EP0438029A1 - Dispositif à percussion - Google Patents

Dispositif à percussion Download PDF

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Publication number
EP0438029A1
EP0438029A1 EP90810866A EP90810866A EP0438029A1 EP 0438029 A1 EP0438029 A1 EP 0438029A1 EP 90810866 A EP90810866 A EP 90810866A EP 90810866 A EP90810866 A EP 90810866A EP 0438029 A1 EP0438029 A1 EP 0438029A1
Authority
EP
European Patent Office
Prior art keywords
piston
impact
percussion
cushion
air
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.)
Granted
Application number
EP90810866A
Other languages
German (de)
English (en)
Other versions
EP0438029B1 (fr
Inventor
Josef Erlach
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.)
Sulzer AG
Original Assignee
Sulzer AG
Gebrueder Sulzer AG
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 Sulzer AG, Gebrueder Sulzer AG filed Critical Sulzer AG
Priority to AT90810866T priority Critical patent/ATE98547T1/de
Publication of EP0438029A1 publication Critical patent/EP0438029A1/fr
Application granted granted Critical
Publication of EP0438029B1 publication Critical patent/EP0438029B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body

Definitions

  • the invention relates to a percussion device with a drive piston actuated via a crank mechanism, which drives a free-flying percussion piston, which is mounted between air cushions and which has a piston rod designed as a bear, via the compression of an air cushion.
  • Striking devices of this type are used for hand-held or hammer-guided drilling and impact tools.
  • DE 21 55 689, DE 28 54 569, DE 28 32 169, DE 20 23 913, DE 24 61 662, DE 26 41 070, DE 22 07 962 and DE 31 21 616 striking devices are shown which have an air cushion Drive the percussion piston that strikes a tool or a tool holder.
  • the non-linear spring behavior and the storage effect of air cushions have advantages in that the transferable force can rise high before mechanical contact via the cushion takes place in the piston surfaces.
  • the object of the invention is to provide a further transmission system for a striking device which, by skillful arrangement, enables a large striking power with low transmission losses and with a small space requirement.
  • the object is achieved in that at least the shock cushion driving in the direction of impact can be charged via a backing pump, which is coupled to the crank mechanism, in that, depending on the stroke path of the impact piston, part of the impact cushion via a center bypass past the impact piston and a rebound cushion. that acts against the direction of impact on the percussion piston, can be supplied, and in that the amount of air outlet for shock pads and rebound pads can be controlled via a stroke of the center piston through a center air outlet.
  • the advantages of the invention lie in the fact that the system inevitably exhibits an irreversible behavior of its air springs during a stroke cycle, in that whenever a piston has reached a certain desired position, part of the air cushion present is effective as a working memory on the opposite side and there the compression increases very quickly compared to the piston movement. This leads to a high impact frequency and small dimensions. The impact performance is increased without reducing the tool life. There is also an air circulation along the moving Instead of parts that solve the lubrication problem when oil mist is clogged, such as by suction with the backing pump from the crankcase. In the course of a cycle, all chambers are vented to the atmosphere so that small leaks are compensated for and do not have a negative effect on the position of the free-flying percussion piston. The crank drive is also required to do work during the return movement for the working piston, which is given to the percussion piston during the pushing movement.
  • the figures show a percussion device with a drive piston 6 actuated by a crank mechanism, which drives a free-flying percussion piston 11, which is mounted between air cushions 10, 20 and which has a piston rod 12 designed as a bear, via the compression of an air cushion.
  • At least the shock cushion 10 driving in the direction of impact 13 can be charged via a backing pump, which is coupled to the crank mechanism 2. that acts against the impact direction 13 on the percussion piston 11, can be fed, and the amount of air outlet for shock pads 10 and recoil pads 20 can be controlled through a center air outlet 14 via the path of the impact piston 11.
