DE19721308A1 - Modular clutch and motor flywheel - Google Patents

Abstract

A modular clutch with a flywheel (2) and a clutch cover (3) and an arrangement of clutch plates (4) forming a single module fixed either directly to the motor crankshaft or to a flexible plate. The modular clutch is constructed and fitted or replaced as a single unit. The clutch cover has a cover (21), a pressure plate (22) and a diaphragm spring (23). The arrangement of clutch plates has a clutch take-up area (31) made of a sintered metallic element.

Description

The present invention relates to a modular dome tion mechanism and in particular a modular clutch mechanism in which a flywheel, a clutch cover assembly and a clutch disc assembly a form a single module or a single module, which as Unit attached to an engine crankshaft and replaced becomes.

A coupling device generally has one Engine crankshaft attached flywheel and a Flywheel attached clutch cover assembly. In addition is a clutch disc assembly between the flywheel and the clutch cover assembly arranged. Usually set the flywheel, clutch disc assembly and the clutch cover assembly are separate elements which repaired independently of the other elements and can be replaced.

In known coupling devices, the flywheel connected to the engine crankshaft by bolts. The dome Lung lid arrangement is in turn on the flywheel by bolts attached and the clutch disc assembly between the Flywheel and clutch cover assembly in sandwich form positioned. An element can be replaced by Ent remove the pin on the clutch cover assembly, remove the clutch cover assembly and the clutch disc assembly achieved as well as replacement of the required component will. In addition, the flywheel can, if it required, maintained or replaced.

The known arrangement mentioned above results in a Problem in that the components - the flywheel and the Clutch cover and clutch disc arrangement - in general  my are expensive to manufacture and only conditionally under high costs can be maintained. Usually will both the clutch cover assembly and the clutch disc assembly replaced together, even if only one of the both components are worn or damaged. Analogous is when replacing the clutch disc and clutch cover Arrangements revised the surface of the flywheel or repaired. As a result, all three components are er renewed, even if only one component is worn out or is damaged.

Modular couplings have been used for some time, if the flywheel, clutch cover assembly and Clutch disc arrangement in advance to a single module be assembled. Such a modular clutch will attached to the engine crankshaft as a single unit. At for example, a flexible plate is in advance at one end the engine crankshaft installed. An outer peripheral area the flexible plate is bolted to an outer um catch area of the flywheel attached. Here, the Bolt inserted from the engine side.

In the known modular coupling described above the clutch cover and the flywheel are lubricated together Stigt, for example by welding or the like, but without Bolt. The omission of the bolts allows a weight and cost reduction. With this semi-permanent fastener type of use by caulking, welding or the like the modular coupling can be replaced completely if ei ne friction surface of the clutch disc arrangement from maximum is used. In the known modular coupling the possibility that the clutch disc assembly is maximal is worn out while the flywheel and clutch cover arrangement can still be used. In the above be written modular arrangement can the clutch discs arrangement cannot be replaced in simple form. As a result it should be ensured that the clutch disc arrangement  voltage can be used for as long as possible.

It is an object of the present invention to provide a modular To create clutch, in which the clutch cover and the flywheel together through a simple arrangement without Disadvantages can be fixed.

The task is achieved through the combination of features of the claim ches 1, 14, 16 or 29 solved; the subclaims have preferred embodiments of the invention to the content.

The present invention provides a modular coupling created which has a longer lifespan or usage has time.

According to one aspect of the present invention created a modular coupling as a single module, wel ches is connected to the output of a motor and a Flywheel, which on one side with a Rei training surface is formed, and on the torque output element of the motor is releasably attached. A clutch Lid assembly has a clutch attached to the flywheel and one inside the clutch cover Nete pressure plate, which one of the friction surface turned printing area includes. The clutch cover assembly also has a biasing element which in the clutch is supported to the pressure plate against the Tension flywheel. A clutch disc assembly is arranged between the friction surface and the pressure surface and includes several friction surfaces between the Rei exercise surface and the printing surface are arranged, the Friction surfaces made of a metallic friction material forms are.

Preferably, the clutch cover is ver with the flywheel stems.  

Preferably, the clutch cover with the flywheel is ver welds.

Preferably, the clutch cover is ge on the flywheel rivets.

The modular coupling preferably also has a around the coupling ring gear arranged on and covers the Clutch cover an outer periphery of the flywheel, wherein the ring gear or ring gear on the clutch cover in such a way is shrink fit that the ring gear tight engagement the clutch cover in the outer circumference of the flywheel works.

The flywheel preferably comprises a first flywheel and an inertial element and is a mechanism for the gate tion vibration damping between the first flywheel and arranged the inertial element and allows a limited te relative rotation between the first flywheel and the Inertia element as well as dampens between these two elements occurring vibrations.

Preferably, the mechanism for damping torsion vibrations are formed with a chamber that fits into it has ordered elastic element and is also a powdery solid lubricant inside the chamber posi worked.

The elastic element preferably consists of a curved one undulated leaf spring.

Preferably, an outer peripheral region touches the curved one NEN leaf spring, the peripheral wall of the receiving chamber, so that a friction generating mechanism is established which friction between the two elements accordingly the relative rotation between the first flywheel and the Inertia element generated.  

The powdery solid lubricant preferably consists of Molybdenum disulfide.

The powdery solid lubricant preferably consists of Tungsten disulfide.

The clutch disc arrangement preferably has a damper tion element, which ver elastically in the axial direction is malleable, and the friction surfaces are against each other overlying surfaces of the damping element attached.

There is preferably the first flywheel and the pressure plate Cast iron with Cr, V and a rare added Earth metal.

According to another aspect of the present invention a modular coupling is created, with a Flywheel, the end face of which with the crankshaft of a Mo tors is connectable, the end face also being in order circumferential bulge extending in the direction of traverse, wel protrudes in the axial direction and along the increase tion of the flywheel radius increases. A clutch cover Order has an axially encompassing the flywheel clutch cover arranged relative to the flywheel, which includes an inwardly curved edge so that the Circumferential bulge is clamped, which holding elements having attached to the drive end surface, wherein the clutch cover is plate-shaped and a peripheral wall has, which is axially over the clutch disc assembly extends, the drive end surface being several in circumference direction spaced base areas corresponding to the holding Has elements, the holding elements along the curved Edge are formed and each holding element radially after inside, aligned with the surface of the base areas is bow, and the clutch cover assembly also a Comprises pressure plate, which is arranged coaxially to the flywheel and the opposite end face of the flywheel  turns. A clutch disc assembly is coaxial arranged relative to the pressure plate and the flywheel and positioned between the two elements. Areas of friction the clutch disc assembly consist of a sintered metal material. Fasteners fastened the Holding elements of the clutch cover on the base areas. A region of the peripheral wall of the clutch cover is radial stepped inwards and forms a stop, which on Edge or marginally against the opposite end face of the Flywheel abuts.

The flywheel and the pressure plate preferably consist of Cast iron with Cr, V and a rare added earth metal.

According to another aspect of the present invention a modular coupling is created, with a Flywheel, which has an outer radial upper surface formed annular area, a first axial surface, which with a corresponding element of an engine is connectable to drive the clutch, the first Axial surface a circumferential extension running in the axial direction chung, and has a second axial surface which the lies opposite the first axial surface. A clutch cover order includes:

• a) an annular pressure plate with an outer radial area which is coaxially adjacent to the flywheel arranges and faces the second axial surface;
• b) a pressure element which is attached to the pressure plate is elastic to the pressure plate to the flywheel to press; and
• c) a uniform clutch cover with an annular against the wall, which is the outer radial surface of the pressure plate and the flywheel, with a wedge  area, which extends from the annular wall stretches and is caulked with the circumferential bulge, with a mounting area, which differs from the extends annular wall and on the second Axialflä che is attached, and with a support area to the Support pressure element. A clutch disc assembly is coaxially between the pressure plate in the flywheel arranges, with friction areas of the clutch discs order consist of a sintered metal material.

Preferably, the flywheel and the ring-shaped Cast iron pressure plate with Cr, V and an added one rare earth metal.

The circumferential bulge is preferably arcuate and points the caulking area corresponds to a circumferential bulge arch form.

The circumferential bulge preferably extends axially direction adjacent to the peripheral edge of the flywheel Outside.

The annular wall preferably has a second reinforcement tion area, which with the peripheral edge of the second Axial surface of the flywheel is caulked, the Flywheel between the caulking area and the second Caulking area is arranged axially in sandwich form.

The second caulking area of the coupling is preferred lid is graduated radially inward and abuts the second axial surface of the flywheel.

