CN104806695B - Centrifugal force pendulum - Google Patents
Centrifugal force pendulum Download PDFInfo
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- CN104806695B CN104806695B CN201410642546.7A CN201410642546A CN104806695B CN 104806695 B CN104806695 B CN 104806695B CN 201410642546 A CN201410642546 A CN 201410642546A CN 104806695 B CN104806695 B CN 104806695B
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- pendulum
- hollow cavity
- centrifugal force
- hollow
- damping device
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- 125000006850 spacer group Chemical group 0.000 claims abstract description 48
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Images
Classifications
-
- 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
- F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
-
- 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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention relates to a centrifugal pendulum for a drivetrain of a motor vehicle, wherein the centrifugal pendulum is rotatable about an axis of rotation, wherein a pendulum flange and at least one pendulum mass pair are provided, wherein the pendulum mass pair comprises a first pendulum mass and a second pendulum mass, wherein the pendulum flange comprises at least one recess having a recess contour, wherein the two pendulum masses are connected by means of at least one spacer bolt which is guided through the recess of the pendulum flange, wherein a damping device is provided on the spacer bolt, wherein the hollow cavity structure is designed to provide a fluid exchange between the interior of the hollow cavity structure and an enclosure of the hollow cavity structure upon tangential contact between the hollow cavity structure and the recess contour.
Description
Technical Field
The invention relates to a centrifugal force pendulum for a drive train of a motor vehicle, wherein the centrifugal force pendulum is rotatable about a rotational axis, wherein, a pendulum flange and at least one pendulum mass pair are provided, wherein, the pendulum mass pair comprises a first pendulum mass and a second pendulum mass, wherein the pendulum flange comprises at least one recess having a recess contour, wherein the two pendulum masses are connected by means of at least one spacer bolt which is guided through the recess of the pendulum flange, wherein the spacing pin bolt is provided with a damping device, which is characterized in that the damping device comprises a hollow cavity structure, wherein the hollow cavity structure is configured to provide fluid exchange between an interior of the hollow cavity and an enclosure of the hollow cavity when in tangential contact between the hollow cavity and the notch profile.
Background
Centrifugal force rockers having a pendulum flange which can be coupled to other components of the drive train are known. The centrifugal force pendulum comprises at least one pendulum mass pair, which comprises a first pendulum mass and a second pendulum mass. The two pendulum masses are arranged opposite one another on both sides of the pendulum flange and are connected to one another by means of spacer bolts. A recess is provided in the pendulum flange, through which the spacer bolt is guided. The pendulum masses are guided by guide means in order to execute a pendulum movement. In this case, the spacer bolt may rest against a section contour of the recess in the pendulum flange. This may result in noise generation. In order to reduce this noise generation, a sleeve-like rubber element is provided on the circumferential side of the spacer bolt, which rubber element is located between the spacer bolt and the sectional contour and dampens the abutment of the spacer bolt on the sectional contour.
Disclosure of Invention
The object of the invention is to provide an improved centrifugal force pendulum.
According to the invention, it is known to provide an improved centrifugal force pendulum by including a pendulum flange and at least one pendulum mass pair, which is rotatable about an axis of rotation, the pendulum mass pair including a first pendulum mass and a second pendulum mass, the pendulum flange including at least one recess having a recess contour, the two pendulum masses being connected by means of at least one spacer bolt, which is guided through the recess of the pendulum flange, furthermore a damping device arranged on the spacer bolt is provided, the damping device including a hollow cavity, wherein the hollow cavity is designed to provide a fluid exchange between the interior of the hollow cavity and the surrounding of the hollow cavity during a tangential contact (Ber ü hrkontakt) between the hollow cavity and the recess contour.
In this way, a particularly light and noise-free centrifugal pendulum can be provided. Furthermore, the hollow chamber is significantly more durable than the rubber elements used for damping until now, so that the centrifugal force pendulum has an increased service life.
In another embodiment, the hollow cavity has a first cavity and at least one second cavity. The first chamber is separated from the second chamber by a chamber wall. The occurring sound waves can thereby be absorbed within the cavity, which are generated by the damping device abutting against the notch contour.
In another embodiment, at least one through opening is provided in the chamber wall, wherein the through opening fluidly connects the first chamber with the second chamber. The sound pressure can thereby be guided further from the first chamber into the second chamber, wherein the sound pressure in the second chamber is lower than the sound pressure in the first chamber by the through-guide through the through-opening, so that overall the sound transmission from the outer contour to the spacer bolt is damped when the damping device rests on the section contour.