  • a free-flying percussion piston 11 and a drive piston 6 with the same diameter are guided in a cylinder 1 and sealed with soft seals 7 on the piston skirt and on the piston rods 12, 18.
  • a pin 5 transmits the movement of a crank mechanism 2 which, with a crank in the direction of rotation 4, runs through a crank path 3 with top dead center 21 and bottom dead center 22.
  • the piston rod 18 has bores 9 which, when passing through the top dead center 21, connect the annular space delimited by the annular piston surface 8 to the crank chamber or the atmosphere. After passing through the top dead center 21, the annular space of the annular piston surface 8 is inevitably closed and the air cushion contained is compressed on the way to bottom dead center from ambient pressure to several atmospheres.
  • the percussion piston 11 has approximately reached its greatest kinetic energy, is located shortly before it hits the tool holder 15 and spatially seen between the connection openings a center bypass 19 which, depending on the path of the percussion piston 11, establishes a connection between the shock cushion 10 and the rebound cushion 20.
  • the recoil cushion 20 is additionally charged to a higher pressure in order to achieve a stronger spring effect for reversing the percussion piston 11 after the impact on the tool holder 15.
  • the percussion piston 11 strikes the tool holder 15. By closing the connection opening of the center bypass 19 on the side of the rebound cushion 20 by the percussion piston 11, the latter simultaneously opened the center air outlet 14 for the shock cushion 10.
  • the shock cushion 10 discharges and improves the balance of forces on the percussion piston 11 in favor of a rapid reversal of movement against the direction of impact 13.
  • the completed rebound cushion 20 is further compressed until the kinetic energy of the percussion piston 11 is used up and a reversal of movement takes place.
  • the spring action of the rebound cushion 20 and the pressure in the space between the piston rod 12 and the tool holder 15 bring the percussion piston 11 back into the starting situation according to FIG. 1A.
  • the reversal of motion must be carried out in idle mode without striking.
  • the kinetic energy of the percussion piston 11 is significantly higher in the striking direction 13 without the delivery of the percussion.
  • the enclosed recoil cushion 20 is compressed to a much greater extent until the percussion piston 11 has reached a reversal point which, as shown in FIG. 2, is much closer to the cylinder cover 16. Without the additional charging of the recoil cushion 20 via the center bypass 19 shown in FIG. 1D, the reversal point would be so close to Cylinder cover 16 that shock could occur. However, the spring action of this rebound cushion is far too great if it can develop over the entire return path of the percussion piston 11.
  • the percussion piston 11 is bridged before the reversal point is reached with an idle bypass 17 whose flow resistance is adjustable and which allows partial relief of the rebound cushion 20 to the shock pad 10, as long as each of the two connection openings from the idle bypass 17 on the cylinder jacket surface also is connected to another air cushion.
  • the pressure curve in the shock cushion 10 and the rebound cushion 20 depends on the path of the impact piston 11 and can be repeated within narrow limits.
  • the bypasses 17, 19, 23 and the center air outlet 14 each have an adjustable smallest cross section with which the throttle effect is fine-tuned.
  • a particular area of application is in mining when drilling blast holes with hand-operated rotary hammers.
  • the required percussion performance is so high in comparison to manual drilling machines that the size dimensioning mentioned at the beginning with the masses growing faster than the pressure forces proves to be a limit, unless other means for increasing the pressure forces are used as in the present invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Physical Deposition Of Substances That Are Components Of Semiconductor Devices (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Electrophonic Musical Instruments (AREA)
  • Lock And Its Accessories (AREA)
  • Disintegrating Or Milling (AREA)
  • Preparation Of Compounds By Using Micro-Organisms (AREA)
  • Compressor (AREA)
  • Earth Drilling (AREA)
EP90810866A 1990-01-15 1990-11-12 Dispositif à percussion Expired - Lifetime EP0438029B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90810866T ATE98547T1 (de) 1990-01-15 1990-11-12 Schlageinrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH120/90 1990-01-15
CH12090 1990-01-15

