CN104508319A - Friction device for a torsional vibration damper - Google Patents
Friction device for a torsional vibration damper Download PDFInfo
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- CN104508319A CN104508319A CN201480001733.5A CN201480001733A CN104508319A CN 104508319 A CN104508319 A CN 104508319A CN 201480001733 A CN201480001733 A CN 201480001733A CN 104508319 A CN104508319 A CN 104508319A
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- Prior art keywords
- friction element
- rubbing
- rubbing device
- master end
- vibration damper
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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
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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
- F16F15/131—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 the rotating system comprising two or more gyratory masses
- F16F15/133—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 the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
- F16F15/134—Wound springs
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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
- F16F15/131—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 the rotating system comprising two or more gyratory masses
- F16F15/139—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 the rotating system comprising two or more gyratory masses characterised by friction-damping means
- F16F15/1395—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 the rotating system comprising two or more gyratory masses characterised by friction-damping means characterised by main friction means acting radially outside the circumferential lines of action of the elastic members
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention relates to a friction device (20) for a torsional vibration damper (10). The friction device comprises at least two friction elements (26) which can be moved independently of each other at least in the circumferential direction about a main rotation axis (14) and can be actuated via a primary-side control (28), and complementary secondary-side friction surfaces (30) which can be actuated via a secondary-side control (32) and on which rests in each case a friction element (26) with friction. The invention further relates to torsional vibration dampers and to a method for mounting a friction device of a torsional vibration damper.
Description
The present invention relates to the rubbing device for torshional vibration damper and torshional vibration damper, and for the method for installing rubbing device with for driving the method for torshional vibration damper.
Torshional vibration damper is open in a large amount of specific embodiments.Torshional vibration damper has primary mass body (or master end) and from mass body (or slave end), wherein slave end can rotate relative to master end, and is provided with the spring damper acted between master end and slave end.The main purpose of design torshional vibration damper has an impact to the damping characteristic relevant to various running state, especially has an impact to the damping characteristic relevant to the relative rotation between master end and slave end.People strive as a rule, have during larger rotational steps and arrange higher damping between master end and slave end.Especially, arrange higher damping when having following rotational speed or speed, wherein under this rotational speed or speed, each system (torshional vibration damper is connected by each system mechanics formula ground effect) can reach resonance zone.
In order to provide the damping matched with various running state, known torshional vibration damper is arranged by means of only limited mode.Such as in patent documentation EP1058028A2, disclose a kind of torshional vibration damper with rubbing device, this rubbing device comprise for damping coupling drag wedge.A kind of vibration damping equipment for double mass flywheel is disclosed in patent documentation WO 2006/079306A1, wherein be provided with multiple parts, these parts extrude owing to being provided with the wedge surface that can slide over each other between flywheel mass body mutually when two flywheel mass bodies reverse, and between two flywheel mass bodies rotated relative to one another, produce rubbing action under the state of extruding mutually.In a similar fashion, disclosed in patent documentation WO2005/064198A1, the damping means of two mass-coupling flywheel is also form based on the parts with wedge surface.In patent documentation US5503595, disclose a kind of torshional vibration damper, wherein rubbing device is configured to annular.
The object of this invention is to provide a kind of substituting rubbing device for torshional vibration damper, utilize this rubbing device on torshional vibration damper can with simple and the mode of practicality realizes desired damping characteristic.
According to the present invention, this object is realized by a kind of a kind of a kind of method of rubbing device for torshional vibration damper, torshional vibration damper, rubbing device for installing torshional vibration damper and a kind of method operating torshional vibration damper, and wherein torshional vibration damper has the technical characteristics of independent claims.Other useful design proposals can find in dependent claims and specification below.
Herein especially, first the design proposal that the control piece in inclination introducing portion and master end is made up of the material identical with friction element can realize corresponding good decoupling, and this can be used for corresponding less sluggishness to operate torshional vibration damper.
This rubbing device can have at least two friction elements that can move independently from one another around main rotating shaft line at least in the circumferential, and these friction elements can be controlled by the control piece in master end.In addition can arrange the rubbing surface of complementary slave end, these rubbing surfaces can be controlled by the control piece of slave end, and on rubbing surface, have friction element rubbing contact with it respectively.
By arranging the rubbing surface of the friction element that can move independently from one another and complementary slave end, under the acting in conjunction of the control piece in master end and the control piece of slave end, can with simple and the mode of practicality realizes or arrange desired damping characteristic.The control piece being for this reason provided with master end for control friction element, by the master end of torshional vibration damper or the transmission of torque of primary mass body to friction element.The control piece being provided with slave end for the rubbing surface controlling slave end, and be especially arranged to by slave end or from the transmission of torque of mass body to the rubbing surface of slave end, and therefore pass to friction element.Or rather, when occurring relatively to rotate between master end and slave end, particularly preferably when exceeding or equal to be the deflection angle between each friction element master end of presetting and slave end by the control piece of slave end, the rubbing surface rubbing contact of friction element and complementary slave end, and play damping effect by the sliding friction on the rubbing surface of the slave end of complementation.Adopt the rubbing device of this design it is advantageous that friction or the damping of regulation can be arranged, wherein especially it is advantageous that the control piece of master end and slave end can be designed neatly, in order to realize the damping characteristic matched with various application.
Preferably, being radial with the surface area of rubbing surface rubbing contact and aiming at main rotating shaft line in the circumferential of rubbing surface and friction element.This has following beneficial effect, namely owing to not having the effect of centrifugal force on the direction of respective normal force, the first order component of frictional force therefore acted between the rubbing surface of slave end and friction element or surface area or the revolution number of first approximation and master end or slave end or speed have nothing to do.
In the embodiment of one of rubbing device of the present invention application, rubbing surface is arranged on a shared friction disk.By arranging shared friction disk, a kind of compact rubbing device with simple structure can be advantageously provided.Especially, the rubbing device of simple and compact structure makes it possible to assemble simply, and correspondingly can dismantle this rubbing device simply in some cases.
