DE102012219011A1 - Torsional vibration damper for power train, has arc-shaped radially outwardly pipe sections that are attached to drive flange distributed over circumference for displaceably receiving damper masses - Google Patents

Torsional vibration damper for power train, has arc-shaped radially outwardly pipe sections that are attached to drive flange distributed over circumference for displaceably receiving damper masses

Info

Publication number
DE102012219011A1
DE102012219011A1 DE201210219011 DE102012219011A DE102012219011A1 DE 102012219011 A1 DE102012219011 A1 DE 102012219011A1 DE 201210219011 DE201210219011 DE 201210219011 DE 102012219011 A DE102012219011 A DE 102012219011A DE 102012219011 A1 DE102012219011 A1 DE 102012219011A1
Authority
DE
Germany
Prior art keywords
torsional vibration
vibration damper
pipe sections
characterized
drive flange
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Withdrawn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
DE201210219011
Other languages
German (de)
Inventor
Andreas Triller
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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
Priority to DE102011084928 priority Critical
Priority to DE102011084928.9 priority
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to DE201210219011 priority patent/DE102012219011A1/en
Publication of DE102012219011A1 publication Critical patent/DE102012219011A1/en
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/32Correcting- or balancing-weights or equivalent means for balancing rotating bodies, e.g. vehicle wheels
    • F16F15/36Correcting- or balancing-weights or equivalent means for balancing rotating bodies, e.g. vehicle wheels operating automatically, i.e. where, for a given amount of unbalance, there is movement of masses until balance is achieved
    • F16F15/363Correcting- or balancing-weights or equivalent means for balancing rotating bodies, e.g. vehicle wheels operating automatically, i.e. where, for a given amount of unbalance, there is movement of masses until balance is achieved using rolling bodies, e.g. balls free to move in a circumferential direction

Abstract

The torsional vibration damper (1) has drive flanges (3) that is rotatable around a rotational axis (2). Several movable damping masses (5) are arranged opposite the drive flange in radial and circumferential direction. Several arc-shaped radially outwardly pipe sections (4) are attached to the drive flange distributed over the circumference. The damper masses are displaceably received in the pipe sections.