In a further embodiment, the damping device comprises at least one protective element, wherein the protective element is arranged between the hollow chamber and the pendulum flange and/or at least one pendulum mass, wherein the protective element is designed to prevent direct contact of the hollow chamber with at least one of the pendulum flange and/or pendulum mass. This prevents undesired flaking or abrasion of the hollow cavity when it rests on the section contour. This ensures a long-term stable damping which exceeds the service life of the centrifugal pendulum.
In a further embodiment, the protective element is arranged on the circumferential side on the hollow cavity and prevents direct contact of the hollow cavity with the section contour. In this way, erosion of the hollow cavity on the peripheral side can be avoided.
In another embodiment, the hollow cavity comprises a first lateral surface and the protective element comprises a second lateral surface, wherein the first lateral surface and the second lateral surface face one of the two pendulum masses, wherein the first lateral surface has a first distance to an end face of the facing pendulum mass and the second lateral surface has a second distance to the end face of the facing pendulum mass, wherein the first distance is smaller than the second distance. Thereby ensuring that: the protective element does not rest on the pendulum mass and, due to the radially outer arrangement, a possible separation between the protective element and the hollow space due to a torque acting on the protective element can be avoided.
In a further embodiment, the spacer pin comprises a longitudinal axis, wherein the longitudinal axis is arranged parallel to the rotational axis, wherein the protective element extends radially outward from the spacer pin with respect to the longitudinal axis. This embodiment makes it possible to prevent the hollow cavity from rubbing on the pendulum mass even when the protective element is arranged between the hollow cavity and the pendulum mass, so that lateral erosion of the hollow cavity can be avoided.
In a further embodiment, the damping device comprises at least one guide sleeve, wherein the guide sleeve is arranged between the hollow cavity and the spacer bolt and is configured to prevent direct contact of the hollow cavity with the spacer bolt. In this way, the damping device can be pushed onto the spacer bolt in a simple manner during the production of the centrifugal force pendulum, while the hollow chamber structure can be pushed onto the spacer bolt without being damaged. This damage is effectively avoided by the guide sleeve, so that a particularly high production quality can be provided in the production of the centrifugal force pendulum.
In another embodiment, the hollow cavity structure includes a first hollow cavity section and a second hollow cavity section. The damping device further comprises a stabilizing element. The stabilizing element is disposed axially between the first hollow cavity section and the second hollow cavity section. The protective element is arranged on a circumferential side of the first hollow cavity section and/or the second hollow cavity section of the hollow cavity and is connected to the stabilizing element. A particularly stable and durable damping device can thereby be provided, since a possible elastic deformation of the first hollow cavity section of the hollow cavity or of the second hollow cavity section of the hollow cavity is only transmitted to a reduced extent to further hollow cavity sections of the hollow cavity.
In a further embodiment, the stabilizing element extends from a radially inner portion to a radially outer portion with respect to a longitudinal axis of the spacer pin. The protective element is arranged on a circumferential side of the first hollow cavity section and/or the second hollow cavity section of the hollow cavity structure. The protective element is connected to the stabilizing element. In this way, a particularly good force transmission of the abutment force of the protective element onto the spacer bolt can be ensured while simultaneously damping sound by means of the hollow cavity. In this way, particularly strong oscillating torques can be absorbed by means of the centrifugal force pendulum, wherein the strong oscillating torques result in strong contact forces.
In another embodiment, the cavities have at least 70 percent of the total volume of the hollow cavity structure and/or the cavities have an extension dimension of less than 1000 microns. Preferably, at least 40 percent of the cavities of the total volume of the hollow cavity structure have an extension dimension of less than 500 microns and greater than 1 micron. Particularly advantageously, at least 10 percent of the total volume of the cavities has an extension greater than 1 micron and less than 10 microns.
Particularly advantageous are: the hollow cavity comprises at least one of the following materials: porous materials, organic materials, fibrous materials, cellulosic fibers, cotton, carbon fibers, glass fibers, metal fibers, steel fibers, aramid fibers, mineral fibers, latex, epoxy, resin, iron oxide, Celite, diatomaceous earth (kieselgur), graphite, mineral fibers.
