WO2015032691A1 - Torsionsschwingungstilger - Google Patents
Torsionsschwingungstilger Download PDFInfo
- Publication number
- WO2015032691A1 WO2015032691A1 PCT/EP2014/068327 EP2014068327W WO2015032691A1 WO 2015032691 A1 WO2015032691 A1 WO 2015032691A1 EP 2014068327 W EP2014068327 W EP 2014068327W WO 2015032691 A1 WO2015032691 A1 WO 2015032691A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- bearing
- flange
- elastic
- bearing portion
- torsional vibration
- Prior art date
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Classifications
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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
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/1414—Masses driven by elastic elements
- F16F15/1435—Elastomeric springs, i.e. made of plastic or rubber
- F16F15/1442—Elastomeric springs, i.e. made of plastic or rubber with a single mass
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/02—Shafts; Axles
-
- 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
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/12—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted for accumulation of energy to absorb shocks or vibration
-
- 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
- F16D3/60—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 pushing or pulling links attached to both parts
- F16D3/62—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 pushing or pulling links attached to both parts the links or their attachments being elastic
-
- 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
- F16D3/78—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 shaped as an elastic disc or flat ring, arranged perpendicular to the axis of the coupling parts, different sets of spots of the disc or ring being attached to each coupling part, e.g. Hardy couplings
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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
- 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
- F16D3/76—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 shaped as an elastic ring centered on the axis, surrounding a portion of one coupling part and surrounded by a sleeve of the other coupling part
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2121—Flywheel, motion smoothing-type
- Y10T74/2131—Damping by absorbing vibration force [via rubber, elastomeric material, etc.]
Definitions
- the present invention relates to a torsional vibration damper for damping vibrations of a shaft assembly, in particular of a motor vehicle drive train, comprising at least one flywheel comprising the first part, and at least one coaxial with the first part formed second part, which is designed for attachment of the torsional vibration on a flange the first part and the second part are connected via at least one elastic element. Furthermore, the present invention relates to a torque transmission device with such a torsional vibration damper.
- Torsionsschwingungstilger the above-mentioned type are known from the prior art.
- the document DE 43 07 583 C1 discloses a torsional vibration damper with a support body and a flywheel, which are connected to each other via six elastic elements.
- the segments are made of rubber and are vulcanized to an inner circumferential surface of the flywheel ring and to an outer circumferential surface of the support body.
- the flywheel ring extends radially outward around the support body.
- the support body serves to connect the torsional vibration damper with a flange, which in turn serves to attach the torsional vibration damper to a shaft portion of a shaft assembly.
- Torsionschwingungstilger which has a rotatable about an axis of rotation inner ring and a coaxial with the inner ring ground ring.
- the mass ring extends radially outwardly around the inner ring and the inner ring serves to connect the torsional vibration damper to a shaft assembly or flange that can be secured to a shaft assembly.
- a plurality of spring elements is arranged between the inner ring and the mass ring.
- the Torsionsschwingungstilger disclosed in the above documents have in common that the Masseringe or flywheels of these absorbers are mounted via spring elements radially on the inner carriers or inner rings of these absorbers, whereby the flywheels of the known absorber under certain Um- tending to tumbling and unbalance.
- the torsional vibration dampers according to the above-mentioned documents are largely optimized in terms of their life and function and have proven themselves in practice quite well.
- the flywheel comprising at least a first part is provided with at least one bearing portion.
- the at least one bearing section is for the radial mounting of the
- the at least one bearing portion is formed for radial mounting of the flywheel on a bearing means which is associated with a flange.
- the torsional vibration damper according to the invention is constructed such that the bearing portion is movably mounted radially on the bearing means associated with the flange. This allows a relative movement between the first part comprising the flywheel and the second part of the torsional vibration damper according to the invention for vibration damping.
- the amount of relative movement between the first part comprising the flywheel and the second part formed to secure the torsional vibration damper to the flange is determined by the at least one elastic element which serves to connect the first part and the second part. Due to the radial bearing of the first part with the flywheel of the invention Torsionsschwingungstilger is very stiff radially.
- the behavior of the absorber is significantly improved in an imbalance in the drive train.
- the flywheel tends due to the radial bearing over the bearing portion on the flange associated bearing means considerably less wobbling, whereby the torsional vibration damper can reliably fulfill its desired function, ie the damping of vibrations in a predetermined frequency range. Since the torsional vibration damper according to the invention has a greatly improved behavior in the case of imbalances, the at least one spring element is subjected to less load, which increases the service life of the torsional vibration damper.
- the bearing means associated with the flange may for example be a section of the flange or else a centering sleeve connected to the flange.
- the natural frequency of Torsionsschwingungstilgers is determined, which counteracts the torsional vibrations, for example, the drive shaft of a motor vehicle drive train.
- the elastic member may be made of an elastomer, a thermoplastic elastomer or a silicone.
- the axial guidance of the first part and the flywheel can take place via the at least one elastic element.
- a positive connection between the first part and the second part is made, so that the axial deflections can be limited so.
- axial stops for example in the form of projecting lugs, may be arranged or formed on the first part and / or the second part.
- the at least one elastic element of the Torsionsschwingungstilgers according to the invention can be made significantly larger in the radial direction.
- the risk of imbalance of the flywheel is not increased, since the flywheel comprising the first part is mounted radially on the bearing portion on a flange associated with the bearing means.
- the bearing portion of the first part may be formed such that the bearing portion slides on a relative movement between the first part and the second part on the bearing means associated with the flange.
- the second part moves with the drive train, Due to the moment of inertia of the flywheel reaches the flywheel or the first part compared with the second part delayed in motion, wherein the at least one elastic element to train, pressure or shear can be claimed. Since the second part of the Torsionsschwingungstilgers rotates with the drive train, the bearing section slides on the bearing means associated with the flange.
- the bearing section may comprise at least one bearing element.
- the at least one bearing element can be arranged on a radial inner surface of the bearing section.
- the at least one bearing element may be a plain bearing.
- the at least one bearing element may for example be a bearing bush or a coated plain bearing. Is used as a bearing element
- this bushing may for example be made of plastic.
- the at least one bearing element may be connected to the first part and in particular to the bearing portion of the first part. For example, the bearing element can be pressed into the bearing section.
- the at least one elastic element may be provided on a radial outer surface of the at least one bearing section.
