JPH11315889A - Device for buffering rotating vibration - Google Patents

Abstract

PROBLEM TO BE SOLVED: To easily, quickly perform an assembling with sure function at a low cost by connecting two preliminarily assembled flywheel mass body units through a connecting member in such a manner as to be axially combinable to each other. SOLUTION: When a flywheel part 4 is rotated to a flywheel part 3 from the resting position, a flange 41 is driven through a fitting connecting part 42. According to this, an inside spring is compressed between circumferential stoppers 65, 66. After the relative rotation by the rotating angle in one rotation direction or in the other rotation direction, the radial area makes contact with the end part of the inside coil spring 48. When both the flywheel parts 3, 4 further additionally relatively rotate at the result, the coil spring 48 is compressed. By the relative rotation by the rotating angle in one rotating direction or the other rotating direction, an outside coil sprint 45 is loaded by a radial arm 44. The coil spring 45 is compressed between circumferential stoppers 55, 55a and the radial arm 44 in the succeeding relative rotation to change the buffering effect.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device manufactured in accordance with a method of manufacturing a device for damping vibration disposed in a power train of a vehicle, for example.

[0002]

SUMMARY OF THE INVENTION It is an object of the present invention to provide a device of this kind which allows a simple, quick, inexpensive and reliable functioning of the device. Another object of the invention is to improve the operation of such a device and to increase its life.

[0003]

The gist of the present invention to solve the above-mentioned problem is to provide at least two fly masses which are supported to be rotatable relative to the buffer means, and one fly mass is provided to the engine. The other flywheel mass can be coupled to the transmission, for example via a clutch, and at least one flywheel mass comprises a chamber at least partially filled with a pasty or viscous medium, wherein: A method of producing a device for damping rotational vibrations, especially in the power train of a vehicle, of the type in which damping means against the relative rotation between the two flywheel masses is accommodated, before the device is balanced, the medium is spread around the chamber. In a device manufactured by rotating at least the flywheel mass with the chamber in order to distribute it as far as possible radially inward level Two preassembled momentum mass unit to assemble a device for damping rotary oscillations is in that they are bondable configured to each other via a mutually combinable and coupling member in the axial direction.

[0004]

The advantage obtained by the present invention is that no state change occurs over the temperature range generated,
When filling the chamber with a paste-like medium which produces as little change in state as possible, that is to say with no significant change in viscosity, a uniform distribution or a uniform filling height over the perimeter is adjusted, and thus the accuracy of the device The balance is made possible.

[0005] In many constructions of the device, it is advantageous if the at least partial filling of the chamber takes place before the flywheel with the chamber has reached the jumping speed, which causes the distribution.

However, it is particularly advantageous if, during the filling of the chamber with the viscous medium, at least the flywheel mass with the chamber rotates at a speed which produces a uniform distribution of the medium over the circumference of the chamber. However, in many applications, it is advantageous when the viscous medium is charged into the room, that at least the flywheel mass provided with the room first bounces off and rotates at a rotational speed below the rotational speed.

[0007] In order to obtain a sufficient distribution of the viscous medium in the room, it is advantageous if the jumping speed is approximately 2 to 15 times the balancing speed. When the present device is used, it is effective that the jumping speed is located at least approximately in the range of the limit speed of the internal combustion engine.

[0008] At the high rotation speed as described above, the air in the free chamber existing between the components is pushed out by the high centrifugal force acting on the viscous medium, so that no air remains in the free chamber. This eliminates the imbalance caused by the later intrusion of air through the viscous medium for a long operating time after the operation of the device. In order to enable accurate balancing and to avoid the occurrence of additional imbalances later, the number of revolutions the device brings before the balancing is generally between 4000 and 7000 rpm. p.
m. Advantageously approximately 5000 to 6000 r.p. p. m.
It is. In that case, it is advantageous if the flywheel mass having at least the chamber is bounced off for 30 seconds to 3 minutes and kept at a rotational speed for a sufficient distribution of the viscous medium in the chamber. The bounce time depends on the viscosity of the medium used and the number of rotations of the bounce.

In order to reduce the splashing time and to obtain a sufficient distribution of the viscous medium in the room, at least the bouncing mass with the room is heated or the viscous medium is heated before being introduced into the room. It is particularly advantageous to heat one or both. According to such heating, the number of spins can be reduced. The target heating temperature of the flywheel mass and / or the viscous medium is 80-250 ° C.

In many embodiments of the present invention, it is advantageous if a viscous medium can be injected or press-fitted into the chamber of the finished mounted fly mass through a closable opening which opens into this chamber. In that case, the complete device is pre-assembled before filling. In another embodiment of the invention, it is also advantageous if the charging of the viscous medium into the chamber and the distribution of the viscous medium within the chamber take place before the assembly or combination of both flywheel masses. Such at least partial filling of the chamber not only simplifies the handling of the flywheel with this chamber, but also charges the viscous medium through the chamber area which is closed off by the combination of both masses. be able to. The advantage of the latter is that no additional filling ports and no closing or sealing means are required. In many applications, it is advantageous if the balancing takes place after the assembly of both flywheel masses forming the device. In that case, the counter rotation speed is 400 to 2000 rpm. p. m. Can be

In another embodiment or embodiment of the device according to the invention, the flywheel mass with the chamber for the viscous medium and the other flywheel mass are separately balanced and then combined into one unit. It is advantageous. Pasty media such as lubricants, greases or the like are suitable as viscous media.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIGS. 1, 2 and 3 show a torque transmitting device for damping a rotational shock, which comprises one flywheel 2 divided into two flywheel parts 3, 4. The flywheel portion 3 is fixed to a crankshaft 5 of an internal combustion engine (not shown) via a fixing screw 6. A switchable friction clutch 7 is fixed to the flywheel portion 4. A clutch plate 9 is provided between the pressure plate 8 of the friction clutch 7 and the flywheel portion 4 and is attached to an input shaft 10 of a transmission (not shown). The pressure plate 8 of the friction clutch 7 is loaded in the direction of the flywheel part 4 by the disc spring 2 pivotably supported on the clutch cover 11. The operation of the friction clutch 7 connects and disconnects the flywheel portion 4 and thus the flywheel 2, that is, the internal combustion engine to the input shaft 10 of the transmission. A first radially outer damper 13 between the flywheel portion 3 and the flywheel portion 4;
A second radially inner bumper 1 connected in parallel to this
4 are provided, both of which allow relative rotation between the two flywheel parts.

