• 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:
    A torsion-damping device comprises two coaxial parts which are mounted to rotate relative to one another within predetermined limits of relative angular displacement and which are free axially relative to one another within the predetermined limits of axial spacing, elastic means which are interposed circumferentially between said coaxial parts and which comprise at least one block of elastically deformable material located in a housing which is fast partly with one of said coaxial parts and partly with the other of these, and friction means which act axially between said coaxial parts and which generate between them a frictional torque during their relative angular displacement each of these blocks confined circumferentially in the housing in which it is located, so that when there is a relative angular displacement between the coaxial parts, the or each block generates between the parts an axial force urging them apart, with the result that the frictional torque caused by the friction means is modulated.
    公开号:SU1256702A3
    申请号:SU823395603
    申请日:1982-02-23
    公开日:1986-09-07
    发明作者:Луазо Пьер
    申请人:Валео (Фирма)；
    IPC主号:
    专利说明:

    The inner part of each bravado of the casing has an additional recess in the form of a collar, the inner surface of which, together with the outer surface of the elastic block, limits the cavity equidistant to the ends of the elastic block.
    5. The coupling according to claim 1, about tl and h and rain and the fact that at least one through longitudinal cut is made on the outer surface of each elastic element.
    6. The coupling according to claim 1, about tl and h and y and the fact that at least one annular transverse collar is made on the outer surface of each elastic element.
    7. Muff prp.1, characterized by the fact that the elastic elements are cylindrical and arranged radially along the generatrix, moreover, elastic elements are installed in the through holes of the coaxial parts of the support element with the possibility of contact with both protrusions through holes.
    The invention relates to mechanical engineering, in particular to the automotive industry, where it can be used in clutches.
    The purpose of the invention is to increase reliability by providing a gradual increase in friction between two axially displaceable coaxial parts of the support element.
    Fig. 1 shows a clutch friction disc, side view; figure 2 is the same, a longitudinal section; on fig.Z - section aa in figure 1 ,; 4 is the same in the operating state; Fig. 5 is a diagram illustrating the operation of the device; figure 6 - friction disc option; Fig.7 - section BB in Fig.6; on fig.Z - section bb In figure 6; in fig. 9-14 - installation of elastic blocks, options; 15 and 16 — installation of retaining means, va8. Clutch a according to claim 1, about t l and m and h-m a so that the elastic elements are made in the form of a truncated knus installed radially along a generator, with the smallest base of the truncated cone located in the direction of the axis of the disk.
    9. The coupling according to claim 1, about tl and h and y-1D and the fact that the elastic elements are made spherical shape.
    10. The coupling according to claim 1, in which it is provided with elastic means, the tightening element of the holding means is made in the form of studs, and the said elastic means are installed with a pre-stress on the studs .
    11. Coupling according to Claim 1, except that it is provided with a crown located above one of the coaxial parts of the support element, which rigidly connects the middle parts of the studs with retaining means, and the shoulders of the latter are made in the form of a friction disk bent to the axis paws,
    Ryanta; in fig. 17 is a diagram illustrating the operation of the device according to an embodiment; 18 - .20 - the form of elastic blocks, variants; FIGS. 21 and 22 — retaining means and installation of friction elements, variants.
    Friction - clutch contains a support element that connects the hub I with the friction part of the disk with the friction linings 2 entering into it. The supporting element is made up of two coaxial, coaxial parts that are mounted with the possibility of rotation one relative to another in within a certain angular deviation with the possibility of axial movement within a certain axial space. One of the coaxial parts A, on the periphery of which is rigidly fixed
    friction lining 2, is complete in the form of a disk or annular flange 3.
    The other coaxial part B is designed as a flange 4, mounted parallel to flange 3 and at some distance from it, flange 4 is mounted radially on hub 1.
    Elastic elements, made in the form of blocks of an elastic deformable material, such as an elastomer, are installed uniformly along the circumference between the coaxial parts.