According to another aspect of the present invention a modular coupling is created, with a Flywheel, which has a radial outer surface and an axial surface and an annular pressure plate with an outer Has radial surface, the annular pressure plate ko  axially adjacent to the flywheel and the Axialflä surface of the flywheel is facing. A clutch cover around engages the outer radial surfaces of the pressure plate and the Flywheel and a radial inner surface of the clutch cover touches the outer radial surface of the flywheel a contact position. A ring gear or a ring gear is on the peripheral surface of the clutch lid fit radially over the contact position, the Ring gear on the peripheral surface of the clutch cover is shrink fit. There are several axially extending slots spaced circumferentially on an inner edge of the dome training cover formed at the contact position. A dome The pulley arrangement is coaxial between the pressure plate and the flywheel, wherein friction areas of the Clutch disc assembly made of a sintered metal mat rial exist.

A positioning element preferably maintains a fixed relay tivposition between the clutch cover and the flywheel at.

The positioning element preferably has a plurality in the coupling Open the lid and the flywheel is there rin inserted pins, the openings around the Alignment of clutch cover and flywheel in alignment are spaced from the contact position.

The positioning element preferably has a stop rich on which as a radially inward step is formed on the clutch cover, the stop area on the axial surface of the flywheel on a radial strikes outward position.

The modular coupling arrangement preferably also has an egg ne attached to a second axial surface of the flywheel re flexible plate.  

The flywheel and the annular pressure preferably exist cast iron plate with Cr, V and one added rare earth metal.

The previous and further tasks, characteristics, aspects and advantages of the present invention will be apparent from the following detailed description in connection with the attached drawing. It shows:

Fig. 1 is a schematic cross-sectional view of a modular clutch according to a first game Ausführungsbei of the present invention, wherein the modular clutch is mounted on a flexible plate attached to an engine crankshaft;

Fig. 2 is a partial sectional view of a Deckelkupplungsbe range of the modular hitch shown in Figure 1, wherein the modular coupling is released from the flexible plate.

Fig. 3 is a cross sectional view are shown of a portion of that shown in Figure 1 the modular coupling to an enlarged scale, with further details of the cover coupling area of Fig. 2.

Fig. 4 is a partial sectional view of a disk plate of the clutch disk assembly of the modular clutch shown in FIG. 1, the clutch disk assembly being detached from the modular clutch;

Fig. 5 is a schematic cross-sectional view of a portion of the clutch disc assembly shown in Fig. 4, showing details of a friction element of the clutch disc assembly according to the first embodiment of the present invention;

Fig. 6 is a partial sectional view of a clutch plate arrangement according to a second embodiment of the present invention;

Fig. 7 is a schematic sectional view of a portion of the clutch plate assembly shown in Fig. 6 along the line VII-VII of Fig. 6, showing details of a friction member and a damping plate of the clutch plate assembly according to the second embodiment of the present invention;

Fig. 8 is a cross sectional view taken along the line VIII-VIII of Fig. 6;

Fig. 9 is a schematic cross-sectional view of a modular clutch according to a third Ausführungsbei game of the present invention with an alterna tive action for fastening the clutch cover assembly to the flywheel;

Fig. 10 is a cross-sectional view of a portion of the modular clutch shown in Figure 9 on an enlarged scale, details of the measure for attaching the clutch cover assembly to the flywheel are Darge.

Fig. 11 is a partial sectional elevation of a portion of the outer side of the clutch cover assembly of the modular clutch shown in Fig. 9;

Fig. 12 is a cross-sectional view analogous to Figure 10 of a modifi ed area of the modu laren coupling shown in Figure 9 on an enlarged scale, with slightly modified details of the measure for mounting the clutch cover assembly on the flywheel are shown.

Fig. 13 is a schematic cross-sectional view of a modular clutch according to a fourth exemplary embodiment of the present invention with further elements for fastening the clutch cover assembly to the flywheel;

Fig. 14 is a schematic cross-sectional view of a modular clutch according to a fifth exemplary embodiment of the present invention with further elements for fastening the clutch cover assembly to the flywheel;

Fig. 15 is a schematic cross-sectional view of a modular clutch according to a sixth Ausführungsbei game of the present invention with a cover coupling unit as a fastening element for the clutch cover assembly to the flywheel;

Fig. 16 is a perspective view of the Deckelkupplungsein unit of the modular coupling shown in Fig. 15 in a slightly enlarged scale;

Fig. 17 is a schematic cross-sectional view of a modular clutch according to a seventh embodiment of the present invention, the flywheel being attached directly to the engine crankshaft;

Fig. 18 is a partial view of a diaphragm spring which is released from the modular coupling shown in Fig. 17;

FIG. 19 is a perspective view of the of the formed Membranfe of Figure 18 aperture.

. FIG. 20 is a perspective view of an alternatively be formed opening of Mem shown in Figure 18 branfeder;

FIG. 21 is a partially sectioned elevational view of a clutch according to an eighth mo dularen exporting approximately example of the present invention;

FIG. 22 is a side sectional view of the modular coupling of FIG. 21 along the line XXII-XXII of FIG. 21;

Fig. 23 is a sectional view analogous to Figure 22 taken along the line XXIII-XXIII of Fig. 21.;

Fig. 24 shows the lubrication characteristics of various solid lubricants which are used in the eighth and ninth embodiments of the present invention; and

Fig. 25 is a cross-sectional view of a modular clutch according to a ninth embodiment of the present invention.

First embodiment

A modular clutch 1 is shown in Fig. 1 and has a flywheel 2 , a clutch cover assembly 3 and a clutch plate assembly 4 , which form a single modular arrangement. A motor E is arranged on the left side of FIG. 1 and a gearbox T on the right side of this figure. In Fig. 1, OO denotes the axis of rotation of the modular coupling 1 . In the following, the left side of FIG. 1 is referred to as the motor side and the right side of FIG. 1 as the transmission side.

The modular clutch 1 represents a device for transmitting a torque from a crankshaft 5 of an engine to a main drive shaft 6 extending from the transmission and for interrupting the transmission. The modular clutch 1 can be attached to or detached from the engine E as a single unit . The modular coupling 1 is attached to a flexible plate 7 , which in turn is fixed at the end of the crankshaft 5 by a plurality of bolts 12 . The flexible plate 7 has a high degree of rigidity in the direction of rotation, but is flexible in the direction of curvature (axial direction). A ring gear or ring gear 13 is on the outer circumferential area of the flexible plate 7 , for example by welding be fastened. The above-mentioned flywheel 2 of the modular hitch be 1 is fixed to the outer peripheral region of the flexible plate 7 by a plurality of bolts 11 or screws. The main drive shaft 6 has a spline which engages in the hub 34 of the clutch disc assembly 4 and will be described later. A release unit 8 is axially movable around the main drive shaft 6 . The release unit 8 can engage in the transmission side of the diaphragm spring 23 , as described below, the clutch cover assembly 3 .

The flywheel 2 is substantially ring-shaped and has a flat friction surface 2 a, which faces the transmission. The flywheel 2 consists, for example, of cast iron with Cr, V and a rare earth element.

As shown in Fig. 2 and 3, the flywheel 2 is formed with a plurality of inclined grooves 2 c, which extend in the circumferential direction on an outer circumferential side surface and face the engine side. Each ge inclined groove 2 c has an inclined bottom or an inclined sole, the depth of which increases as the position moves from the radially outer side to the inner side of the flywheel 2 . Flat areas 2 d are formed between adjacent ge inclined grooves 2 c. Each flat area 2 d has an opening H with a predetermined depth at its essentially central area.

The clutch cover assembly 3 comprises a clutch cover 21 , a pressure plate 22 and a diaphragm spring 23 . The hitch be cover 21 has a plate-shaped plate shape. The clutch cover 21 includes a large opening in its with te, through which the shaft 6 extends. The outer peripheral wall of the clutch cover 21 extends axially and has an end attached to the outer peripheral region of the flywheel 2 .

A cover fastening unit 61 will be described below, which in turn serves for fastening the flywheel 2 and the clutch cover 21 to one another. The hitch be cover 21 is formed at its axial end with an outer cover portion 62 which envelops areas of the outer peripheral surface 2 b of the flywheel 2 and is in direct contact with it. The end of the outer cover portion 62 is formed at its end with a plurality of caulking areas 63 which correspond to the circumferential length of the inclined groove 2 c. The outer cover area 62 is also designed with a fastening area 64 , which is dimensioned and shaped such that it speaks essentially the flat area 2 d, as shown in Fig. 2, ent. The caulking area 63 is bent such that it corresponds to the inclined groove 2 c on the flywheel 2 , as shown in FIG. 3, and covers it. The fastening area 64 extends radially inward beyond the caulking area 63 and is in close contact with the flat area 2 d of the flywheel 2 . The fastening area 64 is fastened to the flat area 2 d by a pin 68 which is inserted into the opening H. In this way, a relative rotation between the flywheel 2 and the clutch cover 21 is prevented. Furthermore, the hitch be cover 21 is formed on an outer peripheral region with an annular contact region 65 which is caulked such that it extends radially inwards and with the outer peripheral edge of the friction surface 2 a of the flywheel 2 from the transmission side, as in Fig. 3 Darge represents, is in contact. The contact area 65 has a recessed surface which is in contact with an outer radial area of the friction surface 2 a. If the hitch be cover 21 is fitted on the outer circumference of the flywheel 2 , this recessed surface is in contact with the friction surface 2 a of the flywheel 2 , so that the flywheel 2 is axially posi tioned relative to the clutch cover 21 .