The two flywheel parts 3, 4 are mounted via bearings 15 so that they can rotate relative to one another. Bearing 15
Consists of a rolling bearing in the form of a single row ball bearing. The outer ring 17 of the ball bearing 16 is inserted into the notch 18 of the flywheel portion 4,
The inner ring 19 is disposed on a cylindrical shaft portion 20 at the center of the flywheel portion 3, which extends in the axial direction in a direction away from the crankshaft 5.

The inner ring 19 is fixed on the shaft by a press fit, and is provided between a shoulder 21 or a flywheel portion 3 of the shaft 20 and a safety plate 22 fixed to an end face of the shaft 20 by a rivet 22a. Has been tightened.

As can be seen in particular from FIG. 2, the ball bearing 14 is axially arranged via two rings 23, 24 of L-shaped cross section, a shoulder 25 of the flywheel part 4 and a second flywheel part via rivets 26. Ring plate 2 fixedly connected to 4
7 is tightened.

The radially inward legs 23a, 24a of the rings 23, 24 extend partially in the radial direction over the inner race 19 and are axially supported by the inner race 19, whereby the ball bearing 16 It is also useful as packing. In order to ensure a sufficient sealing of the ball bearing 16, the radially extending legs 23a, 24a are axially pressed against the end face of the inner race 19 by means of energy storage elements in the form of disc springs 28, 29, respectively.

A packing ring 37 is provided between the inner ring 19 and a step portion 20a provided on the shaft portion 20 of the flywheel portion 3, and is housed in a radial annular groove 37a provided on the step portion 20a. Have been.

As can be seen from FIG. 1, the flywheel part 3 forms a casing which defines an annular chamber 30 in which the dampers 13, 14 are housed. The flywheel part 3 with the annular chamber 30 consists essentially of two casing parts 31,32. The casing parts 31, 32 defining the annular chamber 30 are formed from a casting. The casing portion 32 is provided with an axially cylindrical additional portion 32a around the casing portion 32, and the casing portion 32 is connected to the outer peripheral surface 34 of the casing portion 31 via the inner peripheral surface 35 thereof.
Is positioned on top. The axial fixing of the casing parts 31, 32 takes place via radial pins 38, which are arranged in the region of the outer peripheral surface 34 and the inner peripheral surface 35. The casing part 32 bears on its shoulder 39 a starting crown 40, which partially covers the pin 38 in the axial direction, so that the pin 38 cannot move radially. In order to seal the annular chamber 30 to the outside, a packing ring 3 is provided in the area between the pin 38 and the chamber 30.
6 are arranged.

The two dampers 13, 14 have one common output in the form of a radial flange 41, which is located axially between the two casing parts 31, 32. As can be seen from FIG.
Its radially inner region is non-rotatably connected to the ring plate 27 via an axial fitting connection 42, which ring plate 27 is directed towards the crankshaft 5 and has an additional part of the flywheel part 4. It is fixed to the end face via a rivet 26.

The flange 41 is provided on its outer circumference with a radial arm 44, which on the outside forms a load area for a power storage element in the form of a coil spring 45 of the damper 13. In the radial direction inside the notch 46 for the coil spring 45, which is present between the arms 44 in the circumferential direction, the arm 4
4 has a curved window 47 in which a power storage member in the form of a coil spring 48 of the damper 14 inside is accommodated. Between the notch 46 and the window 47 in the radial direction, the flange 41 forms a circumferentially extending web 49, which is present in the radial arm 44 or in the radial direction of the flange 41 between the windows 47 in the circumferential direction. Area 50 of
Are connected to each other. The radial area 50 forms the load area of the flange 41 for the coil spring 48.

The annular chamber 30 has a radially outwardly extending annular passage-like or torus-like receptacle 51 in which the arm 44 of the flange 41 engages radially.

The annular channel-shaped receiving part 51 for the coil spring 45 is generally formed by axially extending recesses 52, 53 extending circumferentially, which recesses of the casing parts 31, 32. The coil spring 45 is formed in the radial direction, and the area of the coil spring 45 projecting on both sides of the flange 41 protrudes in the axial direction.
The receiving portion 51 is provided with the web 4 of the flange 41 inward in the radial direction.
By 9, apart from the slight gap 54, it is closed.

As can be seen from FIG. 1, the recess 5 in the axial direction
The cross-sections of 2 and 53 are formed such that their curved extension fits at least approximately around the cross-section of coil spring 45. Therefore, the recessed portions 52 and 53 form a support area or a guide area for the coil spring 45, and the coil spring 45 is supported in this area. Recessed part 5
The support area formed by the coil spring 45
The wear due to friction between the limiting surfaces of the recesses 52 and 53 and the wire of the coil spring 45 is significantly reduced. This is because the supporting surface between the coil spring 45 and the concave portion increases.

In order to prevent or reduce wear in the radial support area of the annular passage-shaped receiving part 51 for the coil spring 45, a steel band 81 of high hardness is arranged, which is provided on the receiving part 51. It extends around the circumference and surrounds the coil spring 45. The steel band 81 is formed in a cylindrical shape and has a notch 82.
The notch is formed by a radial cut or a radial recess. When the device 1 rotates, the coil spring 45 is supported by the steel band 81 via its wire loop based on the centrifugal force acting on the coil spring 45.

Due to the load of the coil spring 45, the arm 4
4 are provided with circumferential stoppers 5 in the recesses 52 and 53, respectively.
5, 55a are provided, which in the circumferential direction form a support area for the coil spring 45. The circumferential stoppers 55 and 55a are formed by components suitable for the recesses 52 and 53, for example, cast products or press-formed products.
It is fixedly connected to the casing parts 31, 32 via integrally formed rivets 58. End portions of the circumferential stoppers 55 and 55a viewed in the circumferential direction are provided with flat portions so as to generate a favorable load on the coil spring 45.

As can be seen from FIG. 3, the circumferential stoppers 55, 55a disposed on both sides of the arm 44 of the flange 41 are provided.
Is longer in the circumferential direction than the arm 44, and in the illustrated embodiment the arm 44 is centrally located with respect to the circumferential stops 55, 55a in the rest position shown in FIG. The circumferential stoppers 55 and 55a are connected to the arm 44.
Project the same amount on both sides.

