KR20000052595A - Torque transfer device - Google Patents

Abstract

PURPOSE: A torque transferring apparatus is provided to accomplish an enhanced axial vibration from a crankshaft with respect an overall available speed range and improved assembly while utilizing components having a low abrasion. CONSTITUTION: A torque transferring apparatus(1) for connecting a crankshaft of an internal engine to an output portion of a driving train, the apparatus comprising a first disk(2) which is axially bendable and connected to a crankshaft(8), and a circular element(4) for forming an output portion and a connection portion and which is connected to a radially outer region, wherein the first disk(2) is supported with respect to the circular element(4) by a second disk(3) having a resilience in axial direction in a friction clutch or a fluid clutch like Fottinger clutch or hydrodynamic clutch.

Description

Torque Transmission Device {TORQUE TRANSFER DEVICE}

The present invention relates to a hydrostatic converter or portinger clutch, comprising a torque transmission device for axially elastically connecting the crankshaft of the internal combustion engine to the output of the drive train, in particular a disk connectable to the crankshaft. The annular component, which is associated with the same fluid clutch or friction clutch, forms an output and a connection here, is connected to the radially outer region.

Torque transmissions of this kind are known and named as flexible flywheels because the design of the first disc is made axially bent so that the axial or bending vibrations of the crankshaft can be partially eliminated.

In order to limit the maximum deflection of axially flexible discs, a device is presented in DE OS 44 02 257, which has an axial middle section between the flexible disc and the contact pressure plate to exceed the axial clearance. The intermediate portion then forms a stop for the contact pressure plate to define the axial path of the disc. After using all of these clearances, the device of the above-mentioned type hardens in the axial direction and transmits vibrations from the crankshaft to the components of the motor vehicle which do not cause any deformation, especially in the high speed region. Without the axial stop, it is not possible to satisfactorily operate the clutch by the axial elasticity causing the separation process. The structure of the axially rigid disk reduces axial braking.

It is an object of the present invention to provide a torque transmission device which improves the axial vibration occurring in the crankshaft over the entire useful speed range of the vehicle. It is also an object of the present invention to make a corresponding torque transfer device that is easy and simple to use and assemble, which can be used during the useful life of the vehicle without wear.

This is achieved by a torque transmission device according to the invention, in particular a friction clutch or a fluid clutch, such as a Pottinger clutch or a hydrostatic converter, which axially drives the crankshaft of the internal combustion engine to the output of the drive train. An elastic connection, comprising at least one first disk, which can be axially bent and connected to the crankshaft and to an annular component that is axially bent or fixed in the radially outer region of the first disk; An output and a connection, wherein the first disk is tensioned by the tongue formed out of the first component or by the second axial elastic disk to the annular component, and between the annular component and the second disk. Frictionally actuated joints are radially resilient metal components It made of means.

For this kind of device it is advantageous if a braking device is formed between the first disk and the annular component to suppress the axial and bending vibrations of the first disk through the elastic friction portion. Thus, the axial deflection of the first disk causes the axial elastic action of the second elastic disk while at the same time the friction component is transferred from the internal combustion engine to the first disk through the crankshaft in the microregion between the annular component and the second disk. It is advantageous to provide very little friction to the contacting portion-ie of the annular component and the second disk-that is tensioned to brake the axial vibrations.

For this purpose the second disk is tensioned by an axial end face having an end of the annular component facing the first flywheel disk. In another embodiment, the second disk may be tensioned by the axial end face having an end of the annular component away from the first flywheel disk.

The second disk is secured to the first disk or annular component, which is advantageously secured to the crankshaft together with the first disk, wherein an additional reinforcement portion is mounted in the axial direction between the crankshaft and the first disk or It can be mounted axially between the crankshaft and the reinforcement part and the second disk can be mounted between the screw head for securing the first disk and the component along the axial direction, where the second disk is simultaneously used as a reinforcement ring. Can be used.

Also according to the invention it is advantageous to mount the second disk on the first disk together with the annular component since the second disk is connected radially outwardly of the crankshaft screw. For this purpose the second disc has a radially inflated tongue which expands in the circumferential direction from the inner circumference to frictionally connect and axially support in the annular component, thus widening the frictional surface of the tongue.

And it is advantageous to design the second disk to be elastic in the axial direction, for example a spring ring or a spring ring distributed along the circumference which is to be joined by a fastening means for the first disk with the annular component in a closed spring ring. Can be. Alternating circumferentially to the first disk and the annular component can make an axial elastic connection between the first disk and the annular component in addition to or independently of the axial elastic properties of the first disk. The annular component can alternately or additionally brake with the first disk in a suitable design and the elasticity of the first disk can be freely formed. The spring ring may be formed to have rigid structure and material properties as a fastening ring. The tongue may be attached as a component separate from the fastening device or as an integral part with the spring ring, wherein the tongue is fastened so that the frictional connection of the annular component and the tongue and the axial tongue are frictionally engaged or pretensioned in the axial direction. The fastening device connects the spring ring to the first disk or annular component.

According to the invention the first and second disks can be connected by forming a tongue disposed in at least one or a plurality of circumferential directions axially out of the first disk axially disposed / frictionally coupled to the annular component, wherein In which the tongue is formed radially outwardly radially inwardly or vice versa.

The axial elastic connection between the first disk and the annular component by the spring ring can be defined by an axial stop in at least one direction. The starting gear ring can be provided radially from the outside for this purpose. Further, when the first disk moves axially with respect to the annular component, an additional frictional coupling is made between the axial connecting device and the outer periphery of the annular component at the outer periphery of the first disk.

According to the invention the spring ring can be integrated into the first disk by providing a splitting point of the disk in the first disk in the region of the fastening device which is the rivet connection, in which the axial elasticity is increased. For example, a separation point may be formed radially inward or outward of the fastening device and the tongue may be formed circumferentially or radially inward or outward and free cut where the fastening device is received to connect the annular components. Tongues formed in the circumferential direction may be aligned in the driving direction or the inertia driving direction.

This kind of device is advantageous not only when setting the axial resilience of the torque transmission device but also to insulate the first disk and the annular component. Especially when the torque transmission device is used in connection with the friction clutch where the annular component is used as the contact pressure or pressure plate, the temperature characteristic of the first component during the useful life of the torque transmission device is too high, For example, it may adversely affect elasticity.