The pressure plate 22 is an annular element which is arranged radially inside the clutch cover 21 . The pressure plate 22 consists, for example, of cast iron with Cr, V and a rare earth metal. The pressure plate 22 has a pressure surface 22 a which faces the flywheel 2 . The pressure plate 22 has an annular before jump 22 b, which is in the axial direction from the surface that is opposite the pressure surface 22 a. The ends of a plurality of tangentially extending strip plates 24 are fastened to the outer peripheral region of the pressure plate 22 by bolts 28 , as shown in FIG. 1. The other end of each strip plate 24 is fixed to the clutch cover 21 . The strip plates 24 cause the pressure plate 22 to rotate together with the clutch cover 21 and allow axial movement of the pressure plate 22 relative to the clutch cover 21st The strip plates 24 clamp the pressure plate 22 away from the flywheel 2 .

The diaphragm spring 23 is arranged between the pressure plate 22 and the clutch cover 21 . The diaphragm spring 23 has an annular elastic region 23 a and a plurality of levers 23 b, which extend radially inward from the elastic region 23 a. The elastic region 23 a has an outer circumferential region which is in contact with the annular projection 22 b of the pressure plate 22 and an inner circumferential region which is supported by a support arrangement 25 . The support arrangement 25 has a plurality of stud bolts 26 and two wire rings 27 . The pin screws 26 are attached at one end to the radial inner region of the bottom of the clutch cover 21 and extend to the engine. These stud bolts 26 support the two wire rings 27 . A radial inner region of the elastic element 23 a is arranged between the two wire rings 27 . Each stud screw 26 runs through a rounded, right corner-shaped opening 23 c in the diaphragm spring 23 . The ela tical area 23 a biases the pressure plate 22 to the flywheel 2 in this state.

The release unit 8 is arranged between the diaphragm spring 23 and the transmission T, and is the radially inner ends of the levers 23 b of the diaphragm 23 opposite. If the Löseein unit 8 is moved to the flywheel 2 , the release unit 8 presses the lever 23 to the motor and counteracts the force of the elastic region 23 a, which acts on the pressure plate 22 , and the pressure plate 22 will no longer become the flywheel 2 pressed.

The clutch disc assembly 4 has a clutch grip area 31 , which is arranged between the flywheel 2 and the pressure plate 22 . The clutch disc arrangement 4 also includes clutch and retaining plates 32 and 33 , which define drive elements, a hub 34 , which defines an output element, coil springs 36 , which is arranged between the plate pair 32 and 33 and the flange 35 of the hub 34 , and a friction-generating Mechanism 37 . The hub 34 has a hub flange 34 a, which is formed in one piece with the flange 35 on its outer circumference. The hub flange 34 a is formed in its center with a wedge opening which engages in the main shaft 6 . The coupling and holding plates 32 and 33 are circular plates, which are each positioned on opposite sides of the flange 35 . The coupling and holding plates 32 and 33 have ra diale outer areas which are attached to each other by contact pins 38 . The coil springs 36 are arranged in windows which are formed on the plates 32 and 33 and the flange 35 . The friction generating mechanism 37 has a plurality of disks positioned between the plates 32 and 33 and the flange 35 .

As shown in Figs. 3, 4 and 5, the Kupp consists lung engaging portion 31 consists essentially of a disc plate 41 which is fixed to the clutch plate 32, and -elements for several Reibungspads and 43, respectively, which are fixed to the disk plate 41 . The disc plate 41 is a circular element, as shown in Fig. 4, and is fixed with an inner peripheral portion on the outer peripheral portion of the clutch plate 32 by rivets 39 . The disc plate 41 is formed on its outer circumference with three projections 42 . Each projection 42 supports two friction members 43 on each side (ie, four elements 43 in total). As shown in particular in Fig. 3, this friction element 43 is formed from a core plate 45 , a shield from 46 and a sintered element 47 . Fig. 3 shows that each protrusion 42 and the core plates 45 of the friction members 43 are connected together at their opposite sides by two rivets 44th The sintered element 47 is designed with the rivets 44 corresponding openings.

In Fig. 5 the structure is shown on an enlarged scale and the special structure of Reibungsele element 43 is described below. The shield 46 is positioned on the core plate 45 . The shield 46 consists of a metallic mesh plate and has a corrugated shape. The core plate 45 and the sintered member 47 adhere to the top and bottom of the shield 46, respectively. A space between the core plate 45 and the sintered element 47 is filled with graphite particles 48 . The core plate 45 is formed on its circumference with a projection 45 a, which prevents the graphite 48 from escaping.

The sintered element 47 is arranged on the shield 46 and consists of a mixture of ceramic or graphite powder and a powder of a Cu-Sn alloy.

In the friction element 43 constructed in this way, the gra phit 48 acts as an insulating material between the core plate 45 and the sintered element 47 . As a result, noises occurring during the coupling intervention process can be reduced. The graphite 48 also serves as a heat insulator. Thus, the heat transfer from the sintered element 47 to the disc plate 41 , the clutch plate 32 and the holding plate 33 is minimized and bending and deformation of these plate elements are suppressed. As a result, a higher service life or operating time of the clutch disk arrangement 4 is achieved.

Since the shield 46 is corrugated, it provides an insulating effect. Since the shield 46 is mesh-shaped, the graphite 48 can freely move between its opposite sides. This increases the insulation effects of graphite 48 .

A method of manufacturing the friction member 43 will be described below. First, the shield 46 is positioned on the core plate 45 and the graphite 48 is arranged substantially completely over the shield 46 . The powder mixture of ceramic, graphite or the like and the Cu-Sn powder is then filled or positioned over the graphite 48 . These powders are heated at approximately 700 ° C. and subjected to a predetermined pressure, which, however, does not smooth the shield 46 .

An assembly method of the modular clutch 1 is explained below. First, the diaphragm spring 23 and the pressure plate 22 are attached to the clutch cover 21 to assemble these elements into the clutch cover assembly 3 . At this time, the caulking area 63 and the fastening area 64 of the clutch cover 21 have straight shapes. Then the clutch cover assembly 3 and the clutch disc assembly 4 are assembled together and the flywheel 2 is inserted into the clutch cover 21 . In this step, the end face of the outer peripheral portion of the flywheel 2 is brought into contact with the contact portion 65 of the clutch cover 21 such that the flywheel 2 and the clutch cover 21 are axially positioned together. Then the openings of the clutch cover 21 and the flywheel 2 are aligned with each other to insert the pin 68 in them.

A caulking step is then carried out. Here, each caulking area 63 of the clutch cover 21 is deformed so that it approximately corresponds to the surface and inclination of the inclined groove 2 c of the flywheel 2 or is in conformity therewith. Each fastening area 64 is bent by 90 ° and pressed against the flat area 2 d of the flywheel 2 . Then the pin 68 is fitted into the openings in the flat area 2 d of the flywheel 2 and the fastening areas 64 . This prevents a relative rotation between the flywheel 2 and the clutch cover 21 . After assembly, the modular coupling 1 can be handled as a single module or as a single component.

The completed modular coupling 1 is fastened by bolts 11 to the flexible plate 7 , which is already fastened to the crankshaft 5 . The housing of the transmission T is designed with (not shown) windows or openings to actuate the bolts 11 .

The construction of the fastening unit 61 does not require a fastener such as a bolt in this embodiment, so that the weight of the present invention is reduced compared to known arrangements. Since the flywheel 2 and the clutch cover 21 are axially positioned relative to one another by the caulking area 65 , no element, such as a striker, is required, so that the structure is simplified relative to the prior art and is again relatively inexpensive compared to the prior art. Since the outer peripheral end of the clutch cover 21 is attached to the flywheel 2 by caulking, the clutch cover 21 can be fixed in a reliable manner on the flywheel 2 in a simple manner.

Since this modular clutch 1 uses the friction elements 43 formed from metallic sintered elements 47 , the clutch engagement area 31 can have a longer service life than that of the prior art. So with the modular clutch 1, the clutch disc assembly 4 must not be replaced as often as in the known th arrangements without such sintered elements. Consequently, this modular arrangement of the present invention has only a slight disadvantage, although the flywheel 2 and the clutch cover 21 are coupled to one another by caulking.

The first flywheel 2 and the pressure plate 22 are made of cast iron with Cr, V and a rare earth metal. The wear on the first flywheel 2 of the pressure plate 22 is thus reduced and the complete modular clutch 1 has a longer life expectancy.

Second embodiment

The clutch engagement area 31 'of FIGS. 6 to 8 can be used instead of the clutch engagement area 31 of the first exemplary embodiment. The clutch engagement area 31 'is designed with a plurality of coupling elements 51 of the coupling development. The coupling elements 51 of the clutch are attached to the outer peripheral edge of the disk plate 41 'by rivets 60 and equally spaced apart in the circumferential direction.

