JP2572770B2 - Vibration damper - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention is a vibration damper having a split flywheel mounted between a prime mover and a power transmission, wherein the flywheel is at least two, relative to each other. A flywheel element rotatably supported and drivingly connected to each other via a spring, wherein the one flywheel element is connected to the prime mover and the other flywheel element is connected to the power transmission device; The vibration damping device has a chamber, at least a part of which is filled with a viscous medium, and at least a part of a spring is received in the chamber. Regarding the format.

Although devices of this type have already been proposed, these devices require relatively high costs for manufacture and assembly due to their construction.

The object of the invention is to provide a vibration damping device of the type mentioned at the outset, which can be produced in a particularly simple, reasonable and cost-effective manner. It is another object of the invention to provide a perfect sealing of the chamber filled with the viscous medium. It is another object of the present invention to extend the useful life of such a vibration damping device and to avoid abrasion of structural parts. It is a further object of the invention to improve the function and work style over previously known devices of the type mentioned at the outset.

SUMMARY OF THE INVENTION According to the invention, there is provided a vibration damper, comprising a flywheel mounted between a prime mover and a power transmission, wherein the flywheel is rotatable relative to at least two of each other. , And is divided into flywheel elements that are drivably connected to each other via springs, one of the first flywheel elements being a motor and the other being a power transmission device. Is coupled to or can be coupled to, and the vibration damping device has a chamber,
In the type in which at least a part of the chamber is filled with a viscous medium and at least a part of a spring is received in the chamber, the chamber forms one of the first flywheel elements. Is solved by having at least two shells joined together by welding and at least one of the at least two shells forming the chamber supports a starter gear. ing. This type of connection of the housing parts allows a perfect sealing of the chamber against the outflow of the viscous medium. Such a connection of the housing shells or housing halves is advantageous, inter alia, if they consist of sheet metal parts. It is particularly advantageous for the housing shells to have a weld in their outer region. Such welds are
It can be formed by shell end faces or butt surfaces which are welded face-to-face and butt.

To join the two shell halves or the two casing halves, the area to be welded of the two halves is heated to the welding temperature by a low voltage alternating current of high current strength and then pressed together. Advantageously, a joining welding method is used. For this purpose, the so-called pressure welding method, resistance welding method or capacitor spot welding method is particularly suitable. The supply of the current necessary for the welding can be effected in this case in an impulse-like manner or in an impact manner. In order to carry out such a welding, it is particularly advantageous for the housing halves to be welded to have at least their welding area made of steel with a low carbon content.

During the welding process of the two casing halves, unacceptable local heating of the equipment components occurs, and
In order to avoid coupling with some components which are in contact with the casing half before welding and which are movable with respect to the casing half, the casing shell or the casing half is contacted before welding. However, it is advantageous to provide an electrical insulation between the component parts which are movable relative to them and the shell. The insulation is advantageously provided between the housing half and a component received or assembled in the housing, such as a flange body, a coil spring, an intermediate layer or a spring receiving cup or other movable component. Advantageously it is provided. In this case, it is particularly advantageous to provide an insulating coating in the area of contact of at least one of the thin-plate shells with other components. Also, before welding, at least some of the components, such as the boss flange, the spring, and the spring receiving cup, which are in contact with at least one of the shells, are provided with insulating coatings at least in contact with the shells or the casing. It may be provided. Yet another possible means of avoiding unacceptable local heating or unacceptable welding is to make some of the components, such as spring receiver cups, which are in contact with at least one of the casing shells during welding, from a non-conductive material. That is.

The electrical insulation of at least the individual structural parts of the device can be easily achieved by phosphor coating. However, it is also possible to carry out by means of lacquer coating, plastic coating and ceramic coating. In some applications, it is sufficient to provide a grease layer between the structural parts.

