WO2014194903A1 - Friction clutch for a drive train of a motor vehicle - Google Patents
Friction clutch for a drive train of a motor vehicle Download PDFInfo
- Publication number
- WO2014194903A1 WO2014194903A1 PCT/DE2014/200205 DE2014200205W WO2014194903A1 WO 2014194903 A1 WO2014194903 A1 WO 2014194903A1 DE 2014200205 W DE2014200205 W DE 2014200205W WO 2014194903 A1 WO2014194903 A1 WO 2014194903A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure plate
- friction
- clutch
- friction lining
- lining
- Prior art date
Links
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
-
- 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
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
- F16D13/40—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs in which the or each axially-movable member is pressed exclusively against an axially-located member
- F16D13/42—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs in which the or each axially-movable member is pressed exclusively against an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member
- F16D13/44—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs in which the or each axially-movable member is pressed exclusively against an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member in which the clutching pressure is produced by springs only
-
- 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
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
-
- 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
- F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
- F16D2069/004—Profiled friction surfaces, e.g. grooves, dimples
Definitions
- Friction clutch for a drive train of a motor vehicle with a rotatably mounted about an axis of rotation pressure plate, a pressure plate, and arranged between the pressure plate and the pressure plate and rotatably mounted about the axis of rotation clutch disc, wherein the clutch disc has at least one friction lining, which is predominantly in a normal extends to the rotational axis aligned radial plane and is frictionally clamped or clamped in an engaged state of the friction clutch between the pressure plate and the pressure plate.
- a counterpressure plate such as a flywheel connected to the crankshaft, a secondary mass of a dual mass flywheel, a center pressure plate of a double clutch, or the like, is fixedly connected to a housing.
- a pressure plate is taken from cast iron, which is arranged by means of leaf springs rotatably and axially displaceable.
- friction clutches can also be made wet or dry running.
- dry clutches ever higher demands are made with regard to the friction behavior of frictionally engaged in the engaged state friction pairings.
- the at least one friction lining has at least one aligned transversely to the radial plane survey, which enlarges in a gegen Dermate depression of the pressure plate or pressure plate, the force transmission surfaces between the standing together in force transmitting active contact components.
- This embodiment of the friction lining according to the invention has the particular effect that, without significantly increasing the space of the friction clutch, in particular in the radial direction, the friction surfaces between the clutch disc and the pressure plate or the pressure plate are significantly increased. Due to this enlarged friction surface is at unchanged environmental conditions, d. H. at the same to be transmitted torque values of the internal combustion engine, the surface pressure prevailing in the friction surfaces per unit area significantly reduced. As a result of this reduced surface pressure, the maximum temperature peaks occurring during operation in the clean surfaces are also significantly reduced. Thus, especially in the critical conditions during operation, the removal of material in the friction surfaces is reduced. Since the friction surfaces increase significantly, it is also possible to even reduce the radial space of the friction clutch, without that deteriorates the friction behavior in the friction surfaces over the known solutions.
- the surveys can take various geometric configurations, which can be optimized optimized for the particular application.
- the contact surface of the surfaces standing in frictional contact is thus increased, thereby reducing the surface pressure at the same contact pressure.
- the transmittable torque is substantially increased.
- the wear conditions also improve.
- in the new combustion engine generations, in particular the gasoline and diesel engine technology it is now possible, without significantly changing the radial space of the friction clutch, to provide a friction clutch which also ter increasing torques can secure damage over long periods of operation away.
- the clutch disc comprises a plurality of at least one friction lining, of which friction linings at least a first friction lining on the part of the pressure plate and at least a second friction lining on the pressure plate is arranged on the clutch disc, wherein the at least one first friction lining and the at least a second friction lining each having at least one elevation.
- the friction linings which can be brought into frictional engagement with the pressure plate and with the pressure plate each have the at least one elevation, wherein the elevations extend transversely to the radial plane and in the engaged state flatly on complementary depressions in the Pressure plate and the pressure plate rest.
- a further advantageous embodiment provides that the at least one elevation is aligned concentrically to the axis of rotation.
- the enlarged friction surface of the clutch disc uniformly act around its entire circumference to keep particularly occurring during operation imbalances too low.
- the at least one elevation is configured so that the frictionally engageable with the pressure plate, at least a second friction lining and / or frictionally engageable with the pressure plate, at least a first friction lining wavy and / or sawtooth-shaped extending is / are.