- the second part of the torsional vibration damper formed for attachment to a flange may extend radially outward around the bearing portion of the first part.
- the second part may have at least one receiving section.
- the at least one receiving portion can receive the at least one bearing portion of the first part at least in sections.
- the receiving portion and the bearing portion can be connected via the at least one elastic element.
- the second part may extend with its at least one receiving portion radially outward around the bearing portion of the first part at a predetermined radial distance.
- the bearing portion of the first part and the receiving portion of the second part may be tubular. Between the bearing portion of the first part and the receiving portion of the second part may be provided a predetermined radial distance in which the at least one elastic element is arranged.
- the at least one elastic element can be connected to the receiving portion and / or to the bearing portion. However, it is also conceivable to press the at least one elastic element between the bearing portion and the receiving portion.
- the bearing portion may comprise at least one projection, which may engage in at least one corresponding recess on the receiving portion.
- the at least one elastic element can be arranged between the at least one projection and the at least one recess. The at least one elastic element can thus between the at least one projection of the bearing portion and the at least one recess of the
- the at least one elastic element is mainly loaded on pressure. According to the invention, it is possible for the at least one elastic element to extend between side surfaces of the projections of the bearing section and the rear sections of the receiving section which extend substantially in the radial direction and are therefore subjected almost exclusively to pressure during operation.
- the first part and the second part may have corresponding profilings which serve to set a maximum relative angle between the first part and the second part.
- Relative angle in this context is to be understood as meaning the angle about the central axis of the torsion damper which occurs during a relative movement between the first part and the second part.
- the maximum relative angle also corresponds to the maximum amplitude of the first part comprising the flywheel mass. By setting the maximum relative angle or the maximum amplitude, an overload of the at least one elastic element is prevented.
- the profiling of the first part and / or the second part may be covered with an elastic layer.
- the first part comprising the flywheel may have at least one opening.
- the at least one opening in the first part may allow a torque transmitting connection of the second part to the flange.
- the first part may be formed such that a relative movement between the first part and the second part is possible.
- the second part may be received in the first part between the bearing portion and the flywheel.
- the connection between the flange and the second part must be made through the at least one opening in the first bearing part.
- the first part may be configured such that the flywheel extends around the bearing portion at a predetermined radial distance.
- the first part and / or the second part may for example be made of steel, aluminum or plastic. If the first part is made of plastic or a material with similar sliding properties, the first part made of such a material can also serve directly as a bearing element. This can be dispensed with a separate bushing.
- the first part and / or the second part may be formed with beads or ribs for stiffening.
- At least one sealing element may be provided.
- the at least one sealing element may be a sealing lip which extends radially inwards.
- the at least one sealing element may for example be formed integrally with the at least one elastic element.
- the at least one sealing element can be designed such that the sealing element spans the at least one bearing element.
- the at least one sealing element may further be formed on an elastic layer, which connects the at least one bearing portion with the at least one bearing element.
- the at least one bearing element may have at least one recess.
- the at least one recess may be provided on the inner peripheral surface of the at least one bearing element.
- the at least one recess may extend in the axial direction along the inner peripheral surface of the at least one bearing element.
- the first part of the vibration absorber can be modular.
- the bearing section can form a modular unit.
- the bearing portion may form a modular unit together with the at least one elastic element.
- the at least one bearing section may be a unit with the at least one Form bearing element.
- the at least one bearing section can be connected via an elastic layer to the at least one bearing element.
- the modular unit may also be formed by the at least one bearing section, the at least one elastic element and the at least one bearing element.
- Another modular unit of the first part is formed by the portion of the first part, which supports the flywheel.
- the modular unit with the at least one bearing section and the modular unit for supporting the flywheel mass can be connected to one another via different joining methods. For example, the two units can be connected to each other via a welding process.
- the modular design of the first part has the advantage that after connecting the modular units no further work steps must be made on the first part.
- the at least one flywheel can be connected via a positive connection with the first part.
- the first part and the second part may be formed such that the at least one elastic element is at least partially angled to the central axis of the Torsionsschwingungstilgers.
- the first part may have a radially extending portion.
- the second part may have a radially extending portion.
- the at least one elastic element may extend between the radial portions of the first part and the second part.
- the second part can be arranged on the side facing away from the bearing portion side of the first part. Alternatively, it may also be arranged on the side facing the bearing section.
- the present invention further relates to a torque transmission device for transmitting torques between two shaft sections of a shaft arrangement, in particular of a motor vehicle drive train.
- the torque transmitting device comprises a torsional vibration damper having the features described above and an elastic joint body.
- the elastic joint body is connected to the second part of the Torsionsschwingungstilgers and disposed between the flywheel and the second part of the Torsionsschwingungstilgers. Due to the high radial stiffness of Torsionsschwingungstilgers or by the radial bearing of the first part with the flywheel on a bearing means assigned to the flange, the first bearing part with the flywheel can serve as a centrifugal force protection for the elastic joint body.
- the elastic joint body can serve at high speeds as overload protection for the at least one elastic element of Torsionstilgers.
- the elastic joint body bulges in the radial direction. Due to the bulging elastic joint body torsional movements of the flywheel or the first part are blocked at high speeds. Even in this case, an increase in imbalance can be prevented by the radial bearing of the flywheel on a bearing means associated with the flange or by the thus achieved high radial stiffness of the torsional vibration.
- a predetermined radial gap may be provided between the elastic joint body and a portion of the first part extending circumferentially around the joint body.
- the predetermined radial gap may be dimensioned such that the elastic joint body in the operation of the
- Torque transmission device after exceeding a predetermined speed or a predetermined torque applied to the extending around the joint body portion of the first part.
- the size of the gap can be in the millimeter range.
- the gap may be less than or equal to 4 mm, for example, in a range of 3mm. However, the gap may be less than or equal to 2 mm.
- the torque transmitting device may include a flange.
- the flange may be connected to transmit torque to the second part of the torsional vibration damper and the elastic joint body.
- the flange can be torque-transmitting by means of at least one opening in the first part with the second part and the elastic joint body.
- an arm of the flange may at least partially extend into the at least one opening in the first part or overlap with this opening and be brought into abutment there with the second part to the second part and the elastic joint body with the Can connect flange transmitting torque.
- the second part can be screwed or pressed to the flange, for example.
- the flange can receive a centering sleeve at least in sections.