Drawings
The invention is explained in detail below with reference to the drawings. Here:
fig. 1 shows a longitudinal section through a centrifugal force pendulum with a damping device according to a first embodiment;
FIG. 2 shows a section of the longitudinal section shown in FIG. 1 in the region of the damping device shown in FIG. 1;
fig. 3 shows an enlarged section of the damping device shown in fig. 2;
figure 4 shows a longitudinal section through a damping device according to a second embodiment;
fig. 5 shows a longitudinal section through a variant of the damping device shown in fig. 4;
figure 6 shows a longitudinal section through a damping device according to a third embodiment;
figure 7 shows a longitudinal section through a damping device according to a fourth embodiment;
figure 8 shows a longitudinal section through a damping device according to a fifth embodiment;
fig. 9 shows a section through a longitudinal section through a damping device according to a sixth embodiment.
Detailed Description
Fig. 1 shows a longitudinal section through a centrifugal force pendulum 10 having a damping device 15 according to a first embodiment. Fig. 2 shows a section of the longitudinal section shown in fig. 1 in the region of the damping device 15. Fig. 3 shows an enlarged section of the damping device 15 shown in fig. 2.
The centrifugal force pendulum 10 is mounted so as to be rotatable about an axis of rotation 20. The centrifugal force pendulum 10 can be a component of a drive train and can be coupled by means of one of the components of the drive train. The centrifugal force pendulum 10 comprises a pendulum flange 25 and a pendulum mass pair 30. The pendulum mass pair 30 comprises a first pendulum mass 35, which is arranged on the left side of the pendulum flange 25 in fig. 1. Furthermore, the pendulum mass pair 30 comprises a second pendulum mass 40, which is arranged on the right on the pendulum flange 25 opposite the first pendulum mass 35. The pendulum flange 25 has a first notch 45. The first recess 45 extends parallel to the axis of rotation 20, for example, at the radial height of the pendulum mass pair 30 through the pendulum flange 25. The pendulum masses 35, 40 have a second recess 50. The second recess 50 is also arranged here in an extending manner parallel to the axis of rotation 20. A spacer bolt 55 extends through the openings 45, 50, which spacer bolt connects the pendulum masses 35, 40 to one another. The spacer pin 55 has a longitudinal axis 60 which is arranged parallel to the axis of rotation 20. The pendulum masses 35, 40 are guided in a pendulum movement along a pendulum path by a not shown link guide.
The spacer pin 55 has a cut-out section 65 and fastening sections 70 arranged on both sides of the cut-out section 65. The cutout section 65 is arranged in the first cutout 45 of the pendulum flange 25. The fastening portions 70 are each arranged in the second recess 50 of the respective pendulum mass 35, 40. The securing section 70 has a smaller diameter than the notched section 65. Between the fastening section 70 and the cutout section 65, a flange 75 is provided, on which an end face 80 of the pendulum mass 35, 40 is in contact, which end face faces the pendulum flange 25. At the respective longitudinal end of the spacer bolt 55, a rivet connection 85 is provided, which clamps the pendulum masses 35, 40 against the flange 75 and thus connects the pendulum masses 34, 40 to one another. Obviously also: the two pendulum masses 35, 40 are connected according to a further method.
On the circumferential side of the spacer bolt 55, a damping device 90 is arranged in the first recess 45. The damping device 90 has a hollow cylindrical section 95 which engages around the spacer pin 55 on the circumferential side with an inner circumferential surface 96 on the cutout section 65. Radially with respect to the longitudinal axis 60 of the spacer pin 55, a tapering section 100 adjoins the hollow cylindrical section 95 on the outside. The tapering section 100 has a decreasing width in the direction of the longitudinal axis 60 from the inside to the outside in the radial direction. Radially on the outside, the damping device 90 has an abutment surface 105, which corresponds to the outer circumferential surface of the damping device 90.
The first notch 45 has a cross-sectional profile 110. The segment contour 110 is designed to correspond to a pendulum movement which is generated on the pendulum flange 25 by the not shown gate guides of the pendulum masses 35, 40.
The damping device 90 includes a hollow cavity 115 having a plurality of chambers 120, 125 disposed within an interior of the hollow cavity 115. These chambers 120, 125 are shown schematically in fig. 1 to 3 and can obviously also be designed in another way in terms of their geometric design. Here, the first chamber 120 is separated from the second chamber 125 by a chamber wall 130. The chamber wall 130 has a through opening 135 that fluidly connects the first chamber 120 with the second chamber 125. It is obviously also conceivable to provide a plurality of through-openings 135 in the chamber wall 130. It is also conceivable that some of the chambers 120, 125 are connected by means of partition walls 130, in which no through-openings 135 are provided, but that the other chambers 120, 125 are connected by means of through-openings 135 in the chamber walls 130. Furthermore, in this embodiment, the chambers 120, 125 with chamber walls 130 are arranged diamond-shaped in the damping device 90. It is obviously also conceivable for these chambers 120, 125 to have another type of cross section. It is also contemplated that the chambers 120, 125 each have a different volume. In addition, the chamber walls 130, 140 may also be curved or zigzag-shaped.