The casing parts 31, 32 are provided radially inward of the receiving part 51 with regions 60, 61 forming annular surfaces facing each other, between these regions the annular shape for the flange 41. A passage 62 is formed.

In the embodiment shown in FIGS. 1 and 3, the width of this annular passage 62 is slightly larger than the area of the flange 41 which is accommodated in the passage, and therefore a gap 54 is provided on at least one side of the flange 41. Has occurred.

The casing parts 31, 32 are provided with recesses 63, 64 in the axial direction radially inward of the annular passage 62, into which the inner coil projecting on both sides of the flange 41. The area of the spring 48 at least partially protrudes.

As can be seen from FIG. 1, the recess 6 in the axial direction
The cross section of 3, 64 is adapted around the cross section of the coil spring 48, at least in the region where its arcuate extension is at least radially outward, so that the coil spring 48 is at least axially concave. 64 are held or guided.

Like the outer recesses 52, 53, the inner recesses 63, 64 extend over the entire circumference of the device. This is for example the precast recesses 52, 53 and 63, 6
Advantageously, 4 can be machined by a rotating operation. Due to the load of the coil spring 48, the recesses 63, 6
4 are provided with circumferential stoppers 65 and 66, and the circumferential stoppers 65 and 66 are
5, 55a and are likewise riveted to the casing parts 31, 32. Circumferential stops 65, 66 arranged on both sides of the radial area 50 of the flange 41 serve to load the coil spring 48 in the area 5.
It has a greater extension in the circumferential direction than 0. The arrangement of the circumferential stops 65, 66 relative to the radial region 50 projects on one side with respect to the region 50 in the rest position of the device 1,
The other side is made to coincide with the radial area 50. Further, the displacement of the circumferential stoppers 65, 66 associated with the radial region 50 is such that the circumferential stoppers 65, 66 disposed one after the other in the circumferential direction are opposite to each other, and the circumferential stopper 65 , 66 so as to be shifted with respect to the radial region 50 opposite to the radial region 50. With this configuration, the inner coil spring 48 forms two coil springs 48a and 48b that act stepwise.

The web 49 of the flange 41 is designed in relation to the inner recesses 63, 64 such that the coil spring 48 is supported on the web 49 at least radially under the action of centrifugal force.

This is advantageous because the flange 41 is at least made of hardened steel, so that the wear of the support for the coil spring 48 is reduced.

As can be seen from FIG. 3, a spring receiver 59 is arranged between the arm 44 or the circumferential stoppers 55, 55a and the end of the coil spring 45 facing the arm 44 or the circumferential stoppers 55, 55a. It is adapted to the cross section of the receptacle 51 in the shape of a circle.

The spring receiver 59 has a slightly tapered projection 59.
a, which protrudes axially into the coil spring 45. The end of the projection 59a is formed in a conical shape in the illustrated embodiment, but may be formed in a spherical shape.
With such a configuration of the spring receiver 59, as long as the spring receiver slides out of the spring end during operation, the spring receiver is automatically inserted into the coil spring when the spring receiver is reloaded or the spring is unloaded, Therefore, the coil spring or the spring support is not damaged. When the outer coil spring 45 is compressed and the device 1 rotates at a relatively high speed, the spring receiver 59 slides out. In this operating state, the friction existing between the coil of the coil spring 45 and the radial support areas of the housing parts 31, 32 for this coil spring increases, so that the coil spring 45 experiences a sudden load alternation impact. Sometimes it is not possible to at least completely reduce the load. Due to the compression of the viscous medium redistributed outward under the action of centrifugal force by the radial arm 44 during the load alternation impact,
The spring receiver 59 receives pressure from the end of the coil spring 45 which is not lightened.

A viscous or lubricating medium, such as grease, is present in the annular chamber 30. The level of the viscous or lubricating medium reaches at least up to the central region or the axis of the coil spring 45 outside the damper 13 when the device 1 is rotating. In the embodiment shown, it is advantageous if this level extends at least to the area outside the loop of the inner coil spring 48, so that at least this loop and the area supporting it radially, In this case, lubrication is generated between the flange 41 and the web 49 to reduce wear. In the embodiment shown, it is advantageous if the viscous or lubricating medium is filled up to the axis of the inner coil spring 48.

The annular chamber 30 containing the viscous or lubricating medium is arranged in the flywheel part 3 coupled to the engine and spatially separated from the flywheel part 4 supporting the wear clutch, so that the friction clutch The effect of the heat generated in the context of viscous or lubricating media is largely eliminated.

In addition, between the annular chamber 30 or casing part 32 and the flywheel part 4 there is provided an outwardly open annular passage or annular gap 68 which, in the context of a ventilation passage 69, provides cooling. Improve the action further. The ventilation passage 69 is provided radially inside the friction surface 4 a of the flywheel portion 4 for the clutch plate 9.

As can be seen in particular from FIG. 3, the flange 41 is provided with a central notch 71, the contour of which forms a radially shaped part 72, which engages with the opposite shaped part 73. The opposed molded portion is provided on the outer peripheral portion of the annular plate portion 27 connected to the flywheel portion 4. By means of the shaping part 72 and the opposing shaping part 73 forming the axial mating connection 42, the flange 41 is perfectly positioned between the two casing parts 31, 32, so that
The gap 54 present between the annular passage 62 and the flange 41 can be made very small. In addition, the mating connection makes it possible to increase the axial tolerance between the different contact or support surfaces of the component.

As can be seen in particular from FIG. 2, a seal 74 is provided between the radially inner region of the casing part 32 and the annular plate 27 or the axial addition 43 of the flywheel part 4 for sealing the annular chamber 30. Is arranged. The packing 74 comprises an axially resilient annular plate 75 which, in its radially inner region, is supported by an annular component 76 fixed to the axial addition 43 and has a radial It is axially fixed to a radially inner region of the casing part 32 in a region outside in the direction. The axially deformable plate 75, like a disc spring, has in its radially outer and inner regions a coating 75a, 75b, such as a plastic coating, which is applied, for example, by spraying. The coatings 75a, 75b must have a small coefficient of friction and some elastic or plastic deformability. The radially outer edge area of the plate 75 is tightly crimped in an annular support 80. This caulking of the area outside the plate 75 is performed so that the plate 75 can complete the conical deformation. A region 80b of the support 80 surrounding the outer periphery of the plate 75 is accommodated in an axial recess 77 formed in a region radially inside the casing part. For axial fixation of the outer region of the plate 75, the annular support 80 is provided with a bend region 80a which radially grips the inner edge 32a of the casing part 32. The annular support 80 forms an annular swivel support for the plate 75 which can be deformed in the form of a disc spring.