    In the embodiment shown in Figures 1-5, eight such blocks 5 are provided, each of which has a cylindrical shape and is in fact a segment of a cylindrical roller of circular cross section.
    Each of the blocks 5 is installed in the slot 6, partially made in one of the coaxial parts of the support element and partially in the other. The nests 6 are formed by concave shells 7 and 8 facing one another. The elastic unit 5 is located without a gap between the said shells and has at least one continuous contact line (FIG. 20) running circumferentially from one end to the other such in such a way that, within the angular deviation between the coaxial parts of the support element and along this contact line, block 5 is circumferentially closed in the corresponding slot 6.
    Each shell 7 or 8 of the housing is circumferentially connected to only one part of the support member.
    In Figures 1-5, shells of semi-cylindrical shape, i.e. their cross section has a semicircular shape, and from the ends they are open at both ends.
    45
    In flanges 3 and 4, there are through holes or notches 9 and 10, into which the shells 7 are freely inserted in the axial direction, and 8. Each of the shells is made with side flanges 11 and 12 in the form of supporting shelves whose planes are parallel to the opposite one. one other plane of the coaxial parts of the support element.
    Each of these sinks 7 and 8 (Figures 1-5) forms for the corresponding block 5 parallel to the axis of the device an infinite number of uninterrupted contact lines
    ts
    20
    25 o
    contact with friend5

    five
    2567024
    from one end of the goma.
    In the non-working state, the blot knots 5 are closed around the circumference in the raccoon 5 nests 6, so they provide the alignment of the coaxial parts A, B of the support: the relative element to each other.
    In addition, since between the inner peripheral surface of the flange 3 and the hub 1, the annular radial clearance 3 is intentionally left; these parts are mounted radially floating, i.e. radially free one relative to each other within a certain gap D and relatively elastic elements (blocks 5).
    Each block 5 is installed in the through-holes of the coaxial parts with the possibility of contacting almost both of their ends 13 and 14 with the opposite sides of C1; Thus, blocks 5 are capable of providing a flexible, social return of coaxial parts of one relative to another in the event of their axes displaced (centering).
    Axial parts A, B axially mount freely to one another. However, they are interconnected in the axial direction by means of holding means of a single action in such a way that their own movement. The movement can be carried out only in the same direction, i.e. in the direction of the axial approach of these coaxial parts. The unidirectional holding means include a first set of studs 15, oriented in axial pressure, and a second set of studs 16 fixed on the outer peripheral surface of the flange 4 fixed on the inner peripheral surface of the flange 3. Each stud 15 is screwed into the hole 17 in the flange 4, then passes with a gap through the flange-3, in which a prope-18 is provided for this purpose. A shoulder 19 formed by the base of the head 20 is provided for an abutment into the flange 3 at the end of the studs .15 Netz 3 in axial direction.
    35
    YU
    Friction. Elements that create between the coaxial, axes of the support element the moment of a triangle with deflected angles of the latter are set at a right angle relative to the studs 15. The friction elements (Figures 1-5) are a friction gaiter 21 installed between the flange (; m 3 (on the side opposite to the flange 4j and the distribution washer 22 abutting the shoulders 19 of the stud 15.
    For each stud 15, a spigot 23 is installed, extending from between the flange 4 and the distribution pipe 22.
    For example, the friction washer 21 through the canal; the bus 24 can be worn without a circular gap on the sleeve 23 in such a way that at the very beginning of the angular deviation between the coaxial parts L, B it comes into contact with the flange 4, being already in contact with the flange 3 Alternatively, it may be worn on sleeve 23 with some annular gap. In this case, its connection during rotation with flange 4 takes place after the annular gap disappears. In addition, the friction washer 2 may be divided into several ring sectors reinforced with, for example, glue on the distribution washer 22, which in this case is worn with or without a gap on the pin 5.
