WO2003008156A1 - Marteau hydraulique a piston et cylindre se deplaçant en opposition de phase - Google Patents

Marteau hydraulique a piston et cylindre se deplaçant en opposition de phase Download PDF

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Publication number
WO2003008156A1
WO2003008156A1 PCT/DK2001/000445 DK0100445W WO03008156A1 WO 2003008156 A1 WO2003008156 A1 WO 2003008156A1 DK 0100445 W DK0100445 W DK 0100445W WO 03008156 A1 WO03008156 A1 WO 03008156A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
engine housing
hammer
hammer body
chamber
Prior art date
Application number
PCT/DK2001/000445
Other languages
English (en)
Inventor
Esben Vadstrup
Original Assignee
Breakers A/S
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 Breakers A/S filed Critical Breakers A/S
Priority to PCT/DK2001/000445 priority Critical patent/WO2003008156A1/fr
Publication of WO2003008156A1 publication Critical patent/WO2003008156A1/fr

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
    • B25D17/24—Damping the reaction force
    • 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

Definitions

  • the invention relates to a hydraulic hammer comprising an engine housing with a cylindrical bore in which a piston is placed in an axially displaceable manner, said piston transferring kinetic energy to an auxiliary tool, and means for the supply of oil and also the establishing of a pressure in the engine housing, said pressure bringing about the movement of the piston and also coupling to the source of energy.
  • Such a hydraulic hammer is known, for example, from Swedish patent publication no. 505601 , which is provided with an engine housing with an axially displaceable piston. In the engine housing itself there are also provided intermediate walls which are filled out with a noise-suppressing material, so that noise from the hammer is reduced to a certain degree. This noise re- duction will not, however, be satisfactory, the reason being that the noise can escape in areas other than in just the insulated area. Moreover, the construction will also give rise to strong vibrations for the user, in that with this construction no solution is provided for the very well-known problem that vibrations are transferred from the product to the user, for example in connection with the breaking-up of concrete, asphalt and the like.
  • the objects of the present invention are thus to provide a hydraulic hammer which is not encumbered with the disadvantages of the existing products, and where a very low level of vibration is achieved, corresponding to less than 2 1 /2 m per second 2 , and furthermore also a particularly low level of noise as a consequence of the resulting construction, and finally a simple manufacturing of the product in that the number of components is considerably reduced and can be produced as integrated units.
  • a hydraulic hammer of the kind disclosed in the introduction and further where the hammer also includes a hammer body which at least surrounds the engine housing, and where said engine housing is connected in a flexible manner by first means to the hammer body, and the hammer body comprising a handgrip in the area opposite the auxiliary tool.
  • the hydraulic hammer thus being en- closed in an outer jacket, the noise will naturally be strongly reduced, in that the jacket in itself serves to suppress noise. What is of further importance is the flexible suspension of the engine housing in the heavy outer jacket, so that the transferred vibration is considerably reduced.
  • the piston will thus start at the bottom when the oil is connected. There is a high pressure on the underside of the piston and a low pressure of approx. 10 bar over the top of the piston, while the high pressure or working pressure lies at around 120 bar.
  • the piston moves at almost constant speed up to its uppermost reversing point. Thereafter, the pressure over the piston will be changed from the tank pressure 10 bar to the working pressure 120 bar, whereby the piston accelerates quickly downwards.
  • the effect of the pressure is that the engine housing accelerates upwards.
  • the engine housing is hereby lifted up from the auxiliary tool, for example in the form of a chisel.
  • the hand- grip becomes a part of the hammer body and vibration-damping arrangements are not necessary on the handgrip itself, as is otherwise normally the case.
  • a construction such as that disclosed can in itself result in the hammer body constituting a considerable weight. The large mass is thus insulated from the actual engine housing, and is instead transferred to the stationary part, i.e. the hammer body itself.
  • the external source of energy is preferably a pump which pumps oil to the hammer. In the cases where an excess of oil is pumped in, this is stored in the accumulator and used later.
  • fig. 1 shows a section through an example embodiment according to the invention
  • fig. 2 shows the movement pattern for the piston
  • fig. 3 shows the supply of oil in principle
  • fig. 4 shows the position of the slide when the piston is in the top position
  • fig. 5 shows the position of the slide when maximum pressure is applied to the piston for acceleration of the piston towards the auxiliary tool.
  • Figure 1 shows a section through a hammer 1 , comprising an engine housing 2 in which there is a cylindrical bore 3 for the accommodation of a piston 4 which is axially displaceable.