An annular component 76 with a sealing surface cooperating with the plate 75 is provided with a radially inner plate-like plate fastened axially between the end face of the axial addition 43 and the ring plate 27. An area 76a and an annular outer area 76b are provided, and the plate 75 is in close contact with the area 76b by preloading in the axial direction.

The radially outer region 76b of the annular component 76 is axially relative to the radially inner region 76a,
It is pulled in from the ring plate 27 provided with the opposed forming portion 73 of the fitting connection portion 42. As can be seen from FIG. 2, the packing 74 seals the annular chamber 30 towards the annular gap 68 present between the two flywheel sections 3,4.

The inner diameter of the plate 75 is larger than the outer diameter of the radial projections or the opposing molding 73 in order to enable the axial fit of the two flywheel parts 3, 4. The annular component 7 supporting the plate 75 in the axial direction
The region 76b of the sixth region extends further outward in the radial direction than the opposed molded portion 73.

The mating connection 42 and the packing 74 enable a particularly simple assembly of the torque transmitting device 1. That is, first, both flywheel parts 3,
4 is pre-assembled, and then a safety plate 2
The two are axially connected to one another by being fitted and fixed in the axial direction. For this, first the packing 74 is pre-assembled in the flywheel part 3 and the ball bearing 16
Is fitted to the flywheel portion 4. When the two flywheel portions 3 and 4 are assembled, the inner race 19 is pressed into the step portion 20 a of the shaft portion 20 in the axial direction of the casing portion 31, and the opposed molded portion 73 is engaged with the molded portion 72. Furthermore, when the two flywheel parts 3, 4 are fitted, the coating 75b of the radially inner area of the plate 75 abuts against the opposing sealing surface of the radially outer area 76b of the component part 76, so that the plate 75 is And makes contact with the region 76b by preloading. The final axial fixation of the two flywheel parts 3, 4 to one another is achieved by fixing the safety plate 22 to the shaft 20, as already described.

Next, the operation of the device of the present invention will be described with reference to FIGS.

When the flywheel part 4 rotates relative to the flywheel part 3 from the rest position shown in FIG. 3, the flange 41 is driven via the mating connection 42, whereby the inner spring 48b is first displaced by the circumferential stop 65. , 66 are compressed. After relatively rotating by a rotation angle 79, 80 in one rotation direction or the other rotation direction, the radial region 50 abuts the end of the inner coil spring 48, and as a result, In addition, the coil spring 48a is compressed as the two flywheel parts 3, 4 rotate further relative to each other. When relatively rotated by the rotation angles 79a and 90a in one rotation direction or the other rotation direction, the outer coil spring 45
Therefore, during a subsequent relative rotation, the coil spring is compressed between the circumferential stops 55, 55a and the radial arm 44. In the embodiment shown, the rotation angle 79 corresponds to the rotation angle 79a and the rotation angle 90 corresponds to the rotation angle 90a, so that the coil springs 48a and 45 act simultaneously. This results in a two-stage spring characteristic curve in the embodiment shown in FIGS.
However, the rotation angles 79, 90, 79a, 90a can have only partially the same value or can have different values. Therefore, at least three spring characteristic curves are possible in both rotational directions, or at least two spring characteristic curves in one rotational direction and at least three spring characteristic curves in the other rotational direction. is there.

As indicated by the dashed line in FIG. 3, the circumferential stoppers 65 and 66 can be further retracted to the spring ends of the coil spring 48 which are held down in the flange 41. In this case, A spring force does not occur over a predetermined angle around the zero position of the relative movement between the two flywheel parts 3, 4 and, if necessary, only hydraulic or viscous and / or frictional damping. Only occurs.

In the illustrated embodiment, the coil springs 48a, 48
The common compression of b, 45 takes place until at least the inner coil spring 48a has been compressed to the sealing height, thereby limiting the relative rotation between the two flywheel parts 3,4. When the two flywheel parts 3 and 4 rotate relative to each other, the recess 5
Friction buffering occurs due to the friction of the outer coil spring 45 on the surfaces 2 and 53 or the steel band 81 and the friction of the plate 75 in the region 76b. Radial inner coil spring 4
8 and its radial support area also provide friction damping. The frictional damping that occurs between the coil spring 45 and the radial support region depends on the rotational speed, and the buffering effect increases as the rotational speed increases. Further, a buffering action is generated by the disturbance or pressure of the viscous medium or the paste-like medium existing in the annular chamber 30. In particular, the viscous medium which is present in the closed annular channel-shaped receiving part 51 causes hydraulic or viscous damping. This is because the spring receiver 59 in the annular passage-shaped receiving portion acts like a piston. When the outer coil spring 45 is compressed, the spring receiver 59 loaded by the arm 44 moves toward the spring receiver abutting the circumferential stoppers 55, 55a, whereby the viscous medium present in the coil spring is mainly restricted. Is extruded through a gap 54 similar to.
The other part of the viscous medium is compressed between the spring receiver 59 and the annular passage-shaped receiving part 51. The viscous medium initially displaced inward is once again distributed uniformly around the circumference by the centrifugal force acting on it. When the load on the outer coil spring 45 is reduced, the viscous medium present on the opposite side of the spring receiver 59 from the spring 45 is likewise compressed at the spring receiver and pushed away through the gap 54, and the centrifugal force acting on it Again fills the coil spring. The buffer created by a viscous medium depends on the centrifugal force acting on the viscous medium. In other words, the buffering action increases as the rotational speed increases.

The area of the radially inner coil spring 48 which is immersed in the viscous medium likewise produces a viscous or hydraulic damping action by disturbance.

By providing an axial cutout in at least one spring receiver and by appropriately designing the gap 54 or the outer periphery of the spring receiver, the damping effect produced by the viscous medium can be changed, or in each case, It can be adapted to the conditions of use. In addition, by providing only a few coil springs 45 with spring supports, viscous or hydraulic damping can be adapted. A spring receiver may be provided between the spring end of at least one inner coil spring 48 and the radial region 50 of the flange 44.

