EP0066779A1 - Boring or chiseling hammer - Google Patents

Boring or chiseling hammer Download PDF

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Publication number
EP0066779A1
EP0066779A1 EP82104567A EP82104567A EP0066779A1 EP 0066779 A1 EP0066779 A1 EP 0066779A1 EP 82104567 A EP82104567 A EP 82104567A EP 82104567 A EP82104567 A EP 82104567A EP 0066779 A1 EP0066779 A1 EP 0066779A1
Authority
EP
European Patent Office
Prior art keywords
housing
mass
hammer
handle
striking mechanism
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
EP82104567A
Other languages
German (de)
French (fr)
Other versions
EP0066779B1 (en
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/en
Publication of EP0066779A1 publication Critical patent/EP0066779A1/en
Application granted granted Critical
Publication of EP0066779B1 publication Critical patent/EP0066779B1/en
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, a housing surrounding it and a handle connected to the housing.
  • 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 periodic shock loads in the housing, which stimulate it to oscillate or vibrate.
  • the vibrations are transmitted to the hand or arm of the operator via the handle. These vibrations are not only uncomfortable, but can also lead to long-term damage to the health of the operator. Particularly in the performance class of the breakers, the stresses that are reasonable for the operator are mostly exceeded.
  • the invention has for its object to provide a hammer drill or chisel hammer that is lightweight and easy to use.
  • the additional mass In order to achieve a noticeable effect, the additional mass must have a certain minimum size.
  • the additional mass since the total weight of the hammer is directly influenced by the additional mass and the total weight of the hammer is limited 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 8 to 12 times the additional mass. The preferred proportion of the additional mass in the total weight of the hammer is therefore of the order of magnitude of approximately 10%. In view of the improvement in operating convenience that can be achieved with this, this is entirely acceptable. If larger additional masses are used, the hammers become too heavy and can only be handled with great difficulty.
  • the additional mass is arranged in the axis of the impact transmission to the tool. Since this is usually not possible for structural reasons, only an eccentric arrangement of the additional mass remains on the housing. So that the resulting eccentrically acting forces do not cause the housing to tip, it is advantageous to design the additional mass as a plurality of individually spring-supported mass bodies.
  • the individual mass bodies are preferably arranged symmetrically on the housing. The distributing the additional mass on a plurality of mass bodies results in a further advantage in that the individual mass bodies 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 mass bodies are preferably provided.
  • the individual mass bodies In order to achieve the same movement in the case of a plurality of mass bodies, it is therefore expedient for the individual mass bodies to be designed as pistons mounted in guide cylinders and for the ends of the guide cylinders to be mutually connected via pressure compensation lines.
  • the coupling of the individual mass bodies to one another thus takes place via a medium flowing from one cylinder to the other. This can be liquid or gaseous.
  • the natural frequency of the spring-supported additional mass essentially corresponds to the frequency of the striking mechanism.
  • the natural frequency of the additional mass is determined by the size of the additional mass and by the spring constant of the spring supporting it.
  • the additional mass oscillates essentially in phase with the housing. This partly compensates for the shock excitation exerted on the housing.
  • the shock excitation generated by the striking mechanism and acting on the housing can only be partially compensated for by the additional mass.
  • the natural frequency of the handle is smaller by a factor of / 2 than the frequency of the striking mechanism. With this design, the vibrations in the area of the stroke frequency and above are dampened and transferred to the handle.
  • the natural frequency of the handle is also determined by its mass and by the spring constant of the springs supporting the handle.
  • the drill hammer shown in FIG. 1 has a housing designated overall by 1.
  • the housing 1 consists of a motor part la and a striking mechanism part 1b.
  • a spindle 2 protrudes from the striking mechanism part 1b and carries a chuck 3 for a tool 4.
  • 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 drill on and off.
  • the handle 5 can be moved relative to the housing 1 in the direction of impact, ie in the axial direction of the spindle 2.
  • the handle 5 is guided by means of pins 1c 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 1c 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.
  • the absorber housing 11 is connected to the housing 1 and has two guide cylinders 11a running parallel to the axis of impact direction.
  • Mass bodies 12 are arranged in the guide cylinders 11a.
  • the mass bodies 12 are designed as pistons and are guided in the guide cylinders 11a.
  • 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 for one-sided closing of the guide cylinder 11a.
  • the other end of the guide cylinder 11a 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 bodies 12 acting as pistons, the guide cylinders 11a 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 11b, llc 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 Percussion.
  • 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. For example, 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Golf Clubs (AREA)
  • Earth Drilling (AREA)
  • Drilling Tools (AREA)
  • Processing Of Stones Or Stones Resemblance Materials (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
  • Catalysts (AREA)
  • Ceramic Products (AREA)