Each coupling element 51 of the coupling is formed with first and second core plates 52 and 53 made of steel plates, a damping plate 54 and first and second sintered elements 56 and 57 made of composite material with ceramic and metal, as shown in FIGS. 7 and 8. The first core plate 52 and the damping plate 54 extend radially inward beyond the second core plate 53 and the first core plate 52 and the damping plate 54 are benplatte 41 'attached to the Schei by the rivets 60 . A damping area of the damping plate 54 is stepped or corrugated and arranged between the first and second core plates 52 and 53 . Thus, the damping plate 54 has inner and outer circumferences which are in contact with the first core plate 52 and a radial central region which is in contact with the second core plate 53 as shown in FIG. 8. As also shown in FIGS. 6 and 8, opposite ends of each damping plate 54 and every second sintered element 57 are connected to one another by rivets 55 or attached to one another in the circumferential direction. The first core plate 52 is formed with openings 52 a, which are arranged on the rivets 55 corresponding positions. The first sintered element 56 extends in the circumferential direction between the openings 52 a of the first core plate 52 and the second sintered element 57 extends in the circumferential direction between the rivets 55 of the second core plate 53 . The first and second sintered members 56 and 57 adhere to the first and second core plates 52 and 53, respectively.

The damping plate 54 can reduce vibrations and noise during vehicle start. The elasticity of the damping plate 54 acts in the opposite direction to the pressure of the pressure plate 22 and thus a force is reduced, which is required to depress the clutch pedal. In particular, the relationship between the pressure force required to release the clutch and the elastic force of the diaphragm spring does not vary substantially over the entire service life of the clutch module, since wear of the friction element 57 is suppressed. As a result, a low pedal depression force is maintained. Thus, no complicated friction adjustment mechanism needs to be used.

Alternatively, rubber or other elastic material can be used in place of the damping plate 54 . On the other hand, non-woven fabric such as steel wool with heat resistance can be used.

Third embodiment

A modular clutch 100 is shown in FIGS . 9 to 12 Darge and has similar features as the above-described couplings of the other embodiments. Therefore, only those features are described which differ from the modular coupling of the first embodiment. In the modular coupling 100 , the fastening unit 161 for the cover has a multitude of different features, as will be explained below. The engagement area 31 of the clutch corresponds essentially to that of the first embodiment, but can alternatively be described with reference to the second exemplary embodiment.

In the modular clutch 100 , the clutch cover 121 is formed at its outer peripheral end with a plurality of outer cover strips 72 , which extend axially. The outer cover strips 72 are festge through several slots 73 , which extend axially between the strips, as shown in Fig. 11. The outer cover strips 72 be cover and touch the outer peripheral surface 2 b of the flywheel 2nd

A ring gear 13 or a ring gear is shrink fitted onto the outer cover strips 72 of the clutch cover 121 . The ring gear 13 is formed on its radial outer region with gear teeth which mesh with a pinion of a starter motor. Openings 74 e and 2 e are configured on the outer cover strip 72 of the clutch cover 121 and the outer peripheral surface 2 a of the flywheel 2 . A pin 75 is fitted in the openings 74 e and 2 e. The pins 75 stop relative rotation between the clutch cover 121 and the flywheel 2 .

The outer cover strip 72 of the clutch cover 121 is closely attached to the outer peripheral surface 2 b of the flywheel 2 by the shrink fit ring gear 13 .

An assembly process of the modular clutch 100 is described below. First, the clutch disk assembly 4 is disposed in the clutch cover assembly 3 and the flywheel 2 in the clutch cover 121 of the clutch cover assembly 3 is inserted. In this process, the openings 74 e and 2 e of the clutch cover 121 and the flywheel 2 are aligned with one another and the pin 75 is fitted into these openings. Here, a relative rotation of the clutch cover 121 to the flywheel 2 is prevented.

In this state, the ring gear 13 is heated. If necessary, the clutch cover 121 and the flywheel 2 are cooled. Then the ring gear 13 with a stretched inner diameter is shrink fit due to the heating on the plurality of outer cover strips 72 . The inner diameter of the bevel ring 13 thus fitted shrinks so that the outer cover strips 72 of the coupling cover 121 and the ring gear 13 are closely attached to the outer circumferential surface 2 b of the flywheel 2 . Even if the inner diameter of the clutch cover 121 is larger than the outer diameter of the flywheel 2 , due to machining errors, the outer cover strips 72 are bent in accordance with the shrinking process of the ring gear 13 and consequently in close and close contact with the outer peripheral surface 2 b brought. Consequently, the clutch cover 121 is fixed in a reliable manner on the outer peripheral surface 2 b due to the plurality of outer cover strips 72 , which are defined by the slots 73 . In this way, the modular clutch 100 is completed.

In this embodiment, the ring gear is shrink-fitted to the flywheel 13, while lid 2 of the coupling 121 on the outer circumferential surface 2 b of the flywheel 2 is attached. Thus, only one step is required instead of the known two steps, that is, one step for attaching the ring gear to the flywheel and a subsequent step for attaching the clutch cover to the flywheel. Since the clutch cover 121 and the flywheel 2 are substantially completely secured together by their outer peripheral surfaces, a tight fit can be retained for a long time compared to the known arrangement, which uses a plurality of bolts for fastening. Since a fastener, such as a bolt, is not required, the entire assembly becomes cheaper and has a reduced weight.

In a modification of this embodiment, as shown in FIG. 12, a contact area 77 can be formed radially inward by caulking the outer peripheral area (near the base ends of the outer cover strips 72 ) of the clutch cover 121 . This contact area 77 is formed with a contact surface, which in turn is in contact with the outer peripheral edge of the flywheel 2 near the Reibungsflä surface 2 a. The contact between the contact area 77 and the outer peripheral edge of the flywheel 2 acts as an axial positioning of the clutch cover 121 and the flywheel 2 when they are assembled. No pin 75 is required here.

Fourth embodiment

In the modular clutch 200 shown in FIG. 13, the clutch cover 221 on the flywheel 2 is fixed by rivets. In particular, the lid attachment unit 261 has the following structure. The flywheel 2 is formed on its outer peripheral region with outer projections 2 f, which protrude radially outward. The hitch be cover 221 is designed with outer fastening areas 79 corresponding to the respective outer projections 2 f. The outer projection 2 f and the outer fastening supply area 79 are fastened to one another by rivets 81 .

Fifth embodiment

According to a modular hitch 300 shown in FIG. 14, the clutch cover 321 is welded to the flywheel 2 . In particular, the lid mounting unit 361 has the following structure. The clutch cover 321 has an outer peripheral end which is in contact with the outer peripheral region 2 b of the flywheel 2 in contact. The outer peripheral end of the clutch cover 321 is fixed to the outer peripheral surface 2 b by a welded loading area 82 .

Sixth embodiment

According to a modu laren clutch 400 shown in FIGS . 15 and 16, the clutch cover 421 is attached to the flywheel 2 by bolts. In particular, the fastening unit 461 for the lid has the following structure. The clutch cover 421 is provided at its outer peripheral end with projections 83 which protrude axially from the end surface 421 a. The projections 83 are formed over their entire circumference with the same spaces between them and each have an opening 84 in the middle. The flywheel 2 is designed on its outer peripheral surface 2 b with grooves 2 g. A radial threaded opening 2 h is formed in the groove 2 g. The groove 2 g forms a tan gential flat seat. The projection 84 engages in the groove 2 g and is fastened to the flywheel 2 by a bolt 86 be.

An assembly route of the modular clutch 400 is described below. First, the clutch disc assembly 4 is positioned in the clutch cover assembly 3 and the flywheel 2 is inserted into the clutch cover 421 . In this operation, the projection 83 is fitted into the groove 2 g of the flywheel 2 and the end face 421 a is brought into contact with the flywheel 2 near the friction surface 2 a, all elements being axially positioned together. In this state, the bolt 86 is inserted into the opening 84 of the fastening area 83 and screwed into the threaded opening for 2 hours. As a result, the clutch cover 421 is attached to the flywheel 2 . Since the groove 2 g produces a flat seat surface, the projection 83 of the clutch cover 421 is pressed against the groove 2 g and is smoothed in the process. As a result, the contact between the projection 83 and the surfaces of the groove 2 g and the contact surface between the projection 83 and the seat surface of the bolt 86 provide a rigid connection between the clutch cover 421 and the flywheel 2 .

In this embodiment, there is a sufficiently large contact between the projection 83 of the clutch cover 421 and the flywheel 2 and the projection 83 is fastened by the bolt 86 after the projection 83 has been fitted into the groove 2 g of the flywheel 2 . Thus, shear forces generated in clutch cover 421 do not act directly on bolt 86 . As a result, there is little risk of breakage. As a result, the number of bolts required for fastening the clutch cover 421 can be minimized.