Description

  • The invention relates to a torsional vibration damper, in particular in a drive train with an internal combustion engine having a drive flange rotatable about a rotation axis and a plurality of absorber masses distributed over the circumference and delimited relative to the drive flange at least in the circumferential direction and in the radial direction.
  • Generic torsional vibration damper have long been known. In this case, a circumferentially elastically displaceable additional mass is assigned to a main mass rotating about an axis of rotation, which buffer stores the kinetic energy of rotational irregularities, so that the main mass is calmed in its rotational movement. Here, only a predetermined frequency of torsional vibrations can be redeemed by appropriate tuning of the natural frequency of the absorber masses. Since the excitation frequencies in a drive train with an internal combustion engine change with the speed, so-called speed-adaptive torsional vibration dampers in the form of centrifugal pendulums have been proposed, the additional masses are arranged pendulum in the form of pendulum masses in the centrifugal force field, so that their pendulum frequency changes with the speed and thus excitation frequencies speed-dependent be paid off. From the DE 10 2009 053 482 A1 For example, a centrifugal pendulum is known, in which mutually arranged pendulum masses are arranged on both sides of a drive flange, which roll by means of rolling elements provided in the drive flange and in the pendulum masses careers. To stabilize the pendulum masses precautions must be taken against gravitational changes in position, in particular to prevent noise, especially at low speeds or during standstill of the drive flange.
  • Furthermore, for example, from the DE 199 56 962 A1 Vibrating damper known which eradicate axial and tumble oscillations in a drive train with an internal combustion engine with an axialschwingungsbehafteten crankshaft, in which radially outside the crankshaft, a flywheel is arranged, which is axially elastically coupled to the crankshaft.
  • The object of the invention is the advantageous development of a torsional vibration damper, in particular for the speed-adaptive eradication of torsional vibrations, which may optionally also eradicate axial vibrations and wobble oscillations.
  • The object is achieved by a torsional vibration damper, in particular in a drive train with an internal combustion engine with a drive flange rotatable about a rotation axis and a plurality of circumferentially distributed, relative to the drive flange limited at least in the circumferential direction and displaceable in the radial direction absorber masses, distributed on the drive flange over the circumference are provided radially outwardly arcuate pipe sections in which the absorber masses are added displaced. By accommodating the absorber masses in completely closed pipe sections, they are protected against external impact. Other raceways and rolling elements for receiving the absorber mass can be omitted. Due to the radially outwardly arcuate design of the pipe sections moving absorber masses move in centrifugal force in the radial and circumferential relative to the main mass formed and provided with the pipe sections drive flange and thus form in cooperation with the drive flange a speed-adaptive torsional vibration damper.
  • In the simplest case, the additional masses can be formed as sliding elements, but it has proved to be advantageous if the absorber masses are designed as rolling elements as balls with a smaller cross section than a pipe inner cross section of the pipe sections. In this way, the balls can be displaced not only radially and in the circumferential direction but in addition in the axial direction relative to the pipe sections, so that in addition axial and / or tumble oscillations can be eradicated.
  • Depending on the desired mass and thus dependent on the required vibration isolation with an appropriately adjusted Tilgerfrequenz one (several) or several absorber masses such as balls can be provided in a pipe section. In order to further increase the absorber mass displaceable relative to the main mass of the drive flange, a plurality of tube sections distributed over the circumference may form a row such as a ring arranged in the axial direction about the axis of rotation, wherein a plurality of rows may be arranged axially next to one another. Depending on the available space conditions so that maximum radii and a corresponding number of axially juxtaposed pipe sections can be provided. In an arrangement of several rows in the axial direction, the pipe sections can overlap viewed in the circumferential direction, so that an improved distribution of the absorber masses in the circumferential direction can be achieved. In order to make optimal use of the space, adjacent pipe ends of adjacent pipe sections, for example, lined up seamlessly.
  • The pipe sections can be bent from tubes and attached to the drive flange, for example, welded to this. Alternatively, at least one or more, preferably all pipe sections may be formed from two complementary, axially superimposed and interconnected pipe section halves. These pipe section halves may be embossed, for example, from sheet metal. Particularly advantageous may be the formation of a pipe section half in one piece on the drive flange, to which the second pipe section surface is applied and secured thereto.
  • The arcuate shape of the pipe sections can be circular, oval, elliptical or formed as a freeform depending on the desired eradication of rotational, axial and / or tumbling oscillations. Here, the pipe sections with respect to the center line on a plane or a plane may be arranged to break through. This means, for example, that the course of the pipe section between the pipe ends has a three-dimensional shape. With reference to an average orientation of the pipe section, a plane of an average course of the pipe section between the pipe ends can nevertheless be defined. With respect to this plane and in particular in plan arranged in a plane pipe sections, this level can be tilted by a tilt angle greater than or equal to 30 and less than or equal to 90 ° relative to the axis of rotation. A tilt of 90 ° means that the pipe sections are only radially aligned. An axial vibration damping is exhausted by the axial clearance of the absorber masses in the pipe sections. At tilt angles of less than 90 °, the influence of an eradication of axial and tumble oscillations can be increased by the absorber masses additionally covering an axial path in addition to their radial and circumferential pivoting. The degree of tilt angle can be adapted in a corresponding manner to the occurring Axialschwingungskomponenten such as axial and wobble components.
  • The absorber masses are taken captive in the pipe sections to avoid loss of these in particular at low speeds or at a standstill of the drive flange with little or no centrifugal force. For this purpose, for example, the pipe ends can be closed, covered by appropriate design of the drive flange or attachment of additional components and / or reduced its cross-section at the pipe ends.
  • The absorber masses can be made of the same material as the drive flange or of material of greater density in order to achieve a higher erosion effect with the same diameter.
  • The invention is based on the in the 1 to 4 illustrated embodiment illustrated. Showing:
  • 1 a side view of a torsional vibration damper with pipe sections,
  • 2 a view rotated by a viewing angle of 90 ° view of the torsional vibration of the 1 .
  • 3 a longitudinal section through a pipe section and
  • 4 a section through the pipe section of the 3 along the section line BB.
  • 1 shows a view of the around the axis of rotation 2 arranged torsional vibration damper 1 , The torsional vibration damper 1 is from the around the axis of rotation 2 driven drive flange 3 and the distributed over the circumference and radially outwardly arcuately arranged and with the drive flange 3 firmly connected like welded pipe sections 4 educated. In the pipe sections 4 are absorber masses 5 housed under the centrifugal force of the rotating drive flange 3 be accelerated radially outward. In the drive flange 3 registered torsional vibrations, axial and tumbling vibrations are the absorber masses 5 along the arcs formed by the inner circumference 6 shifted accordingly in the circumferential direction, radial and axial direction and absorb vibration energy during vibration peaks and give them on decay again by taking the radially outermost layer on the sheets 6 again, so that a vibration damping occurs.
  • The drive flange 3 can by means of mounting holes 7 directly on a crankshaft of an internal combustion engine or on an intermediate unit such as friction clutch, flywheel as received at the input part or output part of a split flywheel and / or even functional elements such as a friction surface of a friction clutch or recordings for a torsional vibration damping for additional formation of a torsional vibration damper and the like wear.
  • 2 shows the torsional vibration damper 1 in a side view with the drive flange 3 and the pipe sections 4 , From this view, the inclination of the arranged in the plane E pipe sections 4 opposite the axis of rotation 2 about the tilt angle α - here about 65 ° - significantly, causing the influence of the absorber masses 5 ( 1 ) is increased in the axial direction depending on the interpretation of the tilt angle α in a desired manner. Especially when using the torsional vibration damper 1 to Damping of vibrations of the crankshaft of an internal combustion engine such as internal combustion engine is given the angular dependence of torsional vibrations and the axial and tumble oscillations formed as a result of deflection of the crankshaft during firings of the compressed fuel mixtures of the individual cylinders, so that by tilting the pipe sections simultaneously rotational and axial vibrations can be reduced.
  • 3 shows a longitudinal section through a pipe section 4 of the 1 and 2 , In the pipe section 4 is in the embodiment shown a single absorber mass 5 in the form of the ball 8th accommodated. The ball 8th has a smaller diameter d than the inner diameter D of the pipe section 4 on and under centrifugal force against the inner circumference 9 of the bow 6 accelerates and may be in the presence of torsional vibrations along the double arrow 10 on the inner circumference 9 For example, move to position a, which increases the potential energy of the sphere 8th changes and a vibration damping changes.
  • 4 shows a section of the pipe section 4 of the 3 along the section line BB. By compared to the inner diameter D smaller diameter d, the ball can 8th along the double arrow 11 For example, in the case of existing axial oscillations, shift to position b.
  • LIST OF REFERENCE NUMBERS
  • 1
     A torsional vibration damper
    2
     axis of rotation
    3
     drive flange
    4
     pipe section
    5
     absorber mass
    6
     bow
    7
     fastening opening
    8th
     Bullet
    9
     inner circumference
    10
     double arrow
    11
     double arrow
    a
     position
    b
     position
    d
     diameter
    D
     Inner diameter
    e
     level
    B-B
     intersection
    α
     tilt angle
  • QUOTES INCLUDE IN THE DESCRIPTION
  • This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.
  • Cited patent literature
    • DE 102009053482 A1 [0002]
    • DE 19956962 A1 [0003]

