• 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 friction clutch with a rotatable friction disc and with a housing surrounding the friction disc, in which an axially movable pressure disc that can be acted upon by a pressure medium is arranged, which can be brought into frictional connection with the friction disc, the pressure disc by means of an axially resilient membrane r� The back plate is clamped on the housing on the one hand and on the pressure plate on the other hand is known. According to the invention it is provided that for the axial resetting of the thrust washer a compression spring arrangement is additionally provided, which acts on the thrust washer in parallel to the membrane.
    公开号:BE1018694A3
    申请号:E2007/0346
    申请日:2007-07-11
    公开日:2011-07-05
    发明作者:Matthias Glomm；Friedrich Tronicke
    申请人:Stromag Ag；
    IPC主号:
    专利说明:

    Pressure medium-operated friction clutch or brake
    The invention relates to a fluid-actuated friction clutch or brake with a rotatable friction disc and a surrounding the friction disc housing, e, in which an acted upon by a pressure medium, axially movable pressure disc is arranged, which is frictionally engageable with the friction disc in connection, said pressure plate can be reset by means of an axially resilient membrane which is clamped on the housing on the one hand and on the pressure plate on the other hand
    Such a fluid-actuated friction clutch is known from DE 81 31 995 U1 In order to transmit a torque between the friction disc and housing and thus between the friction disc and thrust washer, the thrust washer is pressurized medium, whereby it is pressed against the friction disc. To vent the clutch, the pressure medium chamber is aerated, whereby the disc diaphragm returns the thrust washer to the released starting position. In this release position, the friction disc can rotate without transmitting torque to the housing and thrust washer. It may be problematic in such a friction clutch that in open, i. released state of the clutch due to vibrations of a corresponding drive motor to which the clutch is coupled, wear and tear occur.
    The object of the invention is to provide a fluid-operated friction clutch or brake of the type mentioned above, which avoids wear occurring due to vibration in the ventilated state.
    This object is achieved in that the membrane in the region of its outer circumference is clamped on the housing side and in the region of its inner circumference on the pressure plate side, and that the housing has an over a housing center axis has open, central cylinder chamber in which a connected to the pressure plate pressure piston is arranged axially movable. In the prior art, the pressure plate and thus the pressure piston was designed as a disc ring. Also serving as a pressure chamber cylinder space of the housing was designed as an annulus. As a result, seals were necessary both radially on the inside and radially on the outside. Accordingly, the membrane was clamped on the inside of the housing and on the outside of the thrust washer. The solution according to the invention reduces the number of components subject to play, which can cause noises or mechanical signs of wear due to vibrations in the released state. The solution according to the invention enables a torsion play-free concept. Characterized in that the pressure piston and the pressure piston overlapping cylinder space, which defines the pressure medium to be acted upon pressure chamber, are arranged centrally, is defined relative to the housing and thus between the pressure piston and cylinder chamber only a single lateral surface, which must be provided with a seal. Due to the arrangement of the diaphragm centering of the pressure piston and thus a centering of the pressure plate is created, whereby by means of the individual seal yet reliably a metallic separation between the pressure piston and the cylinder chamber he is aiming. Even vibrations can thus not lead to metallic Reiberscheinungen between the pressure piston and the cylinder chamber and thus between the pressure piston and housing, so that reliable mechanical wear is avoided. The solution according to the invention is particularly suitable for use in agricultural and forestry machines, in which preferably diesel engine drives are used, which are subject to strong vibrations.
    The object underlying the invention is also achieved in that for the axial return of the pressure plate in addition a compression spring arrangement is provided, which acts in parallel with the diaphragm on the pressure plate. This results in a steep spring characteristic, which allows a very fast pushing back of the pressure plate and the pressure piston in the released starting position. In addition, can be dispensed with a bias of the diaphragm in the released position. The compression spring assembly retains the thrust washer in its released position with great force, so that vibrations acting on the clutch or brake can not vibrate the thrust washer. This avoids ringing noises and mechanical signs of wear due to corresponding metal-frictional contacts.
    According to an embodiment of the invention, the compression spring arrangement comprises mélange, evenly distributed over the circumference of the pressure disk angeord-ïete helical compression springs, which are supported on an outer peripheral portion of the thrust washer. This achieves a particularly fast and reliable release function of the pressure disk.
    ή further embodiment of the invention, the pressure plate on ih-em outer peripheral region on the helical compression springs from e-facing end face on a support contour which forms an axial support surface. Through the axial support surface is a flat contact with the
    Housing or achieved on the membrane, so that the thrust washer remains positioned consistently in its released starting position.