Seventh embodiment

A modular clutch 500 shown in FIGS . 17 to 20 consists essentially of the flywheel 2 , the clutch cover arrangement 3 and the clutch disc arrangement 4 . The modular clutch 500 is attached to the crankshaft 5 accordingly in the following description.

The friction surface 2 a is formed on the transmission side of the outer peripheral region of the flywheel 2 . The flywheel 2 is fixed to the crankshaft 5 by a plurality of bolts 11 A. In particular, the crankshaft 5 is designed with Ge thread openings 5 a and the flywheel 2 with openings 2 i for the bolt 11 A.

The clutch cover assembly 3 consists essentially of a clutch cover 521, the pressure plate 22 and the Mem branfeder 523rd The clutch cover 521 is plate-shaped and has a large opening in the middle. The clutch cover 521 has an outer peripheral portion which extends axially and is in close contact with the outer peripheral surface 2 b of the flywheel 2 , and also has an outer peripheral end which is bent radially inward and with the bottom surface of the flywheel 2 on the Engine side is engaged. The outer peripheral region of the clutch cover 521 and the outer peripheral region 2 b of the flywheel 2 are coupled to one another by a pin 93 .

The membrane spring 523 is arranged in the cover 521 and we sentlichen a circular element which is positioned between the clutch cover 521 and the pressure plate 22 . The diaphragm spring 523 has a radial central region which is supported by the clutch cover 521 by two wire rings 27 . The wire rings 27 are held by a plurality of eyelets 98 , which extend from the inner peripheral edge of the bottom of the clutch cover 521 and have a curved or curved shape. The outer peripheral end of the membrane spring 523 is in contact with the pressure plate 22 and biases the pressure plate 22 to the flywheel 2 . The diaphragm spring 523 is formed with slots 96 which run radially inward from the area near the outer peripheral end, as can be seen in FIG. 18. These slots 96 define a plurality of levers 95 . The membrane spring 523 is formed at its radial central region with a plurality of openings 97 which are equally spaced apart in the circumferential direction. Each opening is concentric with the corresponding slot 96 in the circumferential direction. The opening 97 has a diameter which enables the lead of an assembly tool 550 for fastening the bolt 11 A. As shown in FIG. 19, the diaphragm spring 523 is formed at regions around the openings 97 with burrs 501 which protrude substantially perpendicularly to the plane of the diaphragm spring 523 and have a predetermined height. Thus, the diaphragm spring 523 can have a high level of lever rigidity despite the formation of the openings 97 .

The clutch disk arrangement 4 is essentially formed from the clutch engagement area 31 analogously to that of the one already described in the first exemplary embodiment and from the hub 34 and the plate 17 . The inner peripheral edge of the plate 17 is fixed to the flange of the hub 34 by rivets 19 . The outer peripheral portion of the plate 17 is fixed to the clutch engagement portion 31 by rivets 18 . Meh rere openings 20 are formed on the radial central region of the plate 17 . Each aperture 20 has a diameter which allows inserting a mounting tool 550 for loading consolidate the bolt 11A. The hub 34 has a key opening that is coupled to the main drive shaft 6 of the transmission.

During the assembly process of the modular clutch 1 , the openings for the pin 93 are aligned with one another before the clutch cover 521 is attached to the flywheel 2 . Thus, the opening 2 i of the flywheel 2 is aligned with the opening 93 of the diaphragm spring 523 .

The assembled modular clutch 500 is attached to the crankshaft 5 as follows. The opening 20 of the plate 17 of the clutch disc assembly 4 is aligned with the openings 97 and 2 i. Here, the openings 2 i, 20 and 97 formed on the parts of the modular coupling 1 are axially aligned with one another. The modular clutch 1 is then fitted onto the crankshaft 5 . In this operation, the radial inner flange of the flywheel 2 is brought into close contact with the end face of the crankshaft 5 and the threaded openings of a crankshaft 5 is aligned with the openings 5 of the flywheel 2 i. 2 In this state, the mounting tool 550 holding the bolt 11 A is inserted from the transmission side into the openings 97 , 20 and 2 i of the diaphragm spring 23 , the plate 17 and the flywheel 2 and the bolt 11 A into the threaded opening 5 a of the crankshaft 5 inserted to attach these elements.

In a modification of this embodiment, as shown in FIG. 20, the diaphragm spring 523 can be formed around the openings 97 with tensile areas 502 in order to ensure sufficient rigidity. Since the rigidity of the lever of the diaphragm spring is not reduced, as described above, the clutch can maintain sufficiently clear or strong release properties.

Eighth embodiment

A modular clutch 601 shown in FIGS. 21 to 23 consists essentially of a flywheel 102 , a clutch cover assembly 103 , a clutch disk arrangement 104 and a damping mechanism 109 . A motor (not shown) is located on the left side of FIGS. 22 and 23 and a gear (not shown) on the right side. The modular clutch 601 transmits torque from the crankshaft 105 of the engine to the main drive shaft 106 extending from the transmission and interrupts the transmission. In Figs. 22 and 23 OO refers to the axis of rotation of the modular clutch six hundred and first

A flexible plate 107 and an inertia element 117 (two flywheel) is arranged at the end of the crankshaft 105 . The flexible plate 107 is a circular plate member and a circular plate member 114 is fixed to the inner peripheral portion thereof by rivets 115 . The inner peripheral region of the flexible plate 107 is fixed to the crankshaft 105 on the engine side together with the plate element 104 by bolts 112 . The flexible plate 107 is formed at its radial central region with a plurality of round openings 107 a equally spaced in the circumferential direction. The flexible plate 107 has high rigidity in the circumferential direction, but is flexible in the bending direction.

The inertia member 117 is fixed to the outer peripheral end of the flexible plate 107 by rivets 116 . The inertia element 117 is an axially elongated cylindrical element. A ring gear or ring gear 113 is mounted on the inertia element 117 . The inertial element 117 has at three equally spaced circumferential positions handling openings 117 a to connect the radial inside with the radial outside.

As described above, the flexible plate 107 and the inertia member 117 are arranged in advance on the crankshaft side, and the modular clutch 601 is attached thereto as explained below.

The damping mechanism 109 consists essentially of a first drive plate 141 , a second drive plate 142 , a curved leaf spring 146 and a driven element 143 . The first drive plate 141 is circular and arranged next to the flexible plate 107 . The first drive plate 141 has an outer peripheral portion which is in contact with an inner peripheral surface of the inertia member 117 . The first drive plate 141 has a radial central region which is convex to the gear. The second drive plate 142 is circular and arranged next to the first drive plate 141 . The second drive plate 142 has an outer peripheral end which is in contact with the inner peripheral surface of the support member 117 . The outer circumferential areas of the first and second drive plates 141 and 142 are in contact with each other and by rivets 148 with an interposed sealing ring 150 to each other. The inner circumferential area of the first drive plate 141 extends radially inward beyond the inner circumference of the second drive plate 142 . The inner peripheral region of the first drive plate 141 is formed with an inner projection 141 b, which has a cylindrical shape extending away from the motor side.

The outer peripheral regions of the first and second drive plates 141 and 142 are BEFE on the inertial element 117 by three equally spaced bolts 111 B in the circumferential direction. The bolts 111 B are BEFE Stigt from the transmission side. The inertia element 117 is provided with grooves 117 b at positions corresponding to the respective bolt 111 B.

An annular between the first and second drive plates 141 and 142 defined space forms a Federauf receiving chamber. A pair of curved leaf springs 146 are arranged within half of the spring receiving chamber.

The arcuate leaf spring 146 disposed in each arcuate chamber is explained below. As shown in Fig. 21, each curved leaf spring 146 consists of an elongated plate with a predetermined width, wherein the elongated plate is bent to an undulated or corrugated shape, which defines a plurality of spring areas arranged side by side in series. Each spring area has an annular area 211 and 212 and a Hebelbe area 213 , all of which are continuous. The outer ring region 211 and the inner ring region 212 are arranged alternately to one another and their ends bil the circumferential opposite opposing de narrow spaces. Each end is connected to the end of the opposite ring area by the lever area 213 . The ring areas 213 diverge from the ring area 211 or 212 to the ring area 212 or 211 . Each ring portion 211 and 212 has such an uneven portion that its thickness gradually decreases from the end to the center, and accordingly has less rigidity than the lever portion 213 . The outer ring region 211 has a larger diameter than the inner ring region 212 . The use of the bent leaf spring 146 enables the axial dimensions of the viscous damping mechanism 109 to be minimized in comparison to a similar arrangement with coil springs.

The spring receiving space is filled with powdery solid lubricant, such as molybdenum disulfide. The powdery solid lubricant is mixed with air and arranged in the spring receiving chamber. In addition, the powdery solid lubricant easily adheres to the surfaces of the walls of the spring receiving chamber, that is, the surfaces of the first drive plate 141 , the second drive plate 142 , the driven element 143 and the bent leaf spring 146 . The powdery solid lubricant lubricates the respective sliding areas. Accordingly, the damper mechanism 109 has a longer service life.

