EP2504603A1 - Amortisseur de vibration commandé - Google Patents

Amortisseur de vibration commandé

Info

Publication number
EP2504603A1
EP2504603A1 EP10768900A EP10768900A EP2504603A1 EP 2504603 A1 EP2504603 A1 EP 2504603A1 EP 10768900 A EP10768900 A EP 10768900A EP 10768900 A EP10768900 A EP 10768900A EP 2504603 A1 EP2504603 A1 EP 2504603A1
Authority
EP
European Patent Office
Prior art keywords
mass
reduction system
housing
vibration
vibration reduction
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.)
Withdrawn
Application number
EP10768900A
Other languages
German (de)
English (en)
Inventor
Willy Braun
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2504603A1 publication Critical patent/EP2504603A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect

Definitions

  • the present invention relates to a vibration reduction system for an electric power tool, having a first mass, which is arranged on an elasticity, wherein the first mass is provided for reducing housing vibrations for a relative movement relative to a housing of the power tool, and
  • Vibration reduction system comprises a second mass.
  • the present invention further relates to a power tool having a vibration reduction system according to the invention.
  • FIG. 1 shows a typical housing vibration 100 resulting from vibrations of the housing of drill and percussion hammers 7 caused by a percussion unit 8 in which the club 81 is driven by an eccentric piston 12.
  • the vibration generating case vibration 100 is composed of a plurality of frequency components.
  • the main frequency is derived from the periodic acceleration of the racket 81.
  • Fig. 1 shows that the deflection caused by the periodic acceleration of the racket 81 still further frequency components from other sources of vibration, e.g. from the shock and recoil operations of the percussion chain and unbalanced mass forces of the drive, are superimposed. Because the housing oscillation 100 does not run substantially sinusoidally with the main frequency, but the sinusoidal curve with main frequency are superimposed on other frequency components.
  • a damper is a spring-mass system with a fixed resonant frequency that can achieve significant vibration reduction only in a small region near the resonant frequency.
  • the spring stiffness of a damper is preferably chosen so that the resulting Tilgereigenfrequenz is in the vicinity of the largest disturbing vibration frequency of the housing.
  • the disadvantage of this is that the vibration damping works effectively only in a relatively narrow frequency range, depending on the size and absorber damping and the ratio between absorber and device. Outside this effective range, it may even lead to an increase in the vibration amplitudes.
  • Document EP 1 415 768 A1 discloses a vibration damper for a power tool comprising at least one mass which is movable in at least one spatial direction.
  • the mass is arranged on a spring whose spring constant is matched to the vibrations of the tool in the spatial direction.
  • the main vibration frequency is the beat frequency of the impact frequency
  • the vibration absorbers are additionally driven by the eccentric drive or, as disclosed in EP 1 464 449 A1, by a pressure difference caused by the impact mechanism.
  • the previously known vibration absorbers have in common that their mass
  • the object of the invention is to provide a vibration reduction system whose effective range is increased, so that a housing vibration of a power tool with the vibration reduction system can be reduced more effectively, and which is built very compact, so that it can be integrated in the power tool to save space.
  • Another object of the invention is to provide a power tool with such a vibration reduction system.
  • the object is achieved with a vibration reduction system for an electric power tool, with a first mass, which is arranged on an elasticity, wherein the first mass is provided for reducing housing vibrations for a relative movement relative to a housing of the power tool, wherein the vibration reduction system second mass comprises, wherein the second mass is controllable in dependence on the relative movement of the first mass relative to the housing.
  • a housing oscillation can be compensated by generating counter-forces with the same amount and the same effective direction.
  • the second mass according to the invention in dependence on the relative movement of the first mass relative to the housing is controllable, the amount and / or the direction of the second mass are adjustable so that the sum of the generated by means of the first mass and the second mass counter forces the housing vibration better reduce or even substantially compensate.
  • the amplitude, frequency and / or phase position of the second mass is preferably different from the amplitude, frequency and / or phase position of the first mass. Therefore, the first mass performs a first counter vibration and the second mass therefore performs a second counter vibration, which are different from each other.
  • the effective range of the vibration reduction system according to the invention with the first and the second mass is therefore increased in relation to the effective range of a vibration reduction system with a single mass.