When selecting an insulating coating material, consideration should be given to the fact that the material has corrosion resistance to dampers or room lubricants. According to an advantageous embodiment, the sheet metal part, the flange body and the intermediate layer or the spring receiving cup are provided with a phosphor coating for insulation, but the coil spring is provided with a lacquer coating.

In order to ensure a precise axial position of the two casing shells after welding, an advantageous embodiment provides that an axial stop between these shells is only effective during welding of the casing shells. Is provided.

In order to enable a satisfactory welding of the two housing shells, according to an advantageous embodiment, the housing shells have no coating in the weld area.

In this case, the casing shell-like body or the thin plate shell-like body is completely coated, for example, phosphorus-coated, and then the welded area and the contact area for power supply are provided with the insulating layer provided earlier in these areas. It is advantageous to make it conductive by removing it. This partial removal of the insulating coating can be easily achieved by mechanical processing.

According to one embodiment which is particularly advantageous in terms of construction, function and construction of the device, the housing shell or the sheet shell has a spring-shaped receiving part which extends in the circumferential direction. And a circumferential supporting area of the spring is formed by an axially embossed recess formed in the thin-plate shell body continuing to an end area of the spring receiving section, and a welding process. Occasionally, in order to accurately position the thin-plate shells with respect to each other, the thin-shells are supported by the embossed recesses. In order to precisely position the casing shell during the welding process, the casing shell can also have special positioning means, which can be formed, for example, by stamping.

It is particularly advantageous for the function and service life of the device that the flywheel element connectable to the prime mover has a chamber formed by the shell.
A particularly simple construction of the device is obtained in that the shell itself forms, for example, a flywheel element which can be coupled to the motor.

In order to perfectly seal the chamber for receiving the viscous medium and to precisely position and support the two flywheel elements with respect to one another, according to an advantageous embodiment, the thin shell on the prime mover side has a radius On the inner side in the direction, there is an axial extension extending towards the other flywheel element which can be coupled to the power transmission, on which the other flywheel element is located It is rotatably supported by one of the flywheel elements via a rolling bearing. For some applications, it is advantageous that the above-mentioned axial direction additional portion and the casing shell-like body on the prime mover side are integrally manufactured. It is also advantageous in terms of manufacture that they can be manufactured as separate structural parts and subsequently connected to one another. Coupling in the latter case is, for example, welding, riveting,
This can be done by screwing or swaging.
In order to fix the rolling bearing in the axial direction on the axial direction addition part, it is advantageous to use a disk fixed to the end face of the axial direction addition part. The fixation of the disc to the axial extension can be effected by riveting, screwing or swaging.

According to one embodiment which is particularly advantageous for the function of the device, in particular for its damping action, the passage-shaped receiving part for the spring, which is formed by a thin shell, is adapted to the outer periphery of the spring. And the passage-shaped receptacles forming the individual annular sectors,
It is sealed, leaving a slight gap, by a flange body forming a support area for the spring. In order to enable a simple assembly of the device, the above-mentioned flange body is connected to the other flywheel element in a torque-transmittable manner, but not axially fixed, so that the assembly of the device can be carried out on both flywheels. Advantageously, this is made possible by axially fitting the wheel elements. In order for the load to be transmitted perfectly to the spring by means of the flange body, the flange body has a radial arm which penetrates into the radial area of the channel-shaped receiving part. Advantageously.

According to an advantageous embodiment, the housing shell on the prime mover carries a starter gear which is at least partially welded to the shell.

 The invention will now be described with reference to the illustrated embodiment.