The damping device 90 comprises a delimiting wall 140 which delimits the hollow chamber 115 both on the end side and on the circumferential side. Additional further through-openings 145 are provided in the delimiting wall 140, which connect some or all of the chambers 120, 125 adjoining the delimiting wall 140 to an enclosure 150, which corresponds for example to a clutch interior. Through the further through-openings 145, fluid acting in the enclosure 150, for example cooling fluid present in the clutch device, can thus pass through the further through-openings 145 into the first chamber 120 (see fig. 3). From said first chamber 120, the fluid may further pass through the first through opening 135 into the further chamber 125. The cavities 120, 125 of the hollow cavity 115 form a porous structure with the through openings 135, 134.
During operation of the centrifugal force pendulum 10, it rotates about the axis of rotation 20 with a rotational speed which generally corresponds to the rotational speed of an internal combustion engine connected to the centrifugal force pendulum 10. The chambers 120, 125 in the state not loaded by the cooling fluid, which is a constituent part of the housing of the centrifugal force pendulum in the housing of the damping device, are arranged in an at least partially filled (geflutet) manner. If the housing of the damping device in which the centrifugal force pendulum 10 is arranged is only partially filled with a cooling fluid, the chambers 120, 125 immersed in the cooling fluid are at least partially filled during the rest state of the centrifugal force pendulum 10 and/or during the passage through the cooling fluid. In this case, it is particularly advantageous: the hollow chamber 115 is designed in such a way that during the immersion of the damping device 90, at least 0.25 volume percent, preferably 1 volume percent, of the total volume of the chambers 120, 125 is filled with cooling fluid.
The damping device 90 is guided in the first recess 45 during the pivoting movement of the pivoting masses 35, 40 by coupling to the spacer bolt 55. Depending on the pendulum movement, the damping device 90 can rest with a resting surface 105 on the section contour 110. The resulting abutment force causes an elastic deformation of the hollow cavity 115 and thus of the chambers 120, 125. In this case, the volume of the chambers 120, 125 is reduced, so that the cooling fluid present in these chambers 120, 125 is at least partially pressed into the enclosure 150 through the through- openings 135, 145. As a result, the damping device 90 is particularly effective in reducing the contact of the spacer pin 55 against the sectional contour 110. After the abutment, the hollow space 115 is deformed back into its original state and the cooling fluid is again received in the chambers 120, 125, exiting from the enclosure 150.
Fig. 4 shows a damping device 200 according to a second embodiment. The damping device 200 is constructed analogously to the embodiments shown in fig. 1 to 3. The damping device 200 has a hollow cavity 115 of annular design. Radially outwardly, a protective element 205 is arranged on the hollow cavity 115. In this case, the protective element 205 is of telescopic design and has a material which is substantially formed from a solid material. The protective element 205 is thus arranged between the truncated contour 110 and the hollow cavity 115. The hollow cavity 115 has a first side surface 215 on an end face 210 of the damper 200. The protective element 205 has a second side surface 220 on an end face 210. The two side surfaces 215, 220 are arranged in a common plane perpendicular to the longitudinal axis 60 of the spacer pin 55.
The protective element 205 serves to prevent wear of the hollow cavity 115 during the pendulum movement and to prevent possible tangential contact of the hollow cavity 115 with the segment contour 110. This prevents erosion of the hollow cavity 115 during operation of the centrifugal force pendulum 10. In this case, it is advantageous to make the protective element 205 of a similarly hard material, such as the pendulum flange 25, in order to avoid excessive wear and thus possible particle emissions into the surrounding of the centrifugal force pendulum 10, in particular into the cooling fluid of the damping device and/or of the transmission.
In order to provide a particularly good connection between the hollow cavity 115 and the protection element 205, the protection element is pre-clamped with respect to the hollow cavity 115 and thereby provides a frictional connection between the hollow cavity 115 and the protection element 205. Alternatively, a material-and/or form-locking connection between the protective element 205 and the hollow space 115 is also conceivable.