In addition, the cyclic component or the first disk, depending on whether the second disk is fixed to the first disk or to the annular component, is a component that fixes the frictional connection and axially tensions the first disk and the annular component. And frictional connection.

It is advantageous if the second disk has a smaller axial hardness than the first disk.

According to the invention the second disk has a radially outwardly disposed tongue which is disposed along the circumference and is tensioned axially with the annular component, the leaf spring tongue being able to be fixed in frictional connection with the annular component. have.

And a torque transmission device comprising a first disc that can be bent in an axial direction that connects the crankshaft of the internal combustion engine to the output of the drive train and which can be connected to the crankshaft, wherein the annular configuration is connected to the output. The component is mounted in the radially outer region, and the second disc is fixedly received and rotatably attached to the crankshaft and is in frictional connection with the annular component and the element forming the frictional connection is an annular component, which is in the radial direction. It is elastically and frictionally connected to the annular component or the second disk in the circumference.

This element has a radially outward wavy shape and is used as a friction disk between the second disk and the annular component, the peak of the wavy portion at the outer periphery being frictionally connected to the inner circumference of the annular component and the outer of the trough at the inner circumference. It is frictionally connected to the outer circumference of the second disk. Thus, the cross-sectional shape of the wave shape is rectangular, circular, or the like.

In another example a radially elastic disk is provided which is secured to the crankshaft and is in direct frictional connection at the inner and outer circumferences of the annular component.

The torque transmission device is provided as a friction clutch in which the annular component can form a contact pressure plate for the clutch, and torque which can be engaged or separated with the internal combustion engine is transmitted to the gear input shaft via the friction lining and the contact pressure plate. And in another embodiment the annular component is formed as a mass ring in which the hydrostatic converter or portinger clutch is fixedly mounted to prevent rotation.

Advantageously the starting gear ring is mounted to the annular component at the outer circumference and is arranged circumferentially, for example in a cam arranged at least three axial directions. The cam can be formed in the axial direction in the direction of the crankshaft or in the opposite direction, which is advantageous in terms of space if the cam is aligned in the direction of the crankshaft. A cam-shaped recess corresponding to the cam can be provided in the first disk to save axial structural space such that the cam can be connected and move axially up to the internal combustion engine to secure the starting gear ring. In addition, an ignition marking is formed on the outer periphery with a circumferential region in the axial direction spaced from the starting gear ring. This makes an arrangement to save the space in which the first disk is mounted axially between the starting gear ring and the mass part of the annular component, in which the cam is axially in the direction of the crankshaft in the mass part of the annular component. Disposed around the outer circumference of the annular component.

The cross-sectional area may be provided in the circumferential or radial direction to have a positive influence on the axial strength of the disk in order to make the best use of the first disk. For example, a circumferential tab is provided radially between the annular component and the crankshaft, which tab is advantageously formed concave in the axial direction in the direction of the annular component.

For easier assembly, the first disk can be placed in the center of the annular component by the region shaped for ignition marking so that the annular component can be fitted to a radially aligned center cam. The annular component is then connected to the first disk by riveting or press-fitting. The rivet can be provided circumferentially at a radial height in the region of the contact bearing face for the friction lining of the friction clutch.

An axially curved first disk comprises a component of a split flywheel comprising a first flywheel and a second flywheel that can rotate in a direction opposite to the first flywheel with respect to an energy accumulator running in the circumferential direction. It is advantageous to arrange the above-mentioned torque transmission device in the configuration. Here, the disc which can be deflected in the axial direction can be tensioned in the axial direction by a second disc having a smaller axial strength.

The first and second flywheels partially with respect to vibrations from the crankshaft, which are loaded with axial or bending vibrations, through a component that can bend in at least one axial direction as the force travels between the crankshaft and the clutch. It is advantageous to make the first and second flywheels able to be axially bent so that a component part consisting of a rigid part and an elastic part in the composite structure, or which can be axially bent as an integral disk, is formed so as not to be affected. Thus vibration isolation of the flywheel disc of the second part, for example a pressure plate of the friction clutch, is achieved by a disc which can be bent in an axial direction, which disc is in the form of an energy accumulator operating in the circumferential direction. Mounted on the first part which can rotate in opposition to the operation of the disc, the disc which can be bent in the axial direction is constituted by the disc arranged in the circumferential direction.

According to the present invention each axially bendable component or disc is associated with a second disc, the second disc being composed of discs arranged in the circumferential direction and having a lower strength than the first disc having elasticity in the axial direction. Have The second disk is axially tensioned, directly or indirectly, by an axially bendable disk and forms an annular contact support surface which provides frictional torque when the two disks move axially with respect to each other. This torque compensates for some of the flexural or axial vibrations generated by the crankshaft. It is evident that stopping the vibration to brake the axial or bending vibrations of the crankshaft is advantageous for vibrations occurring in the drive train.

According to an advantageous design for tensioning a disc that can be axially bent into a second, lower strength part, the disc can be received as a first disc in the crankshaft and forms a radially outward annular contact support or friction surface. Or in another embodiment an annular contact support or friction surface for the disc that can be axially bent in the axial direction by means of rivets in the radially outward area and for the disc that can be axially bent in the radially inner area. Can be formed.

In the case of a split flywheel, it is advantageous to apply tension to the disc which can be flexed axially with a less rigid disc, where the tension disc is subjected to axial tension between the second and first parts. Therefore, the friction device can be simultaneously displayed in the case where the first and second portions are relatively rotated in the circumferential direction when the axial relative motion is performed. The friction surface is provided on the disc or the rigid part which can be bent in the axial direction and can secure the second disc to the non-friction component on the opposite side. It is also advantageous not to fix the ring so as to be rotatable to either of the two contact supporting surfaces. Here one friction surface is formed in the second part and one friction surface is formed in the first part.

The invention will be described in detail with reference to FIGS. 1 to 8:

1 is a cross-sectional view of an embodiment of a torque transmission device according to the present invention;

2 is a diagram showing the axial size of the first disk according to the speed of the internal combustion engine compared to the prior art;

3 to 13a are sectional views of yet another embodiment of a torque transmission device according to the invention, which will be explained in detail;

14 to 20 are cross-sectional views of an embodiment of a torque transmission device as a divided flywheel.

