• 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:
    <P> Torsional vibration damper comprising separate friction devices for the idling and the running, these friction devices being disposed respectively on either side of the intermediate disc. For the two friction devices there is provided a common support member in the form of a helical spring 11 which is mounted between the friction drive disc 9 coaxially with the clutch hub 15 at a certain radial distance from this one. </ P> <P> The invention is particularly applicable to motor vehicle clutches. </ P>
    公开号:SU969999A1
    申请号:SU787770126
    申请日:1978-03-09
    公开日:1982-10-30
    发明作者:Клаус Опелт；Альфред Лоренц
    申请人:Феб Ренак-Верке (Инопредприятие)；
    IPC主号:
    专利说明:

    difficulties are associated with ensuring the required parameters of the springs according to DE 2356559.
    Such kind of dampers cannot generally be changed and they can be used, for example, only dp of a certain type of automobile. Adapting them to other cars by changing the dimensions or increasing the friction devices of the yochti is impossible.
    The purpose of the invention is to develop a multi-stage torsional vibration damper whose construction and installation are relatively simple. Torsional vibration damper allows easy modification of its performance without significant cost.
    The objective of the invention is to eliminate the disadvantages of the known designs. The hub design should be simple and friction devices should be removed from the axial space around the hub.
    The friction devices must be designed in such a way that the dimensions and effect of the torsional vibration damper can be changed by changing the diameter of the friction elements and inserting additional friction devices.
    According to the invention, the problem is solved by arranging both frictional UVs necessary for damping on both sides of the intermediate disk.
    The transmission of rotational motion is carried out in the usual way by torsion springs with different characteristics, which are located in the respective notches of the individual discs. The intermediate disc is welded with a clutch disc that carries the clutch linings and can be rotated relative to the hub.
    Idling plate is located between the case disk, which is connected with rivets to the suupice, and the intermediate disk.
    A friction load device located on the other side of the intermediate disk consists of a load body disk, a load friction disk, load friction lining and a load friction leash, held by a friction body connected to the staff with rivets. The thrust pressure required for both friction devices is created by a coil spring located coaxially relative to the adhesion of the clutch and supported on one side against the intermediate disk and on the other side onto the flange of the loading friction leash. Load: the friction device is housed in a friction case, which in its internal
    The radius is connected without scrolling to the clutch hub, while on its outer circumference protrusions or pins are provided that fit into the slots or grooves of the load case disk. The load friction leash is connected to the intermediate disk and torsion springs by means of an eye and captured by them in a range of loads. For this, the eye passes through slots in the intermediate disk and abuts the torsion spring. In a similar way, the loading friction disk is connected to the loading friction driver. This ensures the connection of the friction load device as a whole in the load range.
    The principle of operation is as follows, in the range of idle relative to the movement occurs only between
     case disk and intermediate disk. With increasing load after
    . - overcoming a certain distance, the friction leash is captured by its ear, while the friction disk is also captured at the same time. At this time, the friction linings for the load range are also connected. The friction linings are located between the friction load driver and the load case disk, the load case disk and the load friction disk, and the load friction disk and the friction case. All friction devices are above the hub flange, so the space around the hub remains free. Friction devices can be changed at any time by changing the diameter of the friction linings for the idling range and loads and friction loading discs. As a special option, separate springs can also be used for idling ranges and load ranges. It is advisable that the second spring is a spring or ring spring. This one is - The loading friction spring is located between the loading friction disk and. The friction body, moreover, the supporting disk axially connected to the load friction leash is provided with a uniform distribution of the elastic force. This arrangement allows more precise control of the friction load device, so that the friction tolerance field can be reduced.