- These structures are particularly suitable for forming the elevations. The elevations of these structures are optimally designed for the loads occurring in the friction surfaces. In particular, these structures are also suitable for receiving and transmitting shear forces.
- a further advantageous embodiment provides that the frictionally engageable with the pressure plate, at least a first friction lining to the frictionally engageable with the pressure plate, at least a second friction lining is formed symmetrically with respect to the radial plane. As a result, the friction clutch is particularly well adapted to the high pressure loads. A displacement of the friction linings of the clutch disc to each other is avoided.
- the clutch disc is centered by means of at least one of the elevations of the at least one friction lining to the axis of rotation. So it is possible to provide a particularly durable coupling.
- the number of elevations on the at least one first friction lining which can be brought into frictional engagement with the pressure plate and at least one second friction lining can be brought into frictional engagement with the pressure plate is at least four. Through this number of surveys, an optimal ratio between maximum friction surface and geometric strength of the surveys is achieved.
- At least one depression in the pressure plate is designed such that the surface of the pressure plate which can be brought into frictional engagement with the at least one first friction lining is a negative mold of the at least one first friction lining.
- the entire surface of the friction lining viewed in cross-section of the clutch disc, abut the entire surface of the corresponding friction surface of the pressure plate.
- At least one recess in the pressure plate is designed such that the at least one second friction lining can be brought into frictional engagement surface of the pressure plate is a negative mold of the at least one second friction lining. Even then, a surface-optimized design is possible.
- the area which is available in a dry clutch for the frictional engagement increased.
- the friction surfaces of the pressure plate and the pressure plate, and the friction linings of the clutch disc are provided with concentric with the axis of rotation aligned, annular protrusions / projections and / or depressions.
- the concentric rings are per friction pairing (cooperating friction surface of the pressure plate and the clutch disc as well as sammen mergede friction surface of the pressure plate and the clutch disc) to match each other, to allow an exact centering of the components over the entire surface (and not just about individual ring areas of the surface).
- the surface of the friction surfaces of the pressure plate and the pressure plate / counter-pressure plate, and the friction linings of the clutch disc may be formed substantially sawtooth, being indented for producing the frictional engagement when moving the pressure plate in the axial direction valleys in mountains and mountains in valleys.
- the surface cross section is formed substantially wave-shaped.
- FIG. 1 shows a cross-section along a sectional plane in which the axis of rotation lies, by means of which a first embodiment of the friction clutch according to the invention is illustrated in an engaged state
- Figure 3 is an isometric view of one of the usable in the friction clutch according to the invention clutch disc according to another embodiment
- Figure 4 is a detail view of cooperating via a Reibkraft discourse
- Friction surfaces of the clutch disc, the pressure plate and the pressure plate according to the embodiment of Figures 1 and 2 according to the invention.
- the friction clutch 1 according to the invention shown in FIGS. 1, 2 and 4 is shown by way of example according to an advantageous exemplary embodiment.
- the friction clutch 1 is usually used in a drive train of a motor vehicle, on the one hand a pressure plate 2 is present, which is connected crankshaft side with a markable as a clutch input shaft shaft, said shaft and its connection to the pressure plate 2 for the sake of clarity not shown in detail.
- the pressure plate 2 is also connected to a housing 3, which housing 3 serves as a cover of the other coupling components.
- the friction clutch 1 according to the invention is configured as a dry-running clutch (dry clutch), but alternatively it is also possible to use this friction clutch as a wet-running clutch (wet clutch).
- the pressure plate 2 is rotatably mounted about an axis of rotation 4, which axis of rotation 4 is preferably coaxial with the axis of rotation of the clutch input shaft (the crankshaft) is formed.
- a clutch disc 5 which clutch disc 5 is pressed in a, shown in Figure 1, coupled state of the friction clutch 1 by means of a pressure plate 6 against the pressure plate 2 that the pressure plate 2 and the clutch disc 5 in This coupled state are positively connected to each other.
- the pressure plate 2 and the clutch disc 5 rotate when the internal combustion engine is switched on, that is to say when the crankshaft input shaft rotates, in this engaged state essentially at the same rotational speed.
- the clutch disc 5 and the pressure plate 2 together, provides a usually designed as a plate spring 7 lever element.
