EP2496855A1 - Dispositif d'amortissement, machine-outil équipée d'un dispositif d'amortissement et procédé pour produire un dispositif d'amortissement - Google Patents

Dispositif d'amortissement, machine-outil équipée d'un dispositif d'amortissement et procédé pour produire un dispositif d'amortissement

Info

Publication number
EP2496855A1
EP2496855A1 EP10760963A EP10760963A EP2496855A1 EP 2496855 A1 EP2496855 A1 EP 2496855A1 EP 10760963 A EP10760963 A EP 10760963A EP 10760963 A EP10760963 A EP 10760963A EP 2496855 A1 EP2496855 A1 EP 2496855A1
Authority
EP
European Patent Office
Prior art keywords
spring
region
damping device
mass
damping
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Withdrawn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
EP10760963A
Other languages
German (de)
English (en)
Inventor
Gerd Schlesak
Gerhard Meixner
Christian Koepf
Patrick Heinen
Michael Weiss
Roger Hahn
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 EP2496855A1 publication Critical patent/EP2496855A1/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Withdrawn legal-status Critical Current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
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—Wound springs
    • 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
    • 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
    • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
    • F16F7/116—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on metal springs
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/275—Tools having at least two similar components
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/371—Use of springs

Definitions

  • Damping device machine tool with a damping device and method for producing a damping device
  • the invention relates to a damping device for damping vibrations and a method for producing a damping device according to the preamble of the independent claims.
  • At least one mass body so as to be movable and drivable by a drive device of the machine tool to a periodic movement in and / or on a housing of the machine tool that by the periodic movement of the mass body occurring inertia forces a damping force acting on the vibrations counterforce is generated.
  • mass-spring system which has at least one relative to the housing relatively movably mounted mass body, wherein the mass body via at least one elastic element, preferably a spring element supported on the housing is.
  • the mass-spring system has a substantially determined by a mass m of the mass body and a spring stiffness k of the elastic element
  • the damping device according to the invention with the features of the main claim has the advantage that it is particularly inexpensive to produce, since it comprises as few parts.
  • the spring element of the damping device according to the invention has at least two regions which differ in at least one element parameter and / or one material parameter.
  • an element parameter is understood in particular to be a geometric property of the design of the spring element.
  • a material parameter here means in particular a material property, for example an elasticity, and / or a geometric size of the starting material, for example a material thickness.
  • the spring element of the damping device according to the invention is designed as a helical spring with spring coils.
  • a spring winding is understood as meaning a section, in particular a loop, preferably a wire loop, which essentially extends around a main extension axis, preferably 360 °, around the main extension axis of the helical spring and has an axially oriented winding pitch substantially in the direction of the main extension axis having.
  • an axial distance between a beginning of the spring turn and an end of the spring turn along the main extension axis is understood as a turn pitch.
  • the spring element is formed by a juxtaposition in particular juxtaposed connection of a plurality of spring coils or sections along the main extension axis.
  • the spring coils of the two areas differ in at least one element characteristic and / or material parameter.
  • An element characteristic of a spring winding means in particular the winding diameter, the winding pitch and / or a winding thickness.
  • a winding thickness here means, in particular, a cross-sectional area and / or a cross-sectional diameter of the loop-for example, a wire thickness in a wire loop-in a sectional area perpendicular to the loop.
  • a material parameter in the case of a helical spring is understood in particular to mean an elasticity, a modulus of elasticity, a breaking elongation and / or other material characteristics of a material of the loop or spring coil.
  • the spring element is an evolute spring.