    In a further embodiment of the invention, the housing forms radially within an outer clamping region of the membrane an axial contact surface for the membrane. As a result, a low-tension rest position is achieved for the diaphragm in the released starting position of the thrust washer.
    In a further embodiment of the invention, the support surface of the pressure plate is arranged at the same radial height as the axial contact surface of the housing for the membrane. As a result, a further improvement of a secure and consistent fixed contact of the thrust washer is achieved in its released position.
    In a further embodiment of the invention, the membrane extends between Jer support surface of the pressure plate and the contact surface of the housing.
    As a result of the measures described, the membrane in the ventilated starting position of the thrust washer is substantially stress-free between the axial axial surfaces of the thrust washer and the dome, whereby a relatively large-area contact of the pressure washer with comparatively low surface pressure is achieved Restoring force of the helical compression springs in the ventilated starting position, the safe and constant positioning of the back plate in the ventilated starting position is maintained even with vibrations of the drive or drive train.
    In another embodiment of the invention, the thrust washer is axially recessed on its end face facing the compression coil springs. ) adurch a relatively compact structure can be achieved for the clutch or brake in the axial direction, since the axially oriented helical compression springs axially superimpose the thrust washer in a partial area.
    In a further embodiment of the invention, the membrane is provided with pressure relief holes. This allows pressure equalization between corresponding cavities on the opposite axial end faces of the membrane.
    In a further embodiment of the invention pressure relief profiles or passages are provided on the pressure plate. As pressure relief profiles pressure relief grooves are provided in particular. Pressure relief passages may preferably be formed by pressure relief bores. This can be done when switching on and off the clutch or brake balancing the volume of air between the pressure plate and the diaphragm. In both embodiments described above, it is thus avoided that the thrust washer or the diaphragm must work against an "air cushion" in order to cover the corresponding axial travel.
    Further advantages and features of the invention will become apparent from the claims and from the following description of a preferred embodiment of the invention, which is illustrated by the single drawing.
    The single drawing shows in a sectional view an upper half of an embodiment of an at least largely rotationally symmetrical friction clutch.
    A friction clutch 1 according to the single drawing is provided for the use of> a land or forestry machine and is executed in dargestell-en embodiment as a connection coupling to a white-functional device to a preferably diesel engine to drive to couple. A pulley 2 of the diesel engine drive is shown in phantom in the drawing. An output shaft 3 of the diesel engine drive (not shown) is non-rotatably by means of a splined but axially movably connected to a clutch hub 4. The clutch hub 4 carries a disc-like Reibbelagträger 5, which projects radially to a rotational axis of the output shaft 3 and the clutch hub 4 radially outward. The friction lining carrier 5 carries a plurality of friction lining surfaces 6, which are fastened to mutually opposite end faces of the friction lining carrier 5.
    The Reibbelagträger 5 including its friction linings 6 is surrounded by a clutch housing 7, 8, 9, which is mounted coaxially rotatable relative to the output shaft 3. The output shaft 3 is rotatably mounted relative to the pulley 2. The pulley 2, however, is rotatably connected to the clutch housing 7, 8, 9 of the friction clutch 1. By connecting the friction clutch 1 thus a power flow between the output shaft 3 and pulley 2 is achieved, so that via the pulley 2 a corresponding additional function can be driven, which is switched on or off depending on the switching state of the friction clutch 1.
    The clutch housing 7, 8, 9 has a bell-shaped coupling portion 9, which defines a cylinder for a coaxial with the axis of rotation axially movable pressure piston 10. The pressure piston 10 extends rotationally symmetrically to the axis of rotation beyond this and together with the housing portion 9 form a serving as a central cylinder chamber pressure chamber 16 which is druckmittelbeaufschlagbar. As the only common lateral surface, which is formed between the cylindrical inner side of the housing portion 9 and the cylindrical outer surface of the pressure piston 10, an annular seal 20 is provided. The pressure chamber 16 is therefore sealed pressure-tight. The pressure chamber 16 is acted upon by a pneumatic or hydraulic pressure medium, namely compressed air or oil. For this purpose, a pressure medium connection 17 is provided, which is introduced coaxially to the axis of rotation of the friction clutch 1 in a corresponding connection opening of the housing portion 9.