Publications (2)

Publication Number Publication Date
EP0438029A1 true EP0438029A1 (fr) 1991-07-24
EP0438029B1 EP0438029B1 (fr) 1993-12-15

Family

ID=4179709

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90810866A Expired - Lifetime EP0438029B1 (fr) 1990-01-15 1990-11-12 Dispositif à percussion

Country Status (9)

Country Link
US (1) US5161623A (fr)
EP (1) EP0438029B1 (fr)
JP (1) JPH04217472A (fr)
AT (1) ATE98547T1 (fr)
AU (1) AU632652B2 (fr)
CA (1) CA2033848C (fr)
DE (1) DE59003889D1 (fr)
FI (1) FI94036C (fr)
ZA (1) ZA908924B (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012206445A1 (de) * 2012-04-19 2013-10-24 Hilti Aktiengesellschaft Werkzeugmaschine
CN105722645A (zh) * 2013-11-11 2016-06-29 喜利得股份公司 手持工具机

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19728729C2 (de) * 1997-07-04 2000-11-09 Wacker Werke Kg Luftfeder-Schlagwerk mit Luftausgleich
DE19828426C2 (de) * 1998-06-25 2003-04-03 Wacker Werke Kg Antriebskolben mit geringer Wandstärke für ein Luftfederschlagwerk
DE19843642B4 (de) * 1998-09-23 2004-03-25 Wacker Construction Equipment Ag Luftfederschlagwerk mit Rückholluftfeder
DE10145464C2 (de) * 2001-09-14 2003-08-28 Wacker Construction Equipment Bohr- und/oder Schlaghammer mit anpressdruckabhängiger Leerlaufsteuerung
GB0428210D0 (en) * 2004-12-23 2005-01-26 Black & Decker Inc Mode change mechanism
DE102005019711A1 (de) * 2005-04-28 2006-11-09 Robert Bosch Gmbh Handwerkzeugmaschinenschlagwerkeinheit
DE102012206452A1 (de) * 2012-04-19 2013-10-24 Hilti Aktiengesellschaft Handwerkzeugmaschine und Steuerungsverfahren
EP3181298A1 (fr) * 2015-12-15 2017-06-21 HILTI Aktiengesellschaft Machine-outil a percussion
CN213259295U (zh) 2017-10-20 2021-05-25 米沃奇电动工具公司 用于通过凿子在工件上执行开凿操作的冲击工具
US11059155B2 (en) 2018-01-26 2021-07-13 Milwaukee Electric Tool Corporation Percussion tool
CN116494185B (zh) * 2023-05-29 2023-10-20 浙江德硕科技股份有限公司 一种带防尘和冷却功能的电镐

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2023913A1 (de) * 1970-05-15 1971-11-25 Hilti Ag, Schaan (Liechtenstein) Schlagkolben für elektropneumaüschen Bohrhammer
DE2461662A1 (de) * 1973-12-31 1975-07-03 Atlas Copco Ab Verfahren und vorrichtung zur pneumatischen daempfung des hammerkolbens einer hammervorrichtung
DE2832169A1 (de) * 1978-07-21 1980-01-31 Hilti Ag Motorisch betriebener bohrhammer
DE2854569A1 (de) * 1978-12-18 1980-06-26 Hilti Ag Bohr- und meisselhammer
DE2854953A1 (de) * 1978-12-20 1980-07-10 Licentia Gmbh Bohrhammer
CH649604A5 (en) * 1980-07-11 1985-05-31 Vni I Pk I Percussive machine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1093302A (en) * 1910-03-01 1914-04-14 Pneumelectric Machine Company Pressure-developing pneumatic tool.
US1891411A (en) * 1928-02-24 1932-12-20 Cleveland Rock Drill Co Percussive drill
US1827877A (en) * 1929-03-06 1931-10-20 John H Meeker Power hammer
US1881886A (en) * 1931-04-06 1932-10-11 Independent Pneumatic Tool Co Valve construction for pneumatic tools
US2426409A (en) * 1944-03-31 1947-08-26 Chicago Pneumatic Tool Co Distributing valve for percussive tools
US3114421A (en) * 1960-04-04 1963-12-17 Skil Corp Pneumatic system for a rotary hammer device
DE3539030A1 (de) * 1985-11-02 1987-05-07 Hilti Ag Bohrhammer mit pneumatisch angetriebenem schlagkolben
US4823886A (en) * 1988-04-29 1989-04-25 Vladimir Pyatov Vacuum-compression type percussion power tool

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2023913A1 (de) * 1970-05-15 1971-11-25 Hilti Ag, Schaan (Liechtenstein) Schlagkolben für elektropneumaüschen Bohrhammer
DE2461662A1 (de) * 1973-12-31 1975-07-03 Atlas Copco Ab Verfahren und vorrichtung zur pneumatischen daempfung des hammerkolbens einer hammervorrichtung
DE2832169A1 (de) * 1978-07-21 1980-01-31 Hilti Ag Motorisch betriebener bohrhammer
DE2854569A1 (de) * 1978-12-18 1980-06-26 Hilti Ag Bohr- und meisselhammer
DE2854953A1 (de) * 1978-12-20 1980-07-10 Licentia Gmbh Bohrhammer
CH649604A5 (en) * 1980-07-11 1985-05-31 Vni I Pk I Percussive machine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012206445A1 (de) * 2012-04-19 2013-10-24 Hilti Aktiengesellschaft Werkzeugmaschine
EP2653269A3 (fr) * 2012-04-19 2017-01-04 HILTI Aktiengesellschaft Machine-outil
CN105722645A (zh) * 2013-11-11 2016-06-29 喜利得股份公司 手持工具机

Also Published As

Publication number Publication date
US5161623A (en) 1992-11-10
FI94036B (fi) 1995-03-31
FI906465A0 (fi) 1990-12-31
ATE98547T1 (de) 1994-01-15
JPH04217472A (ja) 1992-08-07
FI906465A (fi) 1991-07-16
CA2033848C (fr) 2000-08-15
EP0438029B1 (fr) 1993-12-15
ZA908924B (en) 1991-08-28
CA2033848A1 (fr) 1991-07-16
DE59003889D1 (de) 1994-01-27
FI94036C (fi) 1995-07-10
AU632652B2 (en) 1993-01-07
AU6933491A (en) 1991-07-18

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