Fig. 5 shows a longitudinal section through a variant of the embodiment 200 shown in fig. 4 of the damping device. The damping device 200 is constructed essentially in accordance with the embodiment shown in fig. 4. In contrast, the hollow cavity 115 is spherically formed on the first lateral surface 215. In this case, the lateral surface 215 has a minimum distance a from the end side 80 of the pendulum mass 35, 40 facing the first lateral surface 2151. The second lateral surface 220 of the protective element 205 has a second distance a from the facing end faces 80 of the pendulum masses 35, 402. The first distance a here1Less than the second pitch a2. The spherical design of the delimiting wall 140 ensures a particularly good transmission of force between the protective element 205 and the spacer bolt 55 via the hollow space 115 with simultaneously low transmission of sound.
Fig. 6 shows a longitudinal section through a damping device 300 according to a third embodiment. The damping device 300 is constructed similarly to the damping device 200 shown in fig. 4. In addition, the damping device 300 has a guide sleeve 305, which is arranged on the inner circumferential surface 96 of the hollow chamber 115 on the radially inner side. The guide sleeve 305 has the advantage that tilting of the damping device 300 and thus possible damage to the hollow chamber 115 are avoided when the damping device 300 is pushed onto the spacer pin 55.
The side surfaces 215, 220 and a third side surface 315 of the guide sleeve 305 facing the end face 80 of the pendulum masses 35, 40 are arranged in a common plane. It is obviously also possible for the side faces 215, 220, 315 to be arranged in different planes and thus spaced apart from one another in the axial direction.
Between the guide sleeve 305 and the protective element 205, the hollow cavity 115 extends radially from the inside to the outside with respect to the longitudinal axis 60. The hollow cavity 115 is configured as explained in fig. 1 to 3 and serves to reduce the transmission of the abutment force between the protective element 205 and the guide sleeve 305. A particularly light centrifugal force pendulum 10 can thereby be provided.
The guide sleeve 305 is advantageously made of the same material as the protective element 205 and/or the hollow space structure 115. Obviously also: the guide sleeve 305 is of a different material than the hollow cavity 115 and/or the protective element 205. In order to provide a particularly wear-free centrifugal force pendulum 10, the guide sleeve 305 can be produced, for example, from a sintered material, in order to provide improved sliding properties of the guide sleeve 305 on the spacer bolt 55 in the region of the cutout section 65. Alternatively, one can consider: the guide sleeve 305 comes into a press-fit connection with the cut-out section 65 of the spacer bolt 55 in order to ensure a secure placement of the damping device 300 on the spacer bolt 55.
Fig. 7 shows a longitudinal section through a damping device 400 according to a fourth embodiment. The damping device 400 comprises a hollow chamber 115, which is configured in a ring-like manner, like the one shown in fig. 1 to 3. In contrast, the hollow cavity 115 does not have a tapered section 100. A protective element 405 is arranged on each of the first lateral surfaces 215 of the hollow space 115, wherein the protective elements 405 extend radially outward from the spacer pin 55 with respect to the longitudinal axis 60 of the spacer pin 55. The protective element 405 is advantageously made of a solid material in order to provide a particularly high protection with respect to the hollow cavity 115. The protective element 405 is thus arranged between the hollow space 115 and the pendulum masses 35, 40. This prevents wear of the pendulum masses 35, 40 and/or possible damage to the hollow space structure 115 due to possible tilting of the pendulum masses 35, 40 during the pendulum movement of the pendulum masses 35, 40 or during the assembly of the centrifugal force pendulum 10. The protective element 405 has a smaller radial extent than the hollow space 115 with respect to the longitudinal axis 60 of the spacer pin 55. This ensures that: the protective element 405 does not rest on the section contour 110 of the pendulum flange 25.