In a preferred embodiment of rubbing device of the present invention, the control piece in master end has the centrifugal force compensation radially-inwardly acted on at least one friction element.By arranging the centrifugal force compensation radially-inwardly acted on at least one friction element, can advantageously avoid or significantly reduce the rubbing contact of the surface area of friction element and the slave end caused due to centrifugal action when the control piece by master end controls.This rubbing contact is especially disadvantageous or does not wish to occur in the outer region of radial direction, more precisely particularly when high revolution or the high frequency needing to be decayed, wherein different in the situation of resonance zone from revolution, vibration damping can cause the unnecessary increase of amplitude, according to the structure of the system that torshional vibration damper is installed, this amplitude increase if necessary can than larger in undamped situation.
In the Another application embodiment of rubbing device of the present invention, the control piece in master end comprises the control panel with at least one groove, be furnished with friction element in a groove, its further groove is greater than the corresponding extension part of layout friction element in a groove in the circumferential around the part of main rotating shaft line.
In above-mentioned Another application embodiment, the control panel as the control piece in master end is prevented rotatably being connected with master end or primary mass body or acting on them being connected.By arranging groove, this groove is greater than the corresponding extension part of wherein arranged friction element in the circumferential around the part of main rotating shaft line, a kind of control piece of master end can be provided, wherein only when the angle of swing exceeded or equal between the master end of presetting for each friction element and slave end or minimum angle of swing (this angle is relevant with corresponding groove extension part in the circumferential), each friction element just starts friction or sliding friction on rubbing surface, namely realizes vibration damping by each friction element.When realizing vibration damping by friction element, friction element preferably contacts with the stop surface defining each groove in the circumferential, or contacts with the stopper region defining each groove in the circumferential.Only have when contacting this stop surface or stopper region, the transmission of torque in master end can be given each friction element by control panel, thus realizes vibration damping by the friction of each friction element on rubbing surface.
This control panel can also be fixedly connected with at least one friction element, have between master end and slave end so very little but be not equal to the angle of swing of zero time, friction element also can rub or frictional movement on rubbing surface.Can provide basic friction in this way, especially when operating torshional vibration damper in very high range of revolution, this rubs substantially is useful.
In above-mentioned Another application embodiment, preferably at least two grooves are set in control panel, in two grooves, arrange friction element respectively, the difference between its further groove size in the circumferential and the size of the corresponding extension part of each friction element arranged in a groove is different for two grooves.
Because the angle of swing between the master end of presetting for each friction element and slave end or minimum angle of swing depend on corresponding groove extension part in the circumferential (see above), therefore by by groove size in the circumferential and arrange each friction element in a groove corresponding extension part size between difference be arranged to different or variable, the friction or damping that increase step by step can be provided.Increase friction or damping can realize in the following manner step by step, and namely due to the difference of change, when having different deflection angles between master end and slave end, friction element plays rubbing action or damping effect.It is advantageous that by arranging the friction increased step by step, customized damping characteristic can be provided for each system.
Preferably, this groove has radially inner guide surface, for the relevant radially outer surface interaction to the friction element arranged in a groove.It is advantageous that the unpredictably radial outward movement of friction element effectively can be avoided in this way.
Particularly preferably, this groove and the friction element be arranged in wherein have at least one inclination introducing portion acted in the circumferential.On the one hand it is advantageous that by arranging inclination introducing portion, can centrifugal force compensation be realized when suitably aiming at inclination introducing portion.On the other hand it is beneficial that, by arranging the inclination introducing portion acted in the circumferential, friction element can enter into each stop position lentamente, i.e. the friction element position (also with reference to above) that contacts with the stop surface defining groove in the circumferential or contact with the stopper region defining each groove in the circumferential.Especially it is advantageous that or the situation starting suddenly to rub can be down to minimum by harsh noise by this slowly entering.
In a preferred embodiment of rubbing device of the present invention, be provided with the extrusion preferably for sharing friction element being pressed to rubbing surface.Extrusion can be arranged so that friction element and corresponding rubbing surface rubbing contact in a prescribed manner.On the one hand, share extrusion useful uniform squeezing action is produced to friction element, this brings again following result, namely friction element can carry out in the axial direction approximately uniform movement (from can independently move in the circumferential different).It is advantageous that these identical movements are conducive to uniform fricting movement.By arranging shared extrusion, rubbing device of the present invention can also be advantageously made to possess simple structure.Especially, the simple rubbing device of structure can realize simple assembling and same simple dismounting.
In addition, rubbing device for torshional vibration damper can carry out by the control piece in master end the friction element that controls with at least one, it is characterized in that, this friction element or the press element axially acting on this friction element have axial projection, this rubbing device is also with the rubbing surface of the slave end of complementation, this rubbing surface can be controlled by the control piece of slave end, and this friction element by act on axial raised extrusion extruding and with rubbing surface rubbing contact.By axial projection being connected with effect extrusion thereon, the friction of regulation can be provided advantageous by the extruding force of regulation, and the friction of regulation advantageously can realize the damping function of the regulation of each system.
At this, axial projection towards friction element or can deviate from friction element, and preferably specifies point of contact, applies extruding force in a prescribed manner at this point of contact place extrusion, this thus produce regulation rubbing action.
Preferably, extrusion comprises disc spring.On the one hand it is advantageous that the extrusion comprising disc spring can extrusion friction element equably, this brings again following result, namely friction element can carry out in the axial direction approximately uniform movement (from can independently move in the circumferential different).It is advantageous that these identical movements are conducive to uniform fricting movement.Rubbing device of the present invention can also be made to possess simple structure by arranging disc spring.Especially, the simple rubbing device of structure can realize simple assembling, and same simple dismounting in some cases.
Preferably, disc spring directly acts in axial projection, thus by friction element very effectively and compact structure be squeezed on the rubbing surface of complementary slave end.
For the rubbing device of torshional vibration damper also with at least one friction element, the feature of this rubbing device is, friction element can be controlled by the control piece in the master end be made up of the material identical with friction element, and the rubbing surface rubbing contact of the slave end with complementation, this rubbing surface can be controlled by the control piece of slave end.
