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EP0066779B1 - Boring or chiseling hammer - Google Patents

Boring or chiseling hammer Download PDF

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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)
French (fr)
Other versions
EP0066779A1 (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, 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Golf Clubs (AREA)
  • Earth Drilling (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
  • Drilling Tools (AREA)
  • Processing Of Stones Or Stones Resemblance Materials (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, mit einem das Schlagwerk umgebenden Gehäuse und mit einem in Schlagrichtung am Gehäuse federnd abgestütztem Handgriff.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.

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, die das Gehäuse zu Schwingungen bzw. Vibrationen anregen. Diese Vibrationen werden über den Handgriff auf die Hand bzw. den Arm der Bedienungsperson übertragen. Die dabei auftretenden Beanspruchungen sind nicht nur unangenehm, sondern können auf die Dauer auch zu gesundheitlichen Schäden 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 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.

Zur Verringerung der auftretenden Beanspruchungen sind in der Vergangenheit bereits verschiedene Massnahmen ergriffen worden. So ist es aus der DE-A-2 204 160 bekannt, den Handgriff auf dem Gehäuse federnd abzustützen. Damit diese Massnahme wirksam wird, muss jedoch der Handgriff relativ weich gefedert werden. Eine solche weiche Federung ergibt jedoch sehr lange Federwege. Dies ist wiederum aus handhabungstechnischen Gründen nachteilig.Various measures have already been taken in the past to reduce the stresses that occur. It is known from DE-A-2 204 160 to resiliently support the handle on the housing. In order for this measure to be effective, however, the handle must be relatively softly sprung. However, such a soft suspension results in very long spring travel. Again, this is disadvantageous for handling reasons.

Weiterhin ist es aus der FR-A-2 237 734 bekannt, eine Zusatzmasse in Schlagrichtung am Gehäuse federnd abzustützen. Eine solche Zusatzmasse führt zu einer gewissen Verbesserung der oben erörterten Schwingungsverhältnisse. Bei Bohr- oder Meisselhämmern der oberen Leistungsklasse sind jedoch die auf die Bedienungsperson einwirkenden Schwingungen immer noch zu stark. Eine geringe Verbesserung wäre theoretisch durch Vergrösserung der Zusatzmasse möglich. Dabei erhöht sich jedoch zwangsläufig das Gesamtgewicht des Hammers, wodurch sich ebenfalls eine verstärkte Belastung der Bedienungsperson ergibt.Furthermore, it is known from FR-A-2 237 734 to resiliently support an additional mass in the direction of impact on the housing. Such an additional mass leads to a certain improvement in the vibration conditions discussed above. In the case of high-performance rotary or chisel hammers, however, the vibrations acting on the operator are still too strong. A small improvement would theoretically be possible by increasing the additional mass. However, the total weight of the hammer inevitably increases, which also results in an increased load on the operator.

Der Erfindung liegt deshalb die Aufgabe zugrunde, einen Bohr- oder Meisselhammer der angegebenen Gattung zu schaffen, der bei Aufrechterhaltung des angestrebten, geringen Gesamtgewichtes eine ausreichende Dämpfung der von dem Hammer auf die Bedienungsperson übertragenen Schwingungen aufweist.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.

Diese Aufgabe wird erfindungsgemäss dadurch gelöst, dass mehrere, in Schlagrichtung am Gehäuse einzeln federnd abgestützte Kolben in Führungszylindern gelagert sind, und dass die Enden der Führungszylinder über Druckausgleichsleitungen wechselseitig miteinander verbunden sind.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.

Zweckmässige Ausführungsformen sind in den Unteransprüchen zusammengestellt.Appropriate embodiments are compiled in the subclaims.

Die mit der Erfindung erzielten Vorteile beruhen auf folgenden Zusammenhängen: Das Zusammenwirken zwischen dem in Schlagrichtung am Gehäuse federnd abgestützten Handgriff einerseits und einer in Schlagrichtung am Gehäuse abgestützten Zusatzmasse andererseits führt zu einer relevanten Verringerung der auf die Bedienungsperson übertragenen Schwingungen. Diese Zusatzmasse übt jedoch Kippmomente auf das Gehäuse aus, die sich nur dann vermeiden lassen, wenn die Zusatzmasse exakt auf der Achse der Schlagübertragung auf das Werkzeug angeordnet wird. Da dies aus baulichen Gründen meist nicht möglich ist, muss die Zusatzmasse aussermittig am Gehäuse angeordnet werden. Dadurch entstehen jedoch wiederum aussermittig angreifende Kräfte, die ein Kippen des Gehäuses verursachen können. Um auch diese Kräfte aufzufangen, wird die Zusatzmasse durch mehrere, einzeln federnd abgestützte Kolben gebildet, die vorzugsweise symmetrisch am Gehäuse angeordnet sind. Die Verteilung der Zusatzmasse auf mehrere Kolben führt dazu, dass die einzelnen Kolben kleiner ausgebildet werden können und durch die Verteilung auf das Gehäuse weniger störend wirken als eine einzige, entsprechend grösser ausgebildete Zusatzmasse. Aus Kostengründen werden vorzugsweise zwei Kolben vorgesehen.The advantages achieved with the invention are based on the following relationships: The interaction between the handle, which is resiliently supported on the housing in the direction of impact, and an additional mass which is supported on the housing in the direction of impact, leads to a relevant reduction in the vibrations transmitted to the operator. However, 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. In order to absorb these forces as well, 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.