Fig. 8 shows a longitudinal section through a damping device 500 according to a fifth embodiment. The damping device 500 is constructed similarly to the damping device shown in fig. 1 to 7. The damping device 500 also includes the hollow cavity 115. The hollow cavity 115 includes a first hollow cavity section 505 and a second hollow cavity section 510. The first hollow cavity section 505 is separated in the axial direction by a stabilizing element 515, which is arranged between the first hollow cavity section 505 and the second hollow cavity section 510. The stabilizing element 515 extends radially from the inside to the outside and is connected radially on the outside to the protective element 205. The protective element 205 is designed analogously to that shown in fig. 6. The stabilizing element 515 has a larger inner diameter than the two hollow cavity sections 505, 510. This prevents: sound can be transmitted between the spacer pin 55 and the stabilizing element 515 via the stabilizing element 515. In fig. 8, therefore, only the hollow space 115 bears on the circumferential side against the spacer bolt 55. It is obviously also conceivable to provide the guide sleeve 305, but it is advantageous to arrange the guide sleeve 305 spaced apart from the stabilizing element 515. By means of the stabilizing element 515: when the damping device 500 comes to bear hard against the section contour 110 of the pendulum flange 20, the hollow cavity 115 is overloaded radially on the outside. By means of the stabilizing element 515, an abutment force is placed in a radially inner region of the hollow cavity 115 with respect to the longitudinal axis 60, so that the hollow cavity 115 is loaded more uniformly in the radial extension upon the abutment than is shown in fig. 6. Thereby providing a more durable damping device 500 as a whole.
Fig. 9 shows a section through a longitudinal section through a damping device 600 according to a sixth embodiment. The damping device 600 is constructed similarly to the damping device shown in fig. 1 to 8. In contrast, the hollow cavity 115 has a plurality of fibers 605 which are arranged next to one another, for example substantially extending in the circumferential direction. Obviously, other orientations are also contemplated. These fibers 605 have a substantially circular cross-section. Additional cross-sections are also contemplated. The fibers 605 are closely arranged such that the lumens 120, 125 are configured between the fibers. These chambers are connected to each other by a through opening 125 and to the enclosure by further through openings. The lumens 120, 125 have an elongated cross-section in this embodiment through the configuration of the fibers 605. Additionally, the fibers 605 have the advantage that they themselves damp the abutment of the spacer pin 55 on the section contour 110 by elastic deformation. Porosity for receiving cooling fluid into the cavities 120, 125 is also provided by the fibers 605.
The hollow cavity 115 of the damping device 15, 200, 300, 400, 500 shown in fig. 1 to 9 can have the following materials, for example: porous materials, organic materials, fibrous materials, cellulosic fibers, cotton, carbon fibers, glass fibers, metal fibers, steel fibers, aramid fibers, mineral fibers, latex, epoxy resins, iron oxides, celite, diatomaceous earth, graphite. The strength of the hollow cavity structure can be increased by means of aramid fibers and/or carbon fibers and/or glass fibers and/or mineral fibers. The fluid storage capacity of the hollow cavity 115 may be enhanced by the use of celite, graphite, iron oxide.
Particularly advantageous are: these cavities 120, 125 have at least 70 percent of the total volume of the hollow cavity 115 and/or these cavities have an extension dimension of less than 1000 microns. Preferably, at least 40 percent of the cavities 120, 125 of the total volume of the hollow cavity 115 have an extension dimension of less than 500 microns and greater than 1 micron. Particularly advantageously, at least 10 percent of the total volume of the cavities 120, 125 has an extension greater than 1 micron and less than 10 microns.
In this case, it is particularly advantageous: the hollow cavity 115 has a strength of at least 100 newtons per millimeter. This avoids: the hollow cavity 115 is too strongly elastically yielding in the event of the abutment and possibly the stabilizing element 515 and/or the protective element 205 can be detached from the hollow cavity 115.
It is noted that the embodiments 15, 200, 300, 400, 500 of the damping device shown in fig. 1 to 8 are exemplary. Obviously also: the features shown in fig. 1 to 8 are combined with each other in order to thus provide a damping device 15, 200, 300, 400, 500 that offers stability or an advantageous use. For example, the protective element 205 shown in fig. 8 with the stabilizing element 515 can be combined with the protective element 405 shown in fig. 7, in order to thus protect the hollow cavity 115 from possible erosion of the hollow cavity 115 and thus from damage of the centrifugal force pendulum 10, both in the axial direction and in the radial direction. Furthermore, it is also possible to ensure by this protection: possible particles which are not produced during the corrosion are introduced into the cooling oil circuit of the transmission, and these particles can also damage the clutch and/or the transmission.