- This disc spring 7 cooperates in a known manner with a Kupplungsausschsystem to the pressure plate between the engaged position ( Figure 1) and a disengaged position ( Figure 2), in which the pressure plate 6 is spaced from the clutch disc 5, back and forth, wherein the plate spring 7 presses the pressure plate 6 against the pressure plate 2 at least in the engaged position by means of a conventional spring mechanism.
- the clutch disc 5 is connected to a clutch output shaft which is not further developed here, preferably with a transmission input shaft which forwards the torque transmitted by the clutch to a transmission.
- Both the pressure plate 6 and the pressure plate 2 each have a friction surface 8 and 1 1, which abut frictionally on corresponding friction surfaces 9 and 10 of two friction linings 19 and 22 of the clutch disc 5.
- the friction surface 8 of the pressure plate 6, hereinafter referred to as the first friction surface 8 extends along an imaginary plane, hereinafter also referred to as the radial plane.
- the radial plane is a plane to which the axis of rotation 4 is designed as normal, ie, the axis of rotation 4 is perpendicular to this imaginary radial plane.
- the friction surface 9, which is in contact with the first friction surface 8 of the pressure plate 6, of a first friction lining 19 of the clutch disk 5, referred to below as the second friction surface 9, extends essentially in this imaginary radial plane.
- the first friction lining 19 thus extends similar to the first friction surface 8 of the pressure plate 6 and is arranged on the pressure plate 6 facing side of the clutch disc 5.
- the clutch disc 5 continues to be frictionally engaged with the pressure plate 2 in the engaged state shown in FIG.
- a third friction surface 10 of a second friction lining 22 of the clutch disc 5 cooperate with a fourth friction surface 11 of the pressure plate 2.
- the third friction surface 10 of the clutch disc 5 is formed similar to the second friction surface 9 of the clutch disc 5, but is used to the side of the pressure plate 2, since the second friction lining 22 is attached to the pressure plate 2 facing side of the clutch disc 5 on the clutch disc 5.
- the first friction lining 19 and the second friction lining 22 are integrally connected to the clutch disc 5. Alternatively, they may also be formed as separate friction linings 19 and 22, which are fastened by means of a fastening means to the clutch disc.
- first elevations 12 are arranged.
- the number of first bumps 12 is four. These elevations 12 all extend by the same distance in the axial direction to the first friction surface 8 of the pressure plate 6. That the elevations 12 extend towards the pressure plate 6 in a direction parallel to the axis of rotation 4.
- These elevations 12 are arranged on the first friction lining 19 of the clutch disc 5, that they are spaced in the radial plane at the same radial distance from each other. This means that the tip 14 of two adjacent first elevations 12 are always separated by the same distance along this radial plane.
- each of the first elevations 12 is arranged to its adjacent elevation 12, that their foot region 13, that is connected to the first friction lining 19 base, directly to the foot region 13 of the adjoining this elevation 12.
- the second friction surface 9 forms a wave-shaped outer contour, which extends substantially along the radial plane.
- this waveform can be described as shown graphically in FIG. 4 that the amplitude of this star Ren contour wave (meaning: contour of the wave-shaped second friction surface 9), the axial distance between the foot portion 13 and the elevation point 14 is.
- the wavelength then corresponds to the radial distance between two elevation peaks 14 of two adjacent first elevations 12.
- the first friction surface 8 of the pressure plate 6 is in the opposite direction to this the first elevations 12 having second friction surface 9 of the friction lining 19 is formed.
- Each first elevation 12 is received in an oppositely shaped recess 15, hereinafter also referred to as the first recess 15, received in the first friction surface 8 of the pressure plate 6.
- the opposite design of the second friction surface 9 to the first friction surface 8 is meant that these two friction surfaces 8 and 9 are complementary to each other, that is, the first friction surface 8 of the pressure plate 6 has a negative to the second friction surface 9 formed shape.
- the first elevations 12 are therefore flat against the first friction surface 8 and fill the first wells 15 completely.
- the first friction surface 8 of the pressure plate 6 is configured wave-shaped, but in opposite directions to the second friction surface 9 of the clutch disc 5.
- the radial distance between the individual valley areas 16 corresponds to the radial distance of the adjacent elevation peaks 14 of the first elevations 12.
- the third friction surface 10, ie that friction surface 10 of the second friction lining 22 has elevations 17, hereinafter referred to as second elevations 17, on.