Abstract

A hammer drill or chipping hammer includes a housing, a striking mechanism movably displaceably mounted within the housing, and a handle spring supported on the housing. To absorb vibrations generated during operation of the drill or hammer, piston-like weighted members are slidably mounted in the housing for movement parallel to the axial direction of the striking mechanism. The weighted members are supported by springs. Each weighted member is located within a separate cylinder and divides the cylinder into separate spaces. The spaces in the cylinders are interconnected by a fluid medium communicating between them for effecting balanced operation of the weighted members.

Description

Die Erfindung betrifft einen Bohr- oder Meisselhammer mit einem Schlagwerk, einem dieses umgebenden Gehäuse und einem mit dem Gehäuse verbundenen Handgriff.The invention relates to a hammer drill or chisel hammer with a striking mechanism, a housing surrounding it and a handle connected to the housing.

Bei Bohr- oder Meisselhämmern werden mittels eines Schlagwerks periodisch Schläge erzeugt und diese auf den Schaft eines Werkzeuges eingeleitet. Das periodische Erzeugen von Schlägen führt jedoch auch beim Gehäuse zu periodisch auftretenden Stossbelastungen, welche dieses zu Schwingungen bzw Vibrationen anregen. Die Vibrationen werden über den Handgriff auf die Hand bzw den Arm der Bedienungsperson übertragen. Diese Vibrationen sind nicht nur unangenehm, sondern können auf die Dauer auch zu gesundheitlichen Schädigungen der Bedienungsperson führen. Insbesondere in der Leistungsklasse der Abbauhämmer werden die der Bedienungsperson zumutbaren Beanspruchungen meist überschritten.In the case of rotary or chisel hammers, strikes are periodically generated using a striking mechanism and these are introduced onto the shank of a tool. However, the periodic generation of impacts also leads to periodic shock loads in the housing, which stimulate it to oscillate or vibrate. The vibrations are transmitted to the hand or arm of the operator via the handle. These vibrations are not only uncomfortable, but can also lead to long-term damage to the health of the operator. Particularly in the performance class of the breakers, the stresses that are reasonable for the operator are mostly exceeded.

Zur Reduktion der auftretenden Beanspruchungen sind in der Vergangenheit bereits verschiedene Massnahmen ergriffen worden. So ist es bekannt, den Handgriff auf dem Gehäuse federnd abzustützen. Damit diese Massnahme wirksam wird, ist eine weiche Federung des Handgriffes notwendig. Eine weiche Federung ergibt jedoch sehr grosse Federwege. Dies ist wiederum aus handhabungstechnischen Gründen nachteilig.Various measures have already been taken in the past to reduce the stresses that occur. So it is known to resiliently support the handle on the housing. A soft suspension of the handle is necessary for this measure to be effective. However, soft suspension results in very long spring travel. Again, this is disadvantageous for handling reasons.

Weiterhin ist es bekannt, eine Zusatzmasse in der Schlagrichtungsachse am Gehäuse federnd abzustützen. Das Anordnen einer Zusatzmasse ergibt zwar eine gewisse Verbesserung der Schwingungsverhältnisse. Bei Bohr- oder Meisselhämmern der oberen Leistungsklasse sind jedoch die auf die Bedienungsperson einwirkenden Schwingungen immer noch zu stark. Durch eine Vergrösserung der Zusatzmasse sind Verbesserungen möglich. Dabei wird jedoch das Gesamtgewicht des Hammers erhöht, was wiederum zu einer verstärkten Belastung der Bedienungsperson führt.Furthermore, it is known to resiliently support an additional mass in the direction of impact on the housing. The arrangement of an additional mass results in a certain improvement in the vibration conditions. In the case of high-performance rotary or chisel hammers, however, the vibrations acting on the operator are still too strong. Improvements are possible by increasing the additional mass. However, the total weight of the hammer is increased, which in turn leads to an increased burden on the operator.