    Each of the studs 16, with its shoulder 25, formed by the base of the head 26, abuts against the flange 3 from the side opposite to the flange 4, while the passage without a gap through the holes made in the friction disk and in the flange 3. The pin 16 passes with a gap through the flange 4, thanks to the holes 27 provided on the outer periphery of the latter, and rests against the flange 4 with its occupant 32, which is a nut 29 screwed onto the end of the pin itself, which acts as an axial stop.
    The friction washers 30 are installed between the flange 4 on the side opposite to the flange 3 and the distribution washer 31 resting on the shoulders 28.
    Between the friction washer 30 and the flange. 3 out of sleeve spreader 32, put on pin 16. Friction washers 30 are put on spire


    KUK 16 through channels 33, prodvoglovannye with this ground.
    In the non-working position of the sink unit 7 and 8, forming the nest of each block 5, are located on the axis exactly opposite each other (FIG. 3). In this case, the angular deviation between the coaxial parts of L and B is absent.
    In accordance with the variant shown in phi. 6-8, the two sinks 7 and 8, forming the nest 6 of each block 3 of elastic deformable material, are integral parts of the corresponding flange 4 and are made directly on these flanges by the method of local deformation. In addition, the studs 15 and 16 are tabs 34 and 33, made together with washers from a single blank.
    In blocks 5, cuts can be made (Fig. 9). In the examples presented, we are talking about the open longitudinal 36, i.e. 6 notches, exit sch1 (x to that i-shi other side of block 5. In practice, these notches are through. In Fig. 9, there is one notch on each of the transverse sides of the block, and in Fig. 10 there are two notches. In addition, each block 3 is a segment of cylindrical roller, but in cross section it has a different shape than the semicircular 4
    It has a rectangular section (Fig. 9) and a section in the shape of a trapezoid with rounded edges (Fig. 10 /, and the shells 7 and 8 have a configuration corresponding to the shape of the blocks. The cutouts 36 impart rigidity to the blocks 5 at least in the first phase the angular deviation between the coaxial parts of the support element before, under the effect of the circular compression force experienced by these blocks, shear cutouts ots. These notches modulate the action of the blocks depending on the magnitude of the angular deviation. Other types of notches can be made on blocks 5. myself blocks may have other sectional shapes depending on the desired characteristics.
    In accordance with the embodiment shown in Fig. 11, in cross section, each block 5 has the shape of a rectangle with rounded sides 7
    each side, and the bottom of each shell 7, 8 is slightly shifted backwards relative to the sides of this shell, so that in the inactive position of the node, cavities 37 and 38 are formed in the middle part of each node 5 between the block itself and the inner surface of the projections 39 and 40 in the form of an annular (dd of all casings) collar. The tabs 39 and 40 are complete 11 | in the middle of the concave part of the cavities, and cavities 37 and 38 are equidistant from the gripping ends of the elastic blocks 5.
    In this connection, each block 5 generates an axial force of separation, however significant, only after at a certain value of the angular deviation between the coaxial parts and under the effect of the force of circular compression acting on it, the block expands its axes and fills cavities 37 and 38.
    In accordance with the variants shown in FIGS. 12-14, for at least one of the radial ends 13 I i of block 5, the contact area of this end with each of the coaxial parts A and B of the support element has such a circular sweep, the dimensions of which are smaller than circular scan of the working part of this block between the radial ends 13, 14. In the embodiments shown in Figs 12 and 13, the reason for this is that each of the ends 13,14 of each block 5 has a protrusion 41, 42 of small section, with which the block rests on the wall of the notches 9, 10 of the nest flanges 3, 4. In the embodiment shown in FIG. 14, the radial rims 13 and 14 of block 5 have a flat shape, as in the embodiment shown in FIGS. 1-5, but in the middle of the wall of the notches 9, 10 are protrusions 43, 44 which are in contact with block 5. Such structural solutions reduce the stiffness of the elastic members.
