• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a friction plate (10) with an annular, in the circumferential direction (13) closed lamellar body (4, 9) having a plurality of recesses, and by a radially inner end face (11) and a radially outer end face (24) is limited. The recesses (14) are at least partially slot-shaped and have a plurality of subregions (20 to 23), wherein at least two subregions (20 to 23) extend in mutually different directions, and further wherein the slot-shaped recesses (14) spaced from the radially inner End face (11) and the radially outer end face (24) are formed.
    公开号:AT519131A4
    申请号:T50808/2016
    申请日:2016-09-12
    公开日:2018-04-15
    发明作者:
    申请人:Miba Frictec Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a friction plate with an annular, closed in the circumferential direction fin body on which optionally at least one friction lining is arranged, wherein the plate body has a plurality of recesses. Furthermore, the invention relates to a disk set comprising in the axial direction a plurality of friction disks arranged one behind the other.
    Friction blades for Lamellenreibsysteme are known per se from the prior art. These can be designed with or without friction lining, depending on whether it is an outer or inner plate. The friction plates are located on plate carriers and are brought together by an actuating device, if necessary, in frictional engagement with each other.
    Friction disks with damping are already known from the prior art. Priority is, however, the vibration damping in the foreground of consideration.
    Object of the present invention is to provide a slat friction system with reduced noise available.
    The object is achieved in the friction plate mentioned above in that the recesses are at least partially slit-shaped and have a plurality of portions, wherein at least two portions extend in mutually different directions, and further wherein the recesses beab-stands to the radially inner end wall and the radial outer end wall are formed and / or that in the embodiment of the disk body with friction lining, the slot-shaped recesses are arranged in the friction lining and the disk body is optionally free of recesses in this embodiment. Further, the object is achieved with a disk set, which has at least one friction plate according to the invention, solved.
    Through the slot-shaped recesses of the "sound body" of the friction plate is "divided" into smaller, acoustically independent body, whereby the noise behavior of the friction plate changes to a lower level. The total noise level decreases. Thus, the noise development is already influenced, so that additional damping devices or damping elements are not necessary. In addition, body vibrations of the friction plate are partially reflected and scattered on the side walls of the slots, so that hinder the vibrations by phase shift in the friction plate itself.
    The noise damping lamella is easy to produce, so that it is also easy to implement on an industrial scale. In addition, can be done by the arrangement and the formation of the slot-shaped recesses easy adaptation to different uses of the friction plate. So it is possible with the friction plate system damping.
    According to a preferred embodiment, it is provided that the recess are formed as apertures. It can thus the noise attenuation can be further improved. For example, it is possible that the areas around the slot-shaped recesses, e.g. due to the configuration of the slot-shaped recesses can be designed tongue-shaped, are set in vibration, these vibrations can be done with a frequency that lead in the overall frequency range of the noise of the friction plate to a noise reduction.
    It can also be provided according to another embodiment that the slot-shaped recesses of at least one further, not slot-shaped, recess, in particular a further breakthrough, are interrupted. These larger recesses affect the coolant flow. In particular, they can be flowed through in training as further breakthroughs of the coolant. Thus, the coolant, for example, a cooling oil, not only contributes to the cooling of the friction plate, but can also be used for noise reduction.
    In order to better adapt the friction plate to a wide variety of applications, and thus not to reduce the above effects, may be provided according to various embodiments of the friction plate, that on the disc body, a friction lining is arranged and that at least a portion of the recesses in the radial direction below the friction lining is formed, and / or that a friction lining is arranged on the disk body and that at least a portion of the recesses formed in the axial direction below the friction lining, and / or that on the disk body, a friction lining is arranged and that at least a portion of the recesses in axial direction through the friction lining and the plate body extends continuously.
    It can also be advantageous if at least some of the recesses are at least partially filled with a material which has a lower rigidity than the lamellar body. It can thus be achieved that by the filling of the slots, the vibration behavior of the acoustically effective body of the friction plate can not fully form, but influence or hinder each other the vibrations. It can thus be achieved a further reduction of the noise of the friction plate.
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    In each case they show in (strongly) simplified, schematic representation:
    1 shows a detail of a disk pack according to the prior art in side view;
    2 shows a first embodiment of the friction plate in an oblique view.
