CN101725666A - Torsional vibration damper and rotation unit with the same - Google Patents

Torsional vibration damper and rotation unit with the same Download PDF

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Publication number
CN101725666A
CN101725666A CN200910309073A CN200910309073A CN101725666A CN 101725666 A CN101725666 A CN 101725666A CN 200910309073 A CN200910309073 A CN 200910309073A CN 200910309073 A CN200910309073 A CN 200910309073A CN 101725666 A CN101725666 A CN 101725666A
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CN
China
Prior art keywords
vibration damper
inner member
torshional vibration
flange
shell
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN200910309073A
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Chinese (zh)
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CN101725666B (en
Inventor
科尼利厄斯·盖斯林格
马提亚·盖斯林格
保罗·皮希勒
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Gaislinger Group Co ltd
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Geislinger GmbH
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Publication date
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Publication of CN101725666A publication Critical patent/CN101725666A/en
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Publication of CN101725666B publication Critical patent/CN101725666B/en
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    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/80—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive in which a fluid is used
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/56—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic metal lamellae, elastic rods, or the like, e.g. arranged radially or parallel to the axis, the members being shear-loaded collectively by the total load
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/1215—Leaf springs, e.g. radially extending
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material

Abstract

A torsional vibration damper (10') comprises a housing (11') with a longitudinal axle (A); an inner unit (12') coaxial with the housing (11'); a plurality of cavities (13') between the housing (11') and the inner unit (12'), wherein the cavities are filled with vibration reduction medium and communicated with each other by fluid channels (14'); a plurality of leaf spring units (15') in the cavities (13') for connecting the housing (11') with the inner unit (12') in torsion flexible way. A rotation unit (20') with the rotation axle (B) comprises a flange (21') connected with the inner unit (12') of the torsional vibration damper (10'). The longitudinal axle (A) of the torsional vibration damper (10') is eccentrically arranged relative to the rotation axle (B) of the rotation unit (20'). For example, in a transmission system, less material is used and the production cost is reduced and free force and/or torque compensation can be obtained by the torsional vibration damper.