* Sign Description

1 ... torque transmission device 2 ... first disc

3 ... second disc 4 ... annular component

5 ... reinforcement ring 6 ... opening

7 ... rivet 8 ... crankshaft

9 ... screw 12 ... centering cam

14 ... socket 15 ... bore

16 ... friction surface 17 ... cam

19 ... starting gear ring 20 ... recessed

21 ... collar 22 ... tongue

23 ... tab

1 shows an embodiment of a torque transmission device 1 having a first disk 2, a second disk 3 and an annular component 4.

The torque transmission device 1 is connected to the crankshaft 8 when the reinforcing ring 5 is fitted to the crankshaft in the axial direction, and is engaged with the screw through the opening 6 provided in the 2, 3, and 5 parts ( By means of 9) it is connected with the second disk 3 on the other side of the first disk 2. The reinforcing rings 5, the first and the second discs 2, 3 are fixed together so that the components are integral, in which the rivets 7 alternately in the circumferential direction with the opening 6 It is formed from the reinforcing ring 5 and fixed to the second disk 2 by pressing in the axial direction.

In the radial path of the first disc 2 to the outside to maximize the required axial space, the disc is axially reinforcement in the direction of the crankshaft 8 around the axial extension of the reinforcement ring 5. The radially outward of 5) is formed at a sharp angle and the desired axial wave arrangement is again aligned parallel to the screw plane of the screw 9. In the outer circumferential region, the first disk 2 has a circumferential region 10 away from the crankshaft 8 in the axial direction, so that the first disk 2 is in the form of a port, where a circumferential ignition marking is formed. This is detected by the transmitter (not shown) and passed to the calculator.

Said annular component 4 lies in the center of the first disk 2 by means of a central cam 12 radially mounted inside the axial region 10 and spaced apart in the circumferential direction. The rivets 13 arranged in the circumferential direction can be fixedly connected to the first disk 2 so as to rotate in the axial direction. The annular component 13 has a friction surface frictionally engaged with the clutch disk with conical rivets 13 circumferentially spaced in the radially outer region for securing the annular component with the first disk in the illustrated embodiment. (16) as well as a clutch having threaded bores 15 and sockets 14 for retaining the remaining clutch components.

At least two, preferably four or six, circumferentially spaced cams 17 are formed in the annular component 4 radially outward of the rivet circle 13 and extend axially in the direction of the crankshaft. Each cam has a radially outward contact support surface 18 into which the starting gear ring 19 is fitted. The starting gear ring 19 can be fixed by welding, caulking and shrink-fit. A window-shaped recess 20 coinciding with the cross section of the cam 17 is provided on the disk 2 at the contact surface between the cam 17 and the first disk 2 so that the cam 17 passes and starts up. The gear ring 19 is mounted at the same axial height as the end of the crankshaft or at the same axial height as the collar 21 belonging to the crankshaft 8 so that the axial space required by the torque transmission device 1 is It is possible to improve the operation of the annular component 4 which is reduced and acts as a flywheel.

The second disk 2 is fixed to the first disk 2 and the reinforcing ring 5 to form one structural unit 1 which is mounted and fixed to the crankshaft 8. On the radially outward side, the second disc 3 extends away from the crankshaft to the end of the annular component 4 along the first disc 2 and towards the first disc, tensioning the peripheral region at the end face, ie the second. The disk is formed elastically in the axial direction and has a lower strength than the first disk 2.

On the radially outer side of the screw (9) or rivet (7) the second disk (3) has a tongue or spring tongue (22) which extends radially outward and is distributed about a circumference which tensions the annular component (4). Since the radially outwardly aligned tabs 23 are formed in the annular component 4 at the contact support surface consistent with the shape and number of the tongues 22, the tabs are additional for the tongues 22 in the circumferential direction. Guides may be formed and improve the frictional engagement of the tongues 22 in the annular component 4.

The function of the torque transmission device 1 is that the bending vibration of the crankshaft generated through the ignition process of the cylinder of each internal combustion engine causes the axial vibration of the first disk 2, which is a part of this vibration compared to the rigid flywheel. It does not absorb and transmit this vibration to the clutch or converter to the same extent as a rigid flywheel. Indeed, decreasing the axial strength improves the transmission of this vibration, but where the adjustment takes place too weakly, the clutch separation process is affected.

In the embodiment showing the torque transmission device 1, as a constituent having a smaller strength in the axial direction, the second disk 3 lies parallel to the first disk 2, where one side-first disk 2 is present. The second disk 2, which is firmly fixed at) and tensioned in the axial direction at the other side, is frictionally engaged.

If the first disc 2 moves axially through the bending vibrations of the crankshaft 8, for example with an amplitude of up to 2 mm, preferably 1 mm, this counteracts the torque generated due to the strength of the clutch. Since the deflection in the radial region preset by the screw 9 as a rivet 13 and a fixed point, the second disk 3 is tensioned by an annular component 4 which decreases in the axial direction with respect to its strength, That is, as the axial deflection increases, a smaller contact support surface is subjected to tensions consistent with the axial movement of the first disk 2 and the annular component 4, and in a radial direction with the second disk 3 in an annular configuration. There is friction between the components.

The effect of the braking device thus formed will be explained in more detail with reference to the diagram shown in FIG. 2. Depending on the speed U of the internal combustion engine, vibrations of amplitude A occur in the drive train. An embodiment of the torque transmission device 1 shows the movement 50 as compared to the movement 50 of the flywheel which is adjusted to eliminate this vibration and which does not have a second disk 3 and which can be bent in the axial direction according to the prior art. 2 is shown.

U ₁ ?? 2000 / min to this is the drive train from the engine speed range between U of U ₂ ?? 6000 / min for comparison with the prior art faster than U, for example, occurs at approximately 4000 U / min. The maximum excitation amplitude is the structure (1) reduced by one half compared with the prior art. This oscillating movement has a lower oscillation amplitude than the structure without the second disk 3 in the entire speed band except at the high speed.

3 to 8 show another embodiment of the torque transmission device according to the invention, in which only the upper half of the device that rotates around the axis of rotation is shown in cross section and the embodiment shown in FIG. 1 except for the differences described below for the corresponding figures. Consistent with Example (1), what is described with reference to FIG. 1 can also be applied to the embodiments described below.