    3 shows a second embodiment of the friction plate in an oblique view.
    4 shows a third embodiment of the friction plate in an oblique view.
    5 shows a fourth embodiment of the friction plate in an oblique view.
    6 shows a fifth embodiment of the friction plate in an oblique view.
    7 shows a sixth embodiment of the friction plate in an oblique view.
    8 shows a seventh embodiment variant of the friction plate in oblique view;
    9 shows an eighth embodiment of the friction plate in an oblique view;
    10 shows a ninth embodiment of the friction plate in an oblique view.
    By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. Also, the location information chosen in the description, such as top, bottom, side, etc. related to the immediately described and illustrated figure and to transmit mutatis mutandis to the new situation in a change in position.
    In Fig. 1, a section of a known disk pack 1 is shown. The disk set 1 has a plurality of inner disks 2 and a plurality of outer disks 3, which can also be referred to as friction disks. The inner disks 2 are arranged alternately with the outer disks 3 in an axial direction 4. Via a corresponding actuating mechanism, the inner disks 2 are adjustable relative to the outer disks 3 in the axial direction 4, so that a frictional engagement is formed between the inner disks 2 and the outer disks 3.
    The inner disks 2 have an at least approximately annular disk body 5 with a first surface 6 and one of these opposite in the axial direction 4 second surface 7. At least one friction lining 8 is arranged in each case on the first and / or the second surface 6, 7. The inner plates 2 are so-called lining plates.
    The friction linings 8 may be formed according to the prior art.
    It can also be provided that the inner disks 2 have no friction linings 8.
    The outer disks 3 also have an at least approximately annular disk body 9, which, however, is free of friction linings. The outer disks 3 are therefore the so-called counter blades, which can be spent in frictional engagement with the friction linings 8 of the inner disk 2. However, there is also the possibility that the friction linings 8 are arranged on the outer disks 3, in particular if no friction linings 8 are arranged on the inner disks 2.
    Preferably, the inner plates 2 and the outer plates 3 made of a steel or include this. However, they can also consist of another suitable, in particular metallic, material. For example, the inner plates 2 may consist of a resin-bonded composite material or of a sintered material, as is known per se. The friction linings 8 arranged on the inner disks can consist, for example, of a carbon material or of a resin-bonded, optionally fiber-reinforced, paper covering or a resin-bonded covering or a sintered material. Such friction linings are known from the prior art, so reference is made to this. It is also possible that the friction linings 8 are arranged on a support (the above-mentioned lamellar body 5). The carrier is preferably made of steel or another suitable material.
    This basic structure of a disk set 1 is known from the prior art. For further details, therefore, reference is made to this relevant prior art.
    The disk set 1 is part of a disk friction system, for example, a (wet-running) multi-plate clutch, a brake, a holding device, a differential lock, etc.
    In Fig. 2, a first embodiment of a friction plate 10 is shown, as used in the plate pack 1 of FIG. Specifically, an inner fin 2 is shown as shown in FIG. However, the friction plate 10 can also be an outer plate 3 (FIG. 1), in which case it has no friction lining 8.
    The friction plate 10 is provided in particular for the so-called wet-running operation.
    The friction plate 10 may have at least one driver element 12, for example in the form of an internal toothing, on a radially inner end face 11.
    It should be mentioned at this point that the outer disks 3 may have at least one driver element on a radially outer end face. About the driver elements, a rotationally fixed connection with a further component of the disk friction system, for example a shaft in the case of the inner disk 2 or the housing of the disk friction system in the case of the outer disk 3, are produced, as is known per se.
    It is also possible for the inner disks 2 or the outer disks 3 to be so-called free-floating disks, that is to say they have no such driver elements, as is known per se.
    The disk body 5 of the friction disk 10 is formed closed in a circumferential direction 11.
    It should be noted at this point that in the following only the fin body 5 is treated. In the event that the friction disk is an outer disk 3 (FIG. 1), the following explanations for the disk body 5 can also be transmitted to the disk body 9 of the outer disk, as long as it is likewise designed according to the invention.