Der Erfindung liegt die Aufgabe zugrunde, einen Bohr- oder Meisselhammer zu schaffen, der ein geringes Gewicht und einen hohen Bedienungskomfort aufweist.The invention has for its object to provide a hammer drill or chisel hammer that is lightweight and easy to use.

Gemäss der Erfindung wird dies erreicht durch eine Kombination der nachstehenden Merkmale:

  • a) Der Handgriff ist in Schlagrichtung am Gehäuse federnd abgestützt,
  • b) eine Zusatzmasse ist in der Schlagrichtungsachse am Gehäuse federnd abgestützt.
According to the invention, this is achieved by a combination of the following features:
  • a) The handle is resiliently supported on the housing in the direction of impact,
  • b) an additional mass is resiliently supported on the housing in the direction of impact.

Die Kombination der beiden für sich einzeln bekannten Merkmale ergibt eine überraschende Verbesserung des Bedienungskomforts, die wesentlich über die mit den einzelnen Massnahmen erzielbaren Verbesserungen hinausgeht. Die beiden Massnahmen üben somit aufeinander eine nicht voraussehbare Wechselwirkung aus.The combination of the two features which are known per se results in a surprising improvement in the ease of use, which goes far beyond the improvements which can be achieved with the individual measures. The two measures therefore exert an unforeseeable interaction on one another.

Um eine spürbare Wirkung zu erzielen, muss die Zusatzmasse eine gewisse Mindestgrösse aufweisen. Da andererseits das Gesamtgewicht des Hammers durch die Zusatzmasse direkt beeinflusst wird, und das Gesamtgewicht des Hammers aus Handhabungsgründen nach oben begrenzt ist, darf die Zusatzmasse nicht zu gross sein. In der Praxis hat es sich als zweckmässig erwiesen, wenn die Masse des Gehäuses das 8- bis 12- fache der Zusatzmasse beträgt. Der bevorzugte Anteil der Zusatzmasse am Gesamtgewicht des Hammers liegt somit in der Grössenordnung von ca 10 %. Dies ist im Hinblick auf die damit erreichbare Verbesserung des Bedienungskomforts durchaus tragbar. Bei Verwendung grösserer Zusatzmassen werden die Hämmer zu schwer und lassen sich nur noch mit grösseren Schwierigkeiten handhaben.In order to achieve a noticeable effect, the additional mass must have a certain minimum size. On the other hand, since the total weight of the hammer is directly influenced by the additional mass and the total weight of the hammer is limited 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 8 to 12 times the additional mass. The preferred proportion of the additional mass in the total weight of the hammer is therefore of the order of magnitude of approximately 10%. In view of the improvement in operating convenience that can be achieved with this, this is entirely acceptable. If larger additional masses are used, the hammers become too heavy and can only be handled with great difficulty.

Kippmomente auf das Gehäuse können vermieden werden, wenn die Zusatzmasse in der Achse der Schlagübertragung auf das Werkzeug angeordnet wird. Da dies aus baulichen Gründen meist nicht möglich ist, bleibt nur noch eine aussermittige Anordnung der Zusatzmasse am Gehäuse. Damit die dabei entstehenden, aussermittig angreifenden Kräfte kein Kippen des Gehäuses verursachen, ist es vorteilhaft, die Zusatzmasse als mehrere einzeln federnd abgestützte Massenkörper auszubilden. Zum Ausgleich der Kräfte werden die einzelnen Massenkörper vorzugsweise symmetrisch am Gehäuse angeordnet. Das Verteilen der Zusatzmasse auf mehrere Massenkörper ergibt einen weiteren Vorteil, indem die einzelnen Massenkörper kleiner ausgebildet werden können und durch die Verteilung am Gehäuse weniger störend wirken als eine einzige, entsprechend grösser ausgebildete Zusatzmasse. Aus Kostengründen werden vorzugsweise zwei Massenkörper vorgesehen.Tipping moments on the housing can be avoided if the additional mass is arranged in the axis of the impact transmission to the tool. Since this is usually not possible for structural reasons, only an eccentric arrangement of the additional mass remains on the housing. So that the resulting eccentrically acting forces do not cause the housing to tip, it is advantageous to design the additional mass as a plurality of individually spring-supported mass bodies. To balance the forces, the individual mass bodies are preferably arranged symmetrically on the housing. The distributing the additional mass on a plurality of mass bodies results in a further advantage in that the individual mass bodies 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 mass bodies are preferably provided.