    The axially displaceable pressure piston 10 carries via a Schraubverbin-; düng a pressure plate 11, which extends parallel to the friction lining 5 radially outward within the clutch housing 7 to 9. The pressure plate 11 is designed as a disc ring and has on its inner circumference an annular flange which is screwed by means of the screw formed by a plurality of evenly distributed in the circumferential direction arranged screw with the plunger 10. Between the annular flange of the pressure plate 11 and the pressure piston 10, a disk-shaped membrane 12 is clamped, which preferably consists of a spring steel. The disk membrane 12 has spring-elastic properties in the axial direction in order to return the pressure disk 11 to a ventilated starting position described in more detail below. The disk membrane 12 extends radially outwards from the pressure piston 10 and is clamped in the coupling housing 7 to 9 in the region of its radial outer circumference by means of a further number of axial screws distributed uniformly over the circumference of the coupling housing 7 to 9. In this case, the membrane 12 is clamped between the coupling portion 9 and an axially extending annular portion 8 of the coupling housing. The coaxial with the axis of rotation of the friction clutch 1 aligned axial annular portion 8 of the clutch housing is in turn bolted to a further housing portion 7 of the clutch housing, which is fixedly connected via unspecified screw with the pulley 2.
    The housing portion 7 forms a frontal friction surface for the friction linings 6. The pressure plate 11 forms a further, the friction surface of the housing portion 7 opposite friction surface for the friction linings 6, so that a two-surface coupling is defined. The Reibbelagträger 5 may be performed resiliently within certain limits to allow for wear of the friction linings 6, a certain elastic compliance and safe investment of all friction surfaces.
    In the region of its outer circumference, the pressure disk 11 has a supporting contour 14, which is supported in a planar manner on the diaphragm 12 in the released state of the pressure disk 11 and of the pressure piston 10. The membrane 12 in turn is supported at the same radial height on a flat support surface 15 of the housing portion 9, so that in ventilated Zu- »stand the pressure disk 11 over a whole end face of the support contour 14 results in a flat Ab support to the housing portion 9. On the side facing away from the membrane 12, the support contour 14 of the pressure plate 11 has a recessed area in which distributed over the circumference of the pressure plate 11 several screw-Î pressure springs 13 axially attack, which are supported in axially aligned blind holes of the annular portion 8 of the coupling housing.
    In a - radially seen - middle region, the pressure plate 11 is provided with open to the membrane 12 recesses 18. Also, the housing portion 9 is provided on the membrane 12 facing front side with narrow recesses 19.
    The clutch hub 4 of the friction lining 5 is held axially slidably on the output shaft 3 by means of the wedge-shaped sliding splines, so that wear of the friction linings 6 can be compensated for by simple axial trailing of the clutch hub 4 on the output shaft 3.
    In order to transfer the friction clutch 1 from the released starting position into a torque transmitting position, the pressure chamber 16 is acted upon in a basically known manner with a pressure medium, which is displaced axially by the pressure piston 10 in the direction of the friction lining carrier 5. As a result, the thrust washer 11 is also displaced axially in the direction of the friction lining carrier 5 and in the direction of the housing section 7. The corresponding end face of the thrust washer 11 presses the friction linings 6 against the opposite end face of the housing section 7, whereby the torque of the rotating friction lining carrier 5 is transmitted to the thrust washer 11 and the housing section 7. The clutch housing 7 to 9 is therefore taken. By the rotational connection with the pulley 2 'this is also set in rotation. The membrane 12 is tensioned by the axial displacement movement of the pressure plate 11 by appropriate elastic bending. The helical compression springs 13 are compressed by the axial displacement of the pressure plate 11. As soon as the pressure chamber 16 is released, the spring forces of the diaphragm 12 and the spring forces of the parallel to the diaphragm 12 coil compression springs 13, the thrust washer 11 back to its original position axially, the helical compression springs 13, the support contour against the diaphragm 12 and against the Press support surface 15 of the housing section 9. As a result, the friction linings 6 and the friction lining carrier 5 are released again, so that no more power transmission between the output shaft 3 and the clutch housing 7 to 9 and thus the pulley 2 takes place. The pulley 2 is thus switched off again.
    In the previously described embodiment according to the single drawing, the clutch hub 4 designed as a toothed hub is the only component with a rotational play. In an embodiment of the invention, not shown, this rotational play of the clutch hub 4 is turned off by a clamping device in the form of a clamping set or the like or a press fit are used. This makes it possible to perform all, in the torque flow of the friction clutch components - seen in the direction of rotation - backlash. Since in the embodiment of the clutch hub 4 without rotational play also a a-axial displacement, which is necessary with appropriate wear for the ventilation of the clutch is missing, in this embodiment, the friction lining 5 is designed as an axially compliant membrane.