    Preferably, the disk body 5 is integrally formed. But it is also possible that the lamellar body 5 is composed of a plurality of interconnected segments.
    In the disk body 5 of the friction plate 10 a plurality of recesses 14 are provided or formed. The recesses 14 are designed according to a preferred embodiment as breakthroughs, thus extending in the axial direction 4 (FIG. 1) continuously through the lamellar body fifth
    The recesses 14 are at least partially formed as a slot-shaped, so as slots 15. In the illustrated embodiment, the recesses are designed entirely as slots 15.
    In the embodiment variant of the friction disk 10 shown in FIG. 7, seven recesses 14 or openings are provided. It should be noted, however, that this number of recesses 14 is not restrictive. Rather, the number of recesses 14 may be between 4 and 40. The exact number depends on the particular geometry and the intended application of the friction plate 10, that is, for example, whether it is used in a brake or a clutch, and can be determined by the skilled person based on the teaching of the present description simply with a few experiments.
    In the illustrated embodiment of the friction plate 10, the recesses 14 in the circumferential direction 13 are distributed evenly distributed in the disk body 4. But it is also possible, although this is not preferred, that the recesses 13 are arranged distributed unevenly in the circumferential direction 13 of the friction plate 10. A distance 16 between two recesses 14 adjacent in the circumferential direction 13 can therefore be the same for all recesses 14 or it can be smaller or larger between at least two adjacent recesses 14 than between the remaining, respectively adjacent recesses 14.
    The slot-shaped recesses 14 have compared to a width 17 (in view in the direction of the axial direction 4 viewed) on a much larger overall length. In particular, the overall length in the context of the invention may generally be greater by a value selected from a range of 5 times to 50 times, in particular from a range of 10 times to 40 times the width 17.
    The width 17 of the slot-shaped recesses 14 may be generally selected within the scope of the invention from a range of 50% to 150%, in particular from a range of 50% to 100%, a thickness 18 of the lamella body 5 (ie without friction linings 8) in the direction considered the axial direction 4.
    As can be seen from FIG. 2, the slot-shaped recesses 14 do not run in a straight line but have a multiple reversal of direction over their entire length. In the specific embodiment, the slot-shaped recesses on a three-way reversal. In the context of the invention, a fictive envelope 19, which is viewed in the direction of the axial direction 4, generally encloses an area which is between 1% and 30%, in particular between 5% and 20%, of the total area of the lamellar body 5 (viewed in the same direction ). The envelope 19 is based on an enveloping circle that figure which surrounds a slot-shaped recess 14 on the outer circumference, as indicated by dashed lines in Fig. 2.
    The slot-shaped recesses 14 therefore preferably have (within the scope of the invention generally) a plurality of subregions which run in mutually different directions. 2, the slot-shaped recesses 14 have four subregions 20 to 23, which are arranged so that the slot-shaped recesses 14 are approximately V-shaped, viewed in the direction of the axial direction 4 (FIG. 1) the end regions are extended and designed to extend radially inwards, as can be seen from FIG. Transitions between the subregions 20 to 23 are preferably rounded (in the context of the invention in general).
    In the context of the invention, the slot-shaped recesses 14 are generally arranged and / or formed at a distance both from the radially inner end face 11 and from a radially outer end face 24 of the disk body 5. The smallest distance to the radially inner end face 11 can be between 1% and 40%, in particular between 5% and 30%, of the outer diameter of the friction disk 10. , The smallest distance to the radially outer end face 24 may be between 1% and 40%, in particular between 5% and 30%, of the outer diameter of the friction disk 10.
    In addition to the slot-shaped recesses 14 of the lamellar body 5 may also have additional openings 25, which serve the oil guide and thus the cooling of the friction plate. The openings 25 pass through the lamellar body 5 in the axial direction 4 (FIG. 1).
    In the context of the invention, generally one or more, for example all, inner disks 2 and / or one or more, for example all, outer disks 3 (FIG. 1) can be formed by the friction disk 10.
    FIGS. 3 to 10 show different and, if appropriate, separate variants of the friction disk 10, the same reference numerals and component designations being used for the same parts as in FIGS. 1 and 2. In order to avoid unnecessary repetition, reference is therefore made to the above detailed description of these parts and reference is made and therefore can be read in the following embodiments of the friction plate 10.