Bei mehreren Massenkörpern besteht die Möglichkeit, dass sich diese ungleich bewegen. So können bspw zwischen den Schwingungen der einzelnen Massenkörper geringe Phasenverschiebungen auftreten. Durch solche Unterschiede kann die Wirkung der Zusatzmasse im Betrieb wesentlich verringert werden. Um eine gleiche Bewegung der einzelnen Massenkörper zu erreichen, könnten diese bspw mechanisch miteinander verbunden werden. Eine solche Lösung scheidet jedoch aus Platz- und Wirtschaftlichkeitsgründen aus.With several mass bodies there is the possibility that they move unevenly. For example, small phase shifts can occur between the vibrations of the individual mass bodies. Such differences can significantly reduce the effect of the additional mass in operation. In order to achieve the same movement of the individual mass bodies, these could be mechanically connected to one another, for example. However, such a solution is ruled out for reasons of space and economy.

Um bei mehreren Massenkörpern eine gleiche Bewegung zu erreichen, ist es daher zweckmässig, dass die einzelnen Massenkörper als in Führungszylindern gelagerte Kolben ausgebildet und die Enden der Führungszylinder über Druckausgleichsleitungen wechselseitig miteinander verbunden sind. Die Koppelung .der einzelnen Massenkörper untereinander erfolgt somit über ein von einem zum anderen Zylinder strömendes Medium. Dieses kann flüssig oder gasförmig sein.In order to achieve the same movement in the case of a plurality of mass bodies, it is therefore expedient for the individual mass bodies to be designed as pistons mounted in guide cylinders and for the ends of the guide cylinders to be mutually connected via pressure compensation lines. The coupling of the individual mass bodies to one another thus takes place via a medium flowing from one cylinder to the other. This can be liquid or gaseous.

Bei der Bewegung eines Kolbens in einem Zylinder entsteht auf der einen Seite ein Ueber- und auf der anderen Seite ein Unterdruck. Durch das wechselseitige Verbinden der Enden der Führungszylinder erfolgt ein Druckausgleich. Bewegt sich ein Kolben schneller als der andere, so wird der sich langsamer bewegende Kolben durch den sich schneller bewegenden Kolben beschleunigt bzw der sich schneller bewegende Kolben vom sich langsamer bewegenden Kolben gebremst. Die Bewegungen der einzelnen, als Kolben ausgebildeten Massenkörper erfolgen somit praktisch gleich.When a piston moves in a cylinder, there is an overpressure on one side and a vacuum on the other side. By mutually connecting the ends of the guide cylinders, pressure equalization takes place. If one piston moves faster than the other, the slower moving piston is accelerated by the faster moving piston or the faster moving piston is braked by the slower moving piston. The movements of the individual mass bodies designed as pistons are thus practically the same.

Um die bestmögliche Vibrationsminderung zu erzielen, ist es vorteilhaft, dass die Eigenfrequenz der federnd abgestützten Zusatzmasse im wesentlichen der Frequenz des Schlagwerkes entspricht. Die Eigenfrequenz der Zusatzmasse wird durch die Grösse der Zusatzmasse sowie durch die Federkonstante der sie abstützenden Feder bestimmt. Bei gleicher Eigenfrequenz der Zusatzmasse mit der Frequenz des Schlagwerkes schwingt die Zusatzmasse im wesentlichen gleichbleibend phasenverschoben zum Gehäuse. Dadurch wird die auf das Gehäuse ausgeübte Stosserregung zum Teil kompensiert.In order to achieve the best possible vibration reduction, it is advantageous that the natural frequency of the spring-supported additional mass essentially corresponds to the frequency of the striking mechanism. The natural frequency of the additional mass is determined by the size of the additional mass and by the spring constant of the spring supporting it. At the same natural frequency of the additional mass with the frequency of the striking mechanism, the additional mass oscillates essentially in phase with the housing. This partly compensates for the shock excitation exerted on the housing.

