EP0066779B1 - Bohr- oder Meisselhammer - Google Patents

Bohr- oder Meisselhammer Download PDF

Info

Publication number
EP0066779B1
EP0066779B1 EP82104567A EP82104567A EP0066779B1 EP 0066779 B1 EP0066779 B1 EP 0066779B1 EP 82104567 A EP82104567 A EP 82104567A EP 82104567 A EP82104567 A EP 82104567A EP 0066779 B1 EP0066779 B1 EP 0066779B1
Authority
EP
European Patent Office
Prior art keywords
housing
handle
mass
hammer
pistons
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
Application number
EP82104567A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0066779A1 (de
Inventor
Walter Weilenmann
Nikolaus Frick
Peter Dr. Phys. Hirt
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.)
Hilti AG
Original Assignee
Hilti 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 Hilti AG filed Critical Hilti AG
Priority to AT82104567T priority Critical patent/ATE12198T1/de
Publication of EP0066779A1 publication Critical patent/EP0066779A1/de
Application granted granted Critical
Publication of EP0066779B1 publication Critical patent/EP0066779B1/de
Expired legal-status Critical Current

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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
    • B25D17/04—Handles; Handle mountings
    • B25D17/043—Handles resiliently mounted relative to the hammer housing
    • 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
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0084—Arrangements for damping of the reaction force by use of counterweights being fluid-driven
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0092—Arrangements for damping of the reaction force by use of counterweights being spring-mounted
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T408/00—Cutting by use of rotating axially moving tool
    • Y10T408/76—Tool-carrier with vibration-damping means