    With the illustrations in Figs. 3 to 5 it should be clarified that the slot-shaped recesses 14, i. the slots 15, may have different gradients in order to influence the reduction of noise during operation of the friction plate 10 can. However, it should be pointed out once again that the concretely illustrated embodiments of the slot-shaped recesses are not restrictive.
    For example, the slot-shaped recesses 14, viewed in the direction of the axial direction 4 (FIG. 1), may be at least approximately W-shaped (FIG. 3) corresponding at least approximately to the image of a spiral spring (viewed in side view) (FIGS Fig. 5, in the latter the check mark) may be formed.
    In general, it should be noted that the slot-shaped recesses 14 of a friction plate 10 can also have mutually different shapes. It is also generally possible that the slot-shaped recesses 14 may be arranged at different radial heights in the friction plate 10, although they are shown lying in the illustrations of FIGS. 2 to 10 each at the same radial height.
    The variants of embodiment of the friction disk 10 according to FIGS. 2 to 5 have in common that at least part of the slot-shaped recesses 14, in particular all, are arranged or formed in the radial direction below the friction lining 8. By the term "at least one part" is meant a number of the total number of recesses 14, so that therefore all subregions 20 to 23 of a recess 14 are arranged or formed in the radial direction below the friction lining 8. But it is also possible that not all portions 20 to 23 of a recess 14 are arranged or formed in the radial direction below the friction lining 8, but one or more portion (s) 20 to 23 of a recess 14 in the axial direction 4 (Fig. 1) is arranged or formed below the at least one friction lining 8 or are.
    6 to 8 show variant embodiments of the friction plate 10, in which at least a portion of the slot-shaped recesses 14 in the axial direction 4 (Fig. 1) below the at least one friction lining 8 is arranged or formed.
    With regard to "at least one part", the above applies.
    In Figs. 6 to 8, a part of the friction pad 8 has been omitted to make the slot-shaped recesses 14 visible. Of course, the friction plate 19, the friction lining 8 in these areas.
    It can further be seen from these FIGS. 6 to 8 that the friction lining 8 can also be formed by a plurality of friction lining segments arranged side by side in the circumferential direction 13 and spaced from each other.
    In this embodiment variant of the friction disk 10, the slot-shaped recesses 14 (or at least part of the slot-shaped recesses 14, i.e. at least some slot-shaped recesses 14) are covered on one side by the friction lining 8 or on both sides by the friction linings 8, in particular completely covered. In this case, the adhesive with which the at least one friction lining 8 is connected to the lamellar body 5 or 9 in the case of FIG. 8, which shows an outer lamella 3, can fill at least partially, in particular completely, at least the slot-shaped recesses 14. It is thus achieved a power flow across the slot-shaped recesses 14 away, but due to the different materials of lamellar body 5, 9 and adhesive the construction of in-phase vibrations is prevented. The vibrations hinder each other, whereby the noise reduction during operation of the friction plate 10 is achieved.
    In the context of the invention, at least part of the slot-shaped recesses 14, in particular all, can generally be filled at least partially, in particular entirely, with a material which has a lower rigidity than the plate body 5, 9. This material can be selected, for example from a group comprising or consisting of polyurethanes, elastomers, such as Natural rubber, (carboxylated) nitrile-butadiene rubber, isoprene rubber, silicone elastomers, etc.
    It should be noted in this context that the slot-shaped recesses 14 of these embodiments of the friction plate 10 may also be at least partially filled by the friction lining 8 or the friction linings 8. For example, this can be achieved by the friction lining 8 or the friction linings 8 are pressed into the slot-shaped recesses 14. It can thus be achieved a positive connection between the lamellar body 4, 9 and the friction lining 8 or the friction linings 8, which can improve the bond strength between friction lining 8 and lamellar body 4, 9.
    As can be seen from FIGS. 7 and 8, according to a further embodiment variant, the friction plate 10 can be provided, which can be interrupted by at least one part, in particular all, of the slot-shaped recesses 14 of at least one further, not slot-shaped, recess 26, in particular a further opening , These further recesses 26 may be formed or arranged in the course of the slot-shaped recesses 14, ie between two subregions 20, 21, or at least one end, in particular both ends, of the slot-shaped recesses 14. It may be provided that the slot-shaped recesses 14 without direction change, so at least approximately rectilinear, as shown in FIG. 8 can be seen.