For this rubbing device, at least one friction element can be controlled by the control piece in the master end be made up of the material identical with friction element, this brings following beneficial effect, between the control piece and friction element in master end, namely provide the rubbing action of regulation.Especially it is advantageous that in the suitable design proposal of the control piece in friction element and master end, minimum owing to adopting identical material that wearing and tearing can also be made substantially to be down to.
Particularly preferably be, friction element is made up of metal, more preferably have between friction element and control piece sclerosis or rolling contact area, or friction element is made up of plastics.Friction element is made up of metal, and preferably there is sclerosis between friction element and control piece or the contact area of rolling, be of value to minimise wear.Arrange the friction element be made up of plastics to have the following advantages, the harsh noise namely can avoided or reduce ear-piercing friction significantly and bring thus.
In an Application Example, around rubbing surface, the control piece in master end is thinner than friction element in the axial direction.By making the control piece in master end have thinner structure around rubbing surface, the friction that the control piece in master end may have advantageously can be avoided.
Especially, the control piece in master end can construct in integrated mode, and wherein the control piece in the master end of one-piece construction by simple and the mode of practicality manufactures, such as, can be manufactured by the material that can cast by casting.
The torshional vibration damper mated with this rubbing device can comprise master end or primary mass body, the slave end that can rotate around the main rotating shaft line of torshional vibration damper relative to master end or from mass body, and the spring damper with corresponding rubbing device acted between master end to slave end.By arranging corresponding rubbing device, can with simple and the mode of practicality realizes as described above or arranges desired damping characteristic on torshional vibration damper.
In one of torshional vibration damper actual embodiment, the control piece in master end is axially inserted on master end in the mode of form fit.By providing this plugability, can realize simple installation or dismounting, wherein carrying out grafting control piece for the arbitrary friction transposition of torshional vibration damper in the mode of form fit is of value to realization and the most simply mounts and dismounts.
In addition, for for master end, the slave end that can rotate around the main rotating shaft line of torshional vibration damper relative to master end and the torshional vibration damper of spring damper that acts between master end and slave end, this spring damper comprises the spring assembly with viscous fluid and for the viscous fluid of described spring assembly and the rubbing device sealed.It is advantageous that for this torshional vibration damper, according to concrete design, viscous fluid can be used as oiling agent and/or be used for viscous damping.For oiling agent, seal friction element is of value to the friction guaranteeing to form regulation, to arrange damping characteristic that is desired or that match.
Preferably, this rubbing device is sealed by contactless Sealing.By arranging contactless Sealing or by arranging mazy Sealing, advantageously can avoiding unnecessary or uncontrolled basic friction.
Particularly preferably, this rubbing device is arranged in the fluid path between spring assembly and the bearing between master end and slave end (being preferably sliding bearing).This has following advantage, namely can provide the sealing for viscous fluid or oiling agent to the Sealing arranged for friction element and bearing.This is especially useful to the bearing of sliding bearing formula, and it may come off or work not in accordance with the mode specified contact lubricated dose time.
For the method for operating torshional vibration damper, and for for master end, the slave end that can rotate around main rotating shaft line relative to master end and the torque-vibration damper of spring damper that acts between master end and slave end, spring damper has the spring system with following static characteristic curve, this static characteristic curve have in the scope of 90% of maximum angle of swing or in the scope that angle of swing adds and subtracts 10 ° be less than 15 Newton meters or be less than maximum engine torque 10% sluggishness.
At this, static characteristic curve of the present invention refers to the characteristic curve when low-down revolution, more precisely wherein centrifugal force negligible revolution time characteristic curve.
It is advantageous that arrange in the interval of specifying be less than 15 Newton meters or be less than maximum engine torque 10% sluggishness can form the friction of regulation, especially play the friction of the regulation of respective action when high frequency and the friction irrelevant with spring system.So-called angle of swing refers to angle of swing between master end and slave end or deflection angle.Produce this very little friction by the spring system of spring damper, this friction is provided by the friction system of spring damper substantially.
At this it is beneficial that, owing to can removing completely in the suitable design proposal of spring damper, closing or bridge joint friction system, therefore the sluggishness of regulation spring system is can measure accordingly, if but remove spring system, finally may change the function of torshional vibration damper completely, and therefore can not compare and measure result.
Preferably, sluggishness is less than 13 Newton meters or is less than 8% of maximum engine torque, is more preferably less than daNm or is less than 7% of maximum engine torque.
In this as additional or alternatively, for the method for operating torshional vibration damper, and for for master end, the slave end that can rotate around main rotating shaft line relative to master end and the torshional vibration damper of spring damper that acts between master end and slave end, spring damper has the spring system with following dynamic characteristic, this dynamic characteristic have in the scope of 90% of maximum angle of swing or in the scope that angle of swing adds and subtracts 10 ° be less than 25 Newton meters or be less than maximum engine torque 15% sluggishness.
At this, dynamic characteristic of the present invention refers to the characteristic curve when the maximum revolution of each drive system.
It is beneficial that, arrange in the interval of specifying be less than 25 Newton meters or be less than maximum engine torque 15% sluggishness can form the friction of regulation, especially when high frequency, (as occurred when high revolution) forms the friction of regulation, and the problem that wherein especially spring assembly causes due to centrifugal force can not be had an impact to vibration damping by friction.Herein, angle of swing also refers to angle of swing between master end and slave end or deflection angle.
Preferably, especially when motor has the maximum torque of 200 Newton meters, the sluggishness of dynamic characteristic is less than 50 Newton meters, is more preferably less than 40 Newton meters.Similarly, especially, when motor has other power, the sluggishness of dynamic characteristic is less than 17% of maximum engine torque, is more preferably less than 10% of motor peak torque, especially, during when high revolution or at high frequency, this point can correspondingly realize good decoupling.
The said numerical value for sluggishness corresponds to the vertical extension part of corresponding experiment curv in angle-turning moment diagram in these cases, so must adopt corresponding unit [Newton meter].
Above-mentioned absolute value refers in particular to low power motor, especially has the motor of 200 Newton-meter of torpues.Relative value is blanket, is especially enough for the motor with higher-wattage, and wherein lower if necessary absolute value is also corresponding useful certainly, because can realize decoupling better.