    The shoulder 28 (FIG. 15 is tilted relative to the axis of the entire assembly. To support this shoulder, on the outer periphery of the flange 4, there is a support surface 45 having the same inclination. In the presented example, the said shoulder 28 forms an acute angle with the middle line of the hairpin 16. Since V. provided for several studs
    567028
    16, the middle parts of all these studs are rigidly connected to each other by a crown 46, common to all. This crown is gedet around the circumference and whose diameter is larger
    5 of the diameter of the flange 4. When the crown 46 and the pins 16 are jointly combined, the shoulders 28 are made in the form of tabs 47 bent to the device axis, and than on one side of the crown 46
     The boards are bent at a right angle and fastened with a flange 3 (for example, by welding), and on the other, the paws are bent under the sharp edge in relation to the crown 46. In addition, the slope of the shoulders
    15 28 allows in - to increase the working surface of the friction washer as compared with the straight shoulder of the same radial dimensions, this tilt leads to what is in the radial plane 20. The bone force between the stiffeners 16 and the flange 4 has a radial component capable of being a nosing force of the centering of the coaxial parts of the support element relative to each other.
     friend in case of violation of this alignment. Consequently, in this case, it is not necessary that the radial ends of the blocks 5 be in contact with c. coherent parts of the support member.
    0 In the variant presented on
    16, the studs 15 and 16 abut at least one of the coaxial parts through elastic members having axial elasticity. In particular, said elastic elements are made in% of the idea of the cup springs 48, which are hoped. you are on the studs 15, 16 and abut against the paddles 19 and 28. The double-barrels,
    The gins are pre-tensioned.
    In the presence of an angular deviation between coaxial portions, the belleville springs initially do not have any
    five
    whom action is like hard rest
    RU. However, starting with a certain amount of this angular deviation, they begin to react elastically to the compressive force along the axis to which they are subjected due to the presence of an angular deviation between the coaxial parts A and B of the support element. When the angular deviation reaches a certain value c /, the elements of the 5 disk springs close and
    Again, do not take any action, work as a hard stop. Thus, it is 1 well defined with a defined area of action, which is shown by the solid line in the diagram (Lig.17). The slight bending of the curve illustrates the change in the torque type of the torque depending on the angle of the angular deviation relative to the genius to the shape that this curve would have in the absence of these elements (shown by dotted lines). Such a design change may be used for some applications of the device.
    In the variant shown in Fig. 8 and 19, blocks of elastically deformable material are used not of a cylindrical shape, but in the shape of a truncated cone, with the smallest base of the cone directed to the axis of the device. At the same time, shells 7 and 8, which form the nest of the block, have a corresponding shape. Such a construction contributes to a better distribution of stresses in blocks 5 as the entire node rotates.
    In the embodiment shown in Fig. 20, about half the height of each block 5 on its outer surface is an annular transverse roller 49. In this case, until a certain amount of angular deviation is reached between the corroded parts of the support element, only roller A9 of such a block 5 is in contact with the casing shells forming its nest 6. In cross-section this roller has a round shape and the contact is made only along a circular link. .Can use several rollers 49.
    The unidirectional means, the retainers (Fig. 21), connecting in axially the coaxial parts of the support element, include studs 15, made in the form of rivets. The studs 16 are replaced with rivets 50. In this embodiment of the wa devices, only one frictional gaiba 21 is used.
    In the embodiment shown in Fig. 22, three friction washers are used at once. In addition to the friction washers 21 and 30, another friction washer 51 is provided, which is fixed on the distribution washer 52. This clamp is pressed against the flange 4 by means of flexible lips 53 that connect the distribution washer 52

    50
    50 ,
    0
    ,
    0 5
    with the distribution washer 31, abutted on the axis of the last} po1o. The friction washer 51 comes into effect at the very beginning of the deviation between the coaxial parts of the support element. In this embodiment, a gap is provided in the inoperative position of the node between the flange 4 and the friction washer 30. Thus, the friction washer 30 comes into effect only when a certain amount of angular deviation is reached, when the increase in the axial size of the elastically deformable blocks 3 is large enough to move the flanges 3 and 4 along the axis.