- the centering sleeve may be as a bearing means associated with the flange.
- the flywheel comprising the first part of the torsion damper can thus be mounted radially with its bearing portion on the centering sleeve.
- the bearing portion of the first part at least partially receive the centering sleeve and perform a relative movement to the vibration damping on the centering or slide in a relative movement on the centering.
- the torsional vibration damper can be mounted radially on the centering sleeve via the bearing section of the second part.
- the torsional vibration damper may be radially supported on the flange via the bearing portion of the second part.
- the flange has a portion which serves as a bearing means associated with the flange.
- the bearing portion of the first part can also be mounted radially on a serving as a bearing means portion of the flange and at the same time radially on a portion of a centering sleeve.
- a bearing element can be provided in the section in which the bearing section is mounted on the centering sleeve.
- the at least one elastic joint body may have a polygonal shape, wherein the predetermined radial gap changes in the circumferential direction.
- the present invention further relates to a shaft assembly, in particular a motor vehicle drive train with a torsional vibration damper with the features described above or a torque transmission device according to the type described above.
- Figure 1 is a perspective view of a torque transmitting device according to a first embodiment of the invention; a plan view of the torque transmitting device of Figure 1; a sectional view of the torque transmitting device according to the first embodiment of the invention along the section line II-II in Figure 2; a perspective view of a torque transmitting device according to a second embodiment of the invention; a plan view of the torque transmitting device of Figure 4; a sectional view of the torque transmitting device according to the second embodiment of the invention along the section line VV in Figure 5; a perspective view of a torque transmitting device according to a third embodiment of the invention; a plan view of the torque transmitting device according to Figure 7; a sectional view of the torque transmitting device according to the third embodiment of the invention along the section line VIII-VIII in Figure 8; a perspective view of a torque transmitting device according to a fourth embodiment of the invention; a plan view of the torque transmitting device of Figure 10; a sectional view of the torque transmitting device according to the fourth embodiment along the section
- FIG. 25 is a plan view of a first part of a torsional vibration damper according to an embodiment of the invention
- Figure 26 is a detail view of the detail X in Figure 25;
- Figure 27 is a sectional view taken along section line XXVI-XXVI in Figure 26;
- FIG. 28 is a plan view of the torque transmission device according to a ninth embodiment.
- Figure 29 is a sectional view taken along line XXIX-XXIX in Figure 28;
- Figure 30 is a detail view of the detail XXX in Figure 28;
- Fig. 31 is a plan view of a torque transmission device according to a tenth embodiment of the invention.
- Figure 32 is a sectional view taken along section line XXXII-XXXII in Figure 31;
- Figure 33 is a detail view of the detail XXXIII in Figure 32;
- Figure 34 is a detail view of the detail XXXIV in Figure 31;
- Figures 35a-35c are views of a bearing element
- Figure 36 is a perspective view of the first part of the torsional vibration damper in the disconnected state
- Figure 37 is a perspective view of the first part of the torsional vibration damper in the connected portion
- Figure 38 is a plan view of the first part of the torsional vibration damper
- Figure 39 is a sectional view taken along section line XXXIX-XXXIX in Figure 38;
- FIGS. 40 and 41 are sectional perspective views of a torsional vibration absorber according to an eleventh embodiment
- Fig. 42 is a plan view of the torsional vibration absorber according to the eleventh embodiment
- Figure 43 is a sectional view taken along section line XLIII-XLIII in Figure 42;
- Figure 44 is a detail view of the detail XLIV in Figure 42;
- FIGS. 45 and 46 are views of a torque transmission device according to the eleventh embodiment.
- FIGS. 47 and 48 are sectional perspective views of a torsional vibration absorber according to a twelfth embodiment of the invention.
- Figure 49 is a plan view of the torsional vibration damper according to the twelfth
- Figure 50 is a sectional view taken along section line L-L in Figure 49;
- Figure 51 is a detail view of the detail LI in Figure 49;
- FIGS. 52 and 53 are views of a torque transmission device according to the twelfth embodiment.
- FIG. 1 shows a perspective view of a torque transmission device according to a first embodiment of the invention.
- the torque transmitting device is generally designated 10.
- the torque transmission device 10 comprises a Torsionsschwingungstil- ger 12 and an elastic joint body 14, which is designed here in the form of a flexible disc.
- the torsional vibration damper 12 comprises an annular first part 16, on which the flywheel 18 and a bearing portion 20 is arranged, and a second part 22. Of the second part 22 of the torsional vibration 12 is only partially a receiving portion 24 can be seen, the bearing portion 20 of the first Part 16 takes up.
- the receiving portion 24 has radial, pocket-shaped recesses 26 into which engage corresponding radial projections 28 of the bearing portion 20 of the first part 16 with play.
- the elastic joint body 14 is known in its construction and has long been produced by the patent applicant in large numbers. It comprises an elastic sheath 38 in which six bushes 40 are accommodated. In each case between two sockets 40 extend in a conventional manner one or more thread packages (not shown), which are also embedded in the rubber-elastic sheath 38.
- FIG. 2 shows a top view of the torque transmission device 10.
- the bearing portion 20 has, in addition to the projections 28 in the circumferential direction extending radially inner portions 42.
- the receiving section 24 of the second part 22 also has circumferentially extending sections 44 and 46.
- the circumferentially extending portions 44 and 46 are each connected by a substantially radially extending wall 48.
- the projections 28 of the bearing portion 20 have side surfaces 50 which are connected via the elastic members 30 with the walls 48 of the receiving portion 24.
- a radial recess 28 of the receiving portion 24 is formed by two walls 48 and a circumferentially extending portion 46.
- the circumferentially extending portions 42 of the bearing portion 24 bear against the slide bushing 32, which in turn abuts the serving as a bearing means portion 34 of the flange 36.
- the projections 28 move due to inertia in the direction of a wall 48 of the recesses 26 of the receiving portion 24, whereby the elastic elements 30 are loaded on pressure.
- the pressure load is significantly more advantageous in terms of the service life of the elastic elements 30 than other types of loads such as tensile or shear stress. obligations.
- the bearing portion 20 moves on serving as a bearing means portion 34 of the flange 36. In other words, slide the sections 42 of the bearing portion 20 via the plain bearing bush 32 on the portion 34 of the flange 36.
- the projections 28 and recesses 26 under heavy load under Mediation of the elastic elements 30 as attacks.