  • the evolving spring has turns a winding diameter, a winding width and / or a winding thickness as preferred element characteristics.
  • a spring element which preferably by winding a previously produced for example by punching Sheet metal section around a spring axis is formed.
  • the winding diameter is preferably to understand essentially analogous to the winding diameter of a coil spring.
  • a winding width is understood in particular to mean a width of the sheet metal section of the winding parallel to the spring axis.
  • the winding thickness preferably corresponds to a thickness of the sheet metal section.
  • the spring element is a plate, leaf or wave spring with segments.
  • a segment is to be understood in particular as meaning a section of the plate, leaf or wave spring, which forms the spring element along a spring direction or axis along a spring direction or axis by stringing together a plurality of these sections in particular.
  • the preferred element characteristics are in particular a leaf or segment spacing, a segment period span and / or a segment dimension - for example, a segment width, thickness and / or area.
  • a segment period range is understood in particular to be the distance between a segment beginning and a segment end along a spring axis.
  • a first region of the spring element is designed as a spring region, while a second region is formed as a mass region.
  • the spring area is characterized in particular by an elasticity.
  • the mass range preferably has a major part of a total mass of the spring element, preferably more than 50% of the total mass, in particular more than 75% of the total mass.
  • the mass region has a denser volume packing of the spring coils or segments relative to the spring region.
  • the number of spring coils or segments per unit volume is based on a volume packing Total volume of the damping device, in particular the spring element understood.
  • the turns or segments of the mass region take up a larger volume fraction than those of the spring region.
  • the volume fraction in particular means a fraction of turns or segments in the total volume of the damping device, in particular of the spring element.
  • the spring element has a third region with at least one element characteristic variable and / or material parameter variable with respect to the other two regions.
  • the third region forms a fastening region with which the spring element can be clamped in relation to a housing and / or a clamping device.
  • a jig is understood in particular an arrangement which is designed so that the spring element relative to an outer coordinate system can be fixed, preferably biased fixed.
  • the spring element is symmetrical, in particular mirror-symmetrical about a median plane, so that a spring region, in particular a spring region and a clamping region is provided at least on two sides of the mass region.
  • a center plane is understood in particular to mean a plane perpendicular to the spring axis.
  • At least one mass body is arranged on the mass region.
  • "arranged on the mass region” means, in particular, connected to the mass region and / or received in the mass region and / or attached to the mass region, in particular in the sense of Screwing, clipping, clamping, pressing and / or gluing.
  • the damping device can be integrated in a machine tool, in particular in a hand-held machine tool, in a particularly simple manner as a preassembled and / or pre-adjusted assembly.
  • the invention relates to a machine tool, in particular a hand-held machine tool with at least one damping device according to the invention for damping vibrations.
  • the damping device according to the invention can be used in particular in machine tools with at least one drive device, which is designed at least for an axially oscillating, in particular impacting drive a tool, to a damping of the vibrations occurring in this drive device.
  • the invention relates to a method for producing a damping device for damping vibrations, in particular for producing a Vibrationstilgers or Resonanzdämpfers, with a spring element, according to the invention, a spring region and a mass range in a first manufacturing step by a variation of at least one element characteristic and / or a material characteristic of the spring element is produced.
  • a damping device can be produced in a particularly cost-effective manner.
  • an additional mass is arranged on and / or in the mass region, preferably attached. It is understood by “attached” in particular "connect” with the mass range, preferably by pressing, pressing, screwing or screwing, gluing, soldering, welding to connect to the mass range.
  • Fig. 1 shows a first embodiment of an inventive
  • Fig. 2 shows a second embodiment of an inventive
  • Fig. 3 shows a third embodiment of an inventive