Show, when in the region being in idle running, namely when low-down rotating speed, although good decoupling can be guaranteed, still have high friction herein.Under high revolution and the high-frequency situation brought thus, there will be the interference being derived from motor, it should by torshional vibration damper and filtering, but friction determines poor decoupling, it finally can be made an explanation by following, and the high frequency namely exported from motor can be conveyed to remaining drive system by the friction element of rubbing device or torshional vibration damper.If there are the parts of other rubbing action, the parts of such as elastic reaction, it is (especially such as when high revolution) and certain rubbing contact when high frequency, so can be coupled by these high frequencies of these parts.By carrying out the above-mentioned spring assembly being separated and designing with corresponding lower sluggishness to friction element and spring assembly, the friction effect caused by this spring assembly can be guaranteed to be down to minimum, and substantially to determine friction effect by rubbing device.To this, only meet the following conditions and rub, namely should rub in rubbing device, could the interference effect of spring assembly be down to minimum, and when suitably designing rubbing device, can friction be on purpose limited in necessary minimum zone, to realize on purpose decoupling to high frequency.
Described spring system has in a preferred embodiment of the above-mentioned torshional vibration damper of the sluggishness of approximate regulation wherein, rubbing device exports and is greater than 300 Newton meters, is preferably greater than 400 Newton meters or is greater than 500 Newton meters for vibration damping, wherein, the share of share, the especially spring system of all the other systems can be correspondingly very little.
In order to install rubbing device, can first the control piece that at least one friction element is relevant to of rubbing device be connected to each other integral, then again they be separated from each other behind friction element location or when locating.By at least one friction element and relevant control piece being arranged to the connection of integral type, very simply can install under such coupled condition, if do not have this connection, this installation may be very expensive and complicated.Only have when mounted or after installing and terminating, wherein friction element completes location, is just separated with at least one friction element described by the control piece connected preferably by least one sheet material and at least one friction element.Preferably, as long as arrange connection by least one sheet material, so just this sheet material is cut off, to be separated with at least one friction element described by described control piece when locating or behind location.
This separation such as by making in a pre-installation skew to occur between friction element and control piece realize, then can change this skew by installing, or is realized by first time skew when debugging.
When installing rubbing device, the control piece of the rubbing device of the friction element for rubbing device axially can also be plugged on the master end of torshional vibration damper in the mode of form fit.Control piece to be plugged on master end and by simple and the mode of practicality is carried out, and simple installation or removal can be realized to rubbing device thus.And the axial grafting of this form fit formula can be set up anti-rotation type and be connected between control piece and master end.
Should be understood that, the feature of above-mentioned or described in the claims technological scheme can also combine, if necessary correspondingly can realize these advantages cumulatively.
Other advantage, object and characteristic of the present invention illustrates by the following description of embodiment, and it is especially shown in appended accompanying drawing.In the drawings:
Fig. 1 is (radial direction) sectional view of first embodiment of torshional vibration damper of the present invention,
Fig. 2 A and B is the plan view of the rubbing device of the torshional vibration damper shown in Fig. 1 respectively,
Fig. 3 is the plan view of second embodiment of torshional vibration damper of the present invention, and the difference shown in itself and Fig. 1 is, is provided with four springs and four flying barrels in the present embodiment, but not three springs and three flying barrels,
Fig. 4 is the enlarged view of the details of Fig. 2 A,
Fig. 5 is the enlarged view of the details of Fig. 1,
Fig. 6 is (radial direction) sectional view of the 3rd embodiment of torshional vibration damper of the present invention,
Fig. 7 is (radial direction) sectional view of the part area of the 4th embodiment of torshional vibration damper of the present invention,
Fig. 8 is the plan view of the substituting rubbing device for torshional vibration damper,
Fig. 9 is (radial direction) sectional view of the rubbing device that Fig. 8 shows,
Figure 10 A to 10D is the perspective view of the control piece in the master end be made up of the material identical with the same friction element illustrated, plan view and (radial direction) sectional view respectively,
Figure 11 A to 11C is with the control piece in the master end of the groove opened wide in side together with the detailed drawing of the plan view of the friction disk of friction element and slave end, (radial direction) sectional view and (radial direction is analysed and observe) respectively,
Figure 12 is the plan view of control piece together with friction element in master end, and the difference shown in itself and Figure 11 is especially, does not arrange the accommodating groove for being axially inserted in the mode of form fit on master end for this control piece,
Figure 13 A and 13B be the rubbing device of torshional vibration damper together with (radial direction) sectional view of the spring of spring damper and plan view,
Figure 14 shows the static characteristic curve of exemplary spring system.
Figure 15 shows the static characteristic curve of the whole system be made up of the spring system and exemplary friction system with the indicatrix shown in Figure 14, and
Figure 16 shows the quasi-static characteristics curve with the characteristic device shown in Figure 14 and Figure 15.
Fig. 1 shows the radial section of first embodiment of torshional vibration damper 10.This torshional vibration damper 10 comprises master end 12 or primary mass body 12, the slave end 16 that can rotate around the main rotating shaft line 14 of torshional vibration damper 10 relative to master end 12 or from mass body 16, and the spring damper 18 with rubbing device 20 of the present invention of effect between master end 12 and slave end 16.As the torshional vibration damper 10 used in a motor vehicle, slave end 16 is arranged for and contacts with the clutch of Motor Vehicle, and master end 12 has for setting up bolted hole 22 with the bent axle of Motor Vehicle.In addition, master end 12 is provided with starter receiver 13.
Rubbing device 20 comprises the friction element 26 that eight (with reference to Fig. 2 A and B) can move independently from one another around main rotating shaft line 14 (with reference to Fig. 1) in the circumferential, friction element can be controlled by the control piece 28 (comprising control panel 28) in master end, also comprise complementary slave end rubbing surface 30, this rubbing surface can be controlled by the control piece 32 of slave end, and on rubbing surface, have friction element 26 rubbing contact with it respectively.Around rubbing surface 30, control panel 28 is thinner than friction element 26 in the axial direction.