Claims (10)

  1. Torsional vibration damper ( 1 ) in particular in a drive train with an internal combustion engine having an axis of rotation ( 2 ) rotatable drive flange ( 3 ) and a plurality of circumferentially distributed, opposite the drive flange ( 3 ) limited at least in the circumferential direction and in the radial direction displaceable absorber masses ( 5 ), characterized in that on the drive flange ( 3 ) distributed over the circumference radially outwardly arcuate pipe sections ( 4 ) are provided, in which the absorber masses ( 5 ) are moved.
  2. Torsional vibration damper ( 1 ) according to claim 1, characterized in that the absorber masses as rolling elements with a smaller diameter (d) than an inner diameter (D) of the pipe sections ( 4 ) are formed.
  3. A torsional vibration damper according to claim 1 or 2, characterized in that a plurality of pipe sections distributed over the circumference form a row arranged in the axial direction about the axis of rotation and a plurality of rows are arranged axially next to one another.
  4. Torsional vibration damper ( 1 ) according to one of claims 1 to 3, characterized in that at least one pipe section ( 4 ) arranged in a plane (E) course of the pipe section ( 4 ) forming pipe.
  5. Torsional vibration damper ( 1 ) according to claim 4, characterized in that the plane (E) by a tilt angle (α) greater than or equal to 30 and less than or equal to 90 ° relative to the axis of rotation ( 2 ) is tilted.
  6. Torsional vibration damper ( 1 ) according to one of claims 1 to 5, characterized in that two adjacent pipe sections ( 4 ) overlap in the circumferential direction.
  7. Torsional vibration damper ( 1 ) according to claim 5, characterized in that adjacent pipe ends of adjacent pipe sections ( 4 ) are strung together without gaps.
  8. Torsional vibration damper ( 1 ) according to one of claims 1 to 7, characterized in that the absorber masses ( 5 ) captive in the pipe sections ( 4 ) are included.
  9. Torsional vibration damper ( 1 ) according to one of claims 1 to 8, characterized in that an arc shape of the pipe sections ( 4 ) is circular, elliptical, oval or formed as a freeform.
  10. Torsional vibration damper ( 1 ) according to one of claims 1 to 9, characterized in that at least one pipe section ( 4 ) is formed of two complementary, axially superimposed and interconnected pipe section halves.
DE201210219011 2011-10-21 2012-10-18 Torsional vibration damper for power train, has arc-shaped radially outwardly pipe sections that are attached to drive flange distributed over circumference for displaceably receiving damper masses Withdrawn DE102012219011A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE102011084928 2011-10-21
DE102011084928.9 2011-10-21
DE201210219011 DE102012219011A1 (en) 2011-10-21 2012-10-18 Torsional vibration damper for power train, has arc-shaped radially outwardly pipe sections that are attached to drive flange distributed over circumference for displaceably receiving damper masses