FIG. 3 shows an embodiment of the torque transmission device 101 in which the first disk 102 has a circumferential tab 123 to maximize the axial strength of the torque transmission device 101, where the tab 123 is used. Includes a concave portion in the axial direction in the direction of the second disk 103.

The second disc 103 is fixed to the crankshaft 108 in the axial direction between the reinforcing ring 105 and the first disc 102.

The annular component 104 is provided as a clutch pressure plate for holding the clutch and has an end face separated from the crankshaft 108 by the shoulder 124 adjacent the second disk 103 which is frictionally engaged under the action of axial tension. Have on. This tension is generated in the axial direction with respect to the first disk 102 as the contact pressure increases, ie as the deflection of the first disk 102 increases, the frictional engagement with the contact pressure increases. In order to fix a defined frictional surface that is not actuated into the shoulder 124, the second disk 103 is guided axially in an arc form around the shoulder 124 and on an outer circumference which is axially away from the shoulder 124. Formed so as to frictionally engage the annular component 104 through the circumferential contact support surface 125.

4 shows an example of a friction device operating radially in the torque transmission device 201. The second disk 203 is tensioned axially between the annular component 204 and the first disk 202 without securing the disk 203 to the crankshaft. The radially inwardly contacting portion 203 with the shoulder 224 provided in the annular component 204 serves to radially fix the second disk 2 which is a diaphragm or leaf spring having a corresponding axial elasticity. Is formed. This spring is reduced in operation when the first disk is deflected in the axial direction and frictionally engaged at the outer and inner circumferences and the second disk 203 is deflected radially outward by compression when the first disk 202 is deflected. Friction friction.

The second disk 202 is a radially outwardly aligned radially spaced tongue aligned with the corresponding recess of the disk 202 or the annular component 204 and fixed circumferentially or radially in the parts 202 and 204. Other devices may be used to secure the first disk 202 and the second disk 203 to the annular component (not shown) on the outer and inner circumferences.

Fig. 5 shows an example of the torque transmission device 301 in which the second disk 303 is annularly configured by the projections 325 aligned with the indents 324 arranged in the circumferential direction and arranged in the circumferential direction. Is fixed with component 304. It is frictionally coupled in the radial direction at two portions 302 and 304.

6 shows that a disk 403 that is elastically at least in the outer periphery is tensioned from the outer periphery to the inner periphery of the torque transmission device 401 having a corresponding contact support surface 423 of the annular component 404. An Example is shown. In order to make the best use of the friction surface, the disc is pulled radially inward from the outer periphery.

The braking action is caused by the first disk 402 inclined at the screw 409 as the point of rotation. The first disk 402 remains radially in the second disk 403 and is frictionally axially coupled between the annular component 404 and the second disk 403.

The torque transmission device 501 shown in FIG. 7 follows the principle of a torque transmission device 401 located below with a modified structure. For this purpose the reinforcing ring 505 is configured radially outward and axially as the second disk so that a circumferential gap is formed between it and the annular component 504. A corrugated ring 526 having a rectangular cross section fits under a radially applied tension in this gap and is rubbed from the inner circumference of the annular component 504 to the outer corrugated portion 526a and inwardly corrugated at the outer circumference of the reinforcing ring 505. Rubbed into portion 526b. Thus, when the first disk 502 deflects in the axial direction, the radial elastic force on the annular component cancels the deflection through the elastic modulus of the wavy ring 526 and the reinforcement ring 505 of the annular component 504. A braking device is formed that is frictionally coupled in the axial direction through friction.

The shoulder 524 provided in the annular component prevents the wavy ring from escaping in the axial direction and the tab 523 of the first disk acts in the other direction.

The wavy ring 526 of FIG. 7 having a rectangular cross section in FIG. 8 is replaced by the wavy ring 626 having a circular cross section. It is fixed in the axial direction by the circumferential groove 624 provided in the annular component 604.

FIG. 9 is a longitudinal sectional view showing an embodiment of the same torque transmission device 701 as the torque transmission device 1 of FIG. 1 except for the following differences.

The connection of the disk 702 in this embodiment is not made directly at the annular component 704, which may be a pressure plate for the friction clutch, the annular component 702 is fixed at one end and the annular component at the other end. 704 is made through a spring ring or through a circumferentially arranged leaf spring that is firmly attached by, for example, rivets. The axial strength of the spring ring or leaf spring 750 may be adjusted to the axial strength of the disk 702 to further brake the axial and bending vibrations of the crankshaft in the direction of the drive train. In certain applications the disk 702 can be made relatively firm, for example, harder than when compensating axial vibrations for resonance frequencies in the 200-250 Hz region, ie between 600 kg / mm and 2200 kg / mm. Harder than in the region according to the clutch mass, the axial vibration is braked by the axial elastic device 750 as the force travels between the disk 702 and the annular component 704.

The second disk 703 is also tensioned through frictional engagement with the annular component 704 by forming a friction device to form a braking system. The other friction device 751 is a component of the disk 702, such as, for example, an ignition marking ring 711, and a circumference that expands radially from the outer periphery and forms friction torque when the two components 702,704 move relative to each other. It may be provided between the components of the annular component 704, such as a shoulder 752 composed of rings or continuous noses spaced in the direction.

In the torque transmission device according to the invention, such as embodiment 701, the axial stop can be mounted in the outer circumferential region and is at distance x in equilibrium with the two parts 702, 704 formed by the starting gear ring 719. It may be provided between the ignition marking ring 711 spaced apart in the axial direction with respect to each other. This distance x occupies an area of 1 mm or less, preferably 0.3 mm or less.

The connection device 750 through the thermally low heat flow properly shields the disk 702 from the annular component 704, which is capable of varying the temperature of the clutch pressure plate significantly because it is frictionally coupled with the friction lining. have. Advantageously the connecting device is made of a material having low thermal conductivity, such as stainless steel. The combination of low thermal conductivity material with axially flexible material is advantageous.

9A shows a spring ring 750 formed of several, preferably four spring rings 750a and forming a connection between two components 702 and 704 (FIG. 9). This spring ring portion is rigidly connected by riveting or screwing, by the disk 702 and the annular component 704 and the openings 753 and 754 formed circumferentially. Unlike when using leaf springs, the spring ring portion 750 is adjusted in the axial direction so that the axial strength is higher. Another embodiment overlaps with the spring ring portion 750 and the disk 702 and the annular component 704 by a fastening device that engages the openings 753 of the two spring ring portions and is defined by the central opening 754. Overlap with other components.