    Elastic blocks 5 can be made of a spherical shape, etc. (not shown).
    The device works in the following way.
    When the friction disk is driven into rotation, for example, in the direction indicated by arrows F (Fig. I, 4), blocks 5, transmitting the corresponding rotational moments from part A to part B, are elastically compressed and between these coaxial portions, a progressively increasing angular deviation D occurs. At the same time, as a result of the angular deviation D, each block 5 is acted upon by a circular compression force, indicated by arrows F- (Fig.4), and the block works to shear, since the points of application of this ring compression force are not in one line, but displaced along one axis relative to another. Each unit 5 is closed around the circumference in the nest 6, where it is installed, and works as a liquid body without leakage, since it is made of an elastically deformable material. In addition, block 5 creates between axial parts A, B a force of axial expansion, indicated by arrows F (Fig. 4), and the magnitude of this force is greater, the greater the magnitude of the force of circular compression acting on block 5, or the larger the magnitude of the angular deviation 13 between the coaxial portions.
    This axial thrust force is coaxial. the parts are opposed by the studs 15 and 16 in such a way that, practically in the axial direction, the coaxial parts A and B remain on the same
    and the same distance from one another. As a result, the axial pressure on the friction washers 21, 30 increases and the frictional moment generated by these washers increases. In the absence of an angular deviation, the moment is very small or even completely absent. This friction moment then increases with an increase in angular deviation.
    Thus, the hysteresis effect, which occurs in this case, continuously changes with the change in the magnitude of the angular deviation between the codc parts A and B, the age with it. This is shown in the diagram (Fig. 5), in which the values of the angular deviation D between the coaxial parts of r and the axis of abscissas are plotted, and the values of the torque G, which is transmitted from one of these parts to the other, along the ordinate axis. With the same magnitude d of the angular deviation of D, the torque C has either the value C with an increase in torque, or the value C with a decrease in torque, and the difference between these C and C increases uniformly together.
    with an increase in the angular deviation.
    From this it follows that with an angular deviation between coaxial tea, a block of elastically deformable material acts not only on a circumferential compression force, but also on a shear force, and the point of application of this circumferentially compressive force on the ends of a block of elastically deformable material they are not circumferentially aligned, but axially displaced one relative to another.
     Under the action of a circumferentially directed compressive force, a block of elastically deformable material thickens in the axial direction, and this thickening is enhanced as a result of the addition of shear force to compressive force.
    As a result of this, and due to the fact that a block of elastic: deformable material is closed in the socket, where it is installed, the block of elastic deformable material has a coaxial shape used in the damping torsion device.
    five
    56702 2
    the parts forming this device are the axial separation force, the magnitude of which increases with the increase in the angular deviation between the said parts. In connection with this, the value of the friction moment generated by the friction elements installed in the device progressively increases. This increase in friction moment starts at the very beginning of the angular deviation between the coaxial parts and continues unabated to its very end.
    In this way, continuously varying hysteresis is obtained, without resorting to this for the use of any other elements, besides elastic, installed around the circumference between the two coaxial parts A and B.
    ten
    15
    20
    five
    0
    five
    0
    five
    five
    In addition, despite the axial thickening, a block of elastically deformable material used in the device is not susceptible to any distant movement around the circumference in the socket, where it is closed and, therefore, not subject to wear.
    A block or blocks of elastically deflected material forming. Elastic elements, in addition to the function of transferring torque from one of the coaxial parts to another and the progressive increase in hysteresis acting between these parts, can perform a third function, consisting in ensuring that the two coaxial parts are centered relative to each other with the possibility of floating in the radial installation direction.