    Also in these embodiments of the friction plate, the above-described openings 25 may be provided for the coolant guide in the disk body 5, 9.
    The further recesses 26 can be used to guide the coolant. But you can also contribute to changing the acoustic behavior of the friction plate 10.
    In general, the apertures 25 and / or the further recesses 26 in the axial direction 4 (FIG. 1) may have different cross-sectional shapes. For example, they may be circular or elliptical or in the form of a polygon (quadrangular, pentagonal, hexagonal, heptagonal, octagonal, etc.), mixtures of which are also possible within a friction plate 10.
    FIG. 7 shows a further embodiment variant of the friction plate 10, in which openings 27 are also formed in the friction lining 8 (or the friction linings 8). With regard to the shape of these openings 27, the statements made with respect to the recesses 26 apply.
    The openings 27 are arranged, in particular in the axial direction (FIG. 1), congruently with the recesses 26, in particular openings, ie. in the axial direction 4 completely overlapping the recesses 26. It can thus a coolant flow through the friction plate 10 in the axial direction 4 can be achieved.
    FIGS. 9 and 10 show variant embodiments of the friction plate 10, in which the slot-shaped recesses 14 are arranged or formed in the friction lining 8 or the friction linings 8. The slot-shaped recesses 14 may be arranged wholly or partially in the friction lining 8 and the friction linings 8, wherein in the latter case, the remainder of the slot-shaped recesses in the lamellar body 5 is arranged or formed. It is also possible that only some of the slot-shaped recesses 14 in the friction lining 8 and the
    Friction linings 8 and the rest of the slot-shaped recesses 14 is arranged or formed in the disk body 5. In the event that slot-shaped recesses 14 are arranged or formed both in the friction lining 8 and the friction linings 8 and in the lamellar body 5, it can be provided that these slot-shaped recesses 14 have the same geometry and / or size. It can further be provided that the slot-shaped recesses 14 in the friction lining 8 and the friction linings 8 in the axial direction 4 (Fig. 1) are above the slot-shaped recesses 14 of the disk body 5, so that the slot-shaped recesses 14 in the axial direction 4 is a continuous Training Breakthrough. This can apply to all slot-shaped recesses 14 or only some, that is to say part of the slot-shaped recesses 14.
    Unlike the above statements on the slot-shaped recesses 14 in the disk body 5, the slot-shaped recesses 14 may be formed in the friction lining 8 or the friction linings 8 on the radially inner end face and / or the radially outer end face of the friction lining 8 or the friction linings 8 starting.
    FIG. 10 shows an alternative form of the slot-shaped recesses 14, in which they are designed such that they enclose a tongue-shaped region of the friction lining 8.
    The embodiment variants of the friction plate 10, in which the slot-shaped recesses 14 are arranged or formed exclusively in the friction lining 8 or the friction linings 8, are preferably used in friction plates 10 with so-called spreading friction linings.
    The embodiments show possible embodiments, it being noted at this point that also various combinations of the individual embodiments are possible with each other.
    For the sake of order, it should finally be pointed out that in order to better understand the construction of the friction disk 10, these or their components have not necessarily been shown true to scale.
    REFERENCE SIGNS LIST 1 lamella packet 2 inner lamella 3 outer lamella 4 axial direction 5 lamellar body 6 surface 7 surface 8 friction lining 9 lamella body 10 friction lamella 11 end face 12 entrainment element 13 circumferential direction 14 recess 15 slot 16 distance 17 width 18 thickness 19 wrapping 20 partial area 21 partial area 22 partial area 23 partial area 24 end surface 25 Breakthrough 26 recess 27 breakthrough
    权利要求:
    Claims (8)
    [1]
    claims
    1. friction plate (10) with an annular, in the circumferential direction (13) closed lamellar body (4, 9) on which optionally at least one friction lining (8) is arranged, wherein the lamellar body (4, 9) has a plurality of recesses, and by a radially inner end face (11) and a radially outer end face (24) is limited, characterized in that the recesses (14) are at least partially slit-shaped and have a plurality of subregions (20 to 23), wherein at least two subregions (20 to 23) extending in mutually different directions, and further wherein the slot-shaped recesses (14) spaced from the radially inner end face (11) and the radially outer end face (24) are formed and / or that in the embodiment of the disk body (4, 9) with friction lining (8) slot-shaped recesses (14) in the friction lining (8) are arranged and the lamellar body (4, 9) in this embodiment optionally free of Recesses is.