    The principle of action of torsion springs is generally known. There are spring sets with different characteristics, in one case there are torsion springs for the range of loads, and in the other case torsion springs for idling. Since the eye of the loading friction leash penetrates through the slot of the intermediate disk and the torsion spring fits to this eye, after overcoming the idling path, the load friction leash is automatically captured, and thereby the entire friction device is connected. In addition to the known embodiment, in which the idle path is provided on both sides of the torsion springs, other arrangements are also possible. So the path of idling can be shifted to the tension side of the torsion springs. The cuts all along their tangential direction are filled with torsion springs of the idle, while the length of the torsion springs is shortened by the length of the idling path. This design is possible because at idle the thrust moment of the gearbox must be overcome, as a result of which the torsion springs of the idling are pretensioned by the thrust momentum. By sampling the corresponding torsion springs, the torsion springs can be rocked so that the available idling path is distributed on both sides of the torsion springs. By changing the parameters of the torsion springs of idling, if necessary, you can provide a different path distribution. A further embodiment consists in arranging torsion idle springs inside torsion springs for a range of loads. The no-load path is calculated only on one side. Torsional idle springs operate in one direction. Due to this arrangement, no special slots are needed for the idle torsion springs. In cases where the distribution of the idling path to one side is not possible, the torsion idle springs are set against each other in order to fix the middle position. During operation, one spring alternately tightens and the other one is weakened.
    In devices with a coaxial arrangement of the idle torsion springs and torsion springs for a range of loads, when moving in the direction of loosening, the preload tension of the idle torsion springs is released. As a result, unwanted noises occur. In order to eliminate this drawback, special pushers are placed on the spring nozzles.
    When the springs move in the direction of loosening, the pusher adjoins the cutter and thereby prevents further weakening of the torsion springs, idling. This eliminates unwanted noise.
    FIG. 1 shows a torsional vibration damper, section; on Fig.2 another damper torsional vibrations section; in fig. 3 shows section A-A in FIG. 1 and 2; in fig. 4 - the same, option; in fig. 5 is a sectional view of FIG. 4, an embodiment.
    FIG. 1 and 2 show two sections of the embodiment of the invention.
    The clutch pads 1 are attached in the usual way to the clutch disc 2 which is welded to the intermediate disc 3. The said intermediate disc 3 can be rotated relative to the hub 15.
    The rotational movement is transmitted in the usual way using torsion springs 13 with different characteristics, which are located in slots 19 of the intermediate disk 3, the body disk 4, the load case disk 8 and the friction load driver 9. To create friction, the idle friction pad 5 is placed between intermediate disc 3 and case disc 4 connected by rivets to the hub 15. A load friction device consisting of a load case disc 8, a load friction disc 10, friction load plates 6 and friction load driver 9, are opposite the idler friction device axially on the other side of the intermediate disk 3 and are held by the friction body 7 which is connected to the hub 15 with rivets. The spring 11 provides the necessary pressure and rests on the flange of the friction load driver 9 and on the intermediate disk 3.
    A load friction leash 9 is connected via an eyelet 21 to an intermediate disc 3 and torsion springs 13 and is caught in a range of loads. For this, the eye 21, through the slot 19, which is located in the intermediate disk 3, protrudes outside and is adjacent to the torsion spring 13. The loading friction leash 9 also has corresponding slots or grooves in which the protrusions of the loading friction disk 10 enter. In the same way the load case disc 8 is connected to the friction case 7, so that in the load range, the entire load friction device is gripped.
    FIG. 2 shows an example of the implementation of a torsional vibration damper. In order to achieve a more precise adjustment of the friction load.
    The device has a special friction spring 12. The friction spring 12 is installed between the friction load disk 10 and the support disk 14. The said support disk 14 is flanged or similarly connected to the flange 20 of the friction flange 20 9. The support disk does not fit directly to friction housing It provides an even distribution of the pressing force. As a load friction spring 12 is provided with a trash or. ring spring.
    As regards torsion springs 13, torsion springs for a range of loads are meant here. For idling, special torsion springs 16 are provided. In accordance with their purpose, the springs have different characteristics. They are placed in the usual way in slots 19 of the intermediate disc 3. The friction load device is connected as described, automatically using the ears 21 of the friction leash 9 adjacent to torsion springs 13. FIG. 3-5, different arrangements of the torsion springs 13 and the idle torsion springs 16 are shown. FIG. 3 shows a known arrangement in which the torsion springs 13 and the torsion springs 16 of the idle ho are placed in slots x 19 in pairs and singly. Their number is not limited to four springs. For example, three pairs of springs with different characteristics can be used. Torsion springs 13 are placed in the middle position, at which the idling path A is distributed on both sides of the GZ torsion springs as A / 2. It is possible to transfer the path. idling A to one side of the torsion springs 13, the tangential stretching of the torsion idle springs 16 corresponds to the length of the slots 19, and the torsion spring 13, taking into account the idling length A, related to one side, reaches the length of the notches 19. As with idling By overcoming the thrust moment of the gearbox, torsion springs 13 can automatically swing and distribute; the idle path A.
