WO2010060626A1 - Drehmomentübertragungsvorrichtung - Google Patents
Drehmomentübertragungsvorrichtung Download PDFInfo
- Publication number
- WO2010060626A1 WO2010060626A1 PCT/EP2009/008439 EP2009008439W WO2010060626A1 WO 2010060626 A1 WO2010060626 A1 WO 2010060626A1 EP 2009008439 W EP2009008439 W EP 2009008439W WO 2010060626 A1 WO2010060626 A1 WO 2010060626A1
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- WIPO (PCT)
- Prior art keywords
- transmission
- segment
- torque
- joint
- sections
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
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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
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/10—Couplings with means for varying the angular relationship of two coaxial shafts during motion
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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
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
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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
- F16D3/64—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts
- F16D3/68—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts the elements being made of rubber or similar material
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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
- F16D3/70—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged in holes in one coupling part and surrounding pins on the other coupling part
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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
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22313—Details of the inner part of the core or means for attachment of the core on the shaft
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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
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member
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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
- F16D2300/00—Special features for couplings or clutches
- F16D2300/22—Vibration damping
Definitions
- the torque transfer device The torque transfer device
- the present invention relates to a torque transmitting device for transmitting torques between two shaft portions of a shaft assembly via a hinge assembly, wherein the hinge assembly is adapted to compensate for angular misalignment between the shaft portions.
- Such devices are known in the art in the form of cardan joints or ball joints, such as, e.g. Ball joints, Kugelretemaschinendmaschinenken and homokinetic joints, known.
- Universal joints have two connectable with one shaft joint forks, which can be coupled together via a hinge part.
- Universal joints are usually used in shaft assemblies in which torques are transmitted via a plurality of shafts which do not run parallel or which are offset by an optionally variable angle to each other.
- Universal joints are used in particular for cardan shafts for transmitting drive forces and steering forces in motor vehicles.
- the elastic damping layer attached to the radial surfaces of the projections of the inner part and the corresponding surfaces of the projections of the outer part, i. the damping layer connects the outer part and the inner part, is subjected to strong shear on these radial surfaces.
- the elastic layer can be sheared off either from the inner part or the outer part with this joint arrangement requiring a relatively large amount of space, whereby the function of the joint arrangement, namely the damping of vibrations, becomes impossible.
- DE 41 16 841 Al discloses a hinge connection between a drive bevel gear and a propeller shaft, which has a two-part flange.
- the flange consists of a first flange part associated with the drive bevel gear and a second flange part assigned to the drive shaft.
- the second flange part is designed as an inner ring, which is formed by the first flange designed as an outer ring. Part is enclosed concentrically with radial distance.
- the connection of the second flange with the propeller shaft via a homokinetic joint.
- the second flange part is connected to the homokinetic joint via a screw.
- a torque is transmitted from the drive shaft to the drive pinion via the elastic arranged between the two flange parts
- the first flange part has for this purpose an internal toothing and on the inner ring of the second flange part a corresponding external toothing is formed.
- the elastic intermediate layer is subjected to extreme shearing, resulting in the torque transmission to a shearing of the intermediate layer either on the outer ring of the first flange or the inner ring of the second flange and adversely affects both the function and the life of the joint assembly.
- the joint arrangement according to DE 41 16 841 A1 has a relatively complex construction with a plurality of individual parts.
- a radially outward component of the homokinetic joint is screwed to the inner second flange part.
- the large number of individual parts and also screw connection between the homokinetic joint and the flange part considerably increase the susceptibility to error of this joint arrangement.
- a torque transmission device of the type described above wherein the torque transmission device comprises a vibration damping device for damping torsional vibrations comprising at least two transmission parts, wherein one of the transmission parts is assigned to one of the shaft sections and the respective other transmission part of the joint arrangement, and wherein the transmission parts in each case have segmental formations with radial segment sections which come into torque-transmitting interaction with one another in a transmission area, at least one damper arrangement which is essentially stressed by pressure being provided between adjacent segment sections in the transmission area.
- the torque transmission device according to the invention not only angular offsets between two shaft sections to be connected can be compensated, but also torsional vibrations occurring during operation of a drive train can be damped.
- the torque transmission device according to the invention requires relatively little space, which is only very limited available in the field of a drive train of a motor vehicle.
- angular misalignments and torsional vibrations can be damped, whereby torques are transmitted almost lossless and transmission of resulting on the drive axle structure-borne sound through the vehicle i5 is avoided.
- the inventive design with interlocking segment formations and arranged therebetween damper arrangements can be achieved that the damper assembly are almost exclusively subjected to pressure, which extends the life of the device according to the invention. Life shortening shear stresses, as they occur in the prior art, are avoided by the device according to the invention.
- a further development of the invention provides that the segment formations of the at least two transmission parts can be brought into engagement with one another in the radial direction for torque transmission.