- FIG. 3 shows a sectional view along the section line II-II in FIG. 2.
- the flange 36 can be seen.
- the flange 36 comprises three arms 52 which serve for the rotationally fixed connection with the second part 22 of the torsional vibration damper 12 and the elastic joint body 14. Of the three arms 52 of the flange 36, only two can be seen in FIG.
- the flange 36 further includes a connecting portion 54 for connection to a shaft portion (not shown) of a shaft assembly of, for example, a motor vehicle drive train.
- the first part 16 of the Torsionsschwingungstilgers 12 has a perpendicular to the central axis M of the torque transmitting device 10 extending portion 56.
- the portion 56 connects the bearing portion 20 with another parallel to the central axis M extending portion 58 to which the flywheel 18 is mounted.
- openings 60 are further formed, which allow a connection of the arms 52 of the flange 36 with the second part 22 and also the joint body 14.
- the second part 22 has for this purpose in the radial direction extending portions 62 which project at least partially into the openings 60 and are themselves provided with openings 64.
- the openings 64 in the sections 62 of the second part 22 receive intermediate elements 66 which serve to connect the flange 36 to the second part 22 and via the bushes 40 of the joint body 14 for connection to the joint body 14.
- the intermediate elements 66 are stepped and abut with a radially extending portion on the second part 22, and are received with a tubular portion in a recess 68 on the arm 52 of the flange 36.
- the intermediate element 66 also has a further recess in which the bushes 40 are received in sections. Since both the arm 52 of the flange 36 and the intermediate member 66 and the bushings 40 each have an opening extending through the arm 52, the intermediate member 66 and the bushes 40, a connecting channel 70.
- the connecting channel 70 about the connecting channel 70, the second part 22 of Torsional vibration damper 12, the joint body 14 and the flange 36 connected to each other to transmit torque, in particular by suitable bolts (not shown) are screwed.
- the hinge body 14 is disposed between the receiving portion 24 of the second part 22 and the axially extending portion 58 of the first part 16.
- the joint body 14, like the second part 22, is received in the first part 16 of the Torsionsschw Trent Techgers 12.
- the second part 22 extends radially around the bearing portion 20 of the first part 16 around.
- the torque is transmitted from the flange 36 to the second part 22 of the torsional vibration damper 12 and to the elastic joint body 14. Due to the moment of inertia of the flywheel 18, the flywheel 18 or the first part 16 begins to move with a delay. How large is this delay or the amplitude of the flywheel 18 is largely determined by the rubber-elastic elements 30 and their rigidity and their damping. After this delay, the first part 16 begins to move with the flywheel 18 with the bearing portion 20 on the portion 34 of the flange 36, d. H. The bearing portion 20 slides over the sliding bushing 32 on the portion 34 of the flange 36. Due to the radial mounting of the first part 16 with the bearing portion 20 on the tubular portion 34 of the flange 36 of the Torsionsschwingungstil- ger 12 is very stiff in the radial direction.
- the openings 60 in the radially extending portion 56 of the first part 16 are dimensioned according to the maximum allowable amplitude and the maximum allowable relative angle between the first part 16 and the second part 22.
- a predetermined radial gap s can be seen between the elastic joint body 14 and the section 58 of the first part 16 extending around the joint body 14 in the circumferential direction. This gap is not uniform over the circumference of the joint body 14.
- the dimension s denotes the maximum gap at rest at one of the points along the circumference of the joint body 14, at which the joint body bulges the most during operation under load.
- the predetermined gap s may be dimensioned such that the elastic joint body 14 in the operation of the torque transmission device 10 after exceeding a predetermined speed and / or a predetermined torque at the around the joint body 14 around extending portion 58 of the first part 16 applies.
- the first part 16 is made of plastic or a material with comparable sliding properties and stored directly with its bearing portion 20 as a sliding body on the tubular portion 34.
- FIG. 4 shows a perspective view of a torque transmission device 110 according to a second embodiment of the invention.
- the second embodiment shown in FIG. 4 largely corresponds to the first embodiment described in FIGS. 1 to 3, but a centering sleeve 172 is accommodated in the tubular section 134 of the flange 136.
- the bearing portion 120 of the first part 116 of the Torsionsschwingungstilgers 112 is movably mounted on the Gleitbuchse 132 on serving as a bearing means portion 134 of the flange 136.
- a centering sleeve 172 is provided, which serves for centering a shaft journal (not shown) of a shaft portion of a shaft assembly.
- FIG. 5 shows a top view of the torque transmission device 110, in which the centering sleeve 172 can be seen.
- FIG. 6 shows a sectional view of the torque transmission device 110 along the section line V-V in FIG. 5.
- the centering sleeve 172 can be seen, which is received in the tubular portion 134 of the flange 136.
- the centering sleeve 172 has an outer bush 174 and an inner bushing 176.
- the outer bushing 174 and the inner bushing 176 are connected to each other via an elastic layer 178.
- the elastic layer 178 spans the outer peripheral surface of the inner bushing 176 and the inner peripheral surface of the outer bushing 174 substantially completely.
- the inner sleeve 176 may be made of a plastic and serves to receive a shaft journal of a shaft portion (not shown), which is connected via the torque transmission device 110 with another shaft portion (not shown).
- the elastic layer has a sealing lip 180 which can come into contact with the shaft journal (not shown).
- the centering sleeve 172 is received in an opening 182 in the tubular portion 134 of the flange 136.
- the opening 182 is a blind opening according to this embodiment
- FIG. 7 shows a perspective view of a torque transmission device 210 according to a third embodiment of the invention.
- the bearing portion 220 of the first part 216 and the receiving portion 224 of the second part 222 are tubular. Between the bearing portion 220 and the receiving portion 224, the elastic member 230 extends.
- FIG. 8 shows a plan view of the torque transmission device 210, in which the tubular sections 220 and 224 are recognized.
- the elastic element 230 extends in the form of a vulcanized on either side or both sides vulcanized or flush pressed elastomeric layer, which fills the radial clearance between the bearing portion 220 and the receiving portion 224. According to this embodiment, therefore, a single elastic element 230 is provided, which is in
- Circumferential direction extends in the free space.
- FIG. 9 shows a sectional view of the torque transmission device 210 along the section line VIII-VIII in FIG. 8.