On the one hand, the control piece 32 of slave end comprises the housing 38 be made up of sheet material be made up of two housing parts 34,36, and wherein the first housing parts 34 is configured to the form of the friction disk 34 shared, and it is furnished with friction element 26.On the other hand, the control piece 32 of slave end also comprises the extrusion of disc spring 40 form and is connected with the anti-rotation type of slave end 16.
Be provided with the rubbing surface 30 of two complementary slave ends in the present embodiment, one of them rubbing surface 30 is arranged on friction disk 34, and another rubbing surface 30 is arranged on disc spring 40.Two rubbing surfaces 30 have friction element 26 rubbing contact with it.This rubbing surface 30 and friction element 26 be radial with the surface area 42 of rubbing surface 30 rubbing contact, and to aim at main rotating shaft line 14 in the circumferential.For this reason, disc spring 40 is arranged to the extrusion shared, all friction elements 26 is pressed to the rubbing surface 30 be arranged on friction plate 34, especially as shown in Fig. 5 (enlarged view of the corresponding details of Fig. 1).Preferably consult the detailed drawing of amplification, friction element 26 has the axial projection 44 directly acting on disc spring 40.
Fig. 2 A and 2B respectively illustrates the plan view of the rubbing device 20 of the torshional vibration damper 10 shown in Fig. 1.These figure demonstrate the structure of control panel 28 especially further.The control panel 28 be connected with master end 12 anti-rotation type has eight grooves 46, in each groove 46, be wherein furnished with a friction element 26 (with reference to Fig. 4).Each groove 46 is greater than the corresponding extension part of layout friction element 26 in a groove in the circumferential around the part of main rotating shaft line 14.
In order to be connected with master end 12 anti-rotation type, it is hexagonal dead slot 48 that control panel 28 has form.Master end 12 is provided with the center piece 50 with the complementary structure of dead slot 48, it axially can be inserted in dead slot 48 in the mode of form fit, makes control panel 28 in the mounted state axially be inserted in (with reference to Fig. 1) on master end 12 or on center piece 50 in form fit ground mode.
By arranging such groove 46, it is greater than the corresponding extension part of the friction element 26 be arranged in wherein in the circumferential around the part of main rotating shaft line 14, a kind of like this control piece 28 of master end can be provided, wherein only when the angle of swing exceeded or equal between the master end 12 of presetting for each friction element 26 and slave end 16 or default minimum angle of swing (size of this angle of swing depends on corresponding groove 46 extension part in the circumferential), each friction element 26 just starts friction or sliding friction on rubbing surface 30, namely begin through each friction element 26 and carry out vibration damping.When carrying out vibration damping by each friction element 26, friction element 26 contacts with the stop surface 52 defining each groove 46 in the circumferential.Only have when contacting with this stop surface 52, control panel 28 can " drive " each friction element or by the transmission of torque in master end 12 give each friction element 26, to realize vibration damping by the friction of each friction element 26 on rubbing surface 30.
Fig. 2 B describes a kind of situation, wherein because friction element 26 contacts with stop surface 52, by achieving vibration damping with friction element 26 bottom topmost in Fig. 2 B.For all the other six friction elements 26, or also do not reach angle of swing or minimum angle of swing, cause friction element 26 herein can not rub on rubbing surface 30, therefore these friction elements 26 do not participate in damping effect.This occurs in following situation, namely groove 46 size in the circumferential and to arrange each friction element 26 in a groove corresponding extension part size between difference be different for each groove 46, thus be of value to the friction or damping that provide and increase step by step.Fig. 2 A shows a kind of situation, and wherein neither one friction element 26 reaches angle of swing or minimum angle of swing, thus does not also exist and rubbed by friction element and the damping effect produced.
Each groove 46 and the friction element 26 be arranged in wherein have two inclination introducing portions acted in the circumferential 54 (right side and Fig. 4 with reference to exemplary diagram 2A).The useful centrifugal force compensation that inclination introducing portion 54 1 aspect can realize friction element 26 is set.In addition it is advantageous that make friction element 26 can enter into each stop position lentamente by arranging the inclination introducing portion 54 that acts in the circumferential, i.e. the wherein position that contacts with the stop surface 52 defining groove 46 in the circumferential of friction element 26.It is beneficial that, by arranging the centrifugal force compensation radially-inwardly acted on caused by inclination introducing portion to friction element 26, when the control piece 28 by master end controls, can avoid due to centrifugal action or reduce the rubbing contact of friction element 26 and the region of slave end or the surface area of slave end significantly, wherein in the embodiment of this display, the surface area of described slave end refers to surface 56 (reference Fig. 1 that the second housing parts 36 of the housing 38 of the control piece 32 of slave end extends in the circumferential, especially Fig. 4, shown in it is the enlarged view of the neighboring area of friction element in Fig. 2 A).
Spring damper 18 (with reference to Fig. 1) comprises spring assembly 60, and it has viscous liquid or oiling agent, and wherein rubbing device 20 is sealed for preventing the oiling agent of spring assembly 60.In the case, rubbing device 20 is arranged in the fluid passage between spring assembly 60 and sliding bearing 62, and by this sliding bearing 62, slave end 16 is bearing on master end 12 in rotatable manner.Rubbing device 20 is sealed according to the mode of labyrinth seal by contactless Sealing 64, it is configured to the shape of integrated annex 64 on friction disk 34, this annex extends radially inwardly from friction disk 34, and avoids thus because centrifugal action is penetrated in rubbing device 20 by the oiling agent that radially outward extrudes.
In addition, in order to install torshional vibration damper 10, first sliding bearing 62 is contained on slave end 16.Then, rubbing device 20 is connected with slave end 16 anti-rotation type, to provide the control piece 32 of slave end.Finally, master end 12 is connected with rubbing device 20 anti-rotation type by dead slot 48, or connects in the mode of form fit.
Fig. 3 shows the plan view of second embodiment of torshional vibration damper 10, and the difference shown in itself and Fig. 1 is, is provided with four springs 66 and four flying barrels 68 in this embodiment, but not three springs 66 and three flying barrels 68.Flying barrel 68 for suppressing the spring 66 of spring damper 18, to compensate centrifugal force or to provide drag.