  • Fig. 4 shows a fourth embodiment of an inventive
  • Fig. 5 shows a fifth embodiment of an inventive
  • FIG. 6 shows a development of the fifth embodiment according to FIG. 5
  • Fig. 7 shows a sixth embodiment of an inventive
  • Fig. 8 shows a seventh embodiment of an inventive
  • Fig. 9 shows an eighth embodiment of an inventive
  • damping device 10 shows a drill and / or percussion hammer as an example of a hand-held machine tool with a damping device according to the invention
  • the helical spring 101 shows a helical spring 101 as a first exemplary embodiment of a spring element 100 of a damping device 99 according to the invention.
  • the helical spring 101 has three regions 120, 130, 140 extending along a main extension axis 110.
  • the regions 120, 130 are provided in a symmetrical manner along the main extension axis 110 on both sides of the region 140.
  • the three regions 120, 130, 140 of the coil spring 101 differ in at least one element characteristic of their spring coils 122, 132, 142.
  • the spring coils 122 of the region 120 have a coil diameter Dl which is smaller than a coil diameter D2 of the spring coils 132 of the region 130, which in turn is smaller than a third winding diameter D3 of the spring coils 142 of the area 140.
  • the spring windings 122, 132, 142 at least partially under the regions 120, 130, 140 deviating Windungsste Trentonen 124, 134, 144 on.
  • the winding pitch 124, 144 is selected in accordance with FIG. 1 such that the spring windings 122, 142 lie close to each other in each of the areas 120, 140.
  • the coil spring 101 is wound in blocks 120, 140 in a block. In this case, we mean by "wound on block” in particular that the helical spring 101 has substantially no elasticity along the main extension axis 110 in this region 120, 140.
  • the region 120 is provided with a fastening region which allows the spring element 100, 101 to be clamped in suitable receptacles.
  • the region 140 Due to its large winding diameter D3 and its dense sequence of spring windings 142 along the main extension axis 110, the region 140 comprises a major portion of a total mass M of the helical spring 101. With a mass m, which in particular at least 50%, preferably at least 75% of the total mass M of the coil spring 101, the region 140 forms a mass range of the spring element 100, 101 according to the invention.
  • the spring windings 132 again have a turn pitch 134, which provides the region 130 with a resilient elasticity along the main extension axis 110.
  • the area 140 as a mass area comprises a denser volume packing of the windings 142 than the area 130 as a spring area.
  • the region 130 therefore has elastic properties which allow the assignment of a finite spring constant k to this region.
  • the region 130 thus forms a spring region of the damping device according to the invention.
  • For the intrinsic or resonant frequency w0 of the damping device is essentially:
  • the spring element 100 can be generated by corresponding variation of the winding parameters during winding of the coil spring 101 from a starting blank, preferably wire in a manufacturing step.
  • FIG. 2 shows a development of the helical spring 101 as a second exemplary embodiment of a damping device 99 according to the invention.
  • the helical spring 101 according to FIG. 2 has three regions 120, 130, 140 analogous to FIG. 1, the regions 120, 130 in this example only with respect to their winding pitch 124, 134, but not with respect to their winding diameter Dl and D2 differ.
  • the region 140 of the helical spring 101 in the form of a mass region according to FIG. 2 learns at this juncture a development such that windings 148 arranged inwardly in an interior 146 of the region 140 are provided, which are enclosed by the spring windings 142. These windings 148 increase a density of the region 140 and in particular a proportion of the mass m of the region 140 on the total mass M of the helical spring 101 and the total mass M of the helical spring 101.
  • This development has the advantage that the mass m of the mass region 140 during manufacture can be varied over a larger range, which advantageously benefits an improved adaptation of the intrinsic or resonant frequency wO to the requirements for a damping device 99 and an increase in the vibration energy received in the resonance case.
  • Fig. 3 shows an alternative to Fig. 2 embodiment of a damping device 99 according to the invention as a third embodiment.
  • a mass body 150 is provided in the interior 146 of the area 140 formed as a mass region.
  • the mass body 150 is surrounded by the spring coils 142, in particular wrapped, preferably wrapped so that the mass body 150 is substantially rigid relative to the spring coils 142.
  • the mass body 150 can also consist of several parts and / or have a different structure.