The powdery solid lubricant filled in the damping mechanism 109 has the following characteristics:

• 1) It has a low coefficient of friction and high lubricity.
• 2) It provides good adhesive properties in relation to each of the element (metal element).
• 3) It can get stuck on any element strongly after sticking.
  Since the powdery solid lubricant generally remains on the surfaces of all sliding areas, the lubricating ability can be maintained for a long time.
• 4) It is lightweight and has a high dispersion probability on.
• 5) It has no self-condensation properties.  
• 6) It is heat resistant in a suitable form.
• 7) It is not made of any harmful material.

Fig. 24 shows the characteristics of various solid lubricants, all of which can be used in the present invention. However, according to the characteristics of Fig. 24, molybdenum disulfide appears as the most suitable solid lubricant in view of the good absorption properties and high adhesive strength. Furthermore, molybdenum disulfide can be used under high loads and is also inexpensive. Tungsten disulfide appears to be the second best substance.

The spring receiving chamber can be filled with a fluid, such as grease or a working fluid. In this case, viscosity resistance is created by the expansion and contraction of the plurality of fluid-filled spaces defined by the arcuate leaf springs 146 in the spring receiving chamber.

The driven element 143 is a circular element and has integral engagement areas 143 a, which extend radially outward. The engagement areas 143 a extend through the spring receiving chamber and are each in contact with circumferentially adjacent ends of the paired curved leaf spring 146 . The first and second drive plates 141 and 142 have support areas 141 a and 142 a, which protrude axially and are in contact with the opposite ends of the curved leaf springs 146 extending in the circumferential direction.

The flywheel 102 has the flat friction surface 102 a on the transmission side of its outer peripheral region. The flywheel 102 is also formed with connection openings 102 j, which are positioned radially within the friction surface 102 a and run between the opposite sides. The driven element 143 is fastened to the radial inner end of the flywheel 102 by rivets 160 . The inner peripheral portions of the flywheel 102 and the driven member 143 are supported by an inner projection 141 b of the first drive plate 141 through a bearing 661 . The flywheel 102 is formed on its outer circumferential surface with three engagement regions 102 k ( FIG. 22) which are equally spaced in the circumferential direction and project radially outward. One end of each engagement region 102 k near the motor is inclined to increase the depth as the position moves radially outward.

The clutch cover assembly 103 consists mainly of a clutch cover 621 , a pressure plate 122 , a Mem branfeder 123 , a clutch plate 128 , a pin screw 126 , two wire rings 127 and a conical spring 129th

The clutch cover 621 is a plate-shaped plate element, in the middle of which a large opening is formed, and is formed on its outer circumferential area with circumferentially equally spaced three extensions 162 with a predetermined width, which extend to the flywheel 102 . Each extension 162 is formed at its end with a curved region 163 which is bent radially inwards. Each curved region 163 engages in the engaging region 102 k of the flywheel 102 . Thus, the clutch cover 621 is not movable relative to the flywheel 102 to the gearbox. The extension 162 is formed at its end with a circumferential recess into which a circumferential plate 164 engages. The plate 164 is attached to the outer peripheral surface 102 b of the flywheel 102 by bolts 165 . Due to this construction, the clutch cover 621 is rotationally fixed relative to the flywheel 102 .

The pressure plate 122 is a in the clutch cover 621 arranged annular element. The pressure plate 122 is provided with a pressure surface 122 a opposite the friction surface 102 a of the flywheel 102 . In the Druckplat te b 122 is formed an annular projection 122 which projects to the gear surface and at the surface of the printing 122 a arranged opposite. The pressure plate 122 has a radially inward flange 122 c.

The diaphragm spring 123 is a circular element and is positioned between the clutch cover 621 and the pressure plate 122 . The diaphragm spring 123 has a ring-shaped elastic region 123 a and a plurality of levers 122 b, which extend radially inward from the region 123 a. There are first openings 123 c between, but radially outside of the lever 123 b. Corresponding to the slots, three second openings 123 d are equally spaced in the circumferential direction. The second opening 123 d extends radially inward beyond the first openings 123 c to a position near the flange 122 c of the pressure plate 122 . The annular elastic portion 123 a has a radial inner end, the opposite sides of which are supported by the wire rings 127 , and it also has a radial outer end, which is in contact with the annular projection 122 b of the pressure plate 122 . In this state, the elastic region 123 a biases the pressure plate 621 to the flywheel 102 .

A support arrangement 125 for supporting the diaphragm spring 123 is explained below. The plurality of stud bolts 126 , which are attached to the radial inner end of the bottom of the clutch cover 621 , extend through the first openings 123 c of the diaphragm spring 123 to the pressure plate 122 . The other end of each stud 126 is attached to the clutch plate 128 , which will be described later. Radially outside the stud bolts 126 , the wire rings 127 are arranged between the clutch plate 128 - to be described later - and the diaphragm spring 123 or between the diaphragm spring 123 and the bottom of the clutch cover 621 . Thus, the radial inner region of the elastic region 123 a of the diaphragm spring 123 is clamped between the wire rings 127 arranged in pairs.

The clutch plate 128 is annular and integrally formed on its inner circumference with three coupling areas 128 a, each of which has a long arc shape and extends in the circumferential direction in the direction R1 of FIG. 21. The end of this coupling area 128 a is attached to the flange 122 c of the pressure plate 122 by a rivet. The rivet is arranged at one of the second opening 123 d of the diaphragm spring 123 speaking position. The coupling area 128 a has a high degree of rigidity in the circumferential direction, but is flexible in the axial direction. The coupling area 128 a clamps the pressure plate 122 away from the flywheel 102 .

The conical spring 129 is arranged on the radial outer region of the clutch plate 128 . The radial inner end of the conical spring 129 is supported by the clutch plate 128 . Its radial outer end biases the radially outer end of the diaphragm spring 123, that is the the ring-shaped protrusion 122 b of the pressure plate 122 adjacent region of the pressure plate 122 away.

As described above, the clutch plate 128 couples the clutch cover 621 and the pressure plate 122 to each other and supports the conical spring 129 . Since the clutch plate 128 has a variety of functions as described above, the number of components can be reduced.

The plurality of engagement areas 164 is attached to the pressure plate 122 by fastening pins 165 and they have ends which, together with the annular projection 122 b of the pressure plate 122, hold the radial outer end of the diaphragm spring 123 , which is arranged between them. The extension 162 is configured at the position corresponding to each engagement region 164 with the opening 621c , as shown in FIG. 22.

The clutch disc assembly 104 is essentially formed from the clutch engagement region 131 , which is similar to that described above with reference to the other exemplary embodiments, and from a hub 134 and a plate 166 . The clutch engagement area 131 is arranged between the friction surface 102 a of the flywheel 102 and the pressure surface 122 a of the pressure plate 122 . The hub 134 is splined to the main drive shaft 106 . The plate 166 has an inner peripheral portion which is fixed to the flange of the hub 134 by rivets 119 , as well as an outer peripheral portion which is fixed to the clutch engagement portion 131 by rivets 118 (see Fig. 23). The plate 166 is designed with a plurality of circumferentially equally spaced openings 166 a.

The main drive shaft 106 extending from the transmission has an end carried by the crankshaft 105 by means of a bearing 169 . The release unit 108 is arranged to be axially movable around the main drive shaft 106 . The release unit 108 has an end engaging in the side surfaces, which are opposite the gear from the lever ends 123 b of the diaphragm spring 123 . When the release unit 108 moves to the motor to move the lever 123 b to the motor, the biasing force of the elastic portion 123 a against the pressure plate 122 is released .

Although shown in Fig. 22 bolts 200, the bolts 200 are not used for the actual operation of the modu stellar clutch six hundred and first The bolts 200 are used for fastening and releasing the clutch cover arrangement 103 on and from the flywheel 102 . The bolts 200 run through the openings, which are formed on the radial inner region of the bottom of the clutch cover 621 , the first openings 123 c of the membrane springs 123 and the clutch plate 128 , and are screwed into the pressure plate 122 , as explained below.

The operation of the modular clutch 601 is described below.

When the crankshaft 105 of the engine rotates, torque is transmitted through the flexible plate 107 to the modular clutch 601 . The torque is transmitted to the flywheel 102 through the damping mechanism 109 and is output to the clutch disc assembly 104 . The pressure plate 122 rotates together with the clutch cover 621 , which is coupled to the plate by the clutch plate 128 . As a result, the rotary drive of the Druckplat te 122 is carried out by the clutch plate 128 , which couple the radial inner regions of the pressure plate 122 and the clutch cover 621 with one another, so that no recess for receiving a strip plate on the outer peripheral region of the clutch cover 621 , in contrast to the prior art is required.