Die durch das Schlagwerk erzeugte, auf das Gehäuse wirkende Stosserregung kann durch die Zusatzmasse nur teilweise kompensiert werden. Zum Abbau der vom Gehäuse auf den Handgriff übertragenen Restwirkung, ist es zweckmässig, dass die Eigenfrequenz des Handgriffes um den Faktor /2 kleiner als die Frequenz des Schlagwerkes ist. Durch diese Auslegung werden die Schwingungen im Bereich der Schlagfrequenz und darüber gedämpft auf den Handgriff übertragen. Die Eigenfrequenz des Handgriffs wird ebenfalls durch dessen Masse sowie durch die Federkonstante der den Handgriff abstützenden Federn bestimmt.The shock excitation generated by the striking mechanism and acting on the housing can only be partially compensated for by the additional mass. To reduce the residual effect transferred from the housing to the handle, it is advisable that the natural frequency of the handle is smaller by a factor of / 2 than the frequency of the striking mechanism. With this design, the vibrations in the area of the stroke frequency and above are dampened and transferred to the handle. The natural frequency of the handle is also determined by its mass and by the spring constant of the springs supporting the handle.

Die Erfindung soll nachstehend anhand der sie bspw wiedergebenden Zeichnungen näher erläutert werden. Es zeigen:

  • Fig. 1 Einen erfindungsgemässen Bohrhammer, teilweise im Schnitt dargestellt,
  • Fig. 2 eine Draufsicht auf den Bohrhammer gemäss Fig. 1 entsprechend dem Pfeil A, mit geschnittenem Absorbergehäuse.
The invention will be explained in more detail below with reference to the drawings, for example. Show it:
  • 1 A hammer drill according to the invention, shown partly in section,
  • Fig. 2 is a plan view of the hammer drill according to FIG. 1 according to arrow A, with a cut absorber housing.

Der aus Fig. 1 ersichtliche Bohrhammer weist ein insgesamt mit 1 bezeichnetes Gehäuse auf. Das Gehäuse 1 besteht aus einem Motorteil la und einem Schlagwerksteil 1b. Aus dem Schlagwerksteil 1b ragt eine Spindel 2, welche ein Spannfutter 3 für ein Werkzeug 4 trägt. An dem dem Spannfutter 3 entgegengesetzten Ende des Gehäuses 1 ist ein insgesamt mit 5 bezeichneter Handgriff angeordnet. Eine Zuleitung 6 für die . elektrische Stromversorgung mündet in den Handgriff 5. Der Handgriff 5 trägt ferner einen Schalter 7 zum Ein- und Ausschalten des Bohrhammers. Der Handgriff 5 ist gegenüber dem Gehäuse 1 in Schlagrichtung, dh in Achsrichtung der Spindel 2, verschiebbar. Die Führung des Handgriffs 5 erfolgt über Zapfen 1c und entsprechende Bohrungen 5a des Handgriffes 5. Der Handgriff 5 wird durch Druckfedern 8 vom Gehäuse 1 weggedrückt. Eine mit dem Zapfen 1c verbundene Schraube 9 dient dabei als Anschlag. Der sich zwischen dem Handgriff 5 und dem Gehäuse 1 ergebende Spalt, der je nach Einfederungsgrad des Handgriffs grösser oder kleiner ist, wird durch einen Faltenbalg 10 ringsherum gegen das Eindringen von Verschmutzungen in das Innere der Maschine abgedichtet. Der Faltenbalg 10 ermöglicht die Relativbewegung zwischen dem Handgriff 5 und dem Gehäuse 1. Am Gehäuse 1 ist ferner ein insgesamt mit 11 bezeichnetes Absorbergehäuse angeordnet.The drill hammer shown in FIG. 1 has a housing designated overall by 1. The housing 1 consists of a motor part la and a striking mechanism part 1b. A spindle 2 protrudes from the striking mechanism part 1b and carries a chuck 3 for a tool 4. On the chuck 3 opposite end of the housing 1, a handle designated 5 overall 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 drill on and off. The handle 5 can be moved relative to the housing 1 in the direction of impact, ie in the axial direction of the spindle 2. The handle 5 is guided by means of pins 1c 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 1c 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. On the housing 1 there is also an absorber housing, generally designated 11.