Fig. 6 shows the radial cross-section of the 3rd embodiment of torshional vibration damper 10.Torshional vibration damper 10 shown here is with the difference shown in Fig. 1, in order to be connected with master end 12 anti-rotation type by control panel 28, is provided with rivet joint 70.In addition, compared with the rubbing device 20 of the torshional vibration damper 10 shown in Fig. 1, the axial projection 44 on friction element 26 is configured in the axial direction more greatly or more outstanding.Two housing parts 34 and 36 of the housing 38 of rubbing device 20 are configured to extend radially inwardly, so that the embodiment being similar to Fig. 1 display constructs contactless Sealing according to the mode of labyrinth seal, like that for the sealing of rubbing device 20 for the oiling agent of spring assembly 60.
Fig. 7 shows the radial cross-section of the part area of the 4th embodiment of torshional vibration damper 10, and the part area of the rubbing device 20 of the 4th embodiment is wherein described further.The rubbing device 20 herein shown is provided with the press element 72 with axial projection 44 acting axially on friction element 26.Friction element 26 contacts with the rubbing surface 30 of the slave end of the complementation of friction disk 34, and wherein friction element 26, by acting on the extruding with the extrusion of disc spring 40 form of axial projection 44, rubbing contact occurs.
Fig. 8 shows a kind of plan view of the substituting rubbing device 20 for torshional vibration damper.Different from rubbing device 20 described above, be provided with the friction element 26 being configured to form of lens herein, it is arranged in the groove 46 that side in control panel 28 opens wide, and wherein groove 46 described in each opens wide towards the annular region 74 of slave end.For such rubbing device 20, when there is relative movement between master end and slave end, due to the effect of centrifugal force, friction element 26 rubs on the internal surface 78 of the slave end of annular region 74, and enters in the slope of inclination introducing portion.It is useful for realizing vibration damping by this way for some application.
Fig. 9 shows the radial cross-section of the rubbing device 20 shown in Fig. 8.Be similar to the situation of the rubbing device 20 of the embodiment of Fig. 7, be also provided with at this press element 72 with axial projection 44 acting axially on friction element 26.Friction element 26 contacts with the rubbing surface 30 of complementary slave end, and wherein friction element 26, by acting on the extruding of the extrusion of disc spring 40 form in axial projection 44, rubbing contact occurs.
Figure 10 A to 10D respectively illustrates the perspective view of the control piece 28 in two other master end, plan view and radial cross-section, and control piece comprises a control panel 28 respectively, and its material identical by the friction element 26 with shown is formed.In order to axially be inserted on master end in the mode of form fit, each control panel 28 have by around the dead slot 48 that defines of wavy boundary 80 or groove 48.In addition, the difference that can not identify in Figure 10 A and 10B between control panel 28 can be found out from radial cross-section (with reference to Figure 10 C and 10D), from wherein drawing on the one hand, for two control panels 28, except a friction element 26, all friction elements 26 are all connected with control panel 28 by sheet material 82.In addition, as can be seen from Figure 10 D, be different from the situation of the control panel 28 of Figure 10 C, the friction element 26 be connected with control panel 28 according to Figure 10 D offsets vertically.Due to this species diversity, the control panel 28 of Figure 10 C and Figure 10 D is applicable to the different embodiment according to the method for installing rubbing device of the present invention.
Wherein in an embodiment, first according to Figure 10 C, friction element 26 and control panel 28 are connected to each other integral, and by separated from one another to control panel 28 and friction element 26 after friction element 26 is located, more precisely, when run duration exists relative rotation between master end with slave end, sheet material 82 can be torn because this relatively rotates.In another embodiment, because sheet material 82 is torn because of the reason of axial dipole field when locating, being therefore separated of control panel 28 and friction element 26 has been completed when locating.
Can find further from Figure 10 A and 10B, a friction element 26 (right side is outer in the drawings) is one with each control panel 28, and be fixedly connected with control panel thus, to realize basic friction in very high range of revolution and when there is very little rotational steps.In the following manner this friction element 26 is implemented to the centrifugal force compensation radially-inwardly acted on, that is, for each groove 46 arranges the radial outer border 84 extended in the circumferential.Different from situation about showing in Fig. 2 A and 2B, for the centrifugal force compensation arranged herein, time especially at return movement or toward back rotation, friction element 26 can occur at border 84 place may disadvantageous circumference friction.
The control piece 28 that Figure 11 A to 11C respectively illustrates master end is together with the detailed drawing of the plan view of the friction disk 34 of friction element 26 and slave end, radial cross-section and radial section form, and wherein control piece comprises the control panel 28 of the groove 46 opened wide with side.Have for being axially inserted in dead slot 48 on master end or groove 48 in the mode of form fit equally at control panel 28 of this display, its by around wavy boundary 80 define, wherein, in the groove 46 that each side that friction element 26 is arranged in control panel 28 is opened wide, and the connection being similarly provided with integral type by sheet material 82 is auxiliary as installation.In addition, the friction element 26 (with reference on the right of outermost) herein for realizing basic friction is one with control panel 28.In radial section, (with reference to Figure 11 B and 11C) does not show friction element 26, but wherein can find from radial section, the control panel 28 in master end and the friction disk 34 of slave end are connected to each other integral in order to provide installation auxiliary by sheet material 86, and this sheet material can have during relative rotation during installation or after mounting between master end with slave end to be torn.
Figure 12 shows the plan view of control piece 28 together with friction element 26 in master end, this control piece comprises control panel 28, wherein the difference of the control panel shown in this control panel and Figure 11 is, does not have to arrange for being axially inserted in the groove on master end in the mode of form fit for this control panel 28.In addition, also show the hole 22 (being similar to Fig. 3) in six master ends in fig. 12, for being connected with the crank shaft bolt of corresponding Motor Vehicle.