- two adjacent segment sections one of which is assigned to one transmission part and the other to the respective other transmission part, are connected to one another.
- the two transmission parts it is conceivable, for example, for the two transmission parts to be connected to one another via the damper arrangement, wherein the damper arrangement is only subjected to pressure in the load case. 5
- the adjacent segment sections are provided in pairs by means of at least one deformable loop. are bound.
- the torques are transmitted not only via a meshing of the segment sections of the transmission parts (pressure load), but also via a connection between two adjacent segment sections by a train loaded loop.
- the torques are transmitted via a tensile force and a compressive force of the one transmission part, which is driven, to the respective other output side transmission part.
- segment sections In connection with the embodiment described above, it can be provided with regard to the structural design of the segment sections that they have at least two projections which are each looped around by a loop for connecting one of the segment sections of a segment formation with an adjacent segment section of the respective other segment formation.
- the loop may be made of rubber and / or a thread layer, preferably of a rubber with a thread insert.
- one of the transmission parts in the transmission region has a segment formation with radially inwardly directed segment sections and the respective other transmission part has a segment formation with radially outwardly directed segment sections, wherein the segment formations engage each other.
- the transmission parts can be arranged one above the other in the radial direction, the one radially outer transmission part having the inwardly directed segment sections and the radially inner transmission part having the outwardly directed segment sections.
- the damper arrangement at least partially surrounds the segment formations in the transmission region.
- the segment portions of the segment formations are thus surrounded by the damper assembly, which is elastically deformed during the torque transmission from the mutually engaged segment sections until the individual adjacent segment sections almost abut each other.
- the damper assembly is deformed more elastically, thereby achieving a progressive damping characteristic.
- the damper assembly may further be provided according to the invention that it has at least one damping material layer, in particular a rubber layer or a plastic layer between the engageable segment formations of the transmission parts.
- the damper arrangement according to the invention may also be formed in multiple layers, wherein at least one layer of a further material is arranged in addition to the at least one damping material layer.
- a further material layer in particular a plastic layer, can be provided between the segment formations coated with a damping material layer.
- the hinge assembly has a receiving opening with an inner profiling, preferably an internal toothing, for non-rotatable Having connected to one of the shaft portions, wherein the respective inner profiling associated shaft portion has a corresponding outer profile, in particular an outer toothing, and wherein the shaft portion is received axially displaceable with the outer profile in the receiving opening with an inner profiling.
- an inner profiling preferably an internal toothing
- the torques to be transmitted are transmitted via a form fit between the inner profiling of the receiving opening of the joint assembly and the corresponding thereto external profiling of one of the shaft sections, whereby the corresponding shaft portion is slidably received in the joint assembly to compensate for axial movements.
- the at least two transmission parts in the transmission region are surrounded by a housing which is connected to at least one of the transmission parts connected is. Since installation space is available only to a limited extent in the drive train of a motor vehicle, according to one embodiment the vibration damping device at least partially surrounds the articulation arrangement.
- the vibration damping device can be arranged on the outer circumference of the joint arrangement. Because of the limited space available, especially in the axial direction of the drive train of a motor vehicle, the vibration damping device is preferably arranged in the radial direction on the outside of the joint assembly, whereby the space required by the joint assembly in the radial direction by the Schwingungsdämp- tion arrangement remains almost the same or only slightly increased.
- the joint assembly is a ball joint.
- the vibration damping device is rotatably connected to a housing part of the ball joint.
- the transmission parts for torque transmission in the coupling region take on each other axially overlapping, wherein one of the shaft sections is axially slidably received in the ball joint.
- the arrangement of the ball joint on the Drehmomentübertragungseinrich- device not only angular offsets between two shaft sections to be joined can be compensated, but by the axially displaceable receiving one of the shaft sections in the ball joint and axial aggregate movements due to the occurring in the drive train of a motor vehicle shocks and shocks are compensated , whereby the life of the joint itself and the connected transmission device and the following components is increased.
- a ball-and-socket joint has an inner hub for fastening or receiving one of the shaft sections, which hub may be in the form of a ball star. Therefore, a preferred embodiment of the invention provides that the receiving opening is formed with the inner profiling in the ball star.
- the ball star is coupled in a torque-transmitting manner to the housing of the ball joint by means of a ball arrangement, the balls being arranged such that the ball star and the shaft section axially displaceable in the receiving opening relative to Longitudinal axis of the other shaft portion are displaced.
- the ball arrangement enables a torque transmission between two shaft sections offset by an angle of up to 40 ° with respect to one another.
- shielding elements in particular of rubber, are provided between the ball star and housing parts of the ball joint.
- the ball joint is non-rotatably connected to one of the transmission parts, preferably welded or pressed, and the other section fixed to the other transmission part connected is.
- the two transmission parts in the coupling region are substantially uniform, wherein the transmission parts each with a damper device, preferably a rubber layer, are provided.