    Floating installation of two coaxial
    .about
    parts, it is very easy to smooth out the consequences of a possible axial deviation between the driving and driven shafts between which these two parts are installed, and, in particular, to avoid the appearance between these coaxial parts of the radial component, which can lead to uneven wear of the friction lining 2, baths on one of these parts, and to make the sought filtering of the vibrations to which they are subjected to uneven or even unreliable, as well as to reject the formation between the various parts involved. Research institutes capable to cause frictional corrosion of these details.
    13
    Prsd / tagga design obsch. 1et It performs several functions using small and inexpensive controls that take up the right place.
    Used in the device, friction washers 21 and 30 participate in the transmission of torque between the coocubiNtH parts of the support element together with blocks 5 of elastically deformable material, which contributes to the absorption of vibration between coaxial parts.
    567021D
     B variant of the design, (Figs. 1-5, where friction washers are used on the bottom, part of the moment of the enemy, 1 c from 1 to these 5 washers, due to the presence of axial force, the separation generated by blocks 5, can reach 50%.
    In addition, there are 10 metal springs in the device, which are absent, which eliminates the need for special and costly maintenance.
    g l g-. tiki (L
    FIG. /
    Fig2
    12
    . 6
    fig:
    d jj
    FIG. five
    fS
    6-6
    FIG. 7
    In d
    /
    / 2
     five
    Fig.8
    to 7 6
    ./
    VTV. L7 / G7
    5 W. / f
    FIG (5
    FIG. f6
    FIG. 20
    FIG. //
    FIG. 22
    权利要求:
    Claims (11)
    [1]
    {. FRICTION CLUTCH, containing a hub connecting the friction pads and friction pads in the form of two coaxial coaxial parts with through holes evenly distributed around the circumference, holding means installed with emphasis on one and the other coaxial parts of the support element, friction friction elements mounted on the axis between the parts of the support element located in said through holes between the coaxial parts of the supporting element, the casings, each of which is made with shells facing one another, elastic Elements in the form of blocks of elastic deformable material located in the nests formed by the shell shells, while the coaxial parts of the supporting elements are interconnected and holding means and are installed with the possibility of axial and angular displacements limited by friction and elastic elements, such that, for the purpose of increase the reliability by ensuring the gradual increase friction 'between the two movable angularly soosnmi portions of the support member, each housing shell is connected to only one coaxial portion of the support member is formed. concave and installed coaxially relative to the through hole of the support element, the concave parts of the shells of each casing are located one opposite the other, and the blocks of elastic elements of charters are f foam between them without a gap with the possibility of less interaction with the shells at ζ less at least one contact line ';
    <** and are closed around the circumference in the enclosure nest covering J5.
    [2]
    2. Coupling pop. 1, characterized in that each shell shell connected to one of the coaxial parts of the support element is made with side flanges in the form of support shelves, the planes of which are parallel to the opposing planes of the indicated parts of the support element.
    [3]
    3. Coupling pop. 1, characterized in that each shell under the elastic block and the coaxial part of the supporting element mating with it is made together, moreover, the shell on the specified component is made in the form of a local recess. ''
    [4]
    4, Coupling according to π.1, with respect to the fact that in the middle of
    I 256 702 of the inside of each shell of the casing, an additional recess is made in the form of a shoulder, the inner surface of which, together with the outer surface of the elastic block, defines a cavity equidistant from the ends of the elastic block.
    [5]
    5. The coupling according to claim 1, with the fact that at least one through longitudinal cutout is made on the outer surface of each elastic element.
    [6]
    6. The coupling according to π.1, with the exception that at least one annular ’transverse bead is made on the outer surface of each elastic element.
    [7]
    7. The coupling according to π.1, characterized in that the elastic elements are made of cylindrical shape and are arranged radially along the generatrix, and the elastic elements are installed in through holes of the coaxial parts of the support element with the possibility of contact by both protects against them with the sides of said through holes.