The torque transmitting device 1 shown in FIGS. 1 and 2 for compensating torsional impact has a flywheel 2,
This flywheel 2 is divided into two flywheel elements 3,4. Flywheel element 3
Are fixed to a crankshaft 5 of an internal combustion engine (not shown) by fixing bolts 6. The flywheel element 4 is provided with a friction clutch 7 that can be switched between connection and disconnection. Press plate 8 of friction clutch 7
A clutch disk 9 is provided between the flywheel element 4 and the flywheel element 4 and is supported on an input shaft 10 of a transmission (not shown). The presser plate 8 of the friction clutch 7 is spring-loaded in the direction of the flywheel element 4 by a diaphragm spring 12 which is supported by a clutch cover 11 so as to be switchable between a clutch connecting position and a closing position. The operation of connecting and disconnecting the friction clutch 7 connects and disconnects the flywheel element 4 and thus the flywheel 2 or the internal combustion engine to the transmission input shaft 10. Between the flywheel element 3 and the flywheel element 4 a damper device 13 is provided, which allows the relative rotation of the two flywheel elements 3,4. The flywheel elements 3 and 4 are supported via a bearing 15 so as to be relatively rotatable relative to each other.

The flywheel element 3 forms a casing, which forms a ring-shaped chamber 30 in which the damper device 13 is received.

The flywheel element 3 having the ring-shaped chamber 30 consists essentially of two housing parts 31, 32, which are connected to one another radially outward.
The two casing parts 31, 32 are formed by sheet metal parts which are connected to one another at their outer periphery by a weld 38. This weld 38 also seals the ring-shaped chamber 30 radially outward. In welding the thin sheet forming members 31, 32, a butt resistance welding or a capacitor spot welding, that is, an alternating current having a high current strength and a low voltage is applied to an area where two structural parts are to be welded in contact with each other. Advantageously, the two parts are heated to the welding temperature and pressed together by pressing.

In order to carry out such welding, both shell-shaped sheet metal forming members 31 and 32 are provided with an end surface area or abutting surface 34 having a predetermined surface defined on the basis of the current intensity used for welding. , 35. Casing part 3
1, 32 are welded by being brought into axial contact with each other in the area of these butting surfaces 34, 35.

In order to position the two casing parts 31, 32 accurately in the radial direction during welding, the casing part 31 has a ring-shaped protrusion 31a on the radially outer side, and the protrusion is formed along the outer periphery of the casing part 32. It surrounds the molded centering surface 35a. Axial recesses 65, 66 are machined in the casing parts 31, 32 for accurate circumferential positioning during welding. In these recesses 65, 66 the pins of the welding device can be engaged, these pins being both casing parts 31,3.
Hold the two in exact angular position with each other during welding.

During the welding of the two thin-sheet forming members (thin-sheet shells) 31, 32, a certain amount of axial movement is performed between these thin-sheet shells based on the formation of the weld bead. It is advantageous to provide for the first time an effective axial stop. In FIG. 1, such a stopper formed on the thin plate shell 32 is indicated by a chain line 67.
By using such a stopper 67, a welding operation can be performed irrespective of the current intensity used for welding. In other words, welding can be performed using a relatively high current intensity. That is, the axial position of the two casing parts 31, 32 is defined by the stopper 67, the axial position being defined by the current intensity and the axial pressure acting on the two casing parts 31, 32 during welding. Because it will never be.

The output of the damper device 13 is formed by a radial flange 41, which in the axial direction
It is located between 1,32. The flange 41 is connected radially inwardly to the ring-shaped disk part 27 via an axial plug-in connection 42, which is the housing part 31 of the flywheel element 4 on the internal combustion engine side. Is fixed by an rivet 26 to the end face of the axial direction additional portion 43 facing the front side.

The flange 41 has radial arms 44 on its outer circumference, which form a load range for a power storage element in the form of a coil spring 45 of the damper device 13.

The two casing parts 31, 32 form a ring-shaped receiving part 51 on the outside in the radial direction, into which the radial arm part 44 of the flange 41 enters. The ring-shaped receiving part 51 for the energy storage member 45 is formed by an axially pressed part or an axial indented part 52, 53 extending substantially in the circumferential direction. The indentations 52 and 53 are machined into casing portions 31 and 32 made of thin sheet, and within the indentation, the range of the energy storage member 45 protruding on both axial sides of the flange 41 is axial. Accepted in the direction. The ring-shaped receiving part 51 is closed radially inward by a ring-shaped area 49 of the flange 41, leaving a slight gap 54 on at least one side of the flange 41.