- a positioning pin is provided between the transmission parts in the coupling region, whereby the device can be braced axially by the positioning pin.
- a positioning pin can position the two transmission parts in the coupling region relative to each other, in particular align with respect to the longitudinal axis substantially coaxially to each other.
- the positioning pin can, albeit to a limited extent, a kind Joint function take over, if the two transmission parts in. Operation not coaxial, but offset or angled run to each other.
- an embodiment of the invention further provides that the joint arrangement is a universal joint.
- the vibration damping device according to an embodiment of the invention is at least partially arranged in a plane spanned by joint axes of the universal joint on the outer circumference of the universal joint.
- the segment formations are produced by deep-drawing processes, forging or machining processes.
- the invention further relates to a shaft arrangement with a torque transmission device of the type described above.
- Fig. 1 is a perspective view of a torque transmitting device according to a first embodiment of the invention
- Fig. 2 is a partially cutaway front view of the torque transmitting apparatus according to the first embodiment of the invention
- Fig. 3 is a sectional view taken along the section line IMI of Fig. 2;
- FIG. 4 is a perspective view of a torque transmitting device according to a second embodiment of the invention.
- Fig. 5 is a partially broken front view of the torque transmission device according to the second embodiment of the invention.
- Fig. 6 is a sectional view taken along section line V-V of Fig. 5; 5
- FIG. 7 is a perspective view of a torque transmission device according to a third embodiment of the invention.
- Fig. 8 is a partially cutaway front view of the torque transmission device according to the third embodiment of the invention.
- FIG. 9 is a sectional view taken along section line VIII-VIII of FIG. 8; FIG.
- FIG. 10 is a perspective view of a torque transmission device according to a fourth embodiment of the invention.
- Fig. 12 is a sectional view taken along section line XI-XI of Fig. 11;
- FIG. 13 shows a perspective view of a torque transmission device according to a fifth embodiment
- FIG. 1 My perspective view of the torque transmission device according to the fifth embodiment without housing
- FIG. 15 is a partially planed front view of the torque transmission device according to the fifth embodiment.
- 16 is a sectional view taken along section line XV-XV of FIG. 15.
- 17 is a perspective view of the torque transmission device according to a sixth embodiment of the invention.
- FIG. 18 is a partially broken front view of the torque transmission device according to the sixth embodiment.
- FIG. 19 is a sectional view taken along the section line XVI-XVI of FIG. 18.
- FIG. 20 is an axially-contained sectional view of a seventh embodiment of the torque transmission device.
- Fig. 1 shows a perspective view of the torque transmission device 10 according to the first embodiment of the invention. From Fig. 1 can be seen in that the torque transmission device 10 has a joint arrangement 12 which is surrounded on its outer circumference by a vibration damping device 14 (FIGS. 2 and 3).
- the hinge assembly 12 according to the first embodiment of the invention 10 is a ball joint, which will be explained in detail with reference to Figures 2 and 3.
- the torque transmission device 10 or the ball joint 12 has a receiving opening 16 with an inner profiling 18.
- FIG. 2 shows a partially cutaway front view of the torque transfer device 10 according to the first embodiment of the invention
- FIG. 3 shows a sectional view along the section line IHI of FIG. 2.
- the hinge assembly 12 is designed in the form of a ball joint, on the outer circumference in the radial direction of the vibration damping device 14 is arranged.
- the ball-and-socket joint 12 has an inner hub 20 in the form of a spherical star, in which the receiving opening 16 is provided.
- the inner profiling 18 is formed, preferably in the form of an internal toothing.
- the internal toothing 18 is preferably made by broaching or milling, i. using cost-effective but highly precise operations.
- the ball star 20 has on its outer peripheral surface of wells in which balls 22 are received. About these balls 22 of the ball star 20 is coupled torque transmitting to a housing part 24.
- a cage 26 which is arranged between the ball star 20 and the housing part 24, it is possible to compensate for angular misalignments of up to 40 ° between two shaft sections (not shown) via the device 10.
- the vibration damping device 14 has two transmission parts 28 and 30, of which the transmission part 30 is fixedly connected to the housing part 24 of the ball joint 12.
- the two transmission parts 28 and 30 are at least partially surrounded by a housing 32.
- the transmission part 28 is connected via a friction-reducing plastic ring 33 to the housing 32 relatively rotatably connected, whereas the transmission part 30 is rotatably connected to the housing 32.
- the housing part 24 and the transmission part 30 are designed as one part, for example in the form of a part made by forging. As can further be seen from a comparison of FIGS.
- the transmission parts 28 and 30 overlap in a transmission region 34 in the axial direction, wherein they have corresponding segment formations 36 and 38 in this transmission region 34.
- the segment formations 36 and 38 each have a plurality of segment sections, of which only the segment section 40 of the segment formation 36 and the segment section 42 of the segment formation 38 are shown in FIG. 3 again shows the segment section 40 of the segment formation 36 of the transmission part 28 as well as the segment section 42 of the segment formation 38 of the transmission part 30.