The rubbing device 20 that Figure 13 A and 13B shows corresponding torshional vibration damper is together with the plan view of the spring 66 of spring damper and radial cross-section.Be with the difference of above-described embodiment, herein the spring of the spring vibration damper 66 of torshional vibration damper inner layout radial relative to friction element 26.
It is advantageous that spring assembly 60 participates in friction respectively as few as possible for said apparatus, and friction determines mainly through rubbing device 20.A corresponding useful design proposal of spring assembly 60 is exemplarily shown in Figure 14 to 16, wherein the rubbing device 60 of Figure 14 has the sluggishness of below 20 Newton meters within the scope of the maximum deflection of 90%, and within the scope of remaining, have even less sluggishness.
Correspondingly, as according to the static characteristic curve of the whole system shown in Figure 15, can sluggishness be determined by rubbing device 20 and accurately keep this sluggishness in the path of regulation.To this, Figure 16 shows quasistatic state, wherein in little self-oscillating, has slowly deflection angle, and in little movement, this indicatrix is substantially consistent with static characteristic curve.
Higher unshowned herein revolution is similarly suitable for, wherein must tests to corresponding high energizing frequency, this is because in this state along with corresponding low frequency can never occur large deflection angle again.
Reference numerals list:
10 torshional vibration dampers
12 master ends
13 starter receivers
14 main rotating shaft lines
16 slave ends
18 spring dampers
20 rubbing devices
22 holes
26 friction elements
The control piece in 28 master ends, control panel
30 rubbing surfaces
The control piece of 32 slave ends
34 housing parts, friction disk
36 housing parts
38 housings
40 disc springs
42 surface areas
44 axial projection
46 grooves
48 dead slots
50 center pieces
52 stop surfaces
54 inclination introducing portions
56 second housing parts surfaces
60 spring assemblies
62 sliding bearings
64 contactless Sealings
66 springs
68 flying barrels (Fliegering)
70 rivet interlacement
72 press elements
74 annular regions
The internal surface of 78 slave ends
80 corrugated borders
82 sheet materials
84 radial outer borders
86 sheet materials
Claims (26)
1. for the rubbing device (20) of torshional vibration damper (10), wherein said rubbing device (20) comprises at least two at least in the circumferential can around the friction element (26) of main rotating shaft line (14) independent movement to each other, described friction element controls by the control piece (28) in master end, described rubbing device also comprises the rubbing surface (30) of complementary slave end, described rubbing surface controls by the control piece (32) of slave end, and on described rubbing surface, have friction element (26) rubbing contact with it respectively, the control piece (28) in described master end comprises the control panel (28) with at least one groove (46), friction element (26) is furnished with in described groove, wherein said groove (46) is greater than the corresponding extension part of the friction element (26) be arranged in described groove in the circumferential around the part of described main rotating shaft line (14), it is characterized in that, described groove (46) and the friction element (26) be arranged in described groove have at least one inclination introducing portion (54) acted in the circumferential.
2. rubbing device according to claim 1 (20), it is characterized in that, being radial with the surface area (42) of described rubbing surface (30) rubbing contact and aiming at main rotating shaft line (14) in the circumferential in described rubbing surface (30) and described friction element (26).
3. rubbing device according to claim 1 and 2 (20), is characterized in that, described rubbing surface (30) is arranged on shared friction disk (34).
4. the rubbing device (20) according to above-mentioned any one claim, it is characterized in that, the control piece (28) in described master end has the centrifugal force compensation radially-inwardly acted on at least one friction element (26).
5. the rubbing device (20) according to above-mentioned any one claim, it is characterized in that, at least two grooves (46) are had in described control panel (28), friction element (26) is furnished with respectively in described groove, wherein, the difference between described groove (46) size in the circumferential and the size of the corresponding extension part of each friction element (26) be arranged in described groove is different for described two grooves (46).
6. the rubbing device (20) according to above-mentioned any one claim, it is characterized in that, described groove (46) has radially inner guide surface, for interacting to the relevant radially inner guide surface of the friction element (26) be arranged in described groove (46).
7. the rubbing device (20) according to above-mentioned any one claim, it is characterized in that, also comprise the extrusion (40) described friction element (26) being pressed to rubbing surface (30), the extrusion preferably shared.
8. the rubbing device (20) according to above-mentioned any one claim, it is characterized in that, described friction element (26) or the press element (72) acting axially on described friction element have axial projection (44), and described friction element (26) is by acting on rubbing surface (30) the extruding type rubbing contact of the extrusion (40) of described axial projection (44) and the slave end with described complementation.
9. rubbing device according to claim 8 (20), is characterized in that, described extrusion (40) comprises disc spring (40).
10. rubbing device according to claim 9 (20), is characterized in that, described disc spring (40) directly acts on described axial projection (44).
11. for the rubbing device (20) of torshional vibration damper (10), it is characterized in that, comprise at least one friction element (26), described friction element is controlled by the control piece (28) in the master end be made up of the material identical with described friction element (26), also comprise the rubbing surface (30) of complementary slave end, described rubbing surface is controlled by the control piece (32) of slave end, and described friction element (26) and described rubbing surface rubbing contact, wherein said friction element (26) is made up of plastics.
12. rubbing devices (20) according to above-mentioned any one claim, it is characterized in that, wherein said rubbing device (26) is made up of metal, preferably have between friction element (26) and control piece (28,32) sclerosis or rolling contact area, or described friction element (26) is made up of plastics.
13. rubbing devices (20) according to above-mentioned any one claim, it is characterized in that, around described rubbing surface (30), the control piece (28) in described master end is thinner than described friction element (26) in the axial direction.
14. rubbing devices (20) according to above-mentioned any one claim, is characterized in that, control piece (28) the integrate shaped type ground structure in described master end.
15. torshional vibration dampers (10), its slave end (16) that there is master end (12), can rotate relative to described master end (12) around the main rotating shaft line (14) of described torshional vibration damper (10), and the spring damper (18) acted between described master end (12) and slave end (16), the rubbing device (20) described in the with good grounds above-mentioned any one claim of wherein said spring damper band.
16. torshional vibration dampers according to claim 15 (10), is characterized in that, the control piece (28) in described master end is axially inserted on described master end (12) in the mode of form fit.