Bei mehr als zwei Kolben besteht die Möglichkeit, dass sich diese ungleich bewegen. So können beispielsweise zwischen den Schwingungen der einzelnen Kolben geringe Phasenverschiebungen auftreten. Diese Unterschiede verringern wiederum die oben erläuterte Wirkung der Zusatzmasse beim Betrieb des Hammers wesentlich. Um die gleichmässige, synchrone Bewegung der einzelnen Kolben zu erreichen, könnten diese beispielsweise mechanisch miteinander verbunden werden. Eine solche Lösung scheidet jedoch aus Platz- und Wirtschaftlichkeitsgründen aus.If there are more than two pistons, there is the possibility that they move unevenly. For example, small phase shifts can occur between the vibrations of the individual pistons. These differences in turn significantly reduce the above-described effect of the additional mass when operating the hammer. In order to achieve the uniform, synchronous movement of the individual pistons, 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 Kolben eine gleichmässige, synchrone Bewegung zu erreichen, werden die einzelnen Kolben in Führungszylindern gelagert, deren Enden über Druckausgleichsleitungen wechselseitig miteinander verbunden sind. Die Koppelung der einzelnen Kolben untereinander erfolgt also über ein Medium, das von einem Führungszylinder zu einem anderen strömen kann. Dabei kann es sich um ein flüssiges oder gasförmiges Medium handeln.In order to achieve a uniform, synchronous movement with several pistons, 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.

Bei der Bewegung eines Kolbens in einem Führungszylinder entsteht auf der einen Seite ein Über-und auf der andere Seite ein Unterdruck. Durch das wechselseitige Verbinden der Enden der Führungszylinder ergibt sich also ein automatischer 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 Kolben erfolgen also synchron.When a piston moves in a guide cylinder, an overpressure is created on one side and a vacuum on the other side. The reciprocal connection of the ends of the guide cylinders results in an automatic pressure compensation. 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 pistons are therefore synchronous.

Um eine spürbare Wirkung zu erreichen, müssen die Kolben eine gewisse Mindestgrösse haben. Da andererseits das Gesamtgewicht des Hammers durch diese Zusatzmasse direkt beeinflusst wird und das Gesamtgewicht des Hammers aus Handhabungsgründen 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 acht bis zwölffache der Zusatzmasse, also der Gesamtmasse der einzelnen Kolben, beträgt. Der bevorzugte Anteil der Zusatzmasse am Gesamtgewicht des Hammers liegt damit in der Grössenordnung von etwa 10%. Dies ist im Hinblick auf die damit erreichbare Verbesserung des Bedienungskomforts durchaus tragbar. Bei Verwendung grösserer Zusatzmasse werden die Hämmer zu schwer und lassen sich nur noch mit grösseren Schwierigkeiten handhaben.In order to achieve a noticeable effect, the pistons must have a certain minimum size. On the other hand, 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.

Um die optimale Dämpfung der Schwingungen zu erreichen, sollte die Eigenfrequenz der federnd abgestützten Kolben im wesentlichen der Frequenz des Schlagwerkes entsprechen. Die Eigenfrequenz der Kolben wird durch ihre Grösse sowie durch die Federkonstante der sie abstützenden Feder bestimmt. Bei Übereinstimmung der Eigenfrequenz der Kolben mit der Frequenz des Schlagwerkes schwingen die Kolben im wesentlichen gleichbleibend phasenverschoben zum Gehäuse. Dadurch wird die auf das Gehäuse ausgeübte Stosserregung zumindest zum Teil kompensiert.In order to achieve the optimal damping of the vibrations, 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.

Die durch das Schlagwerk erzeugte, auf das Gehäuse wirkende Stosserregung kann durch die Kolben nur teilweise kompensiert werden. Zum Abbau der vom Gehäuse auf den Handgriff übertragenen Restkräfte ist es zweckmässig, wenn die Eigenfrequenz des Handgriffes um den Faktor V2 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 Handgriffes wird ebenfalls durch dessen Masse sowie durch die Federkonstante der den Handgriff abstützenden Federn bestimmt.The impact excitation generated by the striking mechanism and acting on the housing can only be partially compensated for by the pistons. To reduce the residual forces transmitted from the housing to the handle, it is expedient if 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.

Die Erfindung wird im Folgenden anhand von Ausführungsbeispielen unter Bezugnahme auf die beiliegenden, schematischen Zeichnungen näher erläutert. Es zeigen:

  • Fig. 1) einen Bohrhammer, teilweise im Schnitt, und
  • Fig. 2) eine Draufsicht auf den Bohrhammer nach Figur 1 entsprechend dem Pfeil A mit geschnittenem Absorbergehäuse.
The invention is explained in more detail below on the basis of exemplary embodiments with reference to the accompanying schematic drawings. Show it:
  • Fig. 1) a hammer drill, partly in section, and
  • Fig. 2) is a plan view of the hammer drill according to Figure 1 according to arrow A with a cut absorber housing.