    权利要求:
    Claims (9)
    [1]
    1. pressure-medium-operated friction clutch or brake with a rotatable friction disc (5, 6) and with a surrounding the friction disc housing (7 to 9), in which an acted upon by a pressure medium, axially movable thrust washer (11) is arranged which frictionally with the friction disk (5, 6) can be brought into connection, wherein the pressure disk (11) can be reset by means of an axially resilient membrane (12) which is clamped on the housing (7 to 9) on the one hand and on the pressure disk (11) on the other hand, characterized in that the membrane (12) in the ίο area of its outer circumference is clamped on the housing side and in the region of its inner circumference pressure plate side, and that the housing (7 to 9) has a housing axis of rotation across open, central cylinder chamber (16) in which a with the pressure plate (11) connected to the pressure piston (10) is arranged axially movable ί £.
    [2]
    Second pressure-actuated friction clutch according to the preamble of claim 1, characterized in that for the axial return of the thrust washer (11) in addition a compression spring arrangement (13) is provided which acts in parallel circuit to the diaphragm 2o (12) on the thrust washer (11) ,
    [3]
    3. pressure-medium-actuated friction clutch according to claim 2, characterized in that the compression spring arrangement (13) comprises a plurality of evenly over the circumference of the pressure disc (11) distributed an-géordnete helical compression springs (13) on a> 2 Â £ · outer peripheral portion of the pressure disc ( 11) are supported.
    [4]
    4. Friction clutch according to claim 3, characterized in that the thrust washer (11) at its outer peripheral region on the helical compression springs (13) facing away from a support contour (14) which forms an axial support surface. Ö.sReibkupplung according to any one of the preceding claims, characterized in that the housing (7 to 9) radially within an outer clamping region of the membrane (12) forms an axial bearing surface (15) for the membrane (12).
    [5]
    6. friction clutch according to claim 5, characterized in that 'K'die support surface of the thrust washer (11) is arranged at the same radial height as the axial bearing surface (15) of the housing (7 to 9) for the membrane (12).
    [6]
    7. friction clutch according to claim 6, characterized in that the membrane (12) between the support surface of the thrust washer (11) Λ5 and the contact surface (15) of the housing (7 to 9) extends.
    [7]
    8. A friction clutch according to claim 3, characterized in that the pressure plate (11) on its the helical compression springs (13) facing the end face is axially recessed.
    [8]
    9. Friction clutch according to one of the preceding claims, characterized in that the membrane is provided with pressure relief bores.
    [9]
    10. Friction clutch according to one of the preceding claims, characterized in that pressure relief profiles or passages are provided on the pressure plate.
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR1460372A|1964-12-30|1966-11-25|Borg Warner|Clutches connecting an air conditioning compressor to the engine of a vehicle|
    US4418807A|1981-05-11|1983-12-06|Horton Industries, Inc.|Friction interface unit for a clutch and a brake|
    DE8131995U1|1981-11-02|1982-10-14|Linnig, Karl-Heinz, 7990 Friedrichshafen|"SWITCHABLE FRICTION CLUTCH"|
    JPS61182422U|1985-05-02|1986-11-14|
    US2608275A|1945-12-13|1952-08-26|Hobbs Transmission Ltd|Power transmission apparatus|
    GB1328712A|1971-06-29|1973-08-30|Stromag Maschf|Clutch and braking device actuatable by fluid pressure|
    US4425993A|1981-02-20|1984-01-17|Horton Industries, Inc.|Fluid engaged spring released fan clutch having a modular mount for a spring engaged fluid released fan clutch|
    DE3114530A1|1981-04-10|1982-11-04|Fichtel & Sachs Ag, 8720 Schweinfurt|FRICTION CLUTCH WITH HYDRAULIC ACTUATOR|
    JPS63214522A|1986-04-18|1988-09-07|Bruderer Ag|Coupling device with single plate clutch mounted between flywheel for drill and pressure plate|DE202009003616U1|2009-03-06|2009-05-28|Stromag Ag|Multi-surface friction clutch or brake|
    JP2018200062A|2017-05-25|2018-12-20|トヨタ自動車株式会社|Clutch engaging/disengaging device|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE102006033426A|DE102006033426B4|2006-07-13|2006-07-13|Fluid-actuated friction clutch|
    DE102006033426|2006-07-13|
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