  • the free end surface 7 of the piston lies in the area opposite the construction's handgrip 11.
  • the engine housing 2 itself is surrounded by a hammer body 9, and where the hammer body 9 as mentioned at least surrounds the engine housing itself, but possibly also parts of the area where the piston has its clearance, and possibly part of the auxiliary tool.
  • the hammer body 9 also has a handgrip 11 which thus constitutes an integral part of the body 9.
  • the hammer body 9 has connection and passage 8 to an oil pump/energy source, from which oil is pumped into a third chamber 19 where there is a working pressure of around 120-130 bar.
  • first channel 18 which connects the chamber to a second chamber 16 when the slide is in its first position, said second chamber 16 lying between the outer surface of the piston 4 and the inner surface of the engine housing 2 and being limited by an axially dis- placeable slide 17, and where this slide/cylindrical sleeve has a first and a second position.
  • connection will be established from the second chamber to a so-called tank chamber 15 which lies in the area between the inner surface of the body 9 and the outer surface of the housing. In this tank chamber there is a pressure of approx. 10 bar.
  • the connection takes place by means of a second channel 20.
  • the slide 17 assumes a second position, which appears from fig. 5, there is instead established a connection between the second chamber 16 and the oil-filled third chamber 19, said third chamber as mentioned having a pressure of around 120 bar, a so-called working pressure.
  • a third channel 21 which connects the third chamber 19 to a fourth chamber 22 which lies at a distance from the other chambers and in the area closer to the free surface of the piston.
  • the pressure in this chamber will thus always assume working pressure.
  • a first control chamber and a second control chamber there is a first control chamber and a second control chamber, said first control chamber 23 and said second control chamber 24 being placed in a circular manner as an annular ring chamber between the outer surface of the piston and the inner surface of the engine housing.
  • the pressure in the second control chamber 24 will depend on the position of the piston and the time in the cycle.
  • the pressure in the second control chamber 24 is t.
  • the pressure in the second control chamber 24 changes to p at the moment that the piston is driven upwards and the edge 29 of the piston opens for connection between the chamber 22 and the second control chamber 24.
  • the pressure p in the second control chamber 24 causes the slide to take up its second position and open for connection between the chamber 19 and the chamber 16.
  • the pressure p in the chamber 16 causes the piston to move downwards, and the pressure in the second control chamber 24 remains p until the chamber 28 forms connection between the first control chamber 23 and the second control chamber 24.
  • the slide assumes its first position again when the pressure in the second control chamber 24 becomes t.
  • the pressure in the second control chamber 24 remains t until connection is opened again between the second control chamber 24 and the chamber 22.
  • the engine housing 2 itself is suspended in first means in the form of springs 10, 10', preferably as helical springs.
  • springs 10, 10' connect the engine housing 2 with the hammer body 9, where in this case use is made of two springs, i.e. a spring placed between a projecting collar 25, the first collar, on the engine housing itself, and a collar 26, the second collar, on the hammer body 9, and a spring placed between the collar 31 on the engine housing and collar 30 on the hammer body.
  • the springs are mounted in such a manner that they are pre-stressed and, to- gether with the guides, ensure that there is no contact between the engine housing and the hammer body.
  • the two springs are thus active in opposite directions, in that the first spring 10' is compressed, whereby the compression of the second spring 10 is reduced, and vice versa.
  • the hammer body also comprises elements, such as an accumulator 14, which increases the weight of the body itself.
  • FIG 2 there is seen a principle diagram for the movements of the piston.
  • the piston starts in bottom position when the oil is supplied.
  • the piston is driven at almost constant speed up to the uppermost reversing point.
  • the pressure over the piston is changed from t to p and the piston accelerates quickly downwards.
  • the pressure causes the engine housing to accelerate upwards.
  • the engine housing is hereby lifted up from the chisel.
  • the movement of the engine housing is absorbed by the spring.
  • the spring influences the hammer body, but the movement of the hammer body is only marginal due to the great inherent weight of the hammer body.
  • the piston reaches the maximum speed immediately before the auxiliary tool is hit.
  • the kinetic energy in the piston is delivered to the chisel, whereby the piston is braked.
  • the pressure is changed again and the piston is again driven upwards as the start of a new cycle.
  • the engine housing is pressed back to the chisel by the weight of the engine housing and the force from the spring.