- FIG. 9 shows the tubular bearing section 220 and the tubular receiving section 224 which are connected via the elastic element 230.
- the elastic element 230 spans the inner peripheral surface of the tubular receiving portion 224 and extends to the radial portion 262 of the second part 222.
- the radial portion also covers the elastic member 230 in sections.
- the elastic member 230 thus extends noticeably between the radial portion 256 of the first part 216 and the radial portion 262 of the second part 222.
- FIG. 10 shows a perspective view of a torque transmission device 310 according to a fourth embodiment of the invention.
- the fourth embodiment of the invention largely corresponds to the embodiment shown in Figures 7 to 9, wherein in the portion 334 of the flange 336 in turn a centering sleeve 372 is added
- FIG. 11 shows a top view of the torque transmission device 310, in which the centering sleeve 372 can likewise be seen.
- FIG. 12 shows a sectional view along the section line XI-XI in FIG. 11.
- the opening 380 in the flange 336 is a through-hole.
- the centering sleeve 372 takes the opening 380 in the axial direction of the central axis M completely.
- the centering sleeve 372 has an outer bush 374 and an inner bushing 376, which are connected to each other via an elastic layer 378.
- the elastic layer 378 extends completely along the inner circumferential surface of the outer bushing 374.
- FIG. 13 shows a perspective view of a torque transmission device 410 according to a fifth embodiment of the invention.
- FIG. 13 shows the tubular bearing section 420 and the tubular receiving section 424, between which the elastic element 430 extends.
- the sliding bearing 432 can be seen in the tubular bearing portion 420 of the first part 416.
- FIG. 14 shows a plan view of the torque transmission device 410, in which the sliding bearing 432 can be seen on the inner circumferential surface of the tubular bearing section 420 of the first part 416.
- the sliding bearing according to the fifth embodiment is made stronger in the radial direction.
- FIG. 15 shows a sectional view of the torque transmission device 410 along the section line XIV-XIV in FIG. 14.
- the first part 416 and the second part 422 of the torsional vibration damper 412 can be seen.
- the tubular bearing portion 420 of the first part 416 and the tubular receiving portion 424 of the second part 422 are connected to each other via the elastic member 430.
- the sliding bearing 432 can be seen in the tubular bearing portion 420.
- the sleeve-shaped slide bearing 432 extends from the right in the direction of the axis M end of the tubular bearing portion 420 in the bearing portion 420 and takes slightly more than half of the axia- len extension of the tubular bearing portion 420 a.
- the flange 436 also has a bearing center in this embodiment!
- FIG. 16 shows a perspective view of a torque transmission device 510 according to a sixth embodiment of the invention.
- the sixth embodiment of the invention corresponds as far as possible to the fifth embodiment of the invention shown in FIGS. 13 to 15, wherein within the sliding bearing 532 and within the section 534 of the flange 536 (FIG)
- Centering sleeve 572 can be seen.
- FIG. 17 shows a top view of the torque transmission device 510 in which the centering sleeve 572 rests against the inner circumferential surface of the sliding bearing 532.
- the bearing portion 520 of the first part 516 and the receiving portion 524 of the second part 522 are also tubular in the fifth embodiment of the invention.
- FIG. 18 shows a sectional view of the torque transmission device 510 along the section line XVII-XVII in FIG. 17.
- FIG. 18 shows the centering sleeve 572, which extends along the inner peripheral surface of the sliding bearing or bearing bush 532 and the inner circumferential surface of the tubular section 534 or the opening 580 of the flange 536.
- the tubular bearing portion 520 is therefore on the one hand on the serving as a bearing means tubular portion 534 and mounted on the slide bearing 532 radially on the centering sleeve 572, which also serves as the flange associated bearing means.
- FIG. 19 is a perspective view of a torque transmission device 610 according to a seventh embodiment of the invention.
- the structure of the torque transmission device 610 largely corresponds to the structure of the torque transmission device 10 according to the first embodiment, wherein the flange 636 not shown in Figure 19 is formed differently.
- FIG. 20 shows a top view of the torque transmission device 610 with the elastic joint body 614 and the torsional vibration damper 612 comprising a first part 616 and a second part 622.
- FIG. 21 shows a sectional view along the section line XX-XX in FIG. 20.
- the flange 636 does not have a tubular section but only serves to connect the second part 622 of the torsional vibration damper 612 and the joint body 614.
- the opening 680 in the flange 636 can be seen, which can serve for receiving, for example, a centering sleeve (not shown).
- a centering sleeve not shown
- the sliding bearing 632 is shown on the inner peripheral surface of the bearing portion 620.
- FIG. 22 shows a perspective view of a torque transmission device 710 according to an eighth embodiment of the invention, which largely corresponds to the embodiment shown in FIGS. 19 to 21.
- the centering sleeve 772 can be seen, which serves as a flange 736 associated bearing means.
- the bearing section 720 is mounted on the centering sleeve 772 via the slide bearing 732.
- FIG. 23 shows a plan view of the torque transmission device 710, in which the centering sleeve 772 in the bearing section 720 and the sliding bearing 732 between the bearing section 720 and the centering sleeve 772 can be seen.
- FIG. 24 shows a sectional view along the section line XXIII-XXIII in FIG. 23.
- the flange 736 has the opening 780, in which the centering sleeve 772 is received at least in sections.
- the centering sleeve 772 is a bearing means associated with the flange 736.
- the bearing section 720 is mounted on the centering sleeve 772 by means of the sliding bearing 732 or the bearing bush 732. The bearing portion 720 can thus perform a relative movement on the centering sleeve 772 via the sliding bearing 732.
- FIG. 25 shows a top view of the first part 16 and the second part 22 of the torsional vibration damper 12.
- the first part 16 and the second part 22 according to this embodiment are provided with corresponding profilings.
- projections 80 are provided, which are each offset by 120 ° about the central axis M to each other.
- the protrusions 80 of the second part 22 are received between protrusions 82 on the first part 16, whereby a maximum relative angle between the first part 16 and the second part 22 is adjusted. Once the protrusions 80 abut the second part 22 on one of the protrusions 82 of the first part 16, no further relative rotation between the first part 16 and the second part 22 is possible.
- FIG. 25 also shows the apertures 60 in the radial portion 56 of the first part 16.
- the radial arms 62 of the second part 22 project into the apertures 60, partially overlapping the apertures 60 so as to connect the arms 62 of the second part 22 with the flange (not shown) and the joint body (not shown).