As can be seen from FIG. 1, the cross-sectional shape of the axial indentations 52, 53 is such that their arc-shaped sections extend at least approximately along the outer circumference of the cross-section of the energy storage member 45. . The outer regions of the indentations 52, 53 thus form an abutment or guidance area for the energy storage element 45, i.e., in which area the energy storage element 45 is supported at least radially under the action of centrifugal force be able to.

In order to reduce the wear of the ring-shaped receiving part 51 in the radial support area for the spring 45, a steel band 81 with a high hardness is provided in the embodiment shown, which is It extends around 51 and surrounds the spring 45. In the embodiment shown, the steel band 81 has a cylindrical shape and is received in a recess 82 which is formed by a radial groove or a radially recessed part. . Spring 45 when device 1 rotates
Is supported on the steel band 81 via the winding of the spring based on the centrifugal force acting on the spring.

Circumferential stoppers 55, 55a are provided in the indentations 52, 53 on both sides of the arm portion 44 for transmitting a load to the energy storage member 45. In the illustrated embodiment, the circumferential stoppers 55 and 55a
Is a radial arm 44 of the flange 41 when viewed in the circumferential direction.
Over the same angular range. As can be seen from FIG.
An intermediate member in the form of a spring receiving cup 59 is provided between the arm 44 and the end of the spring 45 on the arm 44 side. Suitable for cross section.

On the radial inside of the receiving part 51, the casing parts 31, 32 have areas 60, 61 facing each other, forming a circular ring-shaped surface, between which a circular ring-shaped space for receiving the flange 41. 62 are formed.

In the embodiment shown, the axial width of this circular ring-shaped space 62 is only slightly greater than the wall thickness in the region of the flange 41 received in the space 62, so that a very narrow gap 54 is provided on at least one side of the flange 41. Exists.

As can be seen from FIG. 2, four springs 45 are provided over the entire circumference of the device 1, each spring 45 extending at least approximately over the entire circumference over an angular range of 82 degrees. The spring therefore extends over at least approximately 90% of the entire circumference of the device 1.

In order to reduce the stress generated in the spring 45 during compression and to facilitate the assembly of the spring, the spring 45 is preliminarily bent in an arc along an imaginary circle where the spring is arranged.

The ring-shaped chamber 30 is filled with a viscous medium or a lubricant. The viscous medium should in this case fill at least the ring-shaped receptacle 51 when the device 1 rotates.

As can be seen in FIG. 2, the flange 41 has a central opening 71, the contour of which forms a radial shaping 72, which is a ring-shaped disk connected to the flywheel element 4. It engages with a corresponding forming portion 73 provided on the outer periphery of the portion 27. The corresponding shaping 73 is formed by a radial projection, which engages in a correspondingly matching notch 72a of the flange 41. In the area of the radial projection 73 there is further provided a rivet 26 which secures the structural part 27 to the flywheel element 4. The forming part 72 and the corresponding forming part 73 forming the axial insertion coupling part 42 enable perfect positioning of the flange 41 between the two casing parts 31, 32,
Therefore, the gap 54 between the circular ring-shaped space 62 and the flange 41 can be made extremely small. In addition, the axial plug-in connection 42 makes it possible to increase the axial tolerance between the different abutment or support surfaces of the structural part.

A packing 74 is provided between the flywheel element 4 and the radially inner area of the casing part 32 to seal the ring-shaped chamber 30. The packing 74 comprises a circular ring-shaped, axially spring-acting disc 75 which is coated with a synthetic or plastic material and which, on the radial outside, a ring-shaped area of the casing part 32. 32a and casing part 3
2 is fastened in the axial direction to a ring-shaped disk 80 fixed by a rivet joint 32b.