Since the inertia member 117 is attached to the first and second drive plates 141 and 142 , a sufficiently high inertia member can be ensured on the power drive and output systems which are separated from each other by the bent leaf springs 146 . Thus, the resonance frequency can be lower than the operating rotation speed of the motor. Since the inertia element 117 is arranged at the radially outer position, the first and second drive plates 141 and 142 , which are elements that define the spring receiving chamber, can have a smaller axial size. As a result, the modular clutch 601 may have a smaller axial dimension overall. Since the inertial element 117 is long in the axial direction, the complete arrangement does not have an increased radial size. As described above, the arrangement of the Träg of the damping mechanism 109 is not increased integral element 117 on the radially outer position, the radial size of the complet th device, since the clutch mounting seat is eliminated from the flywheel 102, and thus, the inertia member may be disposed at a radially inner position 117th

When a bending vibration is transmitted from the crankshaft 105 , the flexible plate 107 bends in the bending direction to absorb the vibration.

When the torsional vibration is transmitted from the engine, the damping mechanism 109 allows periodic relative rotation of the first and second drive plates 141 and 142 relative to the driven member 143 . In this operation, the curved leaf spring 146 is compressed in the circumferential direction and thereby effectively dampens the torsional vibration.

When a driver depresses the clutch pedal, moving an end of the release unit 108, the lever 123 b of the diaphragm spring 123 to the engine. Thus, the radial outer end of the elastic portion 123 a is spaced from the annular projection 122 b of the pressure plate 122 . As a result, the biasing force moves through the coupling area 128 a of the coupling plate 128, the pressure plate 122 from the clutch engagement area 131 of the clutch disc assembly 104 away. Thus, the transmission of torque from the flywheel 102 on the clutch disc assembly 104 is interrupted. In the above releasing operation, the tapered spring 129 applies a gear load to the diaphragm spring 123 so that the releasing load is lowered and provides a flat characteristic curve, thereby reducing the force required to depress the clutch pedal.

The assembly and assembly of the modular coupling 601 07910 00070 552 001000280000000200012000285910779900040 0002019721308 00004 07791e will now be described.

The flywheel 102 and the damping mechanism 109 are fastened together beforehand by rivets 160 . The clutch cover assembly 103 , the clutch cover 621 and the pressure plate 122 are axially fixed to one another by bolts 200 . The bolts 200 maintain the clutch cover 621 and the pressure plate 122 in adjacent positions despite a load application by the membrane feeder 123 . The clutch cover assembly 103 assembled in this way is moved to the flywheel 102 and the extension 162 of the clutch cover 621 is moved through the space between the engagement areas 102 k of the flywheel 102 . In this state, the clutch cover 621 is rotated to engage in the bent region 163 with the engagement region 102 k. Then the bolt 165 and the plate 164 are actuated through the handling opening 117 a to attach the structure to the flywheel 102 , so that the hitch be cover 621 is rotatably attached to the flywheel 102 . The bolts 200 are removed so that the diaphragm spring 123 axially clamps the pressure plate 122 away from the clutch cover 621 . As a result, the bent portion 163 is largely tensioned to the transmission with respect to the engaging portion 102 k.

The modular coupling 601 thus completed is fastened to the flexible plate 107 and the inertia element 117 by the large number of bolts 111 B, which have already been mounted on the crankshaft 105 . The bolts 111 B run through a region of the clutch cover 621 which does not have the extension 162 , the region of the flywheel 102 which does not have the engagement region 102 k and the groove 117 b of the inertia element 117 , and fixes the outer peripheral regions of the first and second Drive plates 141 and 142 on the inertia element 117 . Since the bolt 111 B is fastened from the transmission side in this way, the machinability is improved compared to the prior art.

Corresponding to the modular clutch 601 , the clutch disk arrangement 104 can be used for a longer time, since it uses friction surfaces made of metallic sintered elements, as already explained in the exemplary embodiments. Therefore, the clutch disc assembly 104 need not be replaced. In this case, the useful life is extended until the useful life of the flywheel 102 itself has passed. The bolt 165 and the plate 164 of the present exemplary embodiment can be replaced by rivets or welding, as already described in the other exemplary embodiments.

Since the clutch disc assembly 104 is formed on the plate 166 with the opening 166 a and the flywheel 102 with the connecting opening 102 j, air flows through these openings and thereby cools the clutch engagement area 131 . Since the clutch cover 621 is designed with the opening 621 c, the clutch engagement area 131 is opened radially outward through areas which the extensions 162 do not have. Furthermore, heat of the clutch handle area 131 can escape through the operating opening 117 a. Because of these openings, the clutch handle area 131 can be cooled to a sufficient extent. As a result, disadvantages such as deformation of the plate 166 due to heat generated by the clutch engagement portion 131 can be suppressed.

When the clutch disc arrangement 104 is replaced, the clutch cover 621 is in turn fastened to the pressure plate 122 by the bolts 200 . Then the bolts 165 and the plate 164 are removed and the clutch cover assembly 103 is rotated to release the bent portion 163 from the engaging portion 102 k. As described above, the replacement of clutch plate assembly 104 only requires removal of clutch cover assembly 103 from flywheel 102 and, consequently, only a simple operation.

Ninth embodiment

A modular coupling 701 shown in FIG. 25 has a structure similar to the previous exemplary embodiments. In this modular clutch 701 , the inertia element 117 forms an element of the modular clutch 701 . In particular, the outer peripheral regions of the first and second drive plates 141 and 142 are welded to the inertia element 117 . The modular coupling 701 constructed in this way is fastened to the flexible plate 107 , which is already mounted on the crankshaft 105 . The radial outer region of the flexible plate 107 is fastened to the radial inner region of the inertia element 117 by bolts 111 C. The bolts 111 C are actuated from the motor side and screwed into the inertia element 117 .

According to the modular coupling of the invention, the Friction surface a considerably longer service life have because the clutch disc assembly friction surfaces has, which consists of a metallic sintered element exist, so that there is a high probability that the modular coupling can be used until the useful life of the Flywheel has passed. So there is no exchange Clutch disc arrangement required, which is no Problem arises even if the clutch cover and that Flywheel rotatably fixed to each other by a simple arrangement are attached.

In summary, the present invention relates to a mo dular clutch with a flywheel 2 , a clutch cover assembly 3 and a clutch disc assembly 4 , which form a single module, which in an exemplary embodiment is fastened directly to the engine crankshaft and is mounted on a flexible plate in an alternative embodiment . The modular coupling is designed such that it can be assembled and replaced as a unit. The clutch cover assembly 3 has a clutch cover 21 , a pressure plate 22 and a membrane 23 . The clutch disc assembly 4 has a clutch engagement portion 31 made of a metallic ge sintered element.

Various details of the present invention can be changed without the scope of the invention leave. Furthermore, the foregoing description of the embodiments according to the present Er Invention only intended for explanation and is intended to do not restrict the invention, which is determined by the attached Claims and their equivalents is defined.

Claims (35)