- opening 64 can be seen in which intermediate elements (not shown) can be accommodated.
- FIG. 26 shows a detailed view of the detail X in FIG. 25.
- the projection 80 on the second part 22 and the projections 82 on the first part 16 can be seen.
- the protrusion 80 on the second part 22 extends between the protrusions 82 on the first part, so that the protrusion 80 strikes against one of the protrusions 82 of the first part 16 for limiting the amplitude of the first part 16 at a predetermined relative angle.
- the projections 80, 82 may be in the form of beads when the parts 16, 22 are made of sheet metal.
- FIG. 27 shows a sectional view along the section line XXVI-XXVI in FIG. 26, in which the projections 80, 82 can be seen.
- the projection 80 on the second part 22 is coated here with an elastomer layer 84.
- the protrusions 82 on the first part 16 are coated with an elastic layer or the protrusions 82 and the protrusion 80 with an elastic layer.
- FIG. 28 shows a plan view of a torque transmission device 810 according to a ninth embodiment of the invention.
- the elastic joint body 814 according to this embodiment has a polygonal shape. Unlike the embodiments with a substantially round elastic joint body described above, the elastic joint body 814 according to this embodiment is polygonal.
- the radial distance between the peripheral surfaces of the hinge body 814 and the inner periphery of the first part 816 varies accordingly in the circumferential direction. An impact of the joint body 814 on the first part 816 or the flywheel 818 of the torsional vibration damper 812 can thereby be effectively prevented.
- FIG. 28 also shows a sealing lip 884 which extends in the radial direction as far as the centering sleeve 872.
- FIG. 29 shows a sectional view along the section line XXIX-XXIX in FIG. 28.
- the elastic joint body 814 has thread packages 885 and collar elements 886 which serve to secure the thread packages 885 to the bushings 840.
- the flywheel 818 has on its inner peripheral surface a shoulder 887, against which the end face of the axially extending portion 858 of the first part 816 applies.
- a sealing element or a sealing lip 884 is formed on the elastic element 830.
- the sealing lip 884 spans the at least one bearing element 832 and the end face of the portion 834 of the flange 836 and abuts the end face of the outer bushing 874 of the centering sleeve 872.
- the sealing lip 884 extends in the radial direction in an arc shape from the elastic element 830 to the end face of the outer bushing 874 of the centering sleeve 872.
- FIG. 30 shows an enlarged view of the detail XXX in FIG. 29.
- the sealing lip 884 is clearly visible.
- the sealing lip 884 is formed integrally with the elastic element 830 and extends from the elastic element 830 to the end face of the outer bushing 874.
- the sealing lip 884 spans the bearing element or the sliding bush 832 and the flange section 834 and then lies against the outer bushing 874 on.
- the sealing lip 884 prevents dirt from penetrating between the individual components and impairing the function of the vibration damper 812. This is particularly important in the area of bushing 832, as the dirt is penetrating the track.
- the bearing portion 820 on the slide bush 832 on the portion 834 of the flange 836 may affect.
- FIG. 31 is a plan view of a torque transmission device 910 according to a tenth embodiment of the invention.
- FIG. 32 shows a sectional view along the section line XXXII-XXXII in FIG. 31.
- the first part 916 or the section 958 of the first part 916 has a radially outwardly bent end 988.
- the outwardly bent end 988 is received in a groove 989 in the flywheel 918.
- the flywheel mass 918 and the first part 916 can thus be additionally secured to each other via a positive connection.
- Layer 990 is provided which connects the bearing portion 920 with the sliding bushing 932.
- the elastic layer 990 has a sealing lip 984 extending radially inward.
- the first part 916 according to this embodiment is constructed in two modular units which are interconnected at the joint FS.
- a modular unit is formed by the bearing portion 920, the elastic member 930, the slide bushing 932 and the elastic layer 990.
- the second modular unit is formed by the radial portion 956 and the axially extending portion 958.
- FIG. 33 shows a detailed view of the detail XXXIII in FIG. 32.
- FIG. 33 shows the sealing lip 984, which spans the sliding bushing 932 and abuts against the section 934 of the flange 936.
- the sealing lip 984 is provided on the elastic layer 990, which connects the bearing portion 920 with the sliding bushing 932.
- the sliding bush 932 has recesses 991 which serve to receive dirt between the slide bushing 932 and the
- Section 934 of the flange 936 has penetrated.
- FIG. 34 shows a detailed view of the detail XXXI in FIG. 31.
- the recesses 991 can be seen in the sliding bushing 932, which extend in the axial direction through the sliding bushing 932. Between the sliding bush 991 and the bearing portion 920 is provided with the elastic layer 990 connecting the slide bushing 932 to the bearing portion 920.
- FIGS. 35a to 35c are views of the slide bushing 932 having the recesses 991 extending on the inner circumferential surface of the slide bush 932 in the axial direction and each occupying a predetermined portion of the inner peripheral surface of the slide bush 932.
- FIG. 36 shows a perspective view of the first part 916 in the separated state of the two modules Mi and M 2 .
- the module Mi is formed by the bearing portion 920, the elastic member 930 and the slide bush 932.
- the elastic member 930 is formed by a plurality of radially extending projections and a layer connecting these projections. This also applies to the embodiment described above.
- the slide bush 932 is connected to the inner periphery of the bearing portion 920 via the elastic layer (not shown in FIG. 36).
- the module Mi has a joining surface FFi, which is formed by an end face of the bearing section 920.
- the module M 2 is formed by the radially extending portion 956 and the axially extending portion 958 of the first part 916. At the portion 958 of the radially outwardly bent end portion 988 can be seen.
- the radially extending portion 956 has an opening 992 around which the joining surface FF 2 extends radially.
- the first module Mi and the second module M 2 can be interconnected.
- the connection between the modules Mi and M 2 can be made for example by welding.
- Figure 37 shows a perspective view of the first part 916 with the modules Mi and M 2 in the connected state.
- the two modules i and M 2 were connected to one another at their joining surfaces FFi and FF 2 (see FIG. 36), the joining surfaces FFi and FF 2 forming the joint FS.
- FIG. 38 shows a top view of the first part 916 in the connected state of the two modules Mi and M 2 .
- FIG. 39 shows a sectional view along the section line XXXIX-XXXIX in FIG. 38.