Fig. 2 zeigt wiederum das Gehäuse 1 mit dem am rückwärtigen Ende des Gehäuses 1 angeordneten Handgriff 5 und dem den Spalt zwischen dem Handgriff 5 und dem Gehäuse 1 abdichtenden Faltenbalg 10. Am entgegengesetzten Ende des Gehäuses 1 ist das auf der Spindel 2 angeordnete Futter 3 für das Werkzeug 4 ersichtlich. Das Absorbergehäuse 11 ist mit dem Gehäuse 1 verbunden und weist zwei parallel zur Schlagrichtungsachse verlaufende Führungszylinder lla auf. In den Führungszylindern 11a sind Massenkörper 12 angeordnet. Die Massenkörper 12 sind als Kolben ausgebildet und werden in den Führungszylindern 11a geführt. Die Massenkörper 12 weisen einen mit einem Federgewinde 12a versehenen Bereich auf. Eine Feder 13 ist auf das Federgewinde 12a aufgeschraubt und somit mit dem Massenkörper 12 verbunden. Das andere Ende der Feder 13 ist mit einem insgesamt mit 14 bezeichneten Widerlager verbunden. Das Widerlager 14 weist ebenfalls ein der Feder 13 angepasstes Federgewinde 14a auf. Der Massenkörper 12 ist somit über die Feder 13 mit dem Widerlager 14 verbunden. Das Widerlager 14 dient zusätzlich zum einseitigen Verschliessen des Führungszylinders 11a. Das andere Ende des Führungszylinders 11a wird durch einen Stopfen 15 verschlossen.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 two guide cylinders 11a running parallel to the axis of impact direction. Mass bodies 12 are arranged in the guide cylinders 11a. The mass bodies 12 are designed as pistons and are guided in the guide cylinders 11a. 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 for one-sided closing of the guide cylinder 11a. The other end of the guide cylinder 11a is closed by a plug 15.

Die Massenkörper 12 und die Feder 13 bilden ein System, welches parallel zur Schlagrichtungsachse verlaufende Schwingungen ausführen kann. Durch die als Kolben wirkenden Massenkörper 12 werden die Führungszylinder 11a in zwei Räume unterteilt. Der eine Raum, in dem auch die Feder 13 angeordnet ist, befindet sich zwischen dem Massenkörper 12 und dem Widerlager 14. Der andere Raum befindet sich zwischen dem Massenkörper 12 und dem Stopfen 15. Die vor und hinter den Massenkörpern 12 liegenden Räume sind durch Druckausgleichsleitungen 11b, llc wechselseitig miteinander verbunden. Durch diese Massnahme wird eine Koppelung der beiden Massenkörper 12 erreicht.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 bodies 12 acting as pistons, the guide cylinders 11a 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 11b, llc mutually connected. A coupling of the two mass bodies 12 is achieved by this measure.

Beim Vorlaufen eines Massenkörpers 12 entsteht auf der einen Seite ein Ueberdruck und auf der anderen Seite ein Unterdruck. Durch die Druckausgleichsleitungen llb, 11c werden diese Druckunterschiede wechselseitig ausgeglichen. Bewegt sich der eine Massenkörper 12 schneller als der andere, so entsteht ein Ueberdruck, der, auf die Rückseite des anderen Massenkörpers 12 geleitet, eine Beschleunigung des sich langsamer bewegenden Massenkörpers 12 bewirkt. Umgekehrt wird der sich schneller bewegende Massenkörper 12 vom sich langsamer bewegenden Massenkörper 12 gebremst. Somit wird erreicht, dass sich beide Massenkörper 12 praktisch gleich bewegen. Durch Füllen der Führungszylinder lla und der Druckausgleichsleitungen 11b, 11c mit einer Flüssigkeit anstelle von Luft kann dabei das Verhalten der beiden Massenkörper 12 innerhalb bestimmter Grenzen verändert werden. Durch die Strömung erfolgt eine Dämpfung der Schwingungen der beiden Massenkörper 12.When a mass body 12 runs forward, an overpressure arises on one side and a negative pressure on the other side. These pressure differences are mutually compensated for by the pressure compensation lines 11b, 11c. If one mass body 12 moves faster than the other, an overpressure is created which, when directed to the rear of the other mass body 12, causes acceleration of the slower moving mass body 12. Conversely, the faster moving mass body 12 is braked by the slower moving mass body 12. It is thus achieved that both mass bodies 12 move practically the same. By filling the guide cylinder 11a and the pressure compensation lines 11b, 11c with a liquid instead of air, the behavior of the two mass bodies 12 can be changed within certain limits. The flow dampens the vibrations of the two mass bodies 12.