  • the housing oscillation can be approximated very precisely, so that the opposing forces generated by means of the first and second mass compensate the housing oscillation very well.
  • the second mass is therefore preferably provided for a relative movement relative to the housing and / or the first mass.
  • vibration reduction system which are particularly caused by other sources of vibration, such as shock or recoil a beating chain, by game between components, by non-linear elasticity only approximately harmonic reaction forces of the impact mechanism or unbalanced mass forces of the drive.
  • multifrequency means an oscillation which can be decomposed by Fourier analysis into a sinusoidal oscillation having a fundamental frequency and at least one harmonics, whereas a uniffrequent oscillation can be decomposed by Fourier analysis into a sinusoidal oscillation which oscillates at the fundamental frequency.
  • the elasticity preferably extends essentially in a main direction of action of a vibration source which decisively causes the housing oscillation.
  • a vibration source which decisively causes the housing oscillation is, for example, a striking mechanism assembly, for example a percussion hammer, the main direction of action then being the direction of impact of the percussion mechanism assembly.
  • the first mass performs a substantially linear movement, so that the first mass acts in a first direction of action.
  • the vibration reduction system in particular the first mass, a limiting means, with which the movement of the second mass, in particular its magnitude and / or its direction is limited.
  • a limiting means is preferably an edge or a backdrop.
  • this is preferably a border that defines an interior in which the second mass is arranged.
  • the second mass also performs a substantially linear movement, so that the second mass acts in a second effective direction.
  • the first direction of action is arranged at an angle to the second direction of action.
  • housing oscillations which act in different directions of action can also be compensated with a vibration reduction system according to the invention.
  • At least the first mass or the second mass acts in and counter to the main direction of action of the vibration source that decisively causes the housing oscillation.
  • at least the first mass or the second mass at least partially compensates for the relevant housing oscillation.
  • both the first and the second mass acts in or against the main direction of action.
  • the course of the countervibrations of the two masses is very well tuned to the course of the caused by the relevant vibration source housing vibration, so that it is very easy to compensate.
  • the vibration reduction system is very compact.
  • the vibration reduction system preferably includes a coupling member which cooperates with a negative feedback member of the second mass to convert the movement of the first mass into the substantially linear motion of the second mass.
  • the coupling component is preferably positively and / or non-positively coupled to the negative feedback component.
  • the coupling component is preferably a guide means, wherein the negative feedback component is also preferably a receiving means, or vice versa.
  • the receiving means is preferably formed as a groove, indentation, web or recess.
  • the guide means is designed as a cam, pin, bolt, bulge or web. The lists are neither conclusive for the receiving means nor for the guide means. But there are other coupling components and negative feedback components used in the
  • the guide means and / or the receiving means is preferably provided with a rotating means, for example a sleeve, a wheel or a rotatable bearing.
  • the second mass is positively driven.
  • the transmission of motion between the first mass and the second mass is unambiguous even at high reaction forces and high operating frequency.
  • no additional pressure means such as springs are needed.
  • no energy required for the pressing force or due to friction and additional wear effects, must be provided by the engine power.
  • the vibration reduction system comprises at least a first transmission component, which cooperates with the coupling component.
  • the first transmission component causes the relative movement of the first mass relative to the housing to be converted into a substantially linear movement of the second mass.
  • the coupling component is arranged on the first transmission component or interacts directly with the first transmission component, or in another preferred embodiment, one or more further transmission components are provided, which are connected to the first transmission component and the
  • Coupling cooperate, so that the first transmission member interacts indirectly with the coupling member.
  • the first transmission component is preferably mounted on the first mass, so that the vibration reduction system is very compact.
  • the other transmission components are also the other transmission components at least partially stored on the first mass to save space.