    FIG. 4 shows the arrangement of the idling springs 16 inside the torsion springs 13. The idling path A is assigned to one side. Inside the torsion springs 13, the torsion springs 16 idle are supported on special nozzles 17
    springs. If the assignment of the idling path is impossible to one side, the torsion springs 16 of the idling may be placed opposite each other (not shown). Since when
    In operation, only one spring is tensioned and one is weakened, then the average position of the torsion springs 13 is set in this way.
    FIG. 5 shows an embodiment of the invention with an improved device, in the spring nozzle 17 a special pusher 18 is positioned protruding through the opening in the spring nozzle 17 and thus continues it.
    The pusher 18 is kept in constant contact with the spring nozzle 17 by torsion springs 16 of idling. If the movement is in the direction of weakening, the pusher 18 is adjacent to the edge of the slot
    权利要求:
    Claims (4)
    [1]
    19. Continued movement results in a reverse shift of the pusher 18, which prevents the idle torsion spring 16 from loosening. Invention Formula
    1. Torsional vibration damper, in particular for car clutches with friction devices separate for the idle range
    course and for a range of loads, ras-. . placed on both sides of the intermediate disc, and with a coil spring coaxially arranged with the hub of the clutch hub, characterized in that for both friction devices there is a joint thrust piece positioned between the intermediate disc 3 and the flange 20 of the friction leash 9 at a radial distance from the hub 15 of the clutch, and the friction load device is placed in the friction housing 7, which
    its inner radius is rigidly connected to the clutch hub 15, with axles or protrusions located in the slots or grooves of the loading friction disk 8 provided on the outer edge bent along the axis.
    2. A damper according to claim 1, characterized in that inside the friction load device between the friction load disk
    [2]
    10 and the supporting disk 14 is installed on the friction load spring 12, preferably a trawler or an annular spring, the supporting disk 14 being axially connected to the friction load driver 9, the spring 11 is placed between the intermediate disk 3 and the friction body 7.
    3. The damper on PP. 1 and. 2, which is due to the fact that. torsion springs 13 and idle torsion springs 16 are provided, located in slots x 19 of the same tangential extent, and are arranged in such a way that the tangential stretching of the idle torsion springs 16 corresponds to the tangential stretch of the slots 19 and tangential stretching of the torsion springs 13 together with the idling length is the same tangential extent as the torsion springs 16 of the idling and slot 19.