Die beiden Massenkörper 12 sind so dimensioniert, dass ihre Masse etwa 10 % des Gehäuses mit dem darin angeordneten Antrieb und Schlagwerk ausmacht. Die Eigenfrequenz der Massenkörper 12 entspricht im wesentlichen der Frequenz des Schlagwerkes. Die Federung des Handgriffs 5 ist so abgestimmt, dass die Eigenfrequenz des Handgriffs 5 etwa um den Faktor

Figure imgb0001
kleiner ist als die Frequenz des Schlagwerkes. Bspw bei einer Frequenz des Schlagwerkes von 45 Hz beträgt die Eigenfrequenz des Handgriffs etwa 35 Hz. Eine solche Abstimmung ergibt eine optimale Reduktion der durch das Schlagwerk erzeugten Vibrationen.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 Percussion. The suspension of the handle 5 is tuned so that the natural frequency of the handle 5 is about a factor
Figure imgb0001
 is less than the frequency of the striking mechanism. For example, 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.

Claims (6)

1. Bohr- oder Meisselhammer mit einem Schlagwerk, einem dieses umgebenden Gehäuse und einem mit dem Gehäuse verbundenen Handgriff, gekennzeichnet durch eine Kombination der nachstehenden Merkmale: a) Der Handgriff (5) ist in Schlagrichtung am Gehäuse (1) federnd abgestützt, b) eine Zusatzmasse ist in der Schlagrichtungsachse am Gehäuse (1) federnd abgestützt. 1. Hammer drill or chisel hammer with a striking mechanism, a housing surrounding it and a handle connected to the housing, characterized by a combination of the following features: a) The handle (5) is spring-loaded on the housing (1), b) an additional mass is resiliently supported in the direction of impact on the housing (1). 2. Hammer nach Anspruch 1, dadurch gekennzeichnet, dass die Masse des Gehäuses (1) das 8- bis 12-fache der Zusatzmasse beträgt.2. Hammer according to claim 1, characterized in that the mass of the housing (1) is 8 to 12 times the additional mass. 3. Hammer nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Zusatzmasse aus mehreren einzeln federnd abgestützten Massenkörpern (12) besteht.3. Hammer according to claim 1 or 2, characterized in that the additional mass consists of several individually resiliently supported mass bodies (12). 4. Hammer nach Anspruch 3, dadurch gekennzeichnet, dass die einzelnen Massenkörper (12) als in Führungszylindern (lla) gelagerte Kolben ausgebildet sind und die Enden der Führungszylinder (lla) über Druckausgleichsleitungen (llb, llc) wechselseitig miteinander verbunden sind.4. Hammer according to claim 3, characterized in that the individual mass bodies (12) are designed as pistons mounted in guide cylinders (lla) and the ends of the guide cylinders (lla) are mutually connected via pressure compensation lines (llb, llc). 5. Hammer nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Eigenfrequenz der federnd abgestützten Zusatzmasse im wesentlichen der Frequenz des Schlagwerkes entspricht.5. Hammer according to one of claims 1 to 4, characterized in that the natural frequency of the resiliently supported additional mass corresponds essentially to the frequency of the striking mechanism. 6. Hammer nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die Eigenfrequenz des Handgriffs (5) um den Faktor /2 kleiner als die Frequenz des Schlagwerkes ist.6. Hammer according to one of claims 1 to 5, characterized in that the natural frequency of the handle (5) is smaller by a factor / 2 than the frequency of the striking mechanism.
EP82104567A 1981-06-10 1982-05-25 Boring or chiseling hammer Expired EP0066779B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82104567T ATE12198T1 (en) 1981-06-10 1982-05-25 HAMMER DRILL OR CHISEL.

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DE19813122979 DE3122979A1 (en) 1981-06-10 1981-06-10 DRILLING OR CHISEL HAMMER
DE3122979 1981-06-10

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EP0066779A1 true EP0066779A1 (en) 1982-12-15
EP0066779B1 EP0066779B1 (en) 1985-03-20

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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
DE2403074A1 (en) * 1974-01-23 1975-07-24 Rheinmetall Gmbh IMPACT TOOL, IN PARTICULAR PNEUMATIC IMPACT TOOL