In particular, as can be seen from FIG.
The component member 3a has a radial arm 86 on the outer periphery thereof, and each of the arms has a screw hole for fixing the friction clutch 7. Some arms 8
6 is provided with holes for receiving pins, which ensure accurate positioning of the clutch cover on the component 3a during assembly.

The radial arms 86 enable a simple construction of the flywheel part 3. In addition, the indentation 86a between the radial arms 86 allows the component 3
a, and thus the cooling effect of the clutch attached thereto is improved. Because the clutch cover and the dent 86
This is because air circulation occurs between the air circulation system and a.

Furthermore, due to the presence of the radial arm 86, the component 3a is formed relatively thick in the area of the friction surface 4a with a given mass, so that overheating in this area is avoided.

The change in the damping effect caused by the viscous medium is such that the annular channel-shaped receiving part 51 does not have a constant cross section over at least a part of the length of the at least one coil spring, so that the cross section is large. A small buffering effect occurs in the region and a large buffering effect occurs in the region having a small cross section. This cross section change of the receiving portion 51 can be provided at an arbitrary position or at a plurality of positions, but it is particularly effective to provide such a cross section change portion or a cross section enlargement portion at the end of the coil spring 45 which is not compressed. It is. In that case, the cross-sectional change may be abrupt or progressive. In that case, the cross-sectional enlargement is advantageously provided in the radially inner half area of the receiving part 51. Such a cross-sectional enlargement is indicated by reference numeral 89 in FIG. The enlarged cross section 89 is formed by the flange 41.
The flange 41 is formed integrally with the receiving portion 51.
Are restricted or closed radially inward. However, the enlarged cross section 89 can also be obtained by suitable shaping of the recesses 52, 53 limiting the receiving part 51.

The charging of the viscous medium into the chamber 30 can take place before the two flywheel parts 3, 4 are assembled or fitted. Such at least partial filling of the chamber 30 is possible by charging a viscous medium through the area of the chamber 30, which is closed by the fitting of both flywheel parts 3,4.

In the embodiment shown in FIGS. 1, 2 and 3, this region is between the plate 75 and the shaft 20.

The chamber 3 is provided by a viscous medium, which can consist of a pasty medium such as a lubricant, grease or the like.
To fill the zero, the flywheel parts 3, 4 are rotated to a speed at which the centrifugal force acting on the viscous medium can distribute it evenly over the circumference. According to such a method, a paste-like medium with as little or as little a state change as possible over the temperature range in which it occurs, that is to say at least a medium with no significant change in viscosity, is used.
Filling in the zero results in a uniform distribution or a uniform filling height over the circumference of the chamber 30, so that a very precise balancing of the device 1 to be performed subsequently is possible.

The number of revolutions is 4000 to 700.
0r. p. m. , Preferably approximately 5000 to 6000
r. p. m. It is. The flywheel part 3 with the chamber can be balanced before assembly with the other flywheel part 4. In that case, the other flywheel part 4 is likewise balanced by itself, so that after the fitting of both flywheel parts 3, 4 the device 1 is balanced. It is also effective to balance after both flywheel parts have been assembled.

The splashing speed which produces a sufficient distribution of the viscous medium in the room is approximately 4000 to 7000 rpm.
p. m. , Preferably 5000 to 6000 r. p.
m. It is. The bounce time is between 30 seconds and 3 minutes, preferably around 1 minute. If the bounce mass or the viscous medium is heated before being filled into the room, the number of revolutions and the time of the splash can be reduced. Such heating improves the distribution of the viscous medium in the chamber 30.

The balance of the flywheel parts 3, 4 or the entire device 1 is 400 to 2000 rpm. p. m. May be performed at the number of rotations.

In the apparatus 101 of the embodiment shown in FIG. 4, at least one hole 191 is provided in the side wall 103a of the flywheel portion 103 facing the engine, through which a viscous medium such as grease is introduced into the chamber 130. Can be charged. After charging the viscous medium, the hole 191 is closed by the sealing plug 92. The seal plug 192 is pressed into the hole 191. In the embodiment shown in FIG.
93, and a packing ring 194 is accommodated in the groove 193.
1 is sealed. Cover 132 that restricts the chamber 130
Is formed by a sheet metal part, which is fixed to the end face of the axial projection 131 by a rivet coupling member 138. A packing 136 is disposed radially inside the rivet coupling member 138 to prevent the viscous medium from flowing out of the chamber 130 due to centrifugal force.

A disc spring-shaped packing member 1 is provided between a radially inner region of the cover 132 and a shoulder of the flywheel portion 104.
75 is tensioned in the axial direction, and the packing member seals the inside of the chamber 130 to the outside.

The two flywheel sections 103, 104 are rotatably supported by rolling bearings 116. Reference numeral 174 denotes a disc spring.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of one embodiment of the present invention.

FIG. 2 is an enlarged view of a portion indicated by reference numeral X in FIG.

FIG. 3 is a diagram showing the clutch removed from FIG. 1 and viewed from the direction of arrow II.

FIG. 4 is a partial sectional view of another embodiment of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Torque transmission device, 2 flywheel, 3, 4 flywheel part, 3a component, 4a friction surface, 5
Crankshaft, 6 fixing screw, 7 friction clutch,
8 pressure plate, 9 clutch plate, 10 input shaft, 1
1 clutch cover, 12 disc springs, 13, 14
Dampers, 15 bearings, 16 ball bearings, 17
Outer ring, 18 Notch, 19 Inner ring, 20 Shaft,
20a step, 21 shoulder, 22 safety plate, 22a
Rivets, 23, 24 rings, 23a, 24a
Legs, 25 shoulders, 26 rivets, 27 ring plates, 28, 29 disc springs, 30 rooms, 31, 32
Casing part, 32a additional part, 32b rim,
34 outer peripheral surface, 35 inner peripheral surface, 38 pins, 4
0 starting crown, 41 flange, 42 mating connection, 44 arm, 45 coil spring, 46
Notch, 47 window, 48, 48a, 48b coil spring, 49 web, 50 area, 51 receiving part,
52, 53 recessed portion, 54 gap, 55, 55a
Circumferential stopper, 58 rivet, 59 spring receiver, 59a projection, 60, 61 area, 62 passage, 63, 64 recess, 65, 66 Circumferential stopper, 68 annular gap, 69 ventilation passage, 71
Notch, 72 molded part, 73 Opposite molded part, 74
Packing, 75 plates, 75a, 75b coating, 7
6 components, 76a, 76b area, 80 support, 80a, 80b area, 81 steel band, 82 notch, 86 arm, 86a dent, 89 cross section enlarged part