  • the mass body 150 has receiving and / or guide structures for arranging the spring coils 142 on a lateral surface.
  • groove structures may be provided for guiding the spring coils 142 on the lateral surface.
  • FIG. 4 Another embodiment of a damping device 99 according to the invention is shown in FIG. 4.
  • this embodiment differs from the embodiment according to FIG. 3 in that the three regions 120, 130, 140 of the helical spring 101 essentially have identical winding diameters D1, D2, D3. Furthermore, only the turn pitch 134 is selected so that the corresponding area 130 is formed as a spring area.
  • a mass body 152 is arranged according to FIG. 4.
  • the mass body 152 has for this purpose a bore 154, which is formed continuously in the present example.
  • the bore 154 serves to receive the coil spring 101, wherein the mass body 152 in an assembled state, the coil spring 101 only in the area 140 touches.
  • the mass body 152 is connected to the region 140 of the coil spring, preferably rigidly connected.
  • the bore 154 is formed so that the coil spring 101 can be screwed with its portion 140 into the bore.
  • the mass body 152 may also be fastened to and / or with the region 140 of the helical spring 101 in such a way that the helical spring 101 is pressed into the bore 154, clipped, glued or otherwise bonded with material, force and / or or positively connected.
  • the damping device 99 shows a further development of the damping device 99 according to the invention, wherein it is provided that the spring element 100, 101 is arranged inside a damper housing 160, in particular accommodated in the damper housing 160.
  • the damper housing 160 of two housing shells 162, 164.
  • a parting plane 166 of the housing shells 162, 164 are preferably around the main extension axis 110 of the coil spring 101 in each housing shell 162, 164 Fixieraus Principle 168, 170 are provided for receiving and Fixing the trained as a mounting portion 120 of the coil spring 101 are used.
  • FIG. 6 shows a development of the damping device 99 according to the invention according to FIG. 5. It is provided that in the damper housing two or more spring elements 100a, 100b, 101a, 101b are arranged. In the embodiment of Fig. 6, the main extension axes 110a, 110b of the coil springs 101a, 101b are substantially parallel to each other.
  • the main extension axis 110b of at least one helical spring 101b is aligned at a non-zero angle W to the main extension axis 110a of a first helical spring 101a, preferably perpendicular to the main extension axis 110a of the first helical spring 101a.
  • an inventive, advantageously two- or multi-axis damping device 99 is achieved.
  • the at least two coil springs 101a, 101b may be arranged in at least one parameter, such as a coil pitch 134a, 134b of the spring portions 130a, 130b and / or a coil diameter and / or mass ma, mb of the regions 140a, 140b - differ. This advantageously achieves that the damping device 99 according to the invention has two or more natural or resonant frequencies.
  • FIG. 1 An alternative embodiment of a damping device 99 according to the invention is shown in FIG.
  • the spring element 100 of the damping device 99 is designed as an evolute spring 102.
  • the evolute spring 102 according to FIG. 2 is formed symmetrically along the main extension axis 110 and has along the main extension axis 110 a winding diameter which increases toward a center plane.
  • the evolute spring 102 is thereby obtained by punching and / or cutting out of a flat blank, preferably sheet metal and subsequent angles about the main extension axis 110.
  • a section of the planar blank forming the central region 240 has, for example, a greater thickness of material or material thickness than the remaining portions of the planar blank.
  • the area 240 is provided with an additional mass and thus forms a mass range of the damping device 99.
  • the Blank is wound around a mass body 250 such that it is fixed in the central region 240 and increases the mass m of this area.
  • FIG. 1 A further alternative embodiment of a damping device 99 according to the invention is shown schematically in FIG.
  • the spring element 100 is designed as a corrugated spring 103.
  • a corrugated spring 103 is understood to mean, in particular, a plane that is planar with respect to the main extension axis 110 as segments 332, 342 and that has elastic properties, in particular in the direction of the main extension axis 110.
  • the wave spring 103 has at least two regions 330, 340 with respect to the segments 332, 342, wherein the segments 332, 342 of the regions 330, 340 differ in at least one element and / or material characteristic.
  • the segments 342 of the region 340 have a smaller spacing along the main extension axis 110 than the segments 332 of the region 330.