- damper arrangement 44 which is loaded essentially with pressure (FIG. 2), which at least partially surrounds the segment formations 36 and 38.
- Damper assembly 44 is multi-layered, i. the individual segment formations 36 and 38 are coated with a damping material layer 46 and 48, preferably a rubber layer, and between these two layers 46 and 48 a further material layer 50, preferably of plastic, is provided.
- the transmission part 28 is driven by a motor shaft section connected to this transmission part 28, whereby the segment formation 36 of the transmission part 28 is displaced relative to the segment formation 38 of the transmission part 30 under elastic deformation of the damper arrangement 44.
- the material layers 46, 48 and 50 of the damper assembly 44 are elastically deformed via the interengaging segment sections 40, 42 of the transmission members 28, 30 under compressive load until the individual adjacent segment sections 40, 42 are nearly in contact with each other, i. the higher the torque to be transmitted, the more the damper assembly is elastically deformed. Since the transmission part 30 is rotatably connected to the housing part 24 of the ball joint 12, the torque is transmitted via the transmission part 30 to the ball joint 12 and thus via the internal teeth 18 on a shaft portion, not shown, in the receiving opening 18.
- the vibration damping device 14 sufficiently dampens the vibrations and torsional vibrations occurring in a drive train through the damper arrangement 44 between the segment formations 36 and 38 of the transmission parts 28 and 30 in order not to transmit a structure-borne noise arising at the drive shaft through the vehicle, with torques essentially transmitted directly between the two shaft sections.
- the segment formations 36, 38 according to the first embodiment of the invention are preferably produced by means of a deep-drawing process, which due to the relatively thin material cross-sections a vibration damping device 14 is achieved with low weight, which increases the weight of a conventional ball joint 12 only slightly
- the shielding element 52 extends over the entire inner diameter of the transmission part 28, whereas the rubber-made shielding element 54 is provided between the ball stud 20 and the transmission part 30. Shields 52 and 54 are intended to prevent debris or possibly friction-abraded particles from entering ball-end joint 12 or migrating outwardly from ball-and-socket joint 12 toward other powertrain components in a motor vehicle.
- Figs. 4 to 6 show a second embodiment of the invention which is relatively similar to the embodiment according to Figs. 1 to 3.
- the reference signs of the individual embodiments for identical or equivalent components are preceded by a respective consecutive number.
- the embodiment according to the figures. 4 to 6 differs from the first embodiment according to the figures. 1 to 3 only in that the inner hub or the ball star 120 of the ball joint joint 112 has a receiving opening 116 in the form of a through hole.
- an inner profiling 118 is formed in the form of an internal toothing.
- both shielding elements 152 and 154 are formed from rubber and the shielding element 152 is arranged between the ball star 120 and the transmission part 128 is. Otherwise, all the components with the corresponding components of the first embodiment according to the figures. 1 to 3 comparable, which is why a detailed description of these components is omitted to avoid repetition.
- a shaft section (not shown here) with an external toothing corresponding to the internal toothing 116 is received in an axially displaceable manner, whereas the other shaft section is fixedly connected to the transfer part 128.
- Torques can be transmitted via the ball joint or the torque-transmitting coupling of the ball star 120 by means of the balls 22 to the housing part 124 via the two shaft sections, which may be angled away from each other. In operation, torques are transmitted by a form fit between the inner teeth 118 and the outer teeth of the shaft portion.
- this connection between the inner toothing 118 and the corresponding outer toothing makes it possible, in addition to the transmission of torque, to compensate axial aggregate movements by means of the shaft section displaceable in the receiving opening 116. These axial aggregate movements thus have no effect on the torque transmission device 110 or the ball joint 112 and on the components following in a drive train.
- the function of the damping device 114 is identical to the function of the damping device 14, which has been described in detail with reference to the embodiment according to Figures 1 to 3.
- FIG. 7 shows a perspective view of the torque transmission device 210 according to the third embodiment of the invention.
- the hinge assembly 212 according to the third embodiment is a universal joint.
- the vibration damping device 214 is arranged at one axial end of the universal joint 212.
- the universal joint 212 comprises an outer joint part 256, also called a joint fork, and an intermediate member 258 arranged in this joint part 256, in which the inner joint part 260 is again arranged.
- bearing openings 262 are formed, through which the intermediate member 258 is coupled to the bearing holes 262 corresponding bearing pin 264 to the yoke 256.
- the intermediate member 258 has an offset to this pair of bearing pins 264 pair of bearing openings 266, through which the inner joint part 260 can be coupled to the bearing holes 266 corresponding bearing pin 268 to the intermediate member 258.