List of reference numerals
10 centrifugal force pendulum
15 damping device
20 axis of rotation
25 pendulum flange
30 pendulum mass pairs
35 first pendulum mass
40 second pendulum mass
45 first notch
50 second notch
55 spacing bolt
60 longitudinal axis
65 notched section
70 fixed section
75 Flange
80 end face
85 rivet connecting device
90 damping device
95 cylinder section
100 tapering section
105 abutting surface
110 section profile
115 hollow cavity structure
120 first chamber
125 second chamber
130 chamber wall
135 through opening
140 delimiting wall
145 other through openings
150 surrounding part
200 damping device
205 protective element
210 end face
215 first side surface
220 second side surface
300 damping device
305 guide sleeve
315 side surface
400 damping device
405 protective element
500 damping device
505 first hollow cavity section
510 second hollow cavity section
515 stabilizing element
600 damping device
605 fiber
Claims (16)
1. A centrifugal force pendulum (10) for a drive train of a motor vehicle,
-wherein the centrifugal force pendulum (10) is rotatable about a rotational axis (20),
-wherein a pendulum flange (25) and at least one pendulum mass pair (30) are provided,
-wherein the pendulum mass pair (30) comprises a first pendulum mass (35) and a second pendulum mass (40),
-wherein the pendulum flange (25) comprises at least one indentation (45) with an indentation profile (110),
-wherein the two pendulum masses (35, 40) are connected by means of at least one spacer bolt (55) which is guided through the recess (45) of the pendulum flange (25),
-wherein a damping device (90; 200; 300; 400; 500) is arranged on the spacer pin (55),
it is characterized in that the preparation method is characterized in that,
-said damping means (90; 200; 300; 400; 500) comprises a hollow cavity (115),
-wherein the hollow cavity (115) is configured for providing a fluid exchange between an interior (120, 125) of the hollow cavity (115) and an enclosure (150) of the hollow cavity (115) upon tangential contact between the hollow cavity (115) and the notch profile (110).
2. The centrifugal force pendulum (10) of claim 1, characterized in that the hollow cavity (115) has a first cavity (120) and at least a second cavity (125), wherein the first cavity (120) is separated from the second cavity (125) by means of at least one cavity wall (130, 140).
3. The centrifugal force pendulum (10) of claim 2, characterized in that at least one through opening (135) is provided in the chamber wall (130, 140), wherein the through opening (135) fluidly connects the first chamber (120) with the second chamber (125).
4. Centrifugal force pendulum (10) according to one of claims 1 to 3, characterized in that the damping device (90; 200; 300; 400; 500) comprises at least one protective element (205, 405),
-wherein the protective element (205, 405) is arranged between the hollow cavity (115) and the pendulum flange (25) and/or at least one pendulum mass (35, 40),
-wherein the protective element (205, 405) is configured to prevent direct contact of the hollow cavity (115) with the pendulum flange (25) and/or at least one pendulum mass (35, 40).
5. The centrifugal force pendulum (10) according to claim 4, characterized in that the protective element (205, 405) is arranged on the circumferential side on the hollow cavity (115) and prevents a direct contact of the hollow cavity (115) with the gap profile (110).
6. The centrifugal force pendulum (10) of claim 5, characterized in that the hollow cavity (115) comprises a first side surface (215) and the protection element (205, 405) comprises a second side surface (220),
-wherein the first side surface (215) and the second side surface (220) face one of two pendulum masses (35, 40),
-wherein the first side surface (215) has a first distance (a) to an end surface (80) of the pendulum mass (35, 40) facing it1) And the second side surface (220) has a second distance (a) from the end surface (80) of the facing pendulum mass (35, 40)2)，
-wherein the first pitch (a)1) Is smaller than the second pitch (a)2)。
7. The centrifugal force pendulum (10) of claim 4, characterized in that the spacer pin (55) comprises a longitudinal axis (60), wherein the longitudinal axis (60) is arranged parallel to the rotational axis (20), wherein the protective element (205, 405) extends radially outward from the spacer pin (55) with respect to the longitudinal axis (60).
8. The centrifugal force pendulum (10) according to one of claims 1 to 3, characterized in that the damping device (90; 200; 300; 400; 500) comprises at least one guide sleeve (305), wherein the guide sleeve (305) is arranged between the hollow cavity (115) and the spacer pin (55) and is configured to prevent a direct contact of the hollow cavity (115) with the spacer pin (55).
9. The centrifugal force pendulum (10) according to claim 4, characterized in that the hollow chamber (115) comprises a first hollow chamber section (505) and a second hollow chamber section (510), wherein the damping device (90; 200; 300; 400; 500) comprises a stabilizing element (515), wherein the stabilizing element (515) is arranged between the first hollow chamber section (505) and the second hollow chamber section (510) of the hollow chamber (115).