FIG. 9B shows a spring ring 750b that is closed against the axially deflectable connection of the components 702 and 704 shown in FIG. 9, where the openings 753a and 754a are connected to the annular component 704 by the disk ( Accepts fastening devices 713, 713a alternately positioned relative to the circumference of FIG. 9 to secure 702.

In general, the connecting portion 750 of FIG. 9 has a single- or multi-stage spring ratio-when viewed in the axial direction, for which purpose the spring ring portion 750a and the spring ring 750b are formed between the opings 753 and 754. Have an axial cross section 755, 755a in the circumferential direction, which divides the spring region between two of the openings 753,754 or 753a, 754a into at least two different bending beams.

The torque transmission device 701 of FIG. 9 includes the elastic devices 702 and 750 described above, and adjusts the friction device with a braking system for braking axial vibration suitable for all types of internal combustion engines, drive trains, drives and vehicles. . For this purpose the braking devices can be combined individually or together with a friction device that generates a single or multi-stage, several, for example two different friction torques. In particular, it may be combined with a friction device providing axial and radial friction parts. It is also advantageous to provide a braking device that is preferred for bending vibration and axial vibration, where the bending vibration can be braked by a braking device mounted radially outwardly. Thus, the connecting device 750 of FIG. 9 can brake one type of vibration-bending vibration or axial vibration-and the other type of vibration can be mainly braked by the elastic disk 702 (FIG. 9), so that the glass Do. The maximum possible number of resonances can be increased by introducing one or more braking elements (e.g. spring ring 750) with different spring coefficients (where applicable with at least one friction device, the greater friction action being increased Because of the axial friction path, this can be achieved by using a radial external friction device-this friction device is advantageous). In this way, a torque transmission device suitable for the drive train can brake the resonant maximum value for axial vibrations of 200 to 300 Hz, and can brake the resonant maximum for flexural vibrations in the range of 600 to 800 Hz, and corresponding drive You can better fit the train. It is possible to provide a braking device according to known low pass filters for axial vibration and bending vibration and to brake the respective resonance frequencies.

10 is a cross-sectional view of an embodiment of the torque transmission device 801, where the disk 802 is directly connected to the annular component 804 by a fixing device 813, such as a rivet. Immediately adjacent to the anchoring device 813, the disk has a splitting point 856, which in the example shown is connected to another splitting point 856a in the radially inner side of the fixing device and provided in the form of a circular segment radially outward. do. Part A of FIG. 10 shown in FIG. 10A illustrates cuts of splitting points 856, 856a for fixing device 813 evenly disposed along the entire circumference.

10B-10E illustrate another advantageous structure, in which radial inner splitting points 856a are provided in FIG. 10B and radial outer splitting points 856 in FIG. 10C, and splitting points 856b and 856c in FIGS. 10D and 10E, respectively. 10 radially outwardly 856c in FIG. 10E and radially inwardly 856b in FIG. 10D, radially around the fixing device 813.

An advantage of the torque transmission device 801 having different points of separation 856, 856a, 856b, 856c is that it thermally blocks the two components 802, 804 from each other and gives flexibility in the axial direction, where By cold reshaping technology, it is constructed in the axial direction. Since the torque transmission device 801 does not require a connection device such as 750 in FIG. 9, the torque transmission device 801 can be manufactured cost effectively.

In the structure of the torque transmission device 901-shown in FIG. 11-similar to the torque transmission device 801, the separation point 956 is guided by forming a tongue 986 cut in the circumferential direction, which is a torque transmission device. 901 are arranged in the driving direction or disposed in the axial direction. The fastening device 913 is disposed on the tongue for connecting the annular component and the disk 902.

Part B of FIG. 11 is shown in FIG. 11A. The tongue 986 is here laid axially parallel by the two folded edges 987, 987a and arranged in the driving direction of the torque transmission device 901. All tongues 986 may be aligned in the driving direction. The advantages of the torque transmission device 901 are the same as those of the torque transmission device 801.

Another advantage of the torque transmission device 1001 is shown in FIG. 12, in which a second disk frictionally coupled with an annular component 1004, such as the disk 3 of FIG. 1, is integrally coupled with the connecting device 1050. For this purpose the connecting device, in this case the spring ring 1050, has a radially inwardly extending projection 1003 which is wavy in the axial direction with respect to the annular component 1004 and forms a frictional engagement portion. Tension is applied in the axial direction by the annular component 1004.

12A shows a spring ring including an opening 1053 for receiving a fastening device 1013 for securing a disk 1002 and an opening 1053 for receiving a fastening device for securing an annular component 1004. 1050 is represented. The protrusion 1003 is disposed in the fastening device for fixing the annular component.

The radially inward protrusions extend in the circumferential direction to increase the contact support surface in the annular component 1004.

12A shows a possible structure of the projection 1003 'in the spring ring 1050'. The circumferentially spaced protrusions 1003 ′ are structurally separated from the spring ring 1050 ′ and secured with an anchor for the annular component 1004 or disk 1002 (FIG. 12). This variant is advantageous when the material properties of the protrusion 1003 are different from the properties of the spring ring 1050 '. This is because the spring ring 1050 'must additionally have thermal barrier properties.

13 and 13a show another advantageous variant of the torque transmission device 1101, 1201, which is produced without the second disk (3 in FIG. 1). In this embodiment frictionally engages the annular component 1104 by circumferentially disposed tongues 1103 and 1203 formed out of the disks 1102 and 1202. Tongue 1103 of torque transmission device 1101 (FIG. 13) is radially outwardly aligned and tongue 1203 (FIG. 13A) of torque transmission device 1201 is radially inwardly aligned. Since the tongues 1203 and 1103 are formed in the axial direction, they are in contact with the annular component 1104 by the axial tension, but the strength of the axial tension can be changed.