- the bearing openings 262 of the yoke 256 and the corresponding bearing pin 264 of the intermediate member 258 define a first hinge axis A and the bearing openings 266 of the intermediate member 258 define together with the bearing pin 268 of the inner joint part 260 a second hinge axis B.
- the two hinge axes A, B pass through the intermediate member 258.
- FIG. 7 it is further possible to see, as in the embodiments according to FIGS. 1 to 5, a receiving opening 216 formed in the inner joint part 260 and an inner profiling 218 formed in the receiving opening 216.
- FIG. 8 shows a partially broken front view of the torque transmitting device 210.
- FIG. 8 again shows that the bearing openings in the yoke 256 and the bearing pins 264 of the intermediate member 258 define a first hinge axis A.
- the bearing openings 266 of the intermediate member 258 and the bearing pins 268 of the inner joint part 260 define a second joint axis B.
- the two hinge axes A, B pass through the intermediate member 258 and cross each other.
- the basic function of the universal joint 212 is achieved, namely the transmission of torque between mutually angled shaft sections, i. a torque transmission with cardanic loads.
- the vibration damping device 214 which is identical to the vibration damping device according to the first two embodiments, can be seen.
- FIG. 9 shows a sectional view along the section line VIII-VIII from FIG. 8.
- the joint fork 256 with the bearing openings 262 and the intermediate element 258 with the bearing pins 264 which form the joint axis A, can be seen again from FIG.
- bearing bushes 270 are arranged on the bearing opening / bearing bolt pairs, here only the pair 262 and 264 are shown. By the bearing bushes 270 friction effects between the bearing openings 262, 266 and the bearing pins 264, 268 avoided.
- the receiving opening 216 is formed in the inner joint part 260 in the form of a through hole.
- a shaft portion (not shown) can be slidably received in the direction of a longitudinal axis.
- outer profile forming a torque can be transmitted by a positive connection between the internal teeth 218 and the outer teeth corresponding to this at one of the shaft sections.
- the internal toothing 218 allows an axially displaceable reception of the shaft section in the receiving opening 216 and at the same time a torque transmission by a positive connection between the internal toothing 218 and an outer toothing corresponding to this on one of the shaft sections.
- an axial end section 271, on which the vibration damping device 214 is arranged, is formed at one end of the yoke fork 256 of the universal joint o 212.
- FIG. 8 shows the segment sections 240 of the segment formation 236 of the transmission part 228 and the segment section 242 of the segment formation 238 of the transmission part 230.
- a damper arrangement 244 is provided of two rubber layers 246, 248 surrounding the segment formations 236, 238 and a further material layer 250, in particular made of plastic, arranged between these two rubber layers 246 and 248.
- the transmission member 230 is rotatably connected to the axial end portion 271 of the cross joint ⁇ 212th In operation, the torque transmission device 210 If one of the transmission parts 228 or 230 is driven by a shaft section and transmits the torque under a deformation of the damper arrangement 244 to the respective other transmission part 228 or 230 and thus also via the universal joint 212.
- the damper arrangement 244 prevents rotation
- Vibrations and vibrations that occur in a drive train in a motor vehicle are transmitted as structure-borne noise through the vehicle or to other components in the drive train.
- the damper assembly 244 it is possible to set a progressive damping characteristic, i. the higher the torques to be transmitted, the stronger the damper arrangement 244 is compacted, whereby high torques can be transmitted almost without loss between the two transmission parts 228 and 230.
- FIG. 10 shows a perspective view of the torque transmission device 310.
- the joint arrangement 312 according to the fourth embodiment is again formed by a universal joint, however
- Vibration damping assembly 314 mounted in the fourth embodiment of the invention directly to the outer periphery of the universal joint 312, so that the axial length compared to the embodiment of FIGS. 7 to 9 is considerably smaller.
- FIG. 11 is a partially cutaway front view of the torque transmission device 310 with the universal joint 312 and the vibration damping device 314, and FIG. 12 is a sectional view taken along the line XI-XI of FIG. 11.
- FIG. 11 is a comparative view shows that the vibration damping device 314 is disposed directly on the outer circumference of the yoke 356 of the universal joint 312 and rotatably connected to the yoke 356. In other words, the vibration damping device 314 lies at least partially in a plane spanned by the joint axes A, B of the universal joint 312 0.
- the transmission part 328 surrounds the transmission part 330, ie is arranged radially outside the transmission part 330.
- the transmission part 330 is non-rotatably connected to the yoke 356 of the cross-joint 312 and is enclosed as a radially inward transmission part 330 of the radially outer transmission part 330 in the transmission region 334.
- Fig. 11 shows that the effetsu ⁇ gstei! 328 has a longitudinal formation 336 with inwardly directed segment sections 340, whereas the transmission part 330, which is arranged on the yoke 356, has a segment formation 338 with radially outwardly directed segment sections 342.
- a damper arrangement 344 which, in addition to the damping material layers 346 and 348 enclosing the segment formations, has a further material layer 350 arranged between these two layers.