10. The centrifugal force pendulum (10) according to claim 9, characterized in that the stabilizing element (515) is arranged axially between the first hollow cavity section (505) and the second hollow cavity section (510), wherein the protective element (205, 405) is arranged on a circumferential side of the first and/or second hollow cavity section (505, 510) of the hollow cavity (115) and is connected with the stabilizing element (515).
11. The centrifugal force pendulum (10) according to claim 2 or 3, characterized in that the first and second chambers (120, 125) have at least 70 percent of the total volume of the hollow cavity (115) and/or the first and second chambers (120, 125) have an extension of less than 1000 micrometers.
12. The centrifugal force pendulum (10) of claim 11, characterized in that at least 40 percent of the first (120) and second (125) chambers of the total volume of the hollow cavity (115) have an extension dimension of less than 500 microns and greater than 1 micron.
13. The centrifugal force pendulum (10) of claim 11, characterized in that at least 10 percent of the total volume of the first and second chambers (120, 125) has an extension dimension greater than 1 micron and less than 10 microns.
14. The centrifugal force pendulum (10) of one of claims 1 to 3, characterized in that the hollow cavity (115) comprises at least one of the following materials: porous materials, organic materials, fibrous materials.
15. The centrifugal force pendulum (10) of one of claims 1 to 3, characterized in that the hollow cavity (115) comprises at least one of the following materials: cellulose fiber, cotton, carbon fiber, glass fiber, metal fiber, mineral fiber, aramid fiber, latex, resin, iron oxide, celite, diatomaceous earth, graphite.
16. The centrifugal force pendulum (10) of claim 15, characterized in that the material of the hollow cavity (115) is epoxy or steel fiber.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013222756.6 | 2013-11-08 | ||
| DE102013222756 | 2013-11-08 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104806695A CN104806695A (en) | 2015-07-29 |
| CN104806695B true CN104806695B (en) | 2020-03-06 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410642546.7A Expired - Fee Related CN104806695B (en) | 2013-11-08 | 2014-11-07 | Centrifugal force pendulum |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN104806695B (en) |
| DE (1) | DE102014220560A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102015215882A1 (en) * | 2015-08-20 | 2017-02-23 | Schaeffler Technologies AG & Co. KG | Centrifugal pendulum device and hydrodynamic torque converter with centrifugal pendulum |
| DE102016217217A1 (en) * | 2015-09-18 | 2017-03-23 | Schaeffler Technologies AG & Co. KG | Torque transfer device |
| DE102016208636A1 (en) * | 2016-05-19 | 2017-11-23 | Zf Friedrichshafen Ag | Connecting arrangement for connecting a plurality of absorber mass elements of a damping mass |
| DE102017102675A1 (en) * | 2017-02-10 | 2018-08-16 | Schaeffler Technologies AG & Co. KG | Spacer bolt and damper device |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2590579A (en) * | 1948-09-17 | 1952-03-25 | Sarazin Gilles Francois | Torsional vibration damper |
| DE102011089236A1 (en) * | 2010-12-23 | 2012-06-28 | Daimler Ag | Centrifugal pendulum device |
| CN102762887A (en) * | 2009-12-21 | 2012-10-31 | 舍弗勒技术股份两合公司 | Centrifugal force pendulum device |
| CN103097765A (en) * | 2010-09-08 | 2013-05-08 | 爱信艾达工业株式会社 | Dynamic vibration absorber |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5316461B2 (en) * | 2010-03-30 | 2013-10-16 | トヨタ自動車株式会社 | Vibration reduction device |
-
2014
- 2014-10-10 DE DE201410220560 patent/DE102014220560A1/en not_active Withdrawn
- 2014-11-07 CN CN201410642546.7A patent/CN104806695B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2590579A (en) * | 1948-09-17 | 1952-03-25 | Sarazin Gilles Francois | Torsional vibration damper |
| CN102762887A (en) * | 2009-12-21 | 2012-10-31 | 舍弗勒技术股份两合公司 | Centrifugal force pendulum device |
| CN103097765A (en) * | 2010-09-08 | 2013-05-08 | 爱信艾达工业株式会社 | Dynamic vibration absorber |
| DE102011089236A1 (en) * | 2010-12-23 | 2012-06-28 | Daimler Ag | Centrifugal pendulum device |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102014220560A1 (en) | 2015-05-13 |
| CN104806695A (en) | 2015-07-29 |
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