    [8]
    8. The clutch according to claim 1, wherein the elastic elements are made in the form of a truncated cone mounted radially along the generatrix, with the smallest base of the truncated cone located towards the axis of the disk.
    [9]
    9. The coupling according to claim 1, about t and h and I am completely happy with the fact that the elastic elements are made spherical in shape.
    [10]
    10. The clutch according to π.1, with the exception that it is equipped with elastic means, the tightening element of the holding means is made in the form of studs, and said elastic means are installed with prestress on the studs .
    [11]
    11. Clutch pop. 1, characterized in that it is equipped with a crown located above one of the coaxial parts of the support element, * rigidly connecting the middle parts of the holding means studs, the shoulders of the latter being made in the form of paws bent to the axis of the friction disk .
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1256702A3|1986-09-07|Friction clutch
    US4819974A|1989-04-11|Pipe coupling
    KR20000052595A|2000-08-25|Torque transfer device
    US4493676A|1985-01-15|Rotary constant velocity joint
    US8960396B2|2015-02-24|Torsional vibration damping arrangement, particularly for the power train of a vehicle
    GB2131914A|1984-06-27|Friction clutch driven plate
    GB2329447A|1999-03-24|Torsional vibration damper with rolling coupling elements moving in slotted guide ways.
    US4412827A|1983-11-01|Universal joint
    US2948129A|1960-08-09|Elliptical vibration damper
    US3759063A|1973-09-18|Laminated diaphragm couplings
    KR100219693B1|1999-09-01|Torsion damper for clutch disk
    JP2006510862A|2006-03-30|Friction disc for clutch and clutch provided with friction disc
    RU2314442C2|2008-01-10|Movable part guide member
    US9885406B2|2018-02-06|Hydrokinetic torque coupling device for a motor vehicle
    JP4913969B2|2012-04-11|Hydrodynamic coupling device especially for automobiles
    US10753445B2|2020-08-25|Torque transmission assembly for a motor vehicle
    GB2337573A|1999-11-24|Clutch disc with hub centring spring
    CN101460763A|2009-06-17|Split flywheel
    US5186293A|1993-02-16|Damper disk
    US2953910A|1960-09-27|Universal joint expansion ball
    JP4260956B2|2009-04-30|Torsional vibration damper
    US10107356B2|2018-10-23|Torque converter including damper assembly with hysteresis control package
    US2945367A|1960-07-19|Torsional vibration dampener
    GB2051976A|1981-01-21|Sheet Metal Release Ring for Diaphragm Spring Clutches
    US10907698B2|2021-02-02|Dynamic damper
    同族专利:
    公开号 | 公开日
    GB2093951A|1982-09-08|
    FR2500900B1|1983-04-01|
    JPS57157827A|1982-09-29|
    FR2500900A1|1982-09-03|
    DE3207047A1|1982-09-16|
    GB2093951B|1984-06-27|
    IT8212453D0|1982-02-26|
    ES8302868A1|1983-01-16|
    US4474276A|1984-10-02|
    ES509942A0|1983-01-16|
    IT1157643B|1987-02-18|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    CA645382A|1962-07-24|Laycock Engineering Limited|Plate clutch centre plates|
    US1760619A|1926-04-12|1930-05-27|Chrysler Corp|Clutch-plate connection|