- the first module Mi is formed by the bearing portion 920, the elastic member 930, the sliding bush 932, and the elastic layer 990.
- the elastic layer 990 connects the sliding bush 932 to the bearing portion 920 and has a sealing lip 984 extending radially inward.
- the second module M 2 is again formed by sections 956 and 958. The two modules Mi, M 2 were connected at their respective joining surfaces FFi and FF 2 , whereby the joint FS is formed.
- the individual components of the module i are connected via vulcanization. As a result, subsequent work steps, such as the press-fitting of the slide bushing 932 can be omitted.
- FIGS. 40 and 41 show perspective sectional views of a torsional vibration absorber 1012 according to an eleventh embodiment of the invention.
- the torsional vibration damper 1012 comprises an annular first part 1016 on which the flywheel 1018 and a bearing section 1020 are arranged, and a second part 1022.
- the first part 1016 and the second part 1022 are connected to one another via an elastic element 1030.
- the second part 1022 includes a receiving portion 1024 through which the bearing portion 1020 of the first part 1016 extends.
- a plain bearing bushing 1032 is provided in the bearing portion 1020 of the first part 1016 of the torsional vibration damper 1012.
- the plain bearing bushing 1032 is disposed between the bearing portion 1020 and a bearing means portion 1034 of a flange 1036.
- the first part 1016 has a radially extending portion 1056 connected to an axially extending portion 1058.
- the flywheel 1018 is provided.
- An inclined portion of the first part 1016 extends between the radially extending portion 1056 and the tubular bearing portion 1020.
- openings 1060 are formed, which connect the arms 1052 of the flange 1036 with the second Allow part 1022.
- the second part 1022 has sections extending in the radial direction 1062, which at least partially project into the openings 1060 and are themselves provided with openings 1064.
- the openings 1064 receive intermediate elements 1066 which serve to connect the flange to the second part 1022.
- the elastic member 1030 extends inter alia between a slanted portion 1093 of the first part 1016 and an oblique portion 1094 of the second part 1022.
- a centering sleeve 1072 is received in the tubular portion 1034 of the flange 1036.
- Figure 42 shows a top view of the torsional vibration damper 1012, in which the first part 1016, the second part 1022 and the centering sleeve 1072 can be seen.
- the second part 1022 has three sections extending in the radial direction 1062, each of which has the intermediate elements 1066 at their radial ends.
- the radial portions 1062 of the second portion 1022 project into the openings 1060 in the radially extending portion 1056 of the first portion 1016.
- FIG. 43 shows a sectional view along the section line XLIII-XLIII in FIG. 42.
- the first part 1016 has, between the bearing portion 1020 and the radially extending portion 1056, the portion 1093 extending obliquely to the center axis M.
- the second part 1022 has a portion 1094 extending at an angle to the center axis M, which is provided between the receiving portion 1024 and the receiving opening 1024 and the radially extending portions 1062, respectively.
- the elastic element 1030 is arranged, which extends between the inclined sections 1093 and 1094 and at least in sections between the radially extending sections 1056 and 1062 of the first part 1016 and the second part 1022 extends.
- the flange 1036 also has an inclined surface 1095, which is adapted in inclination to the inclination of the inclined portions 1093 and 1094 of the first part 1016 and the second part 1022.
- FIG. 44 shows a detailed view of the detail XLIV in FIG. 43.
- the inclined portions 1093 of the first part 1016 and 1094 of the second part 1022 can be seen, between which the elastic element 1030 extends.
- the elastic member 1030 extends radially outward along the radially extending portions 1062 of the second part 1022, ie, projects into the openings 1060 of the first part 1016.
- FIGS. 45 and 46 show views of a torque transmission device 1010 with the torsional vibration damper 1012 according to FIGS. 40 to 44 and a joint body 1014 which may be formed according to the joint bodies according to FIGS. 24, 29 and 32.
- FIGS. 47 and 48 show perspective sectional views of a torsional vibration absorber 1112 according to a twelfth embodiment of the invention.
- the second part 1122 is completely between the flange 1036 and the first part 1116.
- the second part 1122 has radially extending portions 1162.
- the first part 1116 has radially extending portions 1158.
- the elastic member 1130 is provided, which also extends in the radial direction.
- the bearing portion 1120 is supported on the flange portion 1134 via a plain bearing bushing 1132.
- FIG. 49 is a plan view of the torsional vibration absorber 1112 according to the twelfth embodiment.
- the second part 1122 is arranged behind the first part 1116 or on the rear side of the first part 1116.
- the radially extending portions 1162 of the second part 1122 protrude into the openings 1160 in the radial portion 1156 of the first part 1116.
- the intermediate elements 1166 are provided.
- FIG. 50 shows a sectional view along the section line L-L in FIG. 49.
- the second part 1122 is provided in the axial direction of the center axis M between the flange 1136 and the first part 1116. In the axial direction, the following arrangement follows from left to right accordingly: Flange 1136, second part
- the elastic member 1130 is provided between the radially extending portion 1162 of the second part 1122 and the radially extending portion 1156 of the first part 1116.
- the second part 1122 is arranged according to this embodiment on the side facing away from the bearing portion 1120 side SA of the first part 1116.
- FIG. 51 shows a detailed view of the detail LI in FIG. 50.
- the radial portion 1162 of the second part 1122 and the radial portion 1156 of the first part 1116 extend parallel to each other in the radial direction. Between the two radial sections 1156 and 1162, the elastic element 1130 is provided.
- Figures 52 and 53 show views of a torque transmitting device 1110 having a torsional vibration damper 1112 shown in Figures 47 to 51 and a resilient hinge body 1114.
- the resilient hinge body 1114 may be of the type disclosed in Figures 24, 29 and 32.
- the flywheel 18 of the Torsionsschwi- ubenstilgers 12 unlike the prior art - not radially supported by the elastic elements, but on the bearing portion 20 directly on a flange associated with the bearing means, i. a tubular portion 34 of the flange 36 or a centering sleeve 72 radially mounted.