- the clutch disc is designed symmetrically in the region of its two friction linings 19 and 22 such that the friction surfaces 9 and 10 of the first friction pad 19 and the second friction pad 22 are symmetrical to one another with respect to a radial plane defined by the center of the clutch disc 5.
- the second elevations 17 are formed in shape symmetrical to the first elevations 12.
- the second elevations 17 thus point in the axial direction to the pressure plate 2 towards the same Clearre- ckung as the first elevations 12 to the pressure plate 6 and are radially spaced from each other in their foot areas 13 in the same way.
- the second friction lining 22 consequently also forms, by means of its friction surface 10, the third friction surface 10, a wave-like surface.
- shaped outer contour, wherein the rigid contour wave is also defined by the axial distance between a survey peak 14 and the adjoining foot region 13 and the wavelength, ie the radial distance between two adjacent elevations 17 to each other.
- the fourth friction surface 1 1 of the pressure plate 2 is complementary to the third friction surface 10 again, so designed in opposite directions.
- the fourth friction surface 1 1 also recesses 18, hereinafter referred to as second recesses 18.
- the fourth friction surface 1 1 is also negative with respect to its contour shape to the third friction surface 10 is formed.
- the second elevations 17 also extend in the axial direction (parallel to the axis of rotation 4) in such a way that they completely fill the second depressions 18 in the pressure plate 2. Viewed in cross section, there is also a flat and complete contact between the third and the fourth friction surface 10 and 11.
- the third friction surface 10 of the friction lining 19 in abutment on a fourth friction surface 1 1 comprehensive surface of the pressure plate 2.
- the second friction surface 9 of the friction lining 19 then abuts a, her opposite surface of the pressure plate 6, which surface is the first Friction surface 8 includes. Due to the sufficient contact pressure of the pressure plate 6 against the axially displaceable clutch disc 5 and thus against the pressure plate 2 allows in the engaged state, a sufficiently high frictional force between the individual friction surfaces 8, 9, 10 and 1 1, that the pressure applied to the plate 2 engine torques to the Transmission not shown here will be forwarded.
- the second clutch disc 23 shown in FIG. 3 substantially corresponds to the clutch disc 5, hereinafter also referred to as the first clutch disc 5, of the previously described FIGS. 1, 2 and 4 of the first exemplary embodiment. Only in the number of first and second elevations 12 and 17, the two clutch plates 5 and 23 differ. While the first clutch plate 5 is executed with four first and second elevations 12 and 17 on the second and third friction surface 9 and 10, have the Friction surfaces 9 and 10 of the second clutch plate 23 each have five first and five second elevations 12 and 17.
- the first elevations 12 and the second elevations 17 extend in the direction of FIG. sentlichen completely around the entire circumference of the friction linings 19 and 22 of the clutch disc 23, 5, around. These are then in corresponding recesses of the pressure plate 6 and the pressure plate 2 in the engaged state fitting.
- Each of these first and second elevations 12 and 17 of the friction linings 19 and 22 are arranged on the clutch disc 23, 5 so that they are concentric about the axis of rotation 4 around. Through this concentric arrangement, the entire clutch disc 23, 5 is safely centered in operation to the axis of rotation 4.
- a clutch disk 23, 5 can also have transverse grooves 20 incorporated in the friction linings 19 and 22 in the first and / or second friction surfaces 9 and 10.
- These grooves 20 extend in a radial plane, ie the plane on which the rotation axis 4 is perpendicular, from the rotation axis near the inside of the friction lining 19, 22 to a rotary axis remote outside of the friction lining 19, 22 and share the individual elevations 12 and 17 of the second and third friction surface 9 and 10 geometrically into a plurality of subregions.
- the grooves 20 are introduced, for example, by a machining method, wherein preferably only the elevations 12 and 17 are removed and the foot region 13 remains unsurfaced.
- the grooves 20 are preferably not exactly as radial lines running, so as grooves 20 which extend from the center of the clutch disc 23, 5 straight to the outside of the friction lining 19, 22, but extend as straight lines to these radial lines, in a common Considered radial plane, have a certain angular offset.
- the grooves 20 are running transversely to the radial lines running.
- the number of grooves 20 may be different.
- twelve grooves 20, around the circumference of the friction lining 19, 22 around uniformly distributed in the friction lining 19, 22 introduced.
- the grooves 20 are arranged at substantially the same angular distance from each other, that is, each groove 20 at the same radius of the friction lining 19, 22 has the same angular distance to an adjacent groove 20.
