion 61 there is provided a stop means in the form of a bulge shaped projection 66 on the outer expansion chamber wall 58. This projection 66 is formed integrally as a one piece member with the cover 51. This movement limiting arrangement for the membrane support 59 is simple in design as it contain no extra elements.
The end cover arrangement according to the invention means a simpler and less expensive mounting of the cylinder sleeve in the housing, and by forming the piston guide means as a simple two-part arrangement, i.e. cylinder sleeve and end cover with neck portion, there is obtained a substantial cost reduction at manufacturing as well as at maintenance. However the embodiments of the invention are not limited to the described example but can be freely varied within the scope of the claims.

Claims

CI a i ms .
1. Hydraulic breaking hammer, comprising a housing (10) with a longitudinal bore (12) , a cylinder sleeve (14) mounted in said bore (12), a hammer piston (15) sealingly guided in said cylinder sleeve (14), a guide sleeve (21) located in the front end portion of said bore (12) for receiving a working implement, and a rear end cover (16) forming a closure for the rear end of said bore (12) , c h a r a c t e r i z e d in that said rear end cover (16) comprises a tubular neck portion (17) which is formed integral as a one piece member with said end cover (16) and which extends into said bore (12) , said neck portion (17) forms a guide means for the hammer piston (15), and said bore (12) having an axially facing annular shoulder (18), wherein said cylinder sleeve (14) is supported in a correct operating position between said shoulder (18) and said end cover neck portion (17) .
2. Breaking hammer according to claim 1 or 2 , wherein said housing (10) is formed with a mounting means (11) at its rear end for attachment to a mechanical carrier.
PCT/SE2005/000325 2004-03-12 2005-03-07 Hydraulic breaking hammer WO2005087443A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2007502761A JP2007528798A (en) 2004-03-12 2005-03-07 Hydraulic crushing hammer
US10/592,600 US20070175670A1 (en) 2004-03-12 2005-03-07 Hydraulic breaking hammer
DE602005003335T DE602005003335T2 (en) 2004-03-12 2005-03-07 HYDRAULIC BREAKING HAMMER
EP05711176A EP1722931B1 (en) 2004-03-12 2005-03-07 Hydraulic breaking hammer

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0400617-7 2004-03-12
SE0400617A SE528040C2 (en) 2004-03-12 2004-03-12 Hydraulic breaker

Publications (1)

Publication Number Publication Date
WO2005087443A1 true WO2005087443A1 (en) 2005-09-22

Family

ID=32067380

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE2005/000325 WO2005087443A1 (en) 2004-03-12 2005-03-07 Hydraulic breaking hammer

Country Status (7)

Country Link
US (1) US20070175670A1 (en)
EP (1) EP1722931B1 (en)
JP (1) JP2007528798A (en)
DE (1) DE602005003335T2 (en)
ES (1) ES2296139T3 (en)
SE (1) SE528040C2 (en)
WO (1) WO2005087443A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE526992C2 (en) * 2004-03-12 2005-12-06 Atlas Copco Constr Tools Ab Hydraulic pressure accumulator
KR200466458Y1 (en) * 2009-11-11 2013-04-18 주식회사수산중공업 A Solve Device for Accumulator abnormal pressure of Constrbattinguction Machine
PE20150588A1 (en) 2012-10-03 2015-04-26 Martinez De Lahidalga Javier Aracama HYDRAULIC DAMPER DEVICE FOR EXCAVATOR MACHINES
US9151386B2 (en) * 2013-03-15 2015-10-06 Caterpillar Inc. Accumulator membrane for a hydraulic hammer
EP3129514B1 (en) * 2014-04-11 2019-01-02 Comelz S.p.a. Cutting device for machines for cutting hides and the like
US20180133882A1 (en) * 2016-11-16 2018-05-17 Caterpillar Inc. Hydraulic hammer and sleeve therefor
CN110219851B (en) * 2019-04-02 2024-04-26 台州贝力特机械有限公司 Piston guide structure of hydraulic breaking hammer

Citations (5)

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Publication number Priority date Publication date Assignee Title
US4181183A (en) * 1978-01-05 1980-01-01 Nippon Pneumatic Manufacturing Co., Ltd. Impact tool
US4724911A (en) * 1985-12-20 1988-02-16 Enmark Corporation Hydraulic impact tool
US5445232A (en) * 1992-04-29 1995-08-29 Atlas Copco Berema Aktiebolag Hydraulic breaking hammer
JP2001341082A (en) * 2000-05-31 2001-12-11 Toyo Kuki Seisakusho:Kk Hydraulic breaker
JP2003071744A (en) * 2001-09-05 2003-03-12 Nippon Pneumatic Mfg Co Ltd Impact dynamic tool

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Publication number Priority date Publication date Assignee Title
US4062411A (en) * 1975-12-05 1977-12-13 Gardner-Denver Company Hydraulic percussion tool with impact blow and frequency control
JPS58143180U (en) * 1982-03-24 1983-09-27 株式会社小松製作所 lock breaker
US4906049A (en) * 1988-11-28 1990-03-06 N. P. K. Construction Equipment, Inc. Ripper using a hydraulic hammer and a method for making the improvement
WO1997002386A1 (en) * 1995-07-06 1997-01-23 Komatsu Ltd. Hydraulic roller-compactor
US5893419A (en) * 1997-01-08 1999-04-13 Fm Industries, Inc. Hydraulic impact tool
US6510904B1 (en) * 2000-05-26 2003-01-28 Nippon Pneumatic Mfg. Co., Ltd. Protected tool bushing for an impact hammer
FI121139B (en) * 2004-02-02 2010-07-30 Sandvik Mining & Constr Oy Hydraulic hammer and tool sleeve

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4181183A (en) * 1978-01-05 1980-01-01 Nippon Pneumatic Manufacturing Co., Ltd. Impact tool
US4724911A (en) * 1985-12-20 1988-02-16 Enmark Corporation Hydraulic impact tool
US5445232A (en) * 1992-04-29 1995-08-29 Atlas Copco Berema Aktiebolag Hydraulic breaking hammer
JP2001341082A (en) * 2000-05-31 2001-12-11 Toyo Kuki Seisakusho:Kk Hydraulic breaker
JP2003071744A (en) * 2001-09-05 2003-03-12 Nippon Pneumatic Mfg Co Ltd Impact dynamic tool

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
DATABASE WPI Week 200214, Derwent World Patents Index; Class P62, AN 2002-101520, XP003001445 *
PATENT ABSTRACTS OF JAPAN vol. 2003, no. 07 3 July 2003 (2003-07-03) *

Also Published As

Publication number Publication date
SE0400617D0 (en) 2004-03-12
SE528040C2 (en) 2006-08-15
SE0400617L (en) 2005-09-13
JP2007528798A (en) 2007-10-18
EP1722931A1 (en) 2006-11-22
EP1722931B1 (en) 2007-11-14
US20070175670A1 (en) 2007-08-02
DE602005003335T2 (en) 2008-11-06
DE602005003335D1 (en) 2007-12-27
ES2296139T3 (en) 2008-04-16

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