  • the region 330 thus forms a spring region and the region 340 forms a mass region of the spring element 100, 103.
  • Fig. 9 shows another embodiment of a damping device 99 according to the invention, wherein the spring element 100, 105 is formed as a stack of corrugated or disc spring rings 432, 442 as segments.
  • the spring element 100, 105 is formed as a stack of corrugated or disc spring rings 432, 442 as segments.
  • at least two regions 430, 440 differ according to the invention by at least one element and / or material characteristic of their segments 432, 442.
  • an additional mass body 450 can also be arranged here in the region 440 and preferably with the segments 442 be connected.
  • FIG. 10 shows a schematic side view of a drill and / or chisel hammer 10 as an example of a machine tool, in particular a hand-held machine tool.
  • the drill and / or chisel hammer 10 has a housing 12 and a handle device 14 arranged on the housing 12.
  • the handle device 14 may be connected to the housing 12, in particular be elastically connected, or be designed in one piece with the housing 12.
  • a tool holder 18 is further provided at one of the handle device 14 opposite end 16 of the housing 12.
  • the tool holder 18 is in particular rotatably arranged on the housing 12.
  • the tool holder 18 may in particular also be accommodated at least partially in the housing.
  • the tool holder 18 further serves for receiving, in particular for exchangeable receiving a tool 20.
  • the tool 20 has in the present example, a longitudinal extent 22.
  • auxiliary handle device 24 serves to improve the handling of the hammer drill 10.
  • the housing 12 of the hammer drill 10 further includes a drive device 26 which causes known dimensions in one operation vibrations, which can be transmitted via the housing 12 and the handle device 14 and the auxiliary handle device 24 to a user.
  • the drive device 26 has a drive unit 28, a
  • the drive unit 28 is formed by a motor 34, in particular an electric motor 35.
  • the translation unit 30 is provided, a movement, in particular a rotational movement of the output unit 32, 34, 35 in a necessary for the drive of the tool 20 Translate movement.
  • the translation unit 30 comprises a rotary drive gear 36 and an axial drive gear 38.
  • the output unit 32 of the hammer drill 10 comprises a rotary drive 40 for rotationally driving the tool holder 18, which is operatively connected to the rotary drive gear 36, and a striking mechanism 42 for transmission of impact pulses on the tool 20, which in turn is operatively connected to the Axialantriebsgetriebe 38.
  • the tool 20 accommodated in the tool holder 18 is driven to a working or useful movement along its working direction 44, wherein the occurring forces cause vibrations in the drive device 26.
  • These vibrations may be transmitted to the housing 12 and / or the handheld device 14 and / or the auxiliary handle device 24.
  • at least one damping device 99 according to the invention is provided in the drilling and / or chipping hammer 10. If the natural frequency of the damping device 99 is tuned favorably to the dominant frequencies of the vibrations, the damping device 99 acts in a known manner as an absorber on the vibrations.
  • a particular advantage of the damping device 99 according to the invention is that the spring element with at least one spring and at least one mass region is produced in a first production step 502 by a variation of at least one element characteristic and / or material parameter as a production parameter can be.
  • 11 shows a schematic sequence of the method 500 according to the invention.
  • the raw material supplied to the first production step 502 which has either essentially homogeneous and isotropic material properties or else a suitable property profile in at least one material parameter, for example sheet thickness or wire diameter, becomes a spring element 100, 101, 102, 103, 104 formed with at least two regions 130, 140, 230, 240, 330, 340, 430, 440 - for example, wound, drawn, formed or the like, these areas 130, 140, 230, 240 , 330, 340, 430, 440 differ in at least one element and / or material parameter caused by appropriate process control variation of the process parameters.
  • a mass body 150, 152, 250, 350, 450 is supplied to the production step 502, which in the production of the spring element 100, 101, 102,
  • 103, 104 is arranged in the region 140, 240, 340, 440 and is preferably at least partially connected to the turns, elements or segments 142, 242, 342, 442 of the region 140, 240, 340, 440.
  • the mass body 152 is arranged in a subsequent process step on or on the region 140, 240, 340, 440, preferably fastened.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Springs (AREA)