- the disengaged state of the first embodiment is shown in detail for the sake of completeness, in which state the plate spring 7 is guided around a support element 21 connected to the housing 3 by means of the disengagement system, not shown here, that the pressure plate 6 for reaching this disengaged state is pushed away from the pressure plate 2.
- This increases the distance between the pressure plate 6 and the pressure plate 2 and the first friction surface 8 of the pressure plate 6 is removed from the second friction surface 9.
- the disengaged position there is no longer sufficient pressing force by the pressure plate 6 the clutch disc 5 and exerted on the pressure plate 2, resulting in that the third friction surface 10 is spaced from the fourth friction surface 1 1. Clutch disc 5 and pressure plate 2 are then no longer frictionally engaged.
- the dry running friction clutch 1 shown here according to the invention can also be embodied as a wet clutch and, in this context, used as a further development, for example in the form of a double clutch.
- first and second elevations 12 and 17 may be configured in a sawtooth shape according to another embodiment, alternatively to the described waveform. Also, the first and second recesses 15 and 18 then have a negative sawtooth contour. The elevations 12 and 17 are then inserted in the coupled state in the negative thereto designed first and second recesses 15 and 18 and flat against these.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112014002735.9T DE112014002735A5 (en) | 2013-06-06 | 2014-05-12 | Friction clutch for a drive train of a motor vehicle |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013210501.0 | 2013-06-06 | ||
DE102013210501 | 2013-06-06 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014194903A1 true WO2014194903A1 (en) | 2014-12-11 |
Family
ID=50877220
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2014/200205 WO2014194903A1 (en) | 2013-06-06 | 2014-05-12 | Friction clutch for a drive train of a motor vehicle |
Country Status (2)
Country | Link |
---|---|
DE (2) | DE102014208897A1 (en) |
WO (1) | WO2014194903A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN111156263A (en) * | 2018-11-08 | 2020-05-15 | 博格华纳公司 | Lamina, lamina clutch or brake and method for producing lamina |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19901052A1 (en) * | 1999-01-14 | 2000-07-27 | Mannesmann Sachs Ag | Double cone clutch for vehicle has angled linings increasing effective surface area without increase in overall radial dimensions and projection fits into trough giving jamming effect |
DE10015206A1 (en) * | 1999-04-01 | 2000-10-05 | Luk Lamellen & Kupplungsbau | Simple clutch with limited flexibility without springs is for road vehicle, and clutch lining material is linked to clutch disc along flat plane with axial projections forming troughs and peaks |
EP2077399A1 (en) * | 2007-09-27 | 2009-07-08 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Friction coupling with spherical friction contact partners |
DE102011079840A1 (en) | 2010-08-09 | 2012-02-09 | Schaeffler Technologies Gmbh & Co. Kg | friction clutch |
-
2014
- 2014-05-12 DE DE201410208897 patent/DE102014208897A1/en not_active Withdrawn
- 2014-05-12 DE DE112014002735.9T patent/DE112014002735A5/en not_active Withdrawn
- 2014-05-12 WO PCT/DE2014/200205 patent/WO2014194903A1/en active Application Filing
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19901052A1 (en) * | 1999-01-14 | 2000-07-27 | Mannesmann Sachs Ag | Double cone clutch for vehicle has angled linings increasing effective surface area without increase in overall radial dimensions and projection fits into trough giving jamming effect |
DE10015206A1 (en) * | 1999-04-01 | 2000-10-05 | Luk Lamellen & Kupplungsbau | Simple clutch with limited flexibility without springs is for road vehicle, and clutch lining material is linked to clutch disc along flat plane with axial projections forming troughs and peaks |
EP2077399A1 (en) * | 2007-09-27 | 2009-07-08 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Friction coupling with spherical friction contact partners |
DE102011079840A1 (en) | 2010-08-09 | 2012-02-09 | Schaeffler Technologies Gmbh & Co. Kg | friction clutch |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN111156263A (en) * | 2018-11-08 | 2020-05-15 | 博格华纳公司 | Lamina, lamina clutch or brake and method for producing lamina |
CN111156263B (en) * | 2018-11-08 | 2023-08-18 | 博格华纳公司 | Disc, multiplate clutch or brake and method of manufacturing a disc |
Also Published As
Publication number | Publication date |
---|---|
DE112014002735A5 (en) | 2016-03-03 |
DE102014208897A1 (en) | 2014-12-11 |
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