Definitions

  • the invention relates to a hammer drill or chisel hammer with a striking mechanism, with a housing surrounding the striking mechanism and with a handle which is resiliently supported on the housing in the direction of impact.
  • strikes are periodically generated using a striking mechanism and these are introduced onto the shank of a tool.
  • the periodic generation of impacts also leads to periodically occurring shock loads in the housing, which stimulate the housing to oscillate or vibrate. These vibrations are transmitted to the hand or arm of the operator via the handle.
  • the resulting stresses are not only uncomfortable, but can also lead to long-term health damage to the operator. Particularly in the performance class of the breakers, the stresses that are reasonable for the operator are mostly exceeded.
  • the invention is therefore based on the object of providing a hammer drill or chisel hammer of the type specified which, while maintaining the desired, low overall weight, has adequate damping of the vibrations transmitted from the hammer to the operator.
  • This object is achieved according to the invention in that a plurality of pistons, which are individually spring-supported on the housing in the direction of impact, are mounted in guide cylinders, and in that the ends of the guide cylinders are mutually connected to one another via pressure compensation lines.
  • the advantages achieved with the invention are based on the following relationships:
  • this additional mass exerts tilting moments on the housing that can only be avoided if the additional mass is arranged exactly on the axis of the impact transmission to the tool. Since this is usually not possible for structural reasons, the additional mass must be arranged off-center on the housing. However, this creates eccentric forces that can cause the housing to tip.
  • the additional mass is formed by a plurality of individually spring-supported pistons, which are preferably arranged symmetrically on the housing.
  • the distribution of the additional mass over several pistons means that the individual pistons can be made smaller and, due to the distribution on the housing, act less disruptively than a single, correspondingly larger additional mass. For reasons of cost, two pistons are preferably provided.
  • the individual pistons are supported in guide cylinders, the ends of which are mutually connected via pressure compensation lines.
  • the coupling of the individual pistons to one another thus takes place via a medium which can flow from one guide cylinder to another. It can be a liquid or gaseous medium.
  • the pistons In order to achieve a noticeable effect, the pistons must have a certain minimum size.
  • the additional mass since the total weight of the hammer is directly influenced by this additional mass and the total weight of the hammer is limited above for handling reasons, the additional mass must not be too large. In practice, it has proven to be expedient if the mass of the housing is eight to twelve times the additional mass, that is to say the total mass of the individual pistons. The preferred proportion of the additional mass in the total weight of the hammer is thus of the order of about 10%. In view of the improvement in operating convenience that can be achieved with this, this is entirely acceptable. If larger additional mass is used, the hammers become too heavy and can only be handled with great difficulty.
  • the natural frequency of the spring-supported pistons should essentially correspond to the frequency of the striking mechanism.
  • the natural frequency of the pistons is determined by their size and by the spring constant of the spring supporting them. If the natural frequency of the pistons coincides with the frequency of the striking mechanism, the pistons oscillate essentially in phase with the housing. This at least partially compensates for the shock excitation exerted on the housing.
  • the impact excitation generated by the striking mechanism and acting on the housing can only be partially compensated for by the pistons.
  • the natural frequency of the handle is smaller than the frequency of the striking mechanism by a factor of V2. With this design, the vibrations in the area of the beat frequency and above are transmitted to the handle in a damped manner.
  • the natural frequency of the handle is also determined by its mass and by the spring constant of the springs supporting the handle.
  • the hammer drill shown in FIG. 1 has a housing indicated overall by reference number 1.
  • This housing 1 consists of a motor part 1 a and a striking mechanism part 1 b.
  • a handle, generally designated 5 is arranged at the end of the housing 1 opposite the chuck 3, a handle, generally designated 5, is arranged.
  • a supply line 6 for the electrical power supply opens into the handle 5.
  • the handle 5 also carries a switch 7 for switching the hammer on and off.
  • the handle 5 is opposite the housing 1 in the direction of impact, i.e. displaceable in the axial direction of the spindle 2.
  • the handle 5 is guided via pins 1 c and corresponding bores 5a of the handle 5.
  • the handle 5 is pressed away from the housing 1 by compression springs 8.
  • a screw 9 connected to the pin 1 c serves as a stop.
  • the gap between the handle 5 and the housing 1, which is larger or smaller depending on the degree of deflection of the handle, is sealed around by a bellows 10 against the ingress of dirt into the interior of the machine.
  • the bellows 10 enables the relative movement between the handle 5 and the housing 1.
  • FIG. 2 again shows the housing 1 with the handle 5 arranged at the rear end of the housing 1 and the bellows 10 sealing the gap between the handle 5 and the housing 1.
  • the chuck 3 arranged on the spindle 2 is at the opposite end of the housing 1 for the tool 4 can be seen.
  • the absorber housing 11 is connected to the housing 1 and has guide cylinders 11 a running parallel to the direction of impact.
  • Mass bodies 12 are arranged in the guide cylinders 11 a.
  • the mass bodies 12 are designed as pistons and are guided in the guide cylinders 11.
  • the mass bodies 12 have an area provided with a spring thread 12a.
  • a spring 13 is screwed onto the spring thread 12a and thus connected to the mass body 12.
  • the other end of the spring 13 is connected to an abutment generally designated 14.
  • the abutment 14 also has a spring thread 14a adapted to the spring 13.
  • the mass body 12 is thus connected to the abutment 14 via the spring 13.
  • the abutment 14 also serves to unilaterally close the guide cylinder 11 a.
  • the other end of the guide cylinder 11 a is closed by a plug 15.
  • the mass bodies 12 and the spring 13 form a system which can execute vibrations running parallel to the axis of impact direction. Due to the mass body 12 acting as a piston, the guide cylinders 11 a are divided into two spaces. One space, in which the spring 13 is also located, is located between the mass body 12 and the abutment 14. The other space is located between the mass body 12 and the plug 15. The spaces in front of and behind the mass bodies 12 are through pressure compensation lines 11 b, 11 c mutually connected. A coupling of the two mass bodies 12 is achieved by this measure.
  • the two mass bodies 12 are dimensioned such that their mass accounts for approximately 10% of the housing with the drive and striking mechanism arranged therein.
  • the natural frequency of the mass body 12 corresponds essentially to the frequency of the striking mechanism.
  • the suspension of the handle 5 is tuned so that the natural frequency of the handle 5 is about a factor is less than the frequency of the striking mechanism. E.g. at a frequency of the striking mechanism of 45 Hz, the natural frequency of the handle is approximately 35 Hz. Such tuning results in an optimal reduction of the vibrations generated by the striking mechanism.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Earth Drilling (AREA)
  • Golf Clubs (AREA)
  • Processing Of Stones Or Stones Resemblance Materials (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
  • Catalysts (AREA)
  • Ceramic Products (AREA)
  • Drilling Tools (AREA)
EP82104567A 1981-06-10 1982-05-25 Bohr- oder Meisselhammer Expired EP0066779B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82104567T ATE12198T1 (de) 1981-06-10 1982-05-25 Bohr- oder meisselhammer.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19813122979 DE3122979A1 (de) 1981-06-10 1981-06-10 Bohr- oder meisselhammer
DE3122979 1981-06-10