- the torsional vibration damper according to the invention has a high radial rigidity and is significantly less susceptible to imbalances in the drive train than the prior art.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Mechanical Operated Clutches (AREA)
- Motor Power Transmission Devices (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201480059360.7A CN105705826B (zh) | 2013-09-04 | 2014-08-29 | 扭转振动缓冲器 |
US14/916,542 US20160195160A1 (en) | 2013-09-04 | 2014-08-29 | Torsional vibration damper |
DE112014004037.1T DE112014004037A5 (de) | 2013-09-04 | 2014-08-29 | Torsionsschwingungstilger |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201310014717 DE102013014717A1 (de) | 2013-09-04 | 2013-09-04 | Torsionsschwingungstilger |
DE102013014717.4 | 2013-09-04 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2015032691A1 true WO2015032691A1 (de) | 2015-03-12 |
WO2015032691A8 WO2015032691A8 (de) | 2015-05-14 |
Family
ID=51662052
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2014/068327 WO2015032691A1 (de) | 2013-09-04 | 2014-08-29 | Torsionsschwingungstilger |
Country Status (4)
Country | Link |
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US (1) | US20160195160A1 (de) |
CN (1) | CN105705826B (de) |
DE (2) | DE102013014717A1 (de) |
WO (1) | WO2015032691A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015117785A1 (de) | 2015-10-19 | 2017-04-20 | Vibracoustic Gmbh | Wellenkupplung |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3036153B1 (fr) * | 2015-05-12 | 2017-06-09 | Messier Bugatti Dowty | Galet d'entrainement. |
DE102016201352B4 (de) * | 2016-01-29 | 2017-09-07 | Borgward Trademark Holdings Gmbh | Ein Fahrzeug und eine Übertragungsvorrichtung |
US10677312B2 (en) * | 2018-02-15 | 2020-06-09 | General Electric Company | Friction shaft damper for axial vibration mode |
RU184758U1 (ru) * | 2018-06-29 | 2018-11-07 | Федеральное государственное бюджетное образовательное учреждение высшего образования "Казанский национальный исследовательский технический университет им. А.Н. Туполева-КАИ" (КНИТУ-КАИ) | Адаптивный гаситель крутильных колебаний |
DE102018010053A1 (de) * | 2018-12-19 | 2020-06-25 | Siemens Mobility GmbH | Kupplungsvorrichtung |
US10955026B2 (en) * | 2019-03-21 | 2021-03-23 | Optimized Solutions, LLC | Arcuate common vertex and dual arcuate common vertex spring damper systems |
CN109780134A (zh) * | 2019-03-22 | 2019-05-21 | 苏州辉美汽车科技有限公司 | 一种双质量飞轮 |
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GB2258713A (en) * | 1991-08-07 | 1993-02-17 | Luk Lamellen & Kupplungsbau | An elastic coupling with viscous damping for a belt drive pulley |
DE102008051352A1 (de) * | 2008-10-15 | 2010-04-22 | Carl Freudenberg Kg | Schwingungstilger |
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US2512735A (en) * | 1945-08-17 | 1950-06-27 | Schwitzer Cummins Company | Vibration dampener |
US3059499A (en) * | 1960-03-31 | 1962-10-23 | Gen Motors Corp | Flexible flywheel |
DE2534684C2 (de) * | 1975-08-02 | 1982-08-26 | Daimler-Benz Ag, 7000 Stuttgart | Einrichtung zur Schwingungsdämpfung im Antriebsstrang von Fahrzeugen |
DE4307583C1 (de) | 1993-03-10 | 1993-12-09 | Sgf Gmbh & Co Kg | Drehschwingungstilger, insbesondere für den Antriebsstrang von Kraftfahrzeugen |
DE4430036C1 (de) | 1994-08-24 | 1995-08-24 | Sgf Gmbh & Co Kg | Drehschwingungstilger, insbesondere für den Antriebsstrang von Kraftfahrzeugen |
US5875752A (en) * | 1996-11-13 | 1999-03-02 | Cummins Engine Company, Inc. | Engine drive train having a front gear train with improved torsional dynamics |
EP1503103B1 (de) * | 2003-07-28 | 2006-09-20 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Drehschwingungsdämpfer |
EP1744074A3 (de) * | 2005-07-11 | 2008-10-01 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Drehmomentübertragungseinrichtung |
DE102005055800B4 (de) * | 2005-11-21 | 2008-01-03 | Carl Freudenberg Kg | Vorrichtung zur Dämpfung von Torsionsschwingungen und Anordnung |
DE102008056918B4 (de) | 2008-11-12 | 2012-11-08 | SGF SüDDEUTSCHE GELENKSCHEIBENFABRIK GMBH & CO. KG | Schwingungstilger |
DE102008043781A1 (de) * | 2008-11-17 | 2010-05-20 | Zf Friedrichshafen Ag | Torsionsschwingungsdämpfer für den Antriebsstrang eines Fahrzeugs |
JP6269244B2 (ja) * | 2014-03-27 | 2018-01-31 | アイシン精機株式会社 | ダンパ装置 |
-
2013
- 2013-09-04 DE DE201310014717 patent/DE102013014717A1/de not_active Withdrawn
-
2014
- 2014-08-29 WO PCT/EP2014/068327 patent/WO2015032691A1/de active Application Filing
- 2014-08-29 CN CN201480059360.7A patent/CN105705826B/zh not_active Expired - Fee Related
- 2014-08-29 US US14/916,542 patent/US20160195160A1/en not_active Abandoned
- 2014-08-29 DE DE112014004037.1T patent/DE112014004037A5/de not_active Withdrawn
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2258713A (en) * | 1991-08-07 | 1993-02-17 | Luk Lamellen & Kupplungsbau | An elastic coupling with viscous damping for a belt drive pulley |
DE102008051352A1 (de) * | 2008-10-15 | 2010-04-22 | Carl Freudenberg Kg | Schwingungstilger |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015117785A1 (de) | 2015-10-19 | 2017-04-20 | Vibracoustic Gmbh | Wellenkupplung |
WO2017067890A1 (de) | 2015-10-19 | 2017-04-27 | Vibracoustic Gmbh | Wellenkupplung |
DE102015117785B4 (de) | 2015-10-19 | 2019-04-11 | Vibracoustic Gmbh | Wellenkupplung |
Also Published As
Publication number | Publication date |
---|---|
CN105705826B (zh) | 2017-07-21 |
DE102013014717A1 (de) | 2015-03-05 |
CN105705826A (zh) | 2016-06-22 |
DE112014004037A5 (de) | 2016-06-23 |
WO2015032691A8 (de) | 2015-05-14 |
US20160195160A1 (en) | 2016-07-07 |
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