- FIG. 13 shows a perspective view of the torque transmission device 410 with a hinge arrangement 412 and a vibration damping device 414, which is arranged on the outer circumference of the ball joint 412 and surrounded by a housing 432.
- FIG 14 shows a perspective view of the torque transmission device 410 with the vibration damping device 414 without the housing 432.
- each segment portion 440 and 442 has two projections 474 and 476, wherein each of the projection 476 of the segment portion 442 are looped together with the projection 474 of the segment portion 440 of the loop 472.
- the housing part 424 and the transfer part 430 as one part, for example in the form of a part made by forging.
- FIG. 15 shows a partially cut-away front view of the torque transmission device 410.
- FIG. 15 shows again the segment sections 440 and 442 which each have two projections (not shown in FIG. 15 for reasons of clarity), the projection of the segment section 440 and the projection of the segment portion 442 are looped by a loop 472.
- FIG. 16 shows a sectional view along the sectional view XV-XV of FIG. 15. Here too, the loops 472 are visible which connect two successive adjacent segment sections.
- the segment portions 440 of the transmission part 428 can be displaced relative to the fixedly mounted on the housing part 424 segment portions 442 of the transmission part 430 with a transfer of torque.
- a damper assembly 444 comprising two damping material layers 446 and 448, between which two layers 446 and 448 a further layer of material 450 is arranged.
- the segment sections 440 of the transmission part 428 can be relatively displaced relative to the rotationally fixed on the housing part 424 of the ball joint 412 segment sections 442 of the transmission part 430 under elastic deformation of the loops 472 and the damper assembly 444 , In other words, torque is transmitted between the two transmission parts 428 and 430 via the loops 472 and the damper assemblies 444, i. from the driven transfer member 428 to the transfer member 430.
- the slings 472 are therefore preferably made of an elastomer with a suture insert.
- the torque transmission is thus carried out via a tensile force, which is transmitted from the transmission part 428 or the segment portion 440 via the loop 472 on the segment portion 442 of the transmission part, and a compressive force from the transmission part 428 and the segment portion 440 via the damping assembly 444 on the segment portion 442 of the transmission part 430 is transmitted.
- FIG. 17 is a perspective view of the torque transmission device 510 according to a sixth embodiment of the invention.
- FIG. 17 again shows the vibration damping arrangement 514 attached to the joint arrangement 512 - here in the form of a ball joint - the housing 532 has beads 578 according to this embodiment of the invention.
- the housing 532 is connected via the beads 578 with the transmission part 530, whereby the transmission part 530 is further stiffened.
- FIG. 18 is a partially broken front view of the torque transmission device 510 according to the sixth embodiment of the invention
- FIG. 19 is a sectional view taken along the line XVIII-XVIII of FIG. 18.
- FIGS. 18 and 19 A comparative view of FIGS. 18 and 19 again shows that the joint arrangement 512 is designed in the form of a ball-and-socket joint, on the outer circumference of which the vibration damping device 514 is arranged in the radial direction.
- the sixth embodiment of the invention differs from the embodiments described with reference to FIGS. 1 to 6 essentially in that the housing part 524 of the ball joint 512 is formed integrally with the transmission part 528, i. the housing part 524 of the ball joint 512 and the transmission part are made of one piece.
- housing 532 is connected to the transmission part 530 via beads 587 in the housing 532 and stiffens the latter.
- the operation of the torque transmission device 510 corresponds to the function of the embodiments described with reference to FIGS. 1 to 6.
- FIG. 20 shows an axis-containing sectional view of the torque transmission device 610 according to a seventh embodiment of the invention.
- the ball-and-socket joint 612 and the transmission device 614 can be seen from FIG. 20.
- the ball-and-socket joint 612 has an inner hub 616 in the form of a spherical star, in which a receiving opening 618 in the form of a through-bore is provided.
- an inner profiling 620 is formed, preferably in the form of an internal toothing.
- the internal toothing is preferably produced by broaching or milling, ie by means of cost-effective, but highly precise operations.
- the ball star 616 is coupled via the balls 622 to transmit torque to the housing part 624.
- the housing part 626 On the housing part 624, in turn, the housing part 626 is pressed and surrounds the housing part 624 partially.
- angular offsets of up to 40 ° between two shaft sections to be connected can be compensated.
- shielding elements made of rubber 630 and 632 are provided which are intended to prevent residual lubricant or possible Particles which have been rubbed off by friction may penetrate the ball joint 612 or may migrate from the ball joint 612 into the transfer case 614.
- the torque transmission device 614 has a first transmission part 634 and a second transmission part 636.
- the two transmission parts 634 and 636 overlap in a coupling region 638, wherein they have corresponding claw formations 640 and 642 in this coupling region 638.
- the claw formations 640 and 642 of the transmission parts 634 and 636 project in the axial direction.