Figures 14 to 20 show an advantageous embodiment of an axially bendable disc in a split flywheel in which each axially bendable disc is axially tensioned with a second disc of smaller strength. A frictional contact is thus formed at the contact support surfaces of the two disks which brake the axial vibrations when the parts move axially relative to each other. Relative rotation of the two parts occurs with respect to each other so that the friction device is provided in the circumferential direction, wherein the disc which can be axially bent is combined with the first part or the second part and the lower strength second disc is the first part on the one hand. The axial direction is subjected to tension between the components of the component and on the other hand the components of the second part. 14 to 16 show an embodiment having a disc which can be axially bent in the first area and FIGS. 17 to 20 show an axially bendable disc mounted to the second part.

14 is a cross-sectional view of the torque transmission device as the divided flywheel 1301. A first disk 1302 which can be bent in this axial direction is mounted and fixed to the hub 1302a, where the hub is fixed by screws on a crankshaft (not shown). The first disk forms a chamber 1350b radially outward with the flange 1302c which includes an inward biasing device 1302 for the energy accumulator 1350 operating in the circumferential direction. On the radially inner side of the energy accumulator 1350, the disk 1302 is attached to the first disk 1302 by rivets and subjected to axial tension in the inner circumference with the disk 1302. This is a case where the disk 1302 vibrates in the axial direction due to frictional contact in the region 1303a between the disk 1303 and the disk 1302 having a lower strength when the two parts move relative to each other. Can be.

The second disk 1360 is mounted to the hub 1302a by bearings 1361 and rotates against the disk 1302 for operation of the energy accumulator 1350a or energy accumulator 1350 belonging to the second damper stage. Can be. A flange 1370 having a corresponding recess for biasing the energy accumulators 1350, 1350a in the second portion is fixedly connected to the second disk 1360 by means of rivets. The second disk 1360 receives a friction clutch (not shown).

15 shows a disk 1403 as well as a first disk 1402 that can be deflected in the axial direction, a second disk 1460 that can rotate in a direction opposite to the disk 1402 for operation of the energy accumulator 1450. 14 shows a structure of a split flywheel 1401 similar to FIG. 14, wherein the disk 1403 has a reduced strength compared to the strength of the disk 1402 and a bearing dome for the second disk 1460 on the crankshaft. 1460a and in region 1403a having disk 1402 mounted with first disk 1402 and forming a frictional contact that brakes, particularly when the first portion of disk 1402 vibrates in the axial direction. Under tension in the axial direction.

The second disk 1503 is mounted radially inward on the crankshaft (not shown) with the first disk 1502 and is tensioned axially with the energy accumulator 1550 and the disk 1502 radially, with greater strength Although the difference is that the weak disk 1503 is disposed at the center of the disk 1502 by the center nose 1503a, FIG. 16 illustrates an embodiment of a split flywheel 1501 corresponding to the embodiment 1401 of FIG. Indicates. The disk 1503 also has a marking 1503b in the outer periphery area for the engine steering system, which is evaluated by a suitably arranged and designed sensor. The disc 1502 is rebuilt in the axial direction from the outer circumference and has an additional first mass portion 1502a. The divided flywheels 1403 and 1303 of FIGS. 14 and 15 include a reduced first circumference of the circumference, which is not only by the start gear ring but also by the shape of the additional disk 1302c and the disk of FIG. It is formed in the disk 1302.

In the embodiment of the divided flywheel 1601 shown in FIG. 17, the second portion is made to be bent in the axial direction and the second flywheel mass is tensioned against the second disk in the axial direction by the less rigid disk. .

The split flywheel 1601 structure includes a first disk 1602 fixed to the crankshaft, a second disk 1660 fixedly rotatable on a bearing flange 1660a fitted to the first portion, and a rivet. By a second flywheel mass portion 1661 securely coupled to the second disk 1660.

The second disk 1660 and the first disk 1602 are rotatably mounted with respect to the operation of the energy accumulator 1650, which is biased in the first portion by the pocket 1602a and with the corresponding recess 1660c. Biased in the second portion by radially aligned flanges 1660b. Disc 1660 radially between a bearing, for example a sliding bearing 1660d, and a circumferentially arranged rivet 1662 connecting the flange 1660b, the flywheel disk 1662 and the second disk 1660 together. ) Is made axially bendable so that axial or flexural vibrations occurring through the disc 1602 at the crankshaft are blocked in the second area and thus remain away from the clutch, such as a friction clutch.

For this purpose, the disk 1603 having a reduced axial strength compared to the disk 1660 is axially tensioned between the flywheel mass 1662 and the second disk 1660, in the illustrated embodiment the disk. 1603 is supported in a stop shoulder 1661a protruding radially from the inner circumference of the flywheel mass portion 1661 with respect to the second disk 1660 and in the microscopic region when the two parts 1601 and 1660 are in relative motion, Increase the friction torque. The disk 1660 and flywheel mass 1662 act as a friction partner.

FIG. 18 shows the same split flywheel 1701 as the embodiment 1601 of FIG. 17 except for the following differences, which are described in detail below.

The structure of the connection between the flange 1760 and the flywheel mass portion 1701 is different from the flywheel 1601 of FIG. 1. The two parts 1760 and 1701 are radially internally spaced in the circumferential direction by, for example, a rivet 1766 circumferentially spaced from the second disk 1760, and rivets circumferentially spaced from the flywheel mass portion 1701. Joined by 1767 is an axially bendable disk 1765 consisting of disk segments arranged in a plurality of circumferential directions from the outside radially. The second disk 1760 forms an radial flange 1760c integrally with the biasing device 1760c and has an increased strength with respect to the disk 1765 that can bend more axially so that the disk (1) Axial and flexural vibrations occurring through 1702 are blocked in the clutch on disk 1765.

On the radially outer side of the rivet circle 1767, the flywheel disk 1701 is tensioned axially with the flange 1760c and the means for tensioning in the axial direction is the disk 1703, which has a higher strength than the disk 1765 for strength. weak. As shown, the disk is disposed relative to the flange 1760b and is maintained radially inward in the disk 1765 or in the associated rivet 1767. Friction torque may occur between the disk 1765 or flange 1760b on one side and the disk 1703 on the other side. The disk 1765 may be connected radially inward of the fastening portion at the flywheel mass portion 1701 and the second disk 1760.