    [2]
    2. friction plate (10) according to claim 1, characterized in that the slot-shaped recesses (14) are formed as openings.
    [3]
    3. friction plate (10) according to claim 1 or 2, characterized in that the slot-shaped recesses (14) of at least one further, not slot-shaped, recess (26), in particular a further opening, are interrupted.
    [4]
    4. friction plate (10) according to one of claims 1 to 3, characterized in that that at least a part of the slot-shaped recesses (14) in the radial direction below the friction lining (8) is formed.
    [5]
    5. friction plate (10) according to one of claims 1 to 3, characterized in that at least part of the slot-shaped recesses (14) in the axial direction below the friction lining (8) is formed.
    [6]
    6. friction plate (10) according to one of claims 1 to 3, characterized in that at least a portion of the slot-shaped recesses (14) in the axial direction through the friction lining (8) and the lamellar body (4, 9) extends continuously.
    [7]
    7. friction plate (10) according to one of claims 1 to 6, characterized in that at least a portion of the slot-shaped recesses (14) is at least partially filled with a material having a lower stiffness, as the lamellar body (4, 9).
    [8]
    8. plate pack (1) comprising in the axial direction (4) a plurality of successively arranged friction plates (10), characterized in that at least one of the friction plates (10) is designed according to one of claims 1 to 7.
    类似技术:
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    DE2152674C3|1978-04-27|Friction clutch
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    DE102007053758A1|2009-03-19|Segmented carrier plate for a lamella and lamella with such a segmented carrier plate
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    DE19856688B4|2008-06-26|Magnetic structure for a linear motor
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    DE102018005271A1|2019-01-10|friction plate
    AT518482B1|2018-08-15|multi-plate clutch
    DE102017107206B4|2018-07-12|Friction disc and wet-running multi-disc clutch
    EP3179124B1|2018-07-25|Friction disc
    AT521575A1|2020-03-15|Friction device
    DE102018003093B4|2020-10-22|Lamella carrier
    DE102018005273A1|2019-01-10|friction device
    DE112009004796B4|2013-06-27|Viscous coupling and suspension device
    DE102006005349A1|2006-09-07|Torsional vibration damper has each spring of first group arranged on larger diameter connected in series with spring of second group arranged on smaller diameter between input and output parts
    AT522609A1|2020-12-15|Friction device
    WO2019204846A1|2019-10-31|Method for setting the coefficient of friction of a friction disk
    同族专利:
    公开号 | 公开日
    CN109690107A|2019-04-26|
    DE112017004567A5|2019-07-25|
    WO2018045405A1|2018-03-15|
    AT519131B1|2018-04-15|
    US20190195293A1|2019-06-27|
    引用文献:
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    DE102016201508A1|2016-02-02|2017-08-03|Schaeffler Technologies AG & Co. KG|scuffing|DE202018002101U1|2018-04-25|2018-05-11|Miba Frictec Gmbh|friction plate|
    AT522252A1|2019-03-13|2020-09-15|Miba Frictec Gmbh|Friction assembly|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50808/2016A|AT519131B1|2016-09-12|2016-09-12|friction plate|ATA50808/2016A| AT519131B1|2016-09-12|2016-09-12|friction plate|
    CN201780054848.4A| CN109690107A|2016-09-12|2017-09-07|Frictional disk|
    DE112017004567.3T| DE112017004567A5|2016-09-12|2017-09-07|friction plate|
    US16/328,031| US20190195293A1|2016-09-12|2017-09-07|Friction plate|
    PCT/AT2017/060215| WO2018045405A1|2016-09-12|2017-09-07|Friction plate|
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