  • the first transmission component comprises a connecting means, and the housing a mating connecting means corresponding to the connecting means, which cooperate, so that the first gear member performs a movement corresponding to the relative movement between the first mass and the housing.
  • a connecting means and as a counter-connecting means a toothing and a counter-toothing are preferred because they ensure a secure transmission of movement and are simple and inexpensive to produce.
  • other connecting means which in particular ensure a positive and / or non-positive motion transmission, can be used, for example a connection by means of a cam or a groove.
  • the first transmission component is rotatably mounted on the first mass, so that the movement of the first transmission component corresponding to the relative movement between the first mass is a rotary movement about a transmission component axis.
  • transmission components can be used which make a complete revolution about their transmission component axis, or transmission components which execute a partial revolution about their transmission component axis can still be used.
  • the housing cyclically oscillates in and against a main direction of action due to a cyclical back and forth movement of a relevant vibration source, and the relative movement between the first mass and the housing vibration is a cyclically swinging in and against the main direction of movement.
  • the first transmission component and other transmission components and the Kopplungsbau- part and the negative feedback component the cyclic relative movement both in a harmonic and therefore unifrequente oscillation of the second mass, as well as in an inharmonous and therefore multifrequency oscillation of the second mass is changeable.
  • at least one transmission component, the coupling component and / or the negative feedback component has a contour, which is in particular curved.
  • contour in particular its slope, therefore allows both a multiple reciprocating swinging movement of the second mass as well as resting points of the movement. Furthermore, such a contour allows to accelerate the movement of the balancing mass and to perform thrusting operations with the second mass. Likewise, the contour allows a temporal extension of forward and backward movements of the second mass. Therefore, both phase-shifted housing vibrations as well as acceleration and shock processes, which are caused for example by a striking mechanism, can be compensated very well.
  • the control means allows dynamic adjustment of the movement of the second mass even during operation to the current operating state of the power tool, in which the
  • control means also allows control of the second mass independently of the operating point of the power tool.
  • the control means is preferably electrically controllable, in particular as a function of operational variables, or independent of operational variables.
  • Operating variables are, for example, the housing oscillation, the rotational speed and / or the angle of rotation of the drive motor of the power tool, variables of the machine which can be set by an operator or others.
  • Mass in particular their frequency, to be considered as a variable relevant to operation, in particular to avoid an increase in the oscillation amplitudes, when the effective frequency range of the first mass is exceeded.
  • the person skilled in the art understands that, in order to take account of variables relevant to operation, it is necessary to record the operationally relevant variables, for example by means of a sensor.
  • the control or, in particular, adaptive control of the control means is possible after acquisition of the operationally relevant variable and its evaluation, for example by means of a microprocessor-based unit. But it can also be used as an electrical circuit, in particular integrated Circuit, for example, be designed as ASIC (Application Specific Integrated Circuit).
  • ASIC Application Specific Integrated Circuit
  • control means is a pin which is provided to engage in one or more indentations of the second mass.
  • control means makes it possible to stop the movement of the second mass.
  • the second mass is coupled in such a rest phase to the first mass, so that it performs a relative movement relative to the housing together with the first mass.
  • the object is further achieved with a power tool having a vibration reduction system according to the invention.
  • the vibration reduction system enables a very effective reduction of the housing vibration of the power tool.
  • the elasticity is mounted on the housing of the power tool.
  • a single first component mounted on the first mass makes it possible to detect the relative movement of the first mass relative to the housing.
  • FIG. 3 schematically shows an embodiment of a vibration reduction system according to the invention, shows a section of the vibration reduction system of FIG. 3, and
  • FIG Fig. 5 shows schematically a further embodiment of a vibration reduction system according to the invention.