Publications (2)

Publication Number Publication Date
EP0066779A1 EP0066779A1 (de) 1982-12-15
EP0066779B1 true EP0066779B1 (de) 1985-03-20

Family

ID=6134346

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82104567A Expired EP0066779B1 (de) 1981-06-10 1982-05-25 Bohr- oder Meisselhammer

Country Status (14)

Country Link
US (1) US4478293A (enrdf_load_stackoverflow)
EP (1) EP0066779B1 (enrdf_load_stackoverflow)
JP (1) JPS57211482A (enrdf_load_stackoverflow)
AT (1) ATE12198T1 (enrdf_load_stackoverflow)
AU (1) AU8440282A (enrdf_load_stackoverflow)
CA (1) CA1180578A (enrdf_load_stackoverflow)
DE (1) DE3122979A1 (enrdf_load_stackoverflow)
ES (1) ES8305085A1 (enrdf_load_stackoverflow)
FI (1) FI75294C (enrdf_load_stackoverflow)
HU (1) HU183955B (enrdf_load_stackoverflow)
MX (1) MX158199A (enrdf_load_stackoverflow)
NO (1) NO153955C (enrdf_load_stackoverflow)
SU (1) SU1178317A3 (enrdf_load_stackoverflow)
YU (1) YU110182A (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7252157B2 (en) 2003-04-01 2007-08-07 Makita Corporation Power tool

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CA2951975C (en) * 2014-06-16 2022-08-30 Swerea Ivf Ab An impact machine
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FR2237734A1 (en) * 1973-07-16 1975-02-14 Inst Nal Rech Securite Oscillating mass shock absorbers for pneumatic drill - two sliding masses sprung above and below flank drill casing
DE2403074C3 (de) * 1974-01-23 1978-10-26 Demag Ag, 4100 Duisburg Druckluftbetätigtes Schlagwerkzeug
GB1549771A (en) * 1975-07-11 1979-08-08 Post Office Vibratory tool with vibration isolation mechanism

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7252157B2 (en) 2003-04-01 2007-08-07 Makita Corporation Power tool

Also Published As

Publication number Publication date
US4478293A (en) 1984-10-23
ATE12198T1 (de) 1985-04-15
HU183955B (en) 1984-06-28
ES512958A0 (es) 1983-03-16
EP0066779A1 (de) 1982-12-15
YU110182A (en) 1986-06-30
ES8305085A1 (es) 1983-03-16
NO821908L (no) 1982-12-13
AU8440282A (en) 1982-12-16
NO153955C (no) 1986-06-25
JPS57211482A (en) 1982-12-25
NO153955B (no) 1986-03-17
JPS6363358B2 (enrdf_load_stackoverflow) 1988-12-07
FI75294C (fi) 1988-06-09
DE3122979A1 (de) 1983-01-05
CA1180578A (en) 1985-01-08
FI75294B (fi) 1988-02-29
FI821478A0 (fi) 1982-04-28
SU1178317A3 (ru) 1985-09-07
DE3122979C2 (enrdf_load_stackoverflow) 1989-10-05
MX158199A (es) 1989-01-16

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