1. Modular coupling designed as a single module for connection to the engine output, with:
a flywheel ( 2 ), which is formed with a friction surface ( 2 a) on one side and can be detachably attached to a torque output element of an engine;
a clutch cover assembly ( 3 ) with a flywheel ( 2 ) attached clutch cover ( 21 ), an inner half of the clutch cover ( 21 ) arranged pressure plate ( 22 ), the pressure plate ( 22 ) having a pressure surface ( 22 a), which is the friction surface ( 2 a) facing, and with a biasing element ( 23 ) which is supported in the hitch be cover ( 21 ) to bias the pressure plate ( 22 ) against the flywheel ( 2 ); and
a clutch disc assembly ( 4 ), which is arranged between the friction surface ( 2 a) and the pressure surface ( 22 a) and has several friction surfaces between the friction surface ( 2 a) and the pressure surface ( 22 a), which consist of a metallic friction material. 2. Modular clutch according to claim 1, characterized in that the clutch cover ( 21 ) with the flywheel ( 2 ) is caulked. 3. Modular clutch according to claim 1, characterized in that the clutch cover ( 21 ) with the flywheel ( 2 ) is welded. 4. Modular clutch according to claim 1, characterized in that the clutch cover ( 21 ) with the flywheel ( 2 ) is riveted. 5. Modular clutch according to one of claims 1 to 4, characterized by a ring gear ( 13 ) which is arranged around the clutch cover ( 21 ), wherein the clutch cover ( 21 ) engages around an outer circumference of the flywheel ( 2 ) and the ring gear ( 13 ) is shrink-fitted on the clutch cover ( 21 ), so that the ring gear ( 13 ) causes a tight engagement of the clutch cover ( 21 ) in the outer circumference of the flywheel ( 2 ). 6. Modular clutch according to one of claims 1 to 5, characterized in that the flywheel comprises a first flywheel ( 102 ) and an inertial element ( 117 ) and a damping mechanism ( 109 ) for torsional vibrations between the first flywheel ( 102 ) and the inertial element ( 117 ) is arranged, wherein the damping mechanism ( 109 ) for torsional vibrations allows a limited relative rotation between the first flywheel ( 102 ) and the inertial element ( 117 ) and dampens vibrations occurring between them. 7. Modular coupling according to claim 6, characterized in that the damping mechanism ( 109 ) for torsional vibrations is formed with a chamber having an elastic element ( 146 ) arranged therein and powdery solid lubricant is arranged within the chamber. 8. Modular coupling according to claim 7, characterized in that the elastic element is a curved undulated leaf spring ( 146 ). 9. Modular coupling according to claim 8, characterized in that the outer peripheral region of the curved leaf spring ( 146 ) touches a peripheral wall of the receiving chamber, so that a friction-generating mechanism is established, which friction between the two elements according to the relative rotation between the first flywheel ( 102 ) and the inertial element ( 117 ). 10. Modular coupling according to one of claims 7 to 9, characterized in that the powdery solid lubricant consists of molybdenum disulfide. 11. Modular coupling according to one of claims 7 to 9, characterized in that the powdery solid lubricant consists of tungsten disulfide. 12. Modular coupling according to one of claims 1 to 11, characterized in that the clutch disc arrangement ( 4 ) has a damping element ( 54 ) which is elastically deformable in the axial direction, and
the friction surfaces are each attached to opposite surfaces of the damping element ( 54 ). 13. Modular coupling according to one of claims 6 to 12, characterized in that the first flywheel ( 2 ) and the pressure plate ( 22 ) consist of cast iron with Cr, V and an added rare earth element. 14. Modular coupling structure, with:
a flywheel ( 2 ) which can be connected to an end face with an engine crankshaft ( 5 ), the end face also having an axially projecting circumferential bulge extending in the circumferential direction and an axial extension increasing along the direction of the radius increase of the flywheel;
a clutch cover assembly ( 3 ) with a clutch cover ( 21 ) which engages around the flywheel ( 2 ) and is positioned axially relative to the flywheel ( 2 ), the clutch cover ( 2 ) having an inwardly bent edge so that the circumferential bulge is clamped , Which comprises holding elements which are attached to the drive end face and wherein the clutch cover ( 21 ) is plate-shaped and has an axially extending over the clutch disc arrangement ( 4 ) circumferential wall and the drive end face has a plurality of circumferentially spaced base areas which correspond to the holding elements, which are formed along the curved edge, each holding element being bent radially inward and aligned with a surface of the base areas and the clutch cover arrangement also having a pressure plate ( 22 ) which is arranged coaxially with the flywheel ( 2 ) and an opposite end face of the flywheel ( 2 ) facing is;
a clutch disc assembly (4) which is coaxial with the pressure plate (22) and the flywheel (2) and disposed therebetween, said friction areas of the lung Kupp cover assembly (4) consist of a sintered metal material; and
Fastening elements for fastening the holding elements of the clutch cover ( 21 ) to the base areas;
wherein an area of the peripheral wall of the clutch cover ( 21 ) is stepped radially inwards and forms a stop which bumps marginally against the opposite end face of the flywheel ( 2 ). 15. Modular coupling according to claim 14, characterized in that the flywheel ( 2 ) and the pressure plate ( 22 ) consist of cast iron with Cr, V and an added rare earth element. 16. Modular coupling structure, with:
a flywheel ( 2 ) with an annular area, which is formed with an outer radial surface, a first axial surface being connectable to a corresponding element of a motor for power driving the clutch and the first axial surface having an axially extending circumferential bulge and a second axial surface of the first Axial surface is arranged opposite;
a clutch cover assembly ( 3 ) with

• a) an annular pressure plate ( 22 ) with an outer radial surface which is arranged coaxially adjacent to the flywheel ( 2 ) and the second axial surface facing;
• b) a pressure element which is attached to the pressure plate ( 22 ) in order to elastically press the pressure plate ( 22 ) to the flywheel ( 2 );
• c) a unitary clutch cover ( 21 ) with an annular wall, which gives the outer radial surfaces of the pressure plate ( 22 ) and the flywheel ( 2 ) around, with a caulking area which extends from the annular wall to caulk with the circumferential bulge be, with a fastening area which extends from the ringför shaped wall and is fastened to the second axial surface, and with a support area which supports the pressure element; and

a clutch disc assembly ( 4 ), which is arranged coaxially between the pressure plate ( 22 ) and the flywheel ( 2 ), wherein friction areas of the clutch plate assembly ( 4 ) are made of sintered metal material. 17. Modular coupling arrangement according to claim 16, characterized in that the flywheel ( 2 ) and the ring-shaped pressure plate ( 22 ) consist of cast iron with Cr, V and an added rare earth element. 18. Modular coupling arrangement according to claim 16 or 17, characterized in that the circumferential bulge is arcuate and that the caulking area ent speaking the circumferential bulge is arcuate. 19. Modular coupling arrangement according to claim 18, characterized in that the circumferential bulge in the axial direction adjacent to the peripheral edge of the flywheel ( 2 ) extends outwards. 20. Modular coupling arrangement according to claim 18, characterized in that the annular wall has a second caulking area, which is caulked with a peripheral edge of the second axial surface of the flywheel ( 2 ), the flywheel ( 2 ) axially between the caulking area and the second caulking area is richly arranged. 21. Modular clutch arrangement according to claim 20, characterized in that the second caulking area of the clutch cover ( 21 ) is stepped radially inwards and abuts against the second axial surface of the flywheel ( 2 ). 22. Modular coupling arrangement according to claim 18, characterized in that the annular wall has a second caulking area, which with a peripheral edge of the second axial surface of the flywheel ( 2 ) is calked, the flywheel axially between the caulking area and the second caulking area is ordered. 23. Modular clutch arrangement according to claim 22, characterized in that the second caulking area of the clutch cover ( 21 ) is stepped radially inwards and abuts against the second axial surface of the flywheel ( 2 ). 24. Modular coupling arrangement according to claim 16, characterized in that the circumferential bulge extends in the axial direction adjacent to an outer radial edge of the flywheel ( 2 ) to the outside. 25. Modular coupling arrangement according to claim 24, characterized in that the annular wall has a second caulking area which is caulked with a peripheral edge of the second axial surface of the flywheel ( 2 ), the flywheel being arranged axially between the caulking area and the second caulking area. 26. Modular clutch arrangement according to claim 25, characterized in that the second caulking area of the clutch cover ( 21 ) is stepped radially inwards and abuts against the second axial surface of the flywheel ( 2 ). 27. Modular coupling arrangement according to claim 16, characterized in that the annular wall has a second caulking area, which with a peripheral edge of the second axial surface of the flywheel ( 2 ) is calked ver, the flywheel axially between the caulking area and the second caulking area is ordered. 28. Modular clutch arrangement according to claim 27, characterized in that the second caulking area of the clutch cover ( 21 ) is stepped radially inwards and abuts against the second end face of the flywheel ( 2 ). 29. Modular coupling arrangement, with:
a flywheel ( 2 ) with an outer radial surface and an axial surface;
an annular pressure plate ( 22 ) having an outer radial surface, the annular pressure plate ( 22 ) being arranged coaxially adjacent to the flywheel ( 2 ) and facing the axial surface of the flywheel ( 2 );
a clutch cover ( 21 ) which engages around the outer radial surfaces of the pressure plate ( 22 ) and the flywheel ( 2 ), a radial inner surface of the clutch cover ( 21 ) touching the outer radial surface of the flywheel ( 2 ) at a contact position;
a ring gear ( 13 ) which is fitted onto the peripheral surface of the clutch cover ( 21 ) radially above the contact position, the ring gear ( 13 ) being shrink-fitted onto the peripheral surface of the clutch cover ( 21 );
a plurality of axially extending slots which are spaced in the circumferential direction on an inner edge of the coupling cover ( 21 ) at the contact position; and
a clutch plate assembly ( 4 ), which is arranged coaxially between the pressure plate ( 22 ) and the flywheel ( 2 ), wherein friction areas of the clutch plate assembly ( 4 ) are formed from a sintered metal material. 30. Modular clutch arrangement according to claim 29, characterized in that a positioning device maintains a rigid relative rotation between the clutch cover ( 21 ) and the flywheel ( 2 ). 31. Modular clutch arrangement according to claim 30, characterized in that the positioning device has a plurality of openings formed in the clutch cover and the flywheel comprises pins inserted therein, the openings in each case around the circumference of the clutch cover ( 21 ) and the flywheel ( 2 ) in alignment with the Contact position are spaced. 32. Modular clutch assembly according to claim 30, characterized in that the positioning device has a stop area which is designed as a radially inward step on the clutch cover ( 21 ), the stop area on the axial surface of the flywheel ( 2 ) at a radial outer position borders. 33. Modular clutch assembly according to claim 32, characterized by a flexible plate which can be fastened to the second axial surface of the flywheel ( 2 ). 34. Modular clutch assembly according to claim 29, characterized in that the flywheel ( 2 ) and the ring-shaped pressure plate ( 22 ) consist of cast iron with Cr, V and an added rare earth element.