Description

Torshional vibration damper and rotary component with torshional vibration damper
Technical field
The present invention relates to a kind of torshional vibration damper, reach effectiveness in vibration suppression by the damping medium between transfer enclosure and the inner member, inner member can reverse flexibly and be added in the shell.
Background technique
Torshional vibration damper is mainly used in two strokes and four-cycle diesel engine or petrolic transmission system of the large-scale slow-speed of revolution or middling speed, is used to offset torsional vibration.The outer dia of torshional vibration damper reaches 3 meters, for example is connected on the arbor of motor with flange.Yet the torshional vibration damper of above type also can be used on other rotary component, for example, and camshaft, jack shaft, live axle or gearbox.This torshional vibration damper is disclosed in the patent application document of EP0955484B1, EP1304500B1 and DE19839470B4.
Except torsional vibration, compensation free force and/or moment of torsion usually also are essential.In order to reach this purpose, adopt counterbalance usually.In addition, in the application documents of application number AT371578, disclose by means of providing this compensation with respect to its rotating shaft eccentric with the center of gravity of the shell of torshional vibration damper.In order to reach this purpose, must remove material from shell.For example, by on torshional vibration damper, adding the imbalance that hole or fluting obtain this expectation.This need have suitable thickness or material surplus at shell.Yet, especially for large diameter vibration damper, will cause a large amount of amount of debris, just the quantity of material of removing by cutting.So, consider the material and the cost of production of use, the improved solution that proposes in the application documents of application number AT371578.
Summary of the invention
The objective of the invention is to overcome above-mentioned deficiency, more particularly, the present invention uses less material, low cost of production and less effort, obtains free force and/or torque compensation by torshional vibration damper.
For realizing purpose of the present invention, torshional vibration damper is connected on the flange of rotary component.Described torshional vibration damper comprises the shell with longitudinal shaft, the inner member coaxial with the shell longitudinal shaft, the a plurality of cavitys that between shell and inner member, form, be full of damping medium in the cavity, and can interconnect by the fluid passage between the cavity, a plurality of plate spring component that are arranged in the cavity interconnect described shell and inner member to reverse flexible mode.According to the present invention, inner member has the bolt circle with respect to longitudinal shaft off-centre, and bolt circle comprises a plurality of perforates, by bolt circle torshional vibration damper is fixed on the flange.Compare with traditional torshional vibration damper, only moved circumferential bolt hole.No longer need to make the expensive time-consuming machining of groove etc.Therefore, the present invention can be that vibration damper provides counterbalance in very simple mode.
In principle, can further increase counterbalance by the more material of removing from vibration damper.Yet, in a preferred embodiment, the center of gravity that vibration damper can be designed to its shell is positioned on its longitudinal shaft, and in fact, making provides counterbalance by the transfer with respect to the off-centre setting of the bolt circle of the running shaft of rotary component and the vibration damper center of gravity that produced.
In a preferred embodiment, the flange of rotary component has the bolt circle with respect to its rotating shaft coaxle, and bolt circle comprises a plurality of perforates, and the perforate of inner member is corresponding with the perforate of flange.
The advantage of this technological scheme is, does not need to do unnecessary processing for rotary component.On the contrary, about rotary component for example traditional linkage structure of arbor can keep.
In addition, inner member can be provided with and be used for the centring means that links to each other with corresponding centring means on the flange.In a preferred embodiment, centring means comprises a ring-shaped step coaxial with respect to the bolt circle of flange.
Another object of the present invention provides a kind of rotary component with torshional vibration damper.Here, torshional vibration damper comprises a shell with longitudinal shaft, an inner member coaxial with respect to described shell, the a plurality of cavitys that between shell and inner member, form, be full of damping medium in the cavity, a plurality of cavitys interconnect by the fluid passage, and a plurality of plate spring component that is arranged in the described cavity, and plate spring component interconnects described shell and inner member can reverse the flexible mode in ground.Rotary component comprises and is used for the flange that is connected with the inner member of torshional vibration damper.According to the present invention as can be known, the longitudinal shaft of torshional vibration damper is with respect to the rotating shaft eccentric setting of rotary component.Equally, provide counterbalance not need to remove material from vibration damper.
In a preferred embodiment, this technological scheme can be used free uneven vibration damper simply by revising the flange on the rotary component, and in this case, the center of gravity of torshional vibration damper is positioned on its longitudinal shaft.
Preferably, flange has the bolt circle with respect to the rotating shaft eccentric of rotary component, and bolt circle comprises a plurality of perforates, and by perforate, vibration damper links to each other with rotary component.In a preferred embodiment, the inner member of vibration damper has the bolt circle coaxial with respect to the longitudinal shaft of torshional vibration damper, and bolt circle comprises a plurality of perforates, and described a plurality of perforates are corresponding with the perforate of flange.
Here similarly, it is coaxial by centring means flange and inner member to be in mutually.
Below in conjunction with accompanying drawing the specific embodiment of the present invention is described in further detail.
Description of drawings
Fig. 1 is according to the longitudinal cross-section schematic representation of the torshional vibration damper on first embodiment's the rotary component;
The schematic representation of the longitudinal axis torshional vibration damper of Fig. 2 in Fig. 1;
Fig. 3 is according to the longitudinal cross-section schematic representation of the torshional vibration damper on second embodiment's the rotary component;
The schematic representation of the longitudinal axis torshional vibration damper of Fig. 4 in Fig. 3.
Embodiment
Two embodiments comprise torshional vibration damper 10, and its flange is connected to rotary component 20, for example arbor.In these two embodiments, the longitudinal shaft A of torshional vibration damper 10 is provided with prejudicially with respect to the running shaft B of rotary component 20, makes the center of gravity of torshional vibration damper 10 shift for the running shaft B generation of rotary component 20.By means of the imbalance of this expectation, at least in part the free force of compensating action on rotary component 20 and/moment of torsion.For this purpose, do not need to remove material from torshional vibration damper 10.In ideal conditions, the torshional vibration damper 10 of balance or only can use at torshional vibration damper 10 with respect to the combination surface improved of rotary component 20.
In all embodiments, torshional vibration damper 10 comprises along the longitudinal shell 11 that axle A extends and the inner member 12 concentric with shell 11.Between shell 11 and inner member 12, form the cavity 13 of a plurality of isolation, be full of damping medium in the cavity 13, for example, high pressure oil.Cavity 13 along the circumferential direction sets gradually, and interconnects by passage 14.Slit between the outer circumference part of shell 11 inside circumference part and inner member 12 forms passage 14.In cavity 13, be provided with plate spring component 15, shell 11 and inner member 12 are interconnected can reverse the flexible mode in ground, make shell 11 in the several angle scope, to rotate by relative interior parts 12.Along with this relative rotation, plate spring component 15 deforms, and damping medium shifts by passage 14, has produced the effect of vibration damping.
First embodiment as shown in Figure 1 and Figure 2, inner member 12 has circumferential bolt 16, for example has the pitch circle in a plurality of holes, with longitudinal shaft A off-centre, comprises a plurality of perforates 17.Torshional vibration damper 10 is fixed on the flange 21 of rotary component 20 by perforate 17 with bolt or analog (not shown).Correspondingly, flange 21 has corresponding perforate 22, and perforate 22 is corresponding with the perforate 17 on the inner member 12.Perforate 22 on the flange 21 is positioned on the bolt circle 23 around running shaft B.Compare with standard torsional vibration vibration damper 10, only circumferential bolt 16 has been offset the e distance with respect to vibration damper longitudinal shaft A.Therefore, the center of gravity of shell 11 is positioned on the longitudinal shaft A, yet owing to the off-centre of circumferential bolt 16 with respect to longitudinal shaft A, the center of gravity of inner member 12 can produce certain skew.
In addition, inner member 12 and flange 21 are in coaxial mutually.For example, can realize by means of centring pin or step.As implement as shown in the illustration, inner member 12 and with the concentric flange 21 of the bolt circle 23 of flange 21 on be provided with ring- shaped step 18 and 24.
Fig. 3 and 4 shows another kind of situation, provides a counterbalance by torshional vibration damper 10.In this case, use torshional vibration damper 10 ', it is a complete equilibrium with respect to longitudinal shaft A, makes its center of gravity be positioned on the longitudinal shaft A.By flange 21 ' or be arranged on perforate 22 ' acquisition longitudinal shaft A above it and the eccentric distance e between the running shaft B.Perforate 22 ' be positioned at bolt circle 23 ' on, bolt circle 23 ' central point and running shaft B between have a radial displacement e.
Inner member 12 ' the circumferential bolt 16 of perforate 17 ' be positioned at ' on, its central point be positioned at torshional vibration damper 10 ' longitudinal shaft A on.Inner member 12 ' perforate 17 ' with flange 21 ' perforate 22 ' corresponding, can use bolt that two parts are connected.
As the situation among the embodiment 1, can be by centring means 18 ' and 24 ' make flange 21 ' and inner member 12 ' be in coaxial mutually.
In two examples, can use less material, low cost of production and less effort, obtain the compensation of free force and/or moment of torsion by torshional vibration damper, perhaps obtain the reduction of free force and/or moment of torsion at least.Therefore, can reduce the material removal of the torshional vibration damper of the counterbalance that is used to provide expectation greatly, even under ideal state, can avoid material removal fully.