- the two transmission parts 634 and 636 are each coated with a rubber layer, not shown here.
- the two rubber layers form a pressure-loaded first damper device.
- a second pre-damper device 644 which can be claimed for torsion, is provided on the transmission device 614.
- receiving cups 646 and 648 are arranged, which correspond to the claws of the claw formations 640, 642 and receive them form-fittingly with their receiving openings 650 and 652.
- the number of receiving cups 650, 652 corresponds to the number of claws of the claw formations 640, 642.
- the receiving cups 646, 648 are each connected to one of the transfer members 634, 636 by a rubber layer 654, 656, i. vulcanized. 5
- a guide sleeve 658 is arranged in its peripheral area.
- a positioning pin 660 is arranged, whose longitudinal axis is substantially aligned with the longitudinal axis A0.
- the positioning pin 660 serves to align the first transmission part 634 relative to the second transmission part 636.
- the transmission parts 634, 636 are mounted on the positioning pin 660 via bearing bushes 662 and 664. Further, 663 and 664, a central positioning sleeve 666 is provided between the bushings, which is to allow the lowest possible storage of the transmission parts 634 and 6365 on the positioning pin 660.
- the transmission part 636 of the transmission device 614 is fixedly connected to the housing part 624 of the Kugeifestgeienks or can be integrally formed therewith, whereby the ball joint 612 rotatably connected to the transmission device 614 is connected.
- a tube-like portion 668 on the transmission part 34 of the transmission means 614 may be fixedly connected to one of the shaft portions, preferably welded.
- the function of the torque transmission device 610 will be explained in more detail below.
- a shaft portion not shown here, with an external toothing corresponding to the internal toothing 620 is received axially displaceably, whereas the other shaft portion is fixedly connected to the transmission part 634.
- torques on the two, possibly mutually angled extending shaft sections can be transmitted. In operation, torques are transmitted by a positive connection between the internal teeth 620 and the external teeth.
- this connection between inner toothing 620 in the receiving opening 618 and the corresponding outer toothing enables axial aggregate movements in addition to the torque transmission to be compensated by the shaft section displaceable in the receiving opening 618. These aggregate movements thus do not act on the transmission device 14 and the ball joint 612 itself and on the components following in a drive train.
- the transmission device 14 attenuates the vibrations occurring in a drive train as well as torsional vibrations sufficiently in order not to transmit a structure-borne noise arising on the drive axle through the vehicle.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Steering Controls (AREA)
- Mechanical Operated Clutches (AREA)
- General Details Of Gearings (AREA)
- Motor Power Transmission Devices (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2011537887A JP5778580B2 (ja) | 2008-11-26 | 2009-11-26 | トルク伝達装置 |
DE112009004635.5T DE112009004635B4 (de) | 2008-11-26 | 2009-11-26 | Drehmomentübertragungsvorrichtung und Wellenanordnung mit einer Drehmomentübertragungsvorrichtung |
US13/130,794 US8517844B2 (en) | 2008-11-26 | 2009-11-26 | Torque transmitting device |
CN200980147382.8A CN102245920B (zh) | 2008-11-26 | 2009-11-26 | 扭矩传递装置 |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008059039.8 | 2008-11-26 | ||
DE200810059039 DE102008059039A1 (de) | 2008-11-26 | 2008-11-26 | Vorrichtung zum schwingungsreduzierten Übertragen von Drehmomenten |
DE200910040727 DE102009040727A1 (de) | 2009-09-09 | 2009-09-09 | Drehmomentübertragungsvorrichtung |
DE102009040727.8 | 2009-09-09 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010060626A1 true WO2010060626A1 (de) | 2010-06-03 |
Family
ID=41650216
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2009/008439 WO2010060626A1 (de) | 2008-11-26 | 2009-11-26 | Drehmomentübertragungsvorrichtung |
Country Status (6)
Country | Link |
---|---|
US (1) | US8517844B2 (de) |
JP (1) | JP5778580B2 (de) |
KR (1) | KR20110097844A (de) |
CN (1) | CN102245920B (de) |
DE (1) | DE112009004635B4 (de) |
WO (1) | WO2010060626A1 (de) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102628479B (zh) * | 2012-04-20 | 2014-06-18 | 东风汽车公司 | 一种包括万向传动轴及柔性联轴的结构 |