Claims (67)

[Claims] 1. A device for damping rotational vibrations in a drive shaft system of a vehicle, comprising at least two flywheel masses which are supported against each other via a rolling bearing device against one of the damping means. A flywheel mass can be connected to the internal combustion engine, and the other flywheel mass can be connected to the transmission via a clutch such as a friction clutch;
And at least one fly mass has a chamber at least partially filled with a viscous or pasty medium and sealed to the outside via at least one sealing device, wherein both chambers are provided. In the type having a built-in damper that resists relative rotation between the fly masses, two pre-assembled fly mass units are provided for assembling the device (1; 101) for damping rotational vibration. , Characterized in that it is configured to be capable of being combined with each other in the axial direction and capable of being connected to each other via a connecting member,
A device that dampens rotational vibration. 2. One of the two flywheel mass units (3; 1).
03) wherein a sealing member is fixed in position, said sealing member being in contact with a corresponding sealing surface provided on the other flywheel mass unit after combination of the two flywheel mass units. An apparatus according to claim 1. 3. The rolling mass bearing unit according to claim 1, wherein the rolling bearing is fixedly fitted on one of the two mass units, and can be fitted over the seat of the other mass unit when combined. Equipment. 4. One of the two flywheel mass units holds a component having a molded part of a bayonet joint for rotatably coupling the two flywheel mass units, and the other flywheel mass unit corresponds to the bayonet joint. Having a molded part,
Apparatus according to any one of claims 1 to 3. 5. A fly mass which is connectable to an internal combustion engine has a chamber and a damper and together with said chamber and damper constitutes one pre-assembled fly mass unit and the other pre-assembled fly mass unit. 5. The device according to claim 1, wherein the flywheel mass unit has a flywheel mass that can be connected to a transmission. 6. The output member of the damper has a forming portion engageable with a corresponding forming portion provided on one of the two fly mass units, and one of the fly mass units is a double fly mass unit. 6. The device as claimed in claim 1, further comprising a sealing element which, when the units are assembled in a plug-in manner, comes into contact with the corresponding sealing surface of the other flywheel mass unit in a sealing manner. 7. A sealing device formed by the combination of the two flywheel mass units, wherein a chamber at least partially filled with a viscous medium is located between said chamber and one of the two flywheel mass bodies when viewed in the axial direction. 7. The device according to claim 1, wherein the device is located and seals against an outwardly opening ring gap. 8. The damper has a built-in energy storage device acting in the circumferential direction, and an output member of the damper is a flange-shaped component cooperating with the energy storage device, and the flange-shaped component is located at the center. Apparatus according to any one of the preceding claims, comprising a cut-out, wherein the inner peripheral contour of the central cut-out defines a molding. 9. The device according to claim 1, wherein the corresponding molding is provided on the other flywheel mass. 10. The device according to claim 9, wherein the corresponding molding is provided on the outer circumference of the ring-shaped component connected to the other flywheel mass. 11. The device according to claim 10, wherein the ring-shaped component is axially fixed to the end face of the other flywheel mass which faces the flywheel mass which is closer to the internal combustion engine. 12. The rolling bearing according to claim 1, wherein the rolling bearing is mounted on a flywheel mass connectable to a transmission before the two flywheel mass units are axially inserted and assembled. apparatus. 13. A rolling bearing is received in a central recess of the other fly mass and is axially fastened between the shoulder of the fly mass and the ring-shaped component. Apparatus according to any one of the preceding claims. 14. The flywheel mass close to the internal combustion engine has an axial additional portion at the center, which axially extends into the recess of the other flywheel mass, and a rolling bearing. 14. The device according to claim 1, further comprising a seat for mounting the inner race of the vehicle. 15. After the two masses are axially aligned, the inner race of the rolling bearing is at least partially overlapped with the inner race and axially fixed to the end face of the axial addition. 15. The device according to claim 1, which is secured in the axial direction by a ring-shaped safety disk as a connecting member. 16. The rolling bearing according to claim 1, wherein the inner race is fastened between the safety disk and the shoulder of the axial extension.
The device according to any one of claims 1 to 15. 17. The rolling bearing according to claim 1, wherein a sealing member is provided on at least a side of the rolling bearing away from the chamber, the sealing member acting between the outer race and the inner race. Equipment. 18. The rolling bearing according to claim 1, wherein a sealing member for sealing the chamber to the rolling bearing is provided on a side of the rolling bearing near the chamber.
Item. 19. The apparatus of claim 18, wherein the sealing member acts between the outer race and the inner race. 20. A corresponding sealing surface which can be attached in advance to one of the two flywheel mass units, the seal member being provided on the other flywheel mass unit after combining the two flywheel mass units. 20. The device according to claim 18 or 19, wherein the device contacts. 21. The apparatus of claim 20, wherein the seal member is pre-mountable to a fly mass unit including a transmission lean fly mass. 22. The apparatus according to claim 1, wherein a seal member is provided between at least one of the inner and outer races and the flywheel unit holding the race. 23. Apparatus according to claim 1, wherein the sealing member for sealing the chamber against the ring gap is formed by at least one ring-disk-shaped sealing member. 24. The device according to claim 23, wherein the ring-shaped sealing member has a spring-like axial flexibility. 25. The method according to claim 25, wherein the sealing element is held by the flywheel mass close to the internal combustion engine and, after the combination of the two flywheel masses, makes contact with the corresponding contact surface of the other flywheel mass with a preload. Item 25. The apparatus according to any one of Items 1 to 24. 26. Apparatus according to claim 1, wherein the inner diameter of the sealing member sealing the chamber against the ring gap is greater than the outer diameter of the corresponding molding of the bayonet joint. 27. A radial outer edge of the seal member axially contacts a radial wall defining the chamber, the radial wall being opposite to the disk output member of the damper when viewed in the axial direction. 3 to 3 provided between the flywheel and the flywheel.
The device according to any one of the preceding claims. 28. The apparatus of claim 27, wherein a radially outer edge of the seal member is axially fixed to the radial wall. 29. A corresponding contact surface for a sealing member provided on the other flywheel mass is formed by a ring-shaped member, the ring-like member corresponding to the end face of said other flywheel mass. 29. Apparatus according to any one of the preceding claims, wherein the device is axially clamped between a component having a shaped part and extends more radially outward than the corresponding shaped part. 30. The apparatus according to claim 29, wherein the ring-shaped member is formed into a dish shape in a radially outward position and shifted in a direction away from the component having the corresponding formed portion. 31. Apparatus according to claim 1, wherein a viscous medium is loaded into the chamber before the combination of the two flywheel mass units. 32. The viscous medium is loaded through an area of the chamber that is closed during the combination of the two flywheel masses.