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0165341A1 (en) * 1984-03-23 1985-12-27 Metabowerke GmbH & Co. Single space damper and its use in a hand tool
CH669142A5 (en) * 1986-04-04 1989-02-28 Sig Schweiz Industrieges Air driven impact hammer
EP0370952A1 (en) * 1988-11-19 1990-05-30 HILTI Aktiengesellschaft Portable hand tool with a percussive device
EP0680399A1 (en) * 1993-01-27 1995-11-08 Lord Corporation Vibration isolator for hand-held vibrating devices
EP0680399A4 (en) * 1993-01-27 1996-01-10 Lord Corp Vibration isolator for hand-held vibrating devices.
US5839517A (en) * 1993-01-27 1998-11-24 Lord Corporation Vibration isolator for hand-held vibrating devices
WO1998029220A1 (en) * 1997-01-02 1998-07-09 Wacker-Werke Gmbh & Co. Kg Percussion drill and/or jack hammer with handle spring-buffered against the hammer housing
US6148930A (en) * 1997-01-02 2000-11-21 Wacker-Werke Gmbh & Co. Kg Percussion drill and/or jack hammer with handle spring-buffered against the hammer housing
EP1464449A3 (en) * 2003-04-01 2007-03-07 Makita Corporation Power tool
CN1946520B (en) * 2004-08-27 2012-11-14 株式会社牧田 Working tool
CN102837297A (en) * 2004-08-27 2012-12-26 株式会社牧田 Working tool
EP2000264A2 (en) * 2004-08-27 2008-12-10 Makita Corporation Power tool with dynamic vibration reducer
EP1767315B1 (en) * 2004-08-27 2008-12-17 Makita Corporation Power tool with dynamic vibration reducer
EP2000264A3 (en) * 2004-08-27 2008-12-17 Makita Corporation Power tool with dynamic vibration reducer
CN102837297B (en) * 2004-08-27 2015-10-21 株式会社牧田 Power tool
EP2808129A1 (en) * 2004-08-27 2014-12-03 Makita Corporation Power tool
US8561716B2 (en) 2004-08-27 2013-10-22 Makita Corporation Power tool
EP1767315A1 (en) * 2004-08-27 2007-03-28 Makita Corporation Working tool
US7921934B2 (en) 2004-08-27 2011-04-12 Makita Corporation Power tool
US8127862B2 (en) 2004-08-27 2012-03-06 Makita Corporation Power tool
US8235138B2 (en) 2004-08-27 2012-08-07 Makita Corporation Power tool
EP1832394A1 (en) * 2006-03-07 2007-09-12 Hitachi Koki Co., Ltd. Impact tool with vibration control mechanism
US7513317B2 (en) 2006-03-07 2009-04-07 Hitachi Koki Co., Ltd. Impact tool with vibration control mechanism
CN101535005B (en) * 2006-11-03 2011-01-26 罗伯特·博世有限公司 Hand-held machine tool with a vibration-damped handle provided with a switch
GB2451293A (en) * 2007-07-27 2009-01-28 Black & Decker Inc Hammer drill with slidably mounted handle
EP2127821A1 (en) * 2008-05-27 2009-12-02 AEG Electric Tools GmbH Electric tool with vibration dampener
EP2457694A3 (en) * 2010-11-26 2018-03-14 HILTI Aktiengesellschaft Power tool
EP3022019A4 (en) * 2013-07-15 2017-03-08 Milwaukee Electric Tool Corporation Rotary hammer
EP3022019B1 (en) 2013-07-15 2022-04-20 Milwaukee Electric Tool Corporation Rotary hammer

Also Published As

Publication number Publication date
MX158199A (en) 1989-01-16
NO821908L (en) 1982-12-13
ES512958A0 (en) 1983-03-16
NO153955C (en) 1986-06-25
NO153955B (en) 1986-03-17
AU8440282A (en) 1982-12-16
JPS57211482A (en) 1982-12-25
HU183955B (en) 1984-06-28
YU110182A (en) 1986-06-30
US4478293A (en) 1984-10-23
SU1178317A3 (en) 1985-09-07
FI821478A0 (en) 1982-04-28
CA1180578A (en) 1985-01-08
ES8305085A1 (en) 1983-03-16
ATE12198T1 (en) 1985-04-15
JPS6363358B2 (en) 1988-12-07
DE3122979A1 (en) 1983-01-05
EP0066779B1 (en) 1985-03-20
FI75294C (en) 1988-06-09
DE3122979C2 (en) 1989-10-05
FI75294B (en) 1988-02-29

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