  • FIG. 1 shows a housing oscillation 100 of a power tool 1. Furthermore, FIG. 1 shows two sinusoidal examples
  • Vibrations 103, 104 from whose superposition the housing oscillation 100 results.
  • the first of the two sinusoidal oscillations 103 is performed by a first mass 51 and the second of the two sinusoidal oscillations 104 is performed by a second mass 52 of a vibration reduction system 2 according to the invention.
  • the housing oscillation 100 can be compensated.
  • FIG. 2 shows schematically a power tool 1 with a vibration reduction system 2 according to the invention.
  • a hammer drill As a power tool 1, a hammer drill is shown here by way of example, which comprises a striking mechanism assembly 3.
  • a percussion unit 3 is a vibration source that determines the housing vibration 100 significantly.
  • the term rotary hammer is used synonymously for the power tool 1.
  • a racket 121 is provided which is linearly driven via a connecting rod 12 which is eccentrically mounted by means of an eccentric pin 1 1 on an eccentric disc 10 which rotates about an eccentric axis 9.
  • the eccentric 10 is driven by means of a likewise rotatable about the eccentric axis 9 gear 23 which is in engagement with a drive pinion 22 which is rotatably mounted on a drive shaft 21 of a drive motor 20 of the power tool 1.
  • the present invention is not limited to power tools 1 with striking mechanism assembly 3, but also for other power tools 1 used, for example, on drills, jigsaws or the like, which include another or not the housing vibration 100 significantly causing vibration source.
  • the hammer drill 1 has a cover assembly 14, in which an inventive vibration reduction system 2 is arranged.
  • the vibration reduction system 2 has the task of reducing or even compensating for vibrations of a housing 13 of the hammer drill 1.
  • the housing vibrations 100 are provided, for example, by the striking mechanism assembly 3, but also by other sources of vibration, e.g. from shock and recoil operations of a percussion chain or unbalanced mass forces a drive caused.
  • FIG. 3 schematically shows a first embodiment of a vibration reduction system 2 according to the invention.
  • the vibration reduction system 2 has a first mass 51, which is arranged on an elasticity 6, here on a spiral spring.
  • the elasticity 6 is mounted on the housing 13 of the power tool 1 and extends substantially along the direction of impact 4 of the percussion mechanism assembly 3 (see Fig. 2).
  • the first mass 51 is therefore excited to a first vibration 103, wherein the first mass 51 moves in or against the direction of impact 4 of the striking mechanism assembly 3 (see Fig. 2).
  • Due to the inertia of the first mass 51 the first oscillation 103 of the first mass 51 to the housing oscillation 100 is offset in time. There is therefore a relative movement between the first mass 51 and the housing 13.
  • a first transmission component 7 On the first mass 51, a first transmission component 7 is mounted, which has a connecting means 71, here a toothing.
  • connecting means 71 and toothing are used synonymously.
  • the first gear member 7 is arranged on the first mass 51, that the toothing 71 of the transmission means 7 with the counter teeth 131 of the housing 13 is engaged.
  • the first transmission component 7 is here formed from a first spur gear, which is rotatably mounted about a first rotation axis 151, which here extends transversely to the direction of impact 4 of the impact mechanism subassembly 3 (see FIG. In the context of the description of the figures for FIGS. 3 and 4, therefore, the terms first gear component 7 and first spur gear are used synonymously.
  • the second spur gear 16 is rotatably mounted about a second axis of rotation 152 which extends substantially parallel to the first axis of rotation 151.
  • a coupling member 162 is provided, here a pin which is arranged eccentrically rotatable about the second axis of rotation 152.
  • the terms coupling component 162 and pin are used synonymously.
  • FIG. 3 shows a second mass 52 of the vibration reduction system 2, which is arranged on the side of the first spur gear 7 and the second spur gear 16 facing away from the first mass 51.
  • a counter-coupling component 521 corresponding to the pin 162 of the second spur gear 16 a recess is provided in the second mass 52 into which the pin 162 engages. in the Therefore, the terms negative feedback component 521 and recess are used synonymously within the scope of the description of FIGS. 3 and 4.
  • the teeth 71 of the first spur gear 7 with the counter teeth 131 of the housing 13 is engaged, mesh the teeth 7 and the counter teeth 131 in a relative movement of the first mass 51 relative to the housing 13 with each other, so that the first spur gear 7 to the first Rotary shaft 151 rotates.
  • the toothing 71 of the first spur gear 7 is further in engagement with the second toothing 161 of the second spur gear 16, so that the toothing 71 and the second toothing 161 likewise mesh with each other upon rotation of the first spur gear 7.
  • the second spur gear 16 is rotated about the second rotation axis 152, so that the pin 162 rotates eccentrically about the second rotation axis 152.