Claims (10)

1. torshional vibration damper that is connected with the flange of turn parts, described vibration damper comprises:
Shell (11) with longitudinal shaft (A),
The inner member (12) coaxial with the longitudinal shaft (A) of shell (11),
The a plurality of cavitys (13) that between shell (11) and inner member (12), form, cavity is full of damping medium in (13), and a plurality of cavitys (13) interconnect by passage (14), and
A plurality of plate spring component (15) that are arranged in the cavity (13) are reversed shell (11) and inner member (12) flexibly and to be interconnected,
It is characterized in that:
Inner member (12) comprises and the eccentric circumferential bolt (16) that is provided with of longitudinal shaft (A) that described circumferential bolt (16) comprises a plurality of bolts hole (17), by perforate (17) torshional vibration damper is fixed on the flange (21).
2. torshional vibration damper according to claim 1 is characterized in that: the center of gravity of shell (11) is positioned on its longitudinal shaft (A).
3. torshional vibration damper according to claim 1 and 2, it is characterized in that: the flange of rotary component (21) has the circumferential bolt (23) coaxial with its running shaft (B), circumferential bolt (23) comprises a plurality of perforates (22), and the perforate (22) of flange (21) is corresponding with the perforate (17) of inner member (12).
4. according to the described torshional vibration damper of claim 1 to 3, it is characterized in that: on inner member (12), be provided with centring means, be used for flange (21) on corresponding centring means join.
5. torshional vibration damper according to claim 4 is characterized in that: a centring means comprises the ring-shaped step (18,24) coaxial with respect to the circumferential bolt (23) of flange (21).
6. rotary component with torshional vibration damper, wherein, torshional vibration damper (10 ') comprising:
Shell (11 ') with longitudinal shaft (A),
With the concentric inner member of shell (11 ') (12 '),
The a plurality of cavitys (13 ') that between shell (11 ') and inner member (12 '), form, cavity is full of damping medium in (13 '), and a plurality of cavitys (13 ') interconnect by passage (14 '), and
A plurality of plate spring component (15 ') that are arranged in the cavity (13 ') are reversed the flexible mode in ground with shell (11 ') and inner member (12 ') and are interconnected, and
Wherein, rotary component (20 ') comprises and is used for the flange (21 ') that is connected with the inner member (12 ') of torshional vibration damper,
It is characterized in that:
The longitudinal shaft (A) of described torshional vibration damper (10 ') is provided with respect to the running shaft (B) of described rotary component (20 ') is eccentric.
7. the rotary component with torshional vibration damper according to claim 6 is characterized in that: the center of gravity of torshional vibration damper (10 ') is positioned on its longitudinal shaft (A).
8. according to claim 6 or 7 described rotary components with torshional vibration damper, it is characterized in that: flange (21 ') has the circumferential bolt (23 ') eccentric with respect to the running shaft (B) of rotary component (20 '), and circumferential bolt (23 ') comprises a plurality of perforates (22 ').
9. the rotary component with torshional vibration damper according to claim 8, it is characterized in that: inner member (12 ') has the circumferential bolt (17 ') coaxial with the longitudinal shaft (A) of torshional vibration damper (10 '), circumferential bolt (17 ') comprises a plurality of perforates (16 '), and described perforate (16 ') is corresponding with the perforate (22 ') of flange (21 ').
10. according to any described rotary component of claim 6 to 9, it is characterized in that: make flange (21 ') and inner member (12 ') be in coaxial mutually by centring means with torshional vibration damper.
CN2009103090738A 2008-10-29 2009-10-29 Torsional vibration damper and rotation unit with the same Active CN101725666B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008053632A DE102008053632B3 (en) 2008-10-29 2008-10-29 Rotary vibration damper for coupling to flange of rotating component, comprises external housing with longitudinal axis, and inner part concentric to longitudinal axis of external housing
DE1020080536326 2008-10-29