Landscapes

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

Abstract

La présente invention a trait à un marteau hydraulique (1) comportant un carter-moteur (2) présentant un alésage cylindrique (3) dans lequel un piston (4) est disposé de manière à être mobile en direction axiale, ledit piston (4) transférant une énergie cinétique vers un outil auxiliaire (5) et des moyens de fourniture d'huile (8) et également d'établissement de pression dans le carter-moteur (2), ladite pression entraînant le déplacement du piston (4) et un couplage à une source d'énergie, et dans lequel ledit marteau (1) comporte en outre un corps de marteau (9), ledit corps de marteau entourant au moins le carter-moteur (2), et dans lequel ledit carter-moteur (2) est couplé de manière élastique par des premiers moyens (10) au corps de marteau (9) et le corps de marteau (9) comporte une poignée (11) dans la zone opposée à l'outil auxiliaire (5). Ainsi on réalise un marteau hydraulique qui ne présente pas les inconvénients des produits existants, et dans lequel on réalise un niveau de vibration bas, correspondant à moins de 2 1/2 m/s2, et en outre un niveau de bruit particulièrement bas dû à la construction obtenue, et enfin un fabrication simplifiée du produit en raison de la réduction du nombre de pièces et qui peuvent être produites en unités intégrées.
PCT/DK2001/000445 2001-06-26 2001-06-26 Marteau hydraulique a piston et cylindre se deplaçant en opposition de phase WO2003008156A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/DK2001/000445 WO2003008156A1 (fr) 2001-06-26 2001-06-26 Marteau hydraulique a piston et cylindre se deplaçant en opposition de phase

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/DK2001/000445 WO2003008156A1 (fr) 2001-06-26 2001-06-26 Marteau hydraulique a piston et cylindre se deplaçant en opposition de phase

Publications (1)

Publication Number Publication Date
WO2003008156A1 true WO2003008156A1 (fr) 2003-01-30

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Family Applications (1)

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PCT/DK2001/000445 WO2003008156A1 (fr) 2001-06-26 2001-06-26 Marteau hydraulique a piston et cylindre se deplaçant en opposition de phase

Country Status (1)

Country Link
WO (1) WO2003008156A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7648560B2 (en) 2003-10-10 2010-01-19 Osaka Titanium Technologies Co., Ltd. Method for producing Ti or Ti alloy through reduction by Ca
CN108005970A (zh) * 2017-12-25 2018-05-08 马鞍山云林百成机械制造有限公司 一种液压锤集成液压装置
CN109153112A (zh) * 2016-05-18 2019-01-04 株式会社牧田 冲击工具

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3788404A (en) * 1971-02-01 1974-01-29 Naradi Pneumatic impact tool
GB1587611A (en) * 1977-10-14 1981-04-08 Secretary Industry Brit Resilient mountings for fluid reciprocated tools
GB2129733A (en) * 1982-10-27 1984-05-23 Jean Walton More-vibration-free concrete breakers and percussion drills
US4563938A (en) * 1983-08-01 1986-01-14 Atlas Copco Aktiebolag Pressure fluid operated percussive tool

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3788404A (en) * 1971-02-01 1974-01-29 Naradi Pneumatic impact tool
GB1587611A (en) * 1977-10-14 1981-04-08 Secretary Industry Brit Resilient mountings for fluid reciprocated tools
GB2129733A (en) * 1982-10-27 1984-05-23 Jean Walton More-vibration-free concrete breakers and percussion drills
US4563938A (en) * 1983-08-01 1986-01-14 Atlas Copco Aktiebolag Pressure fluid operated percussive tool

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7648560B2 (en) 2003-10-10 2010-01-19 Osaka Titanium Technologies Co., Ltd. Method for producing Ti or Ti alloy through reduction by Ca
CN109153112A (zh) * 2016-05-18 2019-01-04 株式会社牧田 冲击工具
CN109153112B (zh) * 2016-05-18 2021-08-31 株式会社牧田 冲击工具
CN108005970A (zh) * 2017-12-25 2018-05-08 马鞍山云林百成机械制造有限公司 一种液压锤集成液压装置

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