  • the pin 162 is arranged in the recess 521 of the second mass 52 so that the second mass 52 is entrained upon rotation of the pin 162 about the second axis of rotation 152.
  • the second mass 52 reciprocates in the direction of impact 4 of the striking mechanism assembly 3 (see FIG.
  • the pin 162 therefore connects the first spur gear 7 to the second mass 52 so that the second mass 52 moves substantially linearly.
  • the second mass 52 therefore moves relative to the first mass 51 and / or the housing 13.
  • the coupling component 162 is designed as a cam or as a groove, being used as a negative feedback member 521, for example, a arranged on the second mass 52 pin to be guided along the cam, or to engage in the groove and in to be led this.
  • Both the first mass 51 and the second mass 52 extend substantially flat. This makes it possible for the first transmission component 7, as well as further transmission components 16, to be arranged in the region of the first mass 51 are.
  • the second mass 52 is preferably likewise arranged in the region of the first mass 51, specifically on the side of the transmission component or components 7, 16 facing away from the first mass 51.
  • the first and second masses 51, 52 extend essentially parallel to one another , The vibration reduction system 2 is therefore very flat to produce and very well adaptable to the installation conditions.
  • the movement of the first mass 51 is limited by the housing 13 of the power tool 1. Also preferably, the first mass 51 and / or the housing 13 of the power tool 1 limits the movement of the second
  • the first mass 51 has a limiting means 51 1, here a border 51 1, which delimits an inner space 512 (see FIG.
  • the second mass 52 and the transmission components 7, 16 are arranged in the interior of the first mass 52, so that the border 51 1 of the first mass 51 limits the movement of the second mass 52.
  • the movement sequence of the second mass 52 is dependent on the shape and number of the transmission components 7, 16, the shape of the coupling and / or counter-coupling components 162, 521 and / or their eccentricity.
  • the shape of at least one of the transmission components 7, 16, of the coupling component 162 and / or the counter-coupling component 521 has a contour, in particular a curved contour, so that the movement of the second mass 52 is harmonious or inharmonious. In the case of an inharmonic movement of the second mass 52, this includes, for example, accelerations and / or resting phases.
  • Fig. 5 shows schematically a further embodiment of a vibration reduction system 2 according to the invention.
  • the first mass 51 is by means of a first elasticity
  • the first and the second elasticity 61, 62 also extend essentially in the direction of impact 4 of the percussion unit 3 (see Fig. 2), so that the first mass 51 is provided to a vibration which extends in and against the direction of impact 4. Furthermore, here is the second mass 52 in one
  • vibration reduction system 2 also sees the pin as the coupling component 162 and the pin as the counter-coupling component 521
  • a further limiting means 153 in this case a bolt, which engages in a recess 522 of the second mass 52.
  • bolt is used synonymously for the further limiting means 153.
  • a limiting spring 63 is provided, which bears against the bolt 153 and prevents the second mass 52 from striking against the bolt 153.
  • an electrically controllable control means 17 is provided, here in the form of a pin. In the following, therefore, the term pin is used synonymously for the electrically controllable control means 17.
  • the pin 17 is provided for engaging in indentations of the second mass and makes it possible to stop the movement of the second mass 52 relative to the first mass 51. Furthermore, in this embodiment, it makes it possible to couple the second mass 52 to the first mass 51, so that both masses 52, 51 oscillate together. As a result, the amplitude, the frequency and / or the phase angle of the vibration reduction system 2 changes.
  • the pin 17 is electrically controllable by a magnetic button 171, on which the pin 17 is arranged, is moved by means of an electromagnet 172, so that the pin 17 of a engaging in one of the indentations 523 of the second mass 52 Position and in a not in one of the indentations 523 of the second mass 52 engaging position is movable back and forth.
  • an electromagnet 172 with button 171 is, for example, by means of a conventional relay and therefore very inexpensive and space-saving feasible.
  • the electromagnet 172 or the relay requires for this purpose a drive signal 173 that can be generated by a microprocessor-based control (not shown here) that is integrated in the power tool 1.
  • the movement of the first mass 51 and of the housing 13 is detected by means of detection (not shown here), and based on their relative movement to each other for the drive signal 173.
  • FIGS. 3, 4 and FIG. 5 can be combined, so that the control of the second mass 52 is possible both by means of a first transmission component 7 and by means of a control means 17.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