    [3]
    Vr w
    [4]
    4. The damper on the PP. 1 and 2, that is, the torsion springs 13 and the idle torsion springs 16 are coaxial, with the idle torsion springs 16 placed in the spring nozzles 17 located inside the torsion springs 13, and these nozzles 17 of the springs have an opening, which is placed the pusher 18. It is recognized as an invention according to the results of the examination carried out by the Office for the Invention of the German Democratic Republic. /////// A
    hr
    FIG. g
    类似技术:
    公开号 | 公开日 | 专利标题
    SU969999A1|1982-10-30|Torsional oscillations damper, in particular for vehicle friction clutches
    US5080215A|1992-01-14|Torsion vibration damper
    US4537295A|1985-08-27|Clutch disc assembly with torsional oscillation dampers
    JP4106106B2|2008-06-25|Torsional vibration attenuator
    KR101041717B1|2011-06-14|A vibration filter for a transmission with automatic, continuous or discontinuous, gearchange, especially for a motor vehicle
    SU843782A3|1981-06-30|Disc clutch
    US6830139B2|2004-12-14|Multi-clutch arrangement
    US6601682B2|2003-08-05|Clutch disc
    GB2309283A|1997-07-23|Torsional vibration damper
    JP2017075694A|2017-04-20|Torque transmission device of automobile
    JP3887416B2|2007-02-28|Dump flywheel, especially dump flywheel for automobile
    US4254855A|1981-03-10|Coaxial spring damper drive
    US2920733A|1960-01-12|Clutch vibration damper assembly
    US7166030B2|2007-01-23|Torsional vibration damper
    US5636553A|1997-06-10|Flywheel arrangement for a transmission of a motor vehicle
    KR0157620B1|1998-10-15|Torsion damping device for an automotive friction clutch disc
    US5884743A|1999-03-23|Clutch plate with centering feature
    US20210062891A1|2021-03-04|Pendulum damping device
    US9255610B2|2016-02-09|Torque transmission device
    JP2017062029A|2017-03-30|Torsional damping device for motor vehicle transmission system
    US5529161A|1996-06-25|Friction clutch for a transmission of a motor vehicle and a torsional damper for a friction clutch
    GB2075618A|1981-11-18|Pulled diaphragm spring clutch
    JP3299478B2|2002-07-08|Torsional vibration damper
    US5569088A|1996-10-29|Two mass flywheel for a motor vehicle transmission having a seperate thrust bearing between the two masses
    JPH1037975A|1998-02-13|Friction clutch
    同族专利:
    公开号 | 公开日
    GB1602408A|1981-11-11|
    CS218810B1|1983-02-25|
    DD130801A1|1978-05-03|
    FR2387384A1|1978-11-10|
    DD130801B1|1979-08-29|
    FR2387384B1|1982-06-04|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    RU2636840C2|2013-09-13|2017-11-28|Ниссан Мотор Ко., Лтд.|Damping device|
    RU2636844C2|2013-09-13|2017-11-28|Ниссан Мотор Ко., Лтд.|Damping device|
    RU2639845C2|2013-09-13|2017-12-22|Ниссан Мотор Ко., Лтд.|Damping device|FR2225650A1|1973-04-14|1974-11-08|Daimler Benz Ag|FR2492024B1|1980-10-15|1985-04-26|Valeo|
    EP0069458A1|1981-06-25|1983-01-12|Automotive Products Public Limited Company|Friction clutch driven plates|
    DE3126695C2|1981-07-07|1991-04-25|Luk Lamellen Und Kupplungsbau Gmbh, 7580 Buehl, De|
    DE3275580D1|1981-07-14|1987-04-09|Automotive Prod Plc|Friction clutch driven plate|
    DE3136600A1|1981-09-15|1983-03-31|LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl|CLUTCH DISC|
    JPS60112727U|1984-01-05|1985-07-30|
    DE3419497A1|1984-05-25|1985-11-28|Fichtel & Sachs Ag, 8720 Schweinfurt|CLUTCH DISC WITH Torsional Vibration Damper|
    JPS6141019A|1984-07-31|1986-02-27|Daikin Mfg Co Ltd|Damper disc|
    DE4141723C2|1991-12-20|1999-12-16|Mannesmann Sachs Ag|Torsional vibration damper with idle suspension|
    FR2739425B1|1995-09-29|1997-11-28|Valeo|SPACER DAMPER WITH SPACER WASHER, PARTICULARLY FOR MOTOR VEHICLE|
    DE10213978A1|2002-03-28|2003-10-09|Roland Man Druckmasch|Process for cross cutting a running web|
    FR2936850B1|2008-10-06|2010-11-19|Valeo Embrayages|FRICTION CLUTCH WITH A SYMMETRIC DAMPER, IN PARTICULAR FOR A MOTOR VEHICLE, COMPRISING DIFFERENTIAL DAMPING MEANS.|
    DE102018219406A1|2018-11-14|2020-05-14|Zf Friedrichshafen Ag|Torsional vibration damper with wet-running friction device and clutch disc with torsional vibration damper|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DD19835077A|DD130801B1|1977-04-12|1977-04-12|TURNING VEHICLE DAMPER, ESPECIALLY FOR MOTOR VEHICLE COUPLINGS|
    [返回顶部]