DE102012012106A1 (de) * | 2012-06-18 | 2013-12-19 | Robert Bosch Gmbh | Windkraftanlage mit einem zwischen Planetengetriebeund Generator angeordneten Kupplungsmittel zumAusgleich von Axial-, Radial- und Winkelversatz |
JP6254383B2 (ja) * | 2013-08-29 | 2017-12-27 | 株式会社荏原製作所 | ドレッシング装置及びそれを備えた化学的機械的研磨装置、それに用いるドレッサーディスク |
WO2018099982A1 (en) | 2016-11-30 | 2018-06-07 | Saint-Gobain Performance Plastics Rencol Limited | Adjustable torque assembly |
WO2019046346A1 (en) * | 2017-08-29 | 2019-03-07 | Apex Brands, Inc. | ORBITAL HAND KEY |
FR3082579B1 (fr) * | 2018-06-15 | 2022-08-19 | Valeo Embrayages | Dispositif de transmission de couple avec dispositif d'amortissement pendulaire |
DE102019002648A1 (de) * | 2019-04-10 | 2020-10-15 | Süddeutsche Gelenkscheibenfabrik GmbH & Co. KG | Vorrichtung zur Schwingungsentkopplung zweier Wellenabschnitte |
EP4029637A1 (de) * | 2020-08-31 | 2022-07-20 | SHW Werkzeugmaschinen GmbH | Fräskopf mit hoher genauigkeit, fräsmaschine mit einem fräskopf und verfahren zur positionierung eines fräskopfs mit hoher genauigkeit |
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GB731081A (en) * | 1952-09-16 | 1955-06-01 | Croset Louis Paul | Improvements in or relating to universal couplings |
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US3293883A (en) * | 1964-01-24 | 1966-12-27 | Gomma Antivibranti Applic | Torque transmitting resilient joint and manufacturing method |
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GB2347730A (en) * | 1999-03-12 | 2000-09-13 | Gkn Loebro Gmbh | Assembly of a constant velocity joint and a receiving part. |
WO2008003303A1 (de) * | 2006-07-05 | 2008-01-10 | Neumayer Tekfor Holding Gmbh | Drehmomentübertragungseinrichtung, wie kugelgleichlauffestgelenk als gegenbahngelenk und verfahren zur herstellung |
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US987878A (en) * | 1910-06-16 | 1911-03-28 | John Hormby | Shaft-coupling. |
JPS51143158A (en) * | 1975-06-04 | 1976-12-09 | Toyota Motor Corp | Flexible coupling for power transmission |
FR2404556A1 (fr) * | 1977-09-29 | 1979-04-27 | Renault | Dispositif anti-chuintement pour valve de direction assistee |
US4487583A (en) * | 1981-06-15 | 1984-12-11 | Jaycor | Receiver garment for weapons engagement simulation system |
DE3475819D1 (en) * | 1984-07-12 | 1989-02-02 | Wolf Woco & Co Franz J | Pivoted-link universal joint and its use |
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DE10116897B4 (de) * | 2001-04-04 | 2008-09-04 | Carl Freudenberg Kg | Rotationstilger |
JP2003028189A (ja) * | 2001-07-17 | 2003-01-29 | Nok Corp | フレキシブルカップリング |
JP2005214344A (ja) | 2004-01-30 | 2005-08-11 | Ntn Corp | 固定型等速自在継手 |
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- 2009-11-26 JP JP2011537887A patent/JP5778580B2/ja not_active Expired - Fee Related
- 2009-11-26 CN CN200980147382.8A patent/CN102245920B/zh not_active Expired - Fee Related
- 2009-11-26 KR KR1020117013878A patent/KR20110097844A/ko not_active Application Discontinuation
- 2009-11-26 DE DE112009004635.5T patent/DE112009004635B4/de active Active
- 2009-11-26 WO PCT/EP2009/008439 patent/WO2010060626A1/de active Application Filing
- 2009-11-26 US US13/130,794 patent/US8517844B2/en not_active Expired - Fee Related
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GB731081A (en) * | 1952-09-16 | 1955-06-01 | Croset Louis Paul | Improvements in or relating to universal couplings |
NL6412840A (de) * | 1963-11-07 | 1965-05-10 | ||
US3293883A (en) * | 1964-01-24 | 1966-12-27 | Gomma Antivibranti Applic | Torque transmitting resilient joint and manufacturing method |
GB2028968A (en) * | 1978-08-30 | 1980-03-12 | Wright Barry Corp | Flexible couplings |
GB2347730A (en) * | 1999-03-12 | 2000-09-13 | Gkn Loebro Gmbh | Assembly of a constant velocity joint and a receiving part. |
WO2008003303A1 (de) * | 2006-07-05 | 2008-01-10 | Neumayer Tekfor Holding Gmbh | Drehmomentübertragungseinrichtung, wie kugelgleichlauffestgelenk als gegenbahngelenk und verfahren zur herstellung |
Also Published As
Publication number | Publication date |
---|---|
JP5778580B2 (ja) | 2015-09-16 |
DE112009004635A5 (de) | 2012-06-21 |
KR20110097844A (ko) | 2011-08-31 |
CN102245920B (zh) | 2014-12-17 |
DE112009004635B4 (de) | 2020-06-18 |
CN102245920A (zh) | 2011-11-16 |
US20110306431A1 (en) | 2011-12-15 |
JP2012510034A (ja) | 2012-04-26 |
US8517844B2 (en) | 2013-08-27 |
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