La présente invention concerne un système de réduction de vibration (2) pour un outil électrique (1), comprenant une première masse (51), qui est disposée sur une élasticité (6, 61, 62), la première masse (51) étant prévue pour la réduction de vibrations de boîtier (100) pour un déplacement relatif par rapport à un boîtier (13) de l'outil électrique (1), le système de réduction de vibration (2) comprenant une seconde masse (52) et la seconde masse (52) pouvant être entraînée en fonction du déplacement relatif de la première masse (51) par rapport au boîtier (13). La présente invention concerne également un outil électrique (1) doté d'un système de réduction de vibration (2) selon l'invention.
EP10768900A 2009-11-25 2010-10-07 Amortisseur de vibration commandé Withdrawn EP2504603A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009047111A DE102009047111A1 (de) 2009-11-25 2009-11-25 Gesteuerter Schwingungstilger
PCT/EP2010/064960 WO2011064031A1 (fr) 2009-11-25 2010-10-07 Amortisseur de vibration commandé

Publications (1)

Publication Number Publication Date
EP2504603A1 true EP2504603A1 (fr) 2012-10-03

Family

ID=43533192

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10768900A Withdrawn EP2504603A1 (fr) 2009-11-25 2010-10-07 Amortisseur de vibration commandé

Country Status (5)

Country Link
US (1) US20120286461A1 (fr)
EP (1) EP2504603A1 (fr)
CN (1) CN102667221A (fr)
DE (1) DE102009047111A1 (fr)
WO (1) WO2011064031A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104895979A (zh) * 2015-06-18 2015-09-09 无锡众扬金属制品有限公司 一种可调弹簧
CN115648129B (zh) * 2022-10-29 2024-06-21 江苏东成工具科技有限公司 冲击电动工具

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2603688C3 (de) * 1976-01-31 1978-10-26 Ibm Deutschland Gmbh, 7000 Stuttgart Anordnung zum Schwingungsausgleich
FR2749901B1 (fr) * 1996-06-12 2000-12-08 Eurocopter France Dispositif pour reduire les vibrations engendrees par un rotor de sustentation d'un aeronef a voilure tournante
EP1415768A1 (fr) 2002-10-31 2004-05-06 Atlas Copco Electric Tools GmbH Amortisseur d'oscillations
DE602004026134D1 (de) 2003-04-01 2010-05-06 Makita Corp Kraftwerkzeug
US7377529B2 (en) * 2004-11-30 2008-05-27 Trw Automotive U.S. Llc Active roll control system for a vehicle suspension system
JP2008094226A (ja) * 2006-10-11 2008-04-24 Kayaba Ind Co Ltd サスペンション装置

Non-Patent Citations (1)

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Title
See references of WO2011064031A1 *

Also Published As

Publication number Publication date
WO2011064031A1 (fr) 2011-06-03
CN102667221A (zh) 2012-09-12
DE102009047111A1 (de) 2011-05-26
US20120286461A1 (en) 2012-11-15

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