19 shows an embodiment of a split flywheel 1801 in which the disk 1802 is formed to be axially curved and supported axially with respect to the second portion. For this purpose the disk 1803, for example a leaf spring, is axially tensioned between the second part and the flange 1802, the flange 1802a being tightly coupled with the first disk 1802 by, for example, welding. And a chamber 1850a for fixing the energy accumulator 1850. In the illustrated embodiment the disk 1803 is a direct disk in the first portion of the bearing flange 1802b which in turn is connected to the crankshaft and the first disk 1802, for example by means of rivets 1862 arranged in the circumferential direction. An axial fixation is made between the flywheel mass portion 1861, which is rotatably mounted about 1802, and the flange portion 1861b, which represents the biasing device of the second portion for the energy accumulator 1850. Friction contacts are created in the region 1803a between the flange 1802a and the disk 1803 at the outer periphery of the disk 1803. This frictional contact generates friction torque when the first disk 1802 is axially moved in the axial direction through the axial or bending vibration and when the disk 1802 is relatively rotated with respect to the flywheel mass portion 1861. As known as the friction device of a divided flywheel, it acts as a friction device for axial or bending vibration and torsional vibration. The disc 1801 can be mounted so as to be able to rotate relative to the second part by sliding bearings so as to reduce the basic friction during the relative rotation of the two component parts 1802,1861 when the strength increases in the axial direction. It is advantageous. It is also advantageous to be able to rotate with the play so as to provide a torsion play in the friction device from the friction device initially formed as basic friction.

FIG. 20 shows, in principle, the structure of a split flywheel 1901 similar to the embodiment 1801 in FIG. 19 where the elastic force of the disk 1903 between the flange 1902a and the flywheel disk 1961 is the flywheel mass 1961. Offset by a spring 1931a and a compensation spring 1903a axially supported by the disk 1903. The modulus of elasticity of the two leaf springs 1903 and 1903a is such that a small axial force acts on the contact support surface 1902b and a large axial force acts on the contact support surface 1901b of the two leaf springs 1903 and 1903a. Adjusted. Here, the energy accumulator 1950 during the relative movement of the first part and the second part, that is, the disk 1902 having the flange 1902b on one side and the flywheel mass 1961 having the flange 1961b on the other side. A large friction torque occurs in the case where a small friction torque is generated in the friction region 1902b and the disk 1902 having the flange 1902a vibrates in the axial direction, in contrast to the action of Occurs at 1903b.

The claims submitted in this application present unbiased terms to obtain broad patent protection. Applicant reserves the right to require more than the features described so far in the specification or drawings.

The reference used in the dependent claims that refer to different designs of the subject matter of the independent claim, through the features of each appropriate subclaim, shall not be considered indispensable by obtaining independent subject protection for the features of the dependent claim.

However, the subject matter of the dependent claims also forms an independent invention having a design that is independent of the subject matter of the preceding claims.

The present invention is also not limited to the examples in the specification. Various modifications and changes A combination of individual features or elements or process steps obtained in the drawings allows for new subject matter, manufacturing or testing in the embodiments and new process steps described in connection with the invention in particular variations, elements and combinations or materials and general descriptions. And as far as the working process is concerned, features that can be combined in the order of the process steps are possible within the scope of the invention.

Claims (65)