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201210219011 DE102012219011A1 (en) 2011-10-21 2012-10-18 Torsional vibration damper for power train, has arc-shaped radially outwardly pipe sections that are attached to drive flange distributed over circumference for displaceably receiving damper masses

Publications (1)

Publication Number Publication Date
DE102012219011A1 true DE102012219011A1 (en) 2013-04-25

Family

ID=48051497

Family Applications (1)

Application Number Title Priority Date Filing Date
DE201210219011 Withdrawn DE102012219011A1 (en) 2011-10-21 2012-10-18 Torsional vibration damper for power train, has arc-shaped radially outwardly pipe sections that are attached to drive flange distributed over circumference for displaceably receiving damper masses

Country Status (1)

Country Link
DE (1) DE102012219011A1 (en)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009053482A1 (en) 2008-12-11 2010-09-02 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Centrifugal force pendulum for use in torsional vibration damper of drivetrain of motor vehicle, has roller bodies, tracks and/or counter tracks with surface made of material whose elastic modulus is smaller than elastic modulus of steel

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009053482A1 (en) 2008-12-11 2010-09-02 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Centrifugal force pendulum for use in torsional vibration damper of drivetrain of motor vehicle, has roller bodies, tracks and/or counter tracks with surface made of material whose elastic modulus is smaller than elastic modulus of steel

Similar Documents

Publication Publication Date Title
US10400825B2 (en) Vibration damper for a torque transmission device of a motor vehicle
JP6100362B2 (en) Pendulum damper device especially for automobile transmissions
US8479901B2 (en) Hydrodynamic torque converter
EP2667050B1 (en) Torque transmission device for a motor vehicle
US9243681B2 (en) Centrifugal pendulum device
EP2577092B1 (en) Torsion vibration damper assembly and vibration damper device, in particular in a torsion vibration damper assembly
DE112011102382B4 (en) starter
US8747234B2 (en) Vibration absorber
KR101967491B1 (en) Device for absorbing torsion, in particular for a motor vehicle transmission
US9915317B2 (en) Centrifugal pendulum
JP5675363B2 (en) In particular, a power transmission device for transmitting power between a driving machine and a driven part.
DE102009039989B4 (en) Pulley with spring damper device
US8635931B2 (en) Flexible flywheel
DE102011006533A1 (en) Torque transmission assembly, in particular hydrodynamic torque converter, fluid coupling or wet-running clutch
DE202010018635U1 (en) Hydrodynamic torque converter
US8925420B2 (en) Centrifugal pendulum mechanism
JP5473933B2 (en) Force transmission device with speed-adaptive dynamic vibration absorber and method for improving damping characteristics
US6450065B1 (en) Speed-adaptive dynamic-vibration absorber
US10094444B2 (en) Centrifugal pendulum device
DE102011088163A1 (en) Centrifugal pendulum device
CN103443502B (en) Centrifugal pendulum mechanism
WO2014146849A1 (en) Tuned mass damper
JP6363194B2 (en) Simple torsional damper device with pendulum
DE102014211711A1 (en) centrifugal pendulum
DE102009037481B4 (en) Speed-adaptive absorber, in particular centrifugal pendulum device

Legal Events

Date Code Title Description
R081 Change of applicant/patentee

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140218

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140218

R081 Change of applicant/patentee

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20150408

R005 Application deemed withdrawn due to failure to request examination