Abstract

L'invention concerne un dispositif d'amortissement (99) servant à amortir des vibrations, en particulier dans des machines-outils portatives, comportant un élément ressort (100, 101, 102, 103, 104). Selon l'invention, l'élément ressort (100, 101, 102, 103, 104) présente au moins deux zones (130, 140, 230, 240, 330, 340, 430, 440) qui se différencient par au moins une grandeur caractéristique de l'élément et/ou une grandeur caractéristique de matériau.
EP10760963A 2009-11-03 2010-09-20 Dispositif d'amortissement, machine-outil équipée d'un dispositif d'amortissement et procédé pour produire un dispositif d'amortissement Withdrawn EP2496855A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910046348 DE102009046348A1 (de) 2009-11-03 2009-11-03 Dämpfungsvorrichtung, Werkzeugmaschine mit einer Dämpfungsvorrichtung und Verfahren zur Herstellung einer Dämpfungsvorrichtung
PCT/EP2010/063790 WO2011054579A1 (fr) 2009-11-03 2010-09-20 Dispositif d'amortissement, machine-outil équipée d'un dispositif d'amortissement et procédé pour produire un dispositif d'amortissement

Publications (1)

Publication Number Publication Date
EP2496855A1 true EP2496855A1 (fr) 2012-09-12

Family

ID=43828098

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10760963A Withdrawn EP2496855A1 (fr) 2009-11-03 2010-09-20 Dispositif d'amortissement, machine-outil équipée d'un dispositif d'amortissement et procédé pour produire un dispositif d'amortissement

Country Status (4)

Country Link
EP (1) EP2496855A1 (fr)
CN (1) CN102597566A (fr)
DE (1) DE102009046348A1 (fr)
WO (1) WO2011054579A1 (fr)

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JP5557396B2 (ja) * 2011-12-09 2014-07-23 株式会社鷺宮製作所 電磁弁
US10232500B2 (en) 2012-12-17 2019-03-19 Swerea Ivf Ab Impact machine
WO2014095936A1 (fr) * 2012-12-17 2014-06-26 Swerea Ivf Ab Machine à chocs
WO2015193284A1 (fr) 2014-06-16 2015-12-23 Swerea Ivf Ab Machine d'impact
DE102015209406B4 (de) 2015-05-22 2026-05-28 Robert Bosch Gmbh Handwerkzeugmaschine mit einem mechanischen Drehschlagwerk
CN105090309A (zh) * 2015-09-02 2015-11-25 无锡市东赫金属制品有限公司 一种缓冲拉力弹簧
CN105375673B (zh) * 2015-12-07 2024-07-02 珠海格力电器股份有限公司 一种减振装置和减振方法以及空调电机支架
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DE202017104705U1 (de) 2017-08-07 2017-09-12 Scherdel Innotec Forschungs- Und Entwicklungs-Gmbh Druckfeder zur Verwendung in einer Federstütze sowie Federstütze mit einer solchen Druckfeder
CN111963605B (zh) * 2020-09-01 2021-12-14 江苏博发机器人智能装备有限公司 一种变刚度液态阻尼减震器
FR3144238B1 (fr) * 2022-12-23 2025-05-02 Valeo Embrayages ensemble de transmission de couple pour un appareil de mobilité
DE102023126286A1 (de) * 2023-09-27 2025-03-27 Bayerische Motoren Werke Aktiengesellschaft Schwingungstilger, Bauteilanordnung sowie Kraftfahrzeug

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CN102597566A (zh) 2012-07-18
DE102009046348A1 (de) 2011-05-05

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