32. The apparatus according to any one of the above items. 33. Apparatus according to claim 1, wherein the loading of the viscous medium into the chamber is performed while rotating the chamber. 34. The apparatus according to claim 1, wherein the loading and dispensing of the viscous medium into the chamber takes place simultaneously while rotating the chamber. 35. The apparatus according to claim 1, wherein the rotational speed of the flywheel mass unit with the chamber is set to a centrifugal speed that causes a distribution of the viscous medium. 36. Apparatus according to claim 1, wherein a balance correction is performed after dispensing the viscous medium. 37. The apparatus of claim 36, wherein the balance correction of the fly mass unit having the chamber is performed before combining with the other fly mass unit. 38. The apparatus of claim 36, wherein the balance correction is performed after combining the two flywheel mass units. 39. Apparatus according to claim 1, wherein a pasty medium such as a lubricant, grease or the like is used as the viscous medium. 40. Apparatus according to claim 1, wherein the torsional resistance of the damper mechanism is variable. 41. Apparatus according to claim 1, wherein the torsional resistance is variable in relation to predetermined parameters of the motor vehicle and / or the internal combustion engine. 42. Apparatus according to claim 1, wherein the torsional resistance is gradually variable. 43. Apparatus according to claim 1, wherein the torsional resistance is variable as a function of the speed. 44. A change in torsional resistance is effected over a limited torsional rotation range of the two flywheel masses.
44. Apparatus according to any one of the preceding claims. 45. Apparatus according to claim 1, wherein the twist angle between the two flywheel masses is limited. 46. The device according to claim 1, wherein the change in torsional resistance is caused by a change in at least one passing cross section. 47. The device according to claim 1, further comprising at least one torsional elastic damper device between the flywheel masses. 48. The method according to claim 1, wherein friction type damper means is provided between the fly masses.
Item. 49. A damper mechanism for extruding a viscous medium and a torsionally elastic damper device are provided between the fly masses and act in parallel with each other over at least a part of the torsional rotation range. 49. Apparatus according to any one of the preceding claims. 50. The component of one of the fly masses forms at least one annular chamber, which is divided into at least two segment chambers by a partition provided in this chamber. A radial projection connected to the other flywheel mass penetrates into the segment chamber, and the segment chamber is formed such that one variable-volume chamber is formed on each side of one partition body. 50. Apparatus according to any one of the preceding claims, wherein the apparatus is divided. 51. The annular chamber is closed radially outward, and the projection is supported by a ring-shaped member and projects radially outward from the ring-shaped member.
The apparatus of claim 0. 52. Apparatus according to claim 50 or 51, wherein the ring-shaped member defines an annular chamber or chamber from the radial inside. 53. The device according to claim 1, wherein the other wall is riveted to the flywheel. 54. The torsional elastic damper device has at least one input side and at least one output side, and at least one of the side walls of the annular chamber forms an input side. The device according to any one of the preceding claims. 55. A ring-shaped member defining an annular chamber is coupled to an output portion of the torsionally elastic damper device.
55. Apparatus according to any one of the preceding claims. 56. A radial flange of one of the fly masses, an additional portion extending axially from the flange and a wall defining an annular chamber, wherein at least two damper means are provided within the annular chamber. 56. Apparatus according to any of the preceding claims, wherein the damper mechanism, torsional damper device and friction damper means are received. 57. A torsionally elastic damper device having at least one input part and at least one output part, and a power storage member acting circumferentially between the input part and the output part. Claims 1 to 5 are provided
The device according to any one of the preceding claims. 58. The damper mechanism according to claim 1, wherein the damper mechanism has an output-side portion, and the output-side portion is connected to an output-side portion of the torsional elastic damper device. Equipment. 59. The output side portion of the damper mechanism and the output side portion of the torsional elastic damper device are integrated.
An apparatus according to claim 8. 60. Apparatus according to claim 1, wherein the damper mechanism and the damper device are arranged at at least approximately the same axial height. 61. A torsional elastic damper device having two axially spaced disks forming an output side portion, between which the input side portion of the torsional elastic damper device. 61. The device according to any one of claims 1 to 60, wherein a flange is provided that forms 62. The other side wall of the annular chamber forms the input side of a torsional elastic damper device, and the damper means acting between the two fly masses limits and seals the annular chamber in which it is received. 62. The apparatus according to any one of claims 1 to 61, wherein: 63. A device for damping rotational vibration, comprising: a first gear fixed to an output shaft of an internal combustion engine and having a starting gear;
A damper device having a coil spring is provided from the flywheel mass body to a second flywheel mass body rotatable relative to the first flywheel mass body and connectable to an input shaft of a transmission via a friction clutch. A rotational moment is transmitted through the damper device, wherein the damper device is in a chamber that is at least substantially sealed and at least partially filled with a paste-like medium, the chamber being on the one hand a first The first wall of the flywheel mass, on the other hand,
A further radially outer wall of the flywheel mass, the first wall directly engaging the radially extending section of the first flywheel mass. And the mutual location of the first and second fly masses forming the first wall is the only rolling element that provides independent centering and support for both fly masses. Another wall defining the chamber is defined by the bearing location and the radially inner area serves solely to seal the chamber, from the first flywheel mass to the first flywheel mass. It projects radially inward into the axial configuration space between the first flywheel mass and the second flywheel mass and is formed by the first flywheel mass and the further wall. An intermediate flange is provided in the room,
The intermediate flange has, on the one hand, a rotational connection to the second fly mass in the radially inner region, for transmitting a rotational moment from the first fly mass to the second fly mass. In the radially outer region, via a coil spring, which is supported in the circumferential direction in the notch of the intermediate flange and also in the first flywheel mass, with a rotational connection to the first flywheel mass. Format,
Prior to balancing the device, at least the flywheel mass with the chamber is to be rotated to a bouncing speed capable of distributing the medium to a location as radially inward of the chamber as possible. A device for damping rotational vibration. 64. A device for damping rotational vibration, wherein the first device is fixed to an output shaft of an internal combustion engine and has a starting gear.