17. torshional vibration dampers (10), its slave end (16) that there is master end (12), can rotate relative to described master end (12) around the main rotating shaft line (14) of described torshional vibration damper (10), and the spring damper (18) acted between described master end (12) and slave end (16), it is characterized in that, described spring damper (18) comprises the spring assembly (60) with viscous liquid, and for the viscous liquid of described spring assembly (60) and the rubbing device (20) sealed.
18. torshional vibration dampers according to claim 17 (10), is characterized in that, described rubbing device (20) is sealed by contactless Sealing (64).
19. torshional vibration dampers (10) according to claim 17 or 18, it is characterized in that, described rubbing device (20) is arranged in the fluid path between described spring assembly (30) and bearing (62), and described bearing is positioned between master end (12) and slave end (16).
20. for operating the method for torshional vibration damper (10), this torshional vibration damper has master end (12), the slave end (16) that can rotate around the main rotating shaft line (14) of described torshional vibration damper (10) relative to described master end (12), and the spring damper (18) acted between described master end (12) and slave end (16), it is characterized in that, described spring damper (18) has the spring system with static characteristic curve, described static characteristic curve have in the scope of 90% of maximum angle of swing or in the scope that angle of swing adds and subtracts 10 ° be less than 15 Newton meters or be less than motor peak torque 10% sluggishness.
21. operating method according to claim 20, is characterized in that, described sluggishness is less than 13 Newton meters or is less than 8% of motor peak torque, are preferably less than daNm or are less than 7% of motor peak torque.
22. for operating the method for torshional vibration damper (10), described torshional vibration damper has master end (12), the slave end (16) that can rotate around the main rotating shaft line (14) of described torshional vibration damper (10) relative to described master end (12), and the spring damper (18) acted between described master end (12) and slave end (16), it is characterized in that, described spring damper (18) has the spring system with dynamic characteristic, described dynamic characteristic have in the scope of 90% of maximum angle of swing or in the scope that angle of swing adds and subtracts 10 ° be less than 25 Newton meters or be less than motor peak torque 15% sluggishness.
23. method for drivings according to claim 22, is characterized in that, described sluggishness is less than 20 Newton meters or is less than 17% of motor peak torque, are preferably less than 15 Newton meters or are less than 10% of motor peak torque.
24. according to the torshional vibration damper (10) in claim 20 to 23 described in any one, it is characterized in that, described rubbing device (20) exports and is greater than 300 Newton meters, is preferably greater than 400 Newton meters or is greater than 500 Newton meters for vibration damping.
25. for installing the method for rubbing device (20), it is characterized in that, first at least one friction element (26) is connected to each other integral to the relevant control piece (28) of described rubbing device (20), after locating described friction element (26) or when locating, by separated from one another to described control piece (28) and described friction element (26).
26. for installing the method for rubbing device (20), it is characterized in that, be axially inserted in the master end (12) of torshional vibration damper (10) for the control piece (28) of the described rubbing device (20) of the friction element (26) of described rubbing device (20) in the mode of form fit.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013003628.3A DE102013003628A1 (en) | 2013-03-05 | 2013-03-05 | Friction device for a torsional vibration damper and torsional vibration damper and method for mounting a friction device |
| DE102013003628.3 | 2013-03-05 | ||
| PCT/DE2014/000090 WO2014135143A1 (en) | 2013-03-05 | 2014-03-05 | Friction device for a torsional vibration damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104508319A true CN104508319A (en) | 2015-04-08 |
| CN104508319B CN104508319B (en) | 2018-02-09 |
Family
ID=
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114746670A (en) * | 2020-02-27 | 2022-07-12 | 舍弗勒技术股份两合公司 | Torsional vibration damper comprising friction device |
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|---|---|---|---|---|
| DE1575746B1 (en) * | 1966-05-06 | 1970-04-23 | Borg Warner | Torsionally flexible coupling |
| DE3608829A1 (en) * | 1985-03-27 | 1986-10-09 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | Device for compensating torsional impacts |
| EP0641956A1 (en) * | 1993-09-07 | 1995-03-08 | Unisia Jecs Corporation | Torsional damper with friction generating device |
| EP1058028A2 (en) * | 1999-06-04 | 2000-12-06 | Rohs-Voigt Patentverwertungsgesellschaft mbH | Torsional vibration damper and its method of production |
| FR2845745A1 (en) * | 2002-10-15 | 2004-04-16 | Zf Sachs Ag | Automobile transmission torsion oscillation damper comprises first and second friction elements with friction surfaces at different axial levels, axial distance between surfaces compensated by sloping friction surfaces passage segments |
| EP2159445A2 (en) * | 2008-08-27 | 2010-03-03 | Aisin Seiki Kabushiki Kaisha | Damper device |
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1575746B1 (en) * | 1966-05-06 | 1970-04-23 | Borg Warner | Torsionally flexible coupling |
| DE3608829A1 (en) * | 1985-03-27 | 1986-10-09 | LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl | Device for compensating torsional impacts |
| EP0641956A1 (en) * | 1993-09-07 | 1995-03-08 | Unisia Jecs Corporation | Torsional damper with friction generating device |
| EP1058028A2 (en) * | 1999-06-04 | 2000-12-06 | Rohs-Voigt Patentverwertungsgesellschaft mbH | Torsional vibration damper and its method of production |
| FR2845745A1 (en) * | 2002-10-15 | 2004-04-16 | Zf Sachs Ag | Automobile transmission torsion oscillation damper comprises first and second friction elements with friction surfaces at different axial levels, axial distance between surfaces compensated by sloping friction surfaces passage segments |
| EP2159445A2 (en) * | 2008-08-27 | 2010-03-03 | Aisin Seiki Kabushiki Kaisha | Damper device |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114746670A (en) * | 2020-02-27 | 2022-07-12 | 舍弗勒技术股份两合公司 | Torsional vibration damper comprising friction device |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112014001174A5 (en) | 2015-11-12 |
| DE102013003628A1 (en) | 2014-09-11 |
| WO2014135143A1 (en) | 2014-09-12 |
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