The crankshaft of the internal combustion engine at the output of the drive train, comprising an axially bendable first disc connectable to the crankshaft, wherein an annular component forming an output and a connection is connected to the radially outer region. In a torque transmission device, in particular a friction clutch or a fluid clutch, such as a Pottinger clutch or a hydrodynamic converter, the first disk is supported against an annular component by a second disk that is elastic in the axial direction. Torque transmission device characterized in that. Torque transmission for connecting the crankshaft of the internal combustion engine to the output of the drive train, comprising a first disc connectable to the crankshaft, wherein an annular component forming an output and a connection is connected to the radially outer region. Apparatus, in particular friction clutches or fluid clutches, such as a Pottinger clutch or a hydrodynamic converter, wherein the annular component is axially bendable to the first disk. In a torque transmission device, in particular a friction clutch, for connecting the crankshaft of an internal combustion engine to the output of the drive train, the disk and the annular components, which form an output and a connection, and which comprise a disc. Torque transmission device, characterized in that the insulation. The torque transmission device as claimed in claim 1, wherein the second disk forms a braking device with an annular component for stopping the axial vibration of the first disk. The torque transmission device of claim 1, wherein the second disk is received with the first disk in a crankshaft. The device of claim 1, wherein the second disk is tensioned by an axial end face having an end face of an annular component towards the first disk. The torque transmission device of claim 1, wherein the second disk is tensioned by an axial end face having an end face of an annular component away from the first disk. The torque transmission device of claim 1, wherein the second disk is secured to the first disk or to the annular component. The torque transmission device of claim 1, wherein the second disk is connected radially outwardly of the crankshaft with the first disk and the annular component. The torque transmission device of claim 1, wherein the second disk is frictionally coupled with the annular component or the first disk. The torque transmission device of claim 1, wherein the second disk has a lower axial strength than the first disk. The torque transmission device of claim 1, wherein the second disk has a radially outwardly aligned tongue that is axially tensioned by the annular component and extends along the circumference. The torque transmission device as claimed in claim 1, wherein the second component is mounted at the connection between the first disk and the annular component. The torque transmission device of claim 1, wherein the second component is mounted axially between the first disk and the annular component. The torque transmission device of claim 1, wherein the second disk comprises radially inwardly facing tongues disposed along the circumference, the tongues being in frictional contact with the annular component or the first disk. The torque transmission device of claim 1, wherein the tongue extends radially inward from one or two sides in the circumferential direction. The torque transmission device of claim 1, wherein the second disk is formed from an energy accumulator that generates an axial spring action. The torque transmission device of claim 1, wherein the energy accumulator is a spring ring. The torque transmission device of claim 1, wherein the second disk is in at least two portions. The torque transmission device of claim 1, wherein the second disk comprises a tongue and a spring ring formed in separate portions. The torque transmission device of claim 1, wherein the spring ring is formed from two spring rings. The torque transmission device as claimed in claim 1, wherein the spring ring is connected to the disk and the annular component with respect to the circumference. The torque transmission device of claim 1, wherein the axial movement of the disk and the annular component is limited. The torque transmission device of claim 1, wherein the axial motion of the energy accumulator axially acting with respect to the axial relative motion of the disk and the annular component is one or multistep. The method of claim 1, wherein the axial movement of the energy accumulator operating in the axial direction is asymmetrical with respect to the axial relative movement of the disc and the annular component in the direction of the crankshaft or in the direction of the output. Torque transmission device. Connecting the crankshaft of the internal combustion engine to the output of the drive train, including an axially bendable disk that can connect with the crankshaft, wherein an annular component forming the output and the connection is connected to the radially outer region. In a torque transmission device, in particular a friction clutch or a fluid clutch, such as a Pottinger clutch or a hydrodynamic converter, at least one radially enlarged tongue is formed out of the disk and supported on the component. Delivery device. The torque transmission device of claim 1, wherein at least one tongue is supported in the axial direction. The torque transmission device of claim 1, wherein the tongue is frictionally coupled with the annular component. The device of claim 1, wherein the annular component and the first disk have a splitting point of at least one first disk portion having a portion immediately connected adjacently and aligned in the circumferential direction by a fastening device disposed in the circumferential direction. Characterized in that the torque transmission device. The torque transmission device of claim 1, wherein the separation point is disposed radially inward or radially outward of the fastening device. The torque transmission device of claim 1, wherein the separation point is made in the form of a tongue and the fastening means is provided on the tongue. The torque transmission device of claim 1, wherein the tongue is aligned in a radial or circumferential direction. The torque transmission device according to any one of the preceding claims, wherein the tongues spaced apart along the circumference aligned in the circumferential direction are uniformly aligned in the inertia driving direction or the driving direction and are properly mixed in the driving direction and the inertia driving direction. . The crankshaft of the internal combustion engine at the output of the drive train, comprising an axially bendable first disc connectable to the crankshaft, wherein an annular component forming an output and a connection is connected to the radially outer region. In torque transmission devices, in particular friction clutches or fluid clutches, such as a Pottinger clutch or hydrodynamic converter, the second disk is fixedly received and rotatably coupled to the annular component in a crankshaft. Torque transmission device characterized in that. The method of claim 1, wherein the frictional engagement between the second disk and the annular component is formed by a wavy ring having a radially outwardly aligned wavy portion as a friction disk and at the outer periphery the wavy portion rubs against the inner circumference of the annular component. And the wavy portion of the inner circumference is frictionally engaged with the outer circumference of the second disk. The torque transmission device according to claim 1, wherein the cross section of the wavy ring is rectangular or circular. The torque transmission device of claim 1, wherein the second disk is radially elastic, mounted to the crankshaft, and directly frictionally coupled to the inner circumference of the annular component by an outer circumference. The torque transmission device of claim 1, wherein the second disk is mounted axially in a crankshaft between the first disk and the reinforcing ring. The torque transmission device according to claim 1, wherein the annular component is a contact pressure plate for the clutch. The torque transmission device as claimed in claim 1, wherein the starting gear ring is received at an outer circumference of the annular component. The torque transmission device of claim 1, wherein the starting gear ring forms an axial stop for the first disk. The torque transmission device of claim 1, wherein the starting gear ring is received in at least three axially aligned cams spaced about the circumference. The torque transmission device according to claim 1, wherein the cam is aligned in the axial direction in the direction of the crankshaft. The torque transmission device of claim 1, wherein the cam is engaged through a corresponding windowed recess of the first disk. The torque transmission device according to any one of the preceding claims, wherein the first disk has a circumferential region in the axial direction on the outer circumference thereof and an ignition marking is formed thereon. The torque transmission device of claim 1, wherein the first disk extends radially outward in the axial direction between the starting gear ring and the mass portion of the annular component. The torque transmission device of claim 1, wherein the first disk comprises a circumferential tab radially between the locator and the annular component on the crankshaft. The torque transmission device of claim 1, wherein the tab is serrated in the axial direction in the direction of the annular component. The torque transmission device of claim 1, wherein the first disk is disposed at the center of the annular component by the forming region. The torque transmission device of claim 1, wherein the annular component is riveted to the first disk. The torque transmission device according to claim 1, wherein the torque transmission device is fixed in a circumferential direction at a radial height in the region of the contact support surface for the friction lining of the friction clutch. The disk according to claim 1, wherein the disc which can be bent in the axial direction has a first flywheel mass part and a second flywheel mass part which can be rotated in opposition to the first flywheel mass part as opposed to an energy accumulator operating in the circumferential direction. Torque component in the axial direction by a second disk having a lower axial strength. The torque transmission device as claimed in claim 1, wherein the disc which can be bent in the axial direction is coupled with the first flywheel mass part or the second flywheel mass part. The torque transmission device of claim 1, wherein the bendable disc is mounted to be axially bent in the crankshaft. The method of claim 1, wherein the axially bendable disk forms a second disk for holding the friction clutch, wherein the first disk is mounted to the crankshaft and the second disk is mounted overlying the at least one energy accumulator. Torque transmission device, characterized in that it can rotate relative to each other in the circumferential direction with respect to the movement of the. The torque transmission device as claimed in claim 1, wherein the axially bendable disk portion is connected with the pressure plate of the friction clutch and the second disk portion. The torque transmission device of claim 1, wherein the second disk portion is mounted to the crankshaft and is tensioned radially outward and axially by the first disk. 2. The method of claim 1, wherein the second disk portion is riveted radially inwardly or radially outwardly by the first disk about the circumference and is axially tensioned by the first disk in the radially opposite direction. Torque transmission device. The torque transmission device of claim 1, wherein the second disk portion is secured to the second disk and is tensioned in the axial direction relative to the first disk portion or the pressure plate. The device of claim 1, wherein the second disk portion is secured to the pressure plate or the first disk portion and is tensioned in the axial direction against the second disk portion or a component coupled thereto. The torque transmission device of claim 1, wherein the component coupled to the second disk portion is an energy accumulator operating in the axial direction. The torque transmission device of claim 1, wherein the second disk portion is rotatable relative to the first disk portion that can be bent in the axial direction. The method of claim 1, wherein the first disk portion, which can be axially bent together with the second disk portion, forms a friction device in the contact support region by axial relative motion and relative rotation with respect to each other. Torque transmission device. The torque transmission device according to any one of the preceding claims, wherein the friction device has a clearance. The present invention, constructed from one or more features described in the application.