    US1723886A|1927-04-23|1929-08-06|Ernest C Pfaff|Clutch|
    US1861251A|1928-05-14|1932-05-31|Ernest E Wemp|Clutch|
    US1967322A|1931-06-10|1934-07-24|Twin Disc Clutch Co|Clutch|
    GB512009A|1938-02-25|1939-08-28|Noel Banner Newton|Improvements in or relating to clutch plates|
    US2533789A|1948-08-19|1950-12-12|Henry C Goodchild|Cushion for clutch plates|
    GB728830A|1952-05-12|1955-04-27|Laycock Eng Ltd|Improvements in or relating to friction clutch centres|
    GB715512A|1952-05-12|1954-09-15|Laycock Eng Ltd|Improvements in or relating to torque dampers|
    US2826902A|1955-09-01|1958-03-18|Dana Corp|Friction clutch plate|
    US2964930A|1957-10-28|1960-12-20|Aira|Clutch cushion device|
    DE1265509B|1962-04-10|1968-04-04|Gomma Antivibranti Applic|Elastic clutch disc for disc friction clutches, especially for motor vehicles|
    FR1411155A|1964-08-04|1965-09-17|Ferodo Sa|Improvements to damper hub clutch friction|
    JPS5122129B1|1971-02-19|1976-07-07|
    JPS5042935Y2|1971-06-29|1975-12-08|
    JPS52162624U|1976-06-03|1977-12-09|
    US4094395A|1976-09-02|1978-06-13|Borg-Warner Corporation|Two piece driven plate assembly|
    US4092837A|1976-11-19|1978-06-06|Deere & Company|Torsional isolator coupling|FR2524097B1|1982-03-26|1984-06-22|Valeo|
    DE3248119C2|1982-12-24|1992-03-12|Luk Lamellen Und Kupplungsbau Gmbh, 7580 Buehl, De|
    FR2541403B1|1983-02-21|1986-06-20|Valeo|TORSION DAMPING DEVICE, IN PARTICULAR A CLUTCH FRICTION, IN PARTICULAR FOR A MOTOR VEHICLE|
    JPS59160926U|1983-04-12|1984-10-27|
    FR2548303B1|1983-06-30|1985-10-25|Dba|IMPROVEMENTS TO MULTI-DISC BRAKES|
    FR2555686B1|1983-11-30|1989-03-31|Dba|MULTI-DISC BRAKE, COMPRISING A FIRST DISC AND A SECOND SLIDING DISC PROVIDED WITH A GUIDANCE SYSTEM|
    FR2575532B2|1983-12-30|1989-03-31|Valeo|TORSION DAMPING DEVICE WITH ELASTIC CENTERING MEMBER, ESPECIALLY FOR A CLUTCH OF A MOTOR VEHICLE|
    US4714448A|1984-12-27|1987-12-22|Valeo|Torsional damper device|
    DE3409829C2|1984-03-17|1993-04-01|Fichtel & Sachs Ag, 8720 Schweinfurt, De|
    JPS6128920U|1984-07-24|1986-02-21|
    JPS6170634U|1984-10-15|1986-05-14|
    DE3528175C2|1985-08-06|1991-01-17|Fa. Carl Freudenberg, 6940 Weinheim, De|
    DE3621997C2|1986-07-01|1988-12-08|Fa. Carl Freudenberg, 6940 Weinheim, De|
    JPH01145429A|1987-11-30|1989-06-07|Aisin Seiki Co Ltd|Clutch disk|
    JPH0645728Y2|1989-12-22|1994-11-24|株式会社大金製作所|Liquid viscosity damper|
    JPH03114632U|1990-03-07|1991-11-26|
    US5653144A|1993-02-09|1997-08-05|Fenelon; Paul J.|Stress dissipation apparatus|
    US5452622A|1993-02-09|1995-09-26|Magi, L.P.|Stress dissipation gear|
    JPH08270679A|1995-03-28|1996-10-15|Exedy Corp|Plate member and damper disc assembly|
    US5956998A|1996-06-06|1999-09-28|Fenelon; Paul J.|Stress reduction gear and apparatus using same|
    DE102007045246A1|2006-10-11|2008-05-21|Zf Friedrichshafen Ag|Torsionsdämpfvorrichtung|
    CN105431648B|2013-06-04|2019-04-26|离合器实业有限公司|Clutch disc|
    AT520114B1|2017-07-07|2019-03-15|Miba Frictec Gmbh|friction plate|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    FR8103911A|FR2500900B1|1981-02-27|1981-02-27|
    [返回顶部]