Der aus Figur 1 ersichtliche Bohrhammer weist ein insgesamt durch das Bezugszeichen 1 angedeutetes Gehäuse aus. Dieses Gehäuse 1 besteht aus einem Motorteil 1 a und einem Schlagwerksteil 1 b. Aus dem Schlagwerksteil 1 b ragt eine Spindel 2 heraus, die 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, d.h. in Achsrichtung der Spindel 2, verschiebbar. Die Führung des Handgriffs 5 erfolgt über Zapfen 1 c und entsprechende Bohrungen 5a des Handgriffes 5. Der Handgriff 5 wird durch Druckfedern 8 vom Gehäuse 1 weggedrückt. Eine mit dem Zapfen 1 c 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 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 spindle 2, which carries a chuck 3 for a tool 4, protrudes from the striking mechanism part 1b. 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. 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 angeordneten Futter 3 für das Werkzeug 4 ersichtlich. Das Absorbergehäuse 11 ist mit dem Gehäuse 1 verbunden und weist parallel zur Schlagrichtungsachse verlaufende Führungszylinder 11 a auf. In den Führungszylindern 11 a sind Massenkörper 12 angeordnet. Die Massenkörper 12 sind als Kolben ausgebildet und werden in den Führungszylindern 11 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 11 a. Das andere Ende des Führungszylinders 11 a wird durch einen Stopfen 15 verschlossen.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.

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 11 a 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 11 b, 11 c 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 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.

Beim Vorlaufen eines Massenkörpers 12 entsteht auf der einen Seite ein Überdruck und auf der anderen Seite ein Unterdruck. Durch die Druckausgleichsleitungen 11 b, 11 c werden diese Druckunterschiede wechselseitig ausgeglichen. Bewegt sich der eine Massenkörper 12 schneller als der andere, so entsteht ein Überdruck, 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 11 a und der Druckausgleichsleitungen 11 b, 11 c 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 arises which, when directed to the rear of the other mass body 12, causes the slower moving mass body 12 to accelerate. 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 11 a and the pressure compensation lines 11 b, 11 c 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 striking mechanism. 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. 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.

Claims (4)

1. A hammer drill or chisel
a) having a percussion mechanism
b) having a housing (1) surrounding the percussion mechanism, and
c) having a handle (5) resiliently supported on the housing (1) in the percussion direction, characterised in that
d) a plurality of pistons (12), which are resiliently supported individually on the housing (1) in the percussion direction, are mounted in guide cylinders (11 a), and that
e) the ends of the guide cylinders (12a) are connected to one another at opposite sides via pressure- equalizing conduits (11 b, 11 c).
2. A hammer drill or chisel as claimed in claim 1, characterised in that
f) the mass of the housing (1) amounts to eight to twelve times the mass of the pistons (12).
3. A hammer drill or chisel as claimed in one of the claims 1 or 2, characterised in that
g) the characteristic frequency of the resiliently supported pistons (12) substantially corresponds to the frequency of the percussion mechanism.
4. A hammer drill or chisel as claimed in one of the claims 1 to 3, characterised in that
h) the characteristic frequency of the handle (5) is lower, by the factor
Figure imgb0003
, than the frequency of the percussion 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.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3122979 1981-06-10
DE19813122979 DE3122979A1 (en) 1981-06-10 1981-06-10 DRILLING OR CHISEL HAMMER

Publications (2)

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

Family

ID=6134346

Family Applications (1)

Application Number Title Priority Date Filing Date
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US (1) US4478293A (en)
EP (1) EP0066779B1 (en)
JP (1) JPS57211482A (en)
AT (1) ATE12198T1 (en)
AU (1) AU8440282A (en)
CA (1) CA1180578A (en)
DE (1) DE3122979A1 (en)
ES (1) ES8305085A1 (en)
FI (1) FI75294C (en)
HU (1) HU183955B (en)
MX (1) MX158199A (en)
NO (1) NO153955C (en)
SU (1) SU1178317A3 (en)
YU (1) YU110182A (en)

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DE3122979A1 (en) 1983-01-05
NO153955B (en) 1986-03-17
ES512958A0 (en) 1983-03-16
AU8440282A (en) 1982-12-16
ES8305085A1 (en) 1983-03-16
YU110182A (en) 1986-06-30
FI75294B (en) 1988-02-29
JPS57211482A (en) 1982-12-25
MX158199A (en) 1989-01-16
SU1178317A3 (en) 1985-09-07
NO821908L (en) 1982-12-13
NO153955C (en) 1986-06-25
EP0066779A1 (en) 1982-12-15
HU183955B (en) 1984-06-28
US4478293A (en) 1984-10-23
ATE12198T1 (en) 1985-04-15
FI821478A0 (en) 1982-04-28
DE3122979C2 (en) 1989-10-05
FI75294C (en) 1988-06-09
CA1180578A (en) 1985-01-08
JPS6363358B2 (en) 1988-12-07

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