Publications (2)

Publication Number Publication Date
CN101725666A true CN101725666A (en) 2010-06-09
CN101725666B CN101725666B (en) 2012-10-10

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JP (1) JP4712107B2 (en)
KR (1) KR101133114B1 (en)
CN (1) CN101725666B (en)
DE (1) DE102008053632B3 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202012005657U1 (en) 2012-06-12 2012-09-28 Ellergon Antriebstechnik Gmbh Torsionally elastic damper or coupling with a flange for connection to a flange of another component
DE102012209767A1 (en) 2012-06-12 2013-12-12 Ellergon Antriebstechnik Gesellschaft M.B.H. Torsionally elastic damper or coupling with a flange for connection to a flange of another component
DE102020122661B3 (en) 2020-08-31 2022-02-24 Schaeffler Technologies AG & Co. KG Crankshaft arrangement with targeted imbalance on the torsional vibration damper
DE102022101972B3 (en) 2022-01-28 2023-07-06 Schaeffler Technologies AG & Co. KG Rotor arrangement for an electric axial flow machine and electric axial flow machine

Family Cites Families (14)

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Publication number Priority date Publication date Assignee Title
AT371578B (en) * 1981-12-04 1983-07-11 Geislinger Co Schwingungstechn TURN VIBRATION DAMPER
DE3505633A1 (en) * 1984-03-01 1985-09-19 Volkswagenwerk Ag, 3180 Wolfsburg Spring-action hydraulic torsional vibration damper
JPS61117937U (en) * 1985-01-10 1986-07-25
JPS6322450U (en) * 1986-07-29 1988-02-15
JP3223515B2 (en) * 1991-03-20 2001-10-29 スズキ株式会社 Two-stroke cycle crankshaft
JP3058254B2 (en) * 1996-08-20 2000-07-04 住友ゴム工業株式会社 Cable damping device
JPH1113832A (en) * 1997-06-20 1999-01-22 Mitsubishi Jidosha Tekunometaru Kk Variable speed type damper
AT405866B (en) * 1997-09-23 1999-12-27 Geislinger Co Schwingungstechn TORQUE DAMPER OR VIBRATION DAMPING AND TURN-ELASTIC CLUTCH
AT406702B (en) * 1998-05-08 2000-08-25 Ellergon Antriebstech Gmbh TORQUE DAMPER OR TURN-ELASTIC CLUTCH
JP2000088045A (en) * 1998-09-16 2000-03-28 Honda Motor Co Ltd Dynamic damper device
AT410829B (en) * 2001-10-22 2003-08-25 Ellergon Antriebstech Gmbh DRIVE TRAY WITH A ROTARY VIBRATION DAMPER AND A TURNOVER CLUTCH
GB0222480D0 (en) * 2002-09-27 2002-11-06 Ricardo Consulting Eng Torsionally damped rotary shafts
JP4826937B2 (en) * 2002-11-14 2011-11-30 シェフラー テクノロジーズ ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト Device for connecting two shafts
JP4610537B2 (en) * 2006-08-16 2011-01-12 心平 朱 Piston engine

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Publication number Publication date
DE102008053632B3 (en) 2009-12-24
JP2010107042A (en) 2010-05-13
KR20100047820A (en) 2010-05-10
KR101133114B1 (en) 2012-04-06
CN101725666B (en) 2012-10-10
JP4712107B2 (en) 2011-06-29

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