A damper device having a coil spring is provided from the flywheel mass body to a second flywheel mass body rotatable relative to the first flywheel mass body and connectable to an input shaft of a transmission via a friction clutch. A rotational moment is transmitted through the damper device, wherein the damper device is in a chamber that is at least substantially sealed and at least partially filled with a paste-like medium, the chamber being on the one hand a first The first wall of the flywheel mass, on the other hand,
A further radially outer wall of the flywheel mass, the first wall directly engaging the radially extending section of the first flywheel mass. Wherein the mutual position of the first and second flywheel masses is determined via a single rolling bearing point which provides sole centering and support of both flywheel masses. An intermediate flange is provided in a chamber formed by the first flywheel mass and the another wall, the intermediate flange transmitting a rotational moment from the first flywheel mass to the second flywheel mass. In order to have, on the one hand, a rotational connection to the second flywheel mass in the radially inner area and, on the other hand, in the radially outer area,
The device is of the type having a rotational connection to the first flywheel mass via a coil spring which is supported in the notch in the intermediate flange and also in the first flywheel mass in the circumferential direction. Prior to alignment, at least the flywheel mass with the chamber is adapted to be rotated to a flipping speed capable of distributing the medium to a location as radially inward of the chamber as possible. A device that dampens rotational vibration. 65. A split flywheel for an internal combustion engine, comprising a first flywheel removably secured to a shaft of the internal combustion engine together with a bearing flange, the bearing comprising a first flywheel with respect to the first flywheel by bearings. A second flywheel bearing on a bearing flange so as to be relatively rotatable, having a torsion damper device between the first and second flywheels, the torsion damper device comprising a center disk and the center. A cover lamella connected to each other, arranged on both sides of the disc, one of the cover lamellas being an integral part of one of the flywheels, and a window-shaped notch in the center disc and the cover lamella; And the other cover lamella and the center disc are mounted on one and the other of the two flywheels. The flywheel is torqueably connected via a coil spring, and at least the torsion damper device forms a unit which is sealed against lubricant, in which the window-like cutout of the cover plate is directed outwards. The cover plate on the crankshaft side of the internal combustion engine is an integral structural part of the first flywheel to which the other cover plate is fixedly connected, and is formed as a curved liquid-tight recess. A thin plate defining a radially outwardly liquid-tight inner chamber at least partially filled with lubricant and receiving a coil spring; A first packing disposed between the cover lamella and a portion that is torque-coupled to the second flywheel, and disposed on and across the bearing; In a type which is sealed by means of a second packing, before the device is balanced, the fly mass with at least the chamber distributes the medium to a location as radially inward as possible of the chamber. A split flywheel for an internal combustion engine, characterized in that the split flywheel is adapted to be rotated at a revolving speed capable of performing the jumping. 66. A split flywheel for an internal combustion engine, comprising a first flywheel removably secured to a shaft of the internal combustion engine with a bearing flange, the bearing comprising a first flywheel with respect to the first flywheel by bearings. A second flywheel bearing on a bearing flange so as to be relatively rotatable, having a torsion damper device between the first and second flywheels, the torsion damper device comprising a center disk and the center. It has a cover plate connected to each other, which is arranged on both sides of the disk, and has a coil spring disposed in a window-shaped notch of the center disk and the cover plate, and the cover plate and the center disk have both fly plates. Both flywheels are connected to one and the other of the wheels via a coil spring so as to transmit torque, and The shock damper device forms a unit sealed with respect to the lubricant, in which a window-shaped notch of the cover sheet is formed as a liquid-tight recess curved outward, and one liquid-tight cover sheet is formed. If it is an integral structural part of the first flywheel and this one cover sheet is connected to the other liquid-tight cover sheet or the cover sheet is constructed in an open manner, the cover sheet is ,
In a liquid-tight inner chamber with respect to the outside of the first flywheel,
If a flywheel mass oriented towards the internal combustion engine is arranged and connected to the first flywheel and a liquid-tight cover plate is used, the cover plate is at least partially A radially outwardly fluid-tight inner chamber, which is filled with lubricant and receives a coil spring, the inner chamber being, on the one hand, a cover plate or adjoining the second flywheel, Sealed via a first packing disposed between an additional cover lamella adjacent to the second flywheel and a part which is torqueably connected to the second flywheel, and on the other hand Wherein the inner chamber is of a type which is sealed via a second packing which is sealed via rolling bearings, and before the device is balanced, at least the flywheel mass with the chamber There, characterized in that adapted to be rotated in the rotational speed skip splashed can be distributed medium as constant as possible a radially inner position of the chamber, divided flywheel for an internal combustion engine. 67. A split flywheel of an internal combustion engine, comprising: a first flywheel releasably secured to two parts, ie, to a crankshaft; and a rolling bearing for the first flywheel. A torsion damper device disposed between the second flywheel and the second flywheel, which is limited and rotatably supported via
The torsion damper device includes a center disk extending between the first flywheel and the second flywheel, and a radially inner region of the center disk is coupled to the second flywheel so as to transmit torque. The radially outer region has a window-shaped notch for accommodating a plurality of coil springs, and these coil springs project from the window-shaped notch at both ends in the axial direction. In the protruding area, it is operable via members which are connected to the first flywheel in a non-rotatable manner, one of these members being connected to a second flywheel formed as a cover sheet. The member is axially disposed between the center disk and the outer periphery of the member is firmly and airtightly connected to the first flywheel, and the center of the member operates the coil spring. Having a window-like cut-out has a curved portion which is closed towards the second flywheel,
A radially inner region of the member having a packing for forming a closed interior of an at least partially lubricated torsion damper device with respect to the second flywheel; The inner chamber of the device is
A first packing disposed between a cover lamella adjacent to the flywheel and a portion of the second flywheel that is communicatively coupled to the second flywheel, and a seal via a second packing bridging the rolling bearings Prior to balancing the device, at least the flywheel mass with the chamber is rotated to a bouncing speed capable of distributing the medium to a location as radially inward of the chamber as possible. A split flywheel for an internal combustion engine, characterized in that it is adapted to be squeezed.