The ring-shaped area 32a of the casing part 32 extends radially inward from the outer diameter area of the spring-loaded packing disk 75, in which case the radial direction between the ring-shaped area 32a and the packing disk 75 Space 32c is formed. A small amount of a viscous medium (possibly a viscous medium passes between the inner area of the packing disk 75 and the corresponding contact area 76b) is accommodated in the radial space 32c which is opened inward in the radial direction. When the rotation speed becomes high, the centrifugal force acts to pass the space between the ring-shaped area 32a and the packing disk 75 and into the ring-shaped chamber 30 again. Will be returned. The area of contact between the inner area of the packing disc 75 and the corresponding packing contact area 76b is within the axially extending area of the radial space 32c.

An axial recess or an axial step 91 is formed in the inner area of the casing part 32, and its radially outer peripheral surface (step inner peripheral surface) is axially engaged with the outer area of the packing disk 75. doing.

The casing portion 31 on the internal combustion engine side supports an additional portion 20 in the axial direction on the inner side, and a rolling bearing 16 that supports the flywheel elements 3 and 4 so as to be relatively rotatable relative to each other is provided on the outer periphery of the additional portion. Mated. The thin sheet forming member 31 is centered on the fitting seat 20b of the additional portion 20, and the seat 2
0b is followed by a radial surface 20c provided on the additional portion 20
Are supported in the axial direction.

The connection between the thin-plate forming member or casing part 31 and the axial direction additional part 20 can be performed by screw connection, rivet connection, welding or caulking.

Assembling of both flywheel elements 3, 4 is performed as follows. That is, the rolling bearing 16 is first assembled to the flywheel element 4 and the packing disk 75 is assembled to the flywheel element 3 in advance. Next, when the rolling bearing 16 is pressed onto the fitting seat portion 20a of the additional portion 20, the connection by the insertion connecting portion 42 is obtained, and the packing disk 75 is provided in the corresponding packing contact surface area 76b provided on the flywheel element 4. Is tightened in the axial direction. Next, a fixed disk 22 that is radially overlapped with the inner ring of the rolling bearing 16 is mounted on the end face of the additional portion 20, so that the two flywheel elements 3, 4 are axially fixed to each other. The above mounting of the disk 22 can be performed by rivets, but bolts may be used instead of rivets.

When welding the two thin-plate casing portions 31, 32, a structural portion in contact with the casing portion, for example, a particularly movable structural portion, is locally welded to the casing portion,
Further, in order to prevent the welding seam from being changed due to local excessive heating, an electric insulating portion is provided between these structural portions and the thin-plate casing portions 31, 32. During the welding process, the dangerous parts are, in particular, springs 45, flanges 41,
Further, a spring receiving cup 59 is provided.

The insulating coating is provided on the casing parts 31, 32 and / or the structural parts 45, 41, 59, 55, 55a in contact with said casing parts.
Can be provided. In this case, the insulation coating may be provided only locally. In other words, it can be provided only in the contact area between the casing part and the above-mentioned structural part.

The insulation can advantageously be obtained by applying a phosphorus coating to the individual structural parts. In addition, individual structural parts, such as the spring receiving cup 59 and the circumferential stoppers 55, 5
5a may be made from a non-conductive material.

It is particularly advantageous to phosphor coat the sheet metal part and / or the flange for insulation. The spring 45 is advantageously rack-coated, but may be phosphorus-coated.

It is also possible to use a ceramic coating layer, a synthetic or plastic coating layer or a grease layer to insulate the casing parts 31, 32 against the structural parts in contact with these parts. Such a coating can be provided, in particular, on the housing parts 31, 32.

When the sheet metal forming members 31 and 32 are completely covered by insulation treatment, for example, phosphorus coating, the insulation coating layer provided earlier in the welded area and the contact area for power supply may be subjected to, for example, mechanical coating. Advantageously, it is removed by processing so that these regions have an excellent conductivity.

When choosing an insulating material, it must always be resistant to the viscous medium filled in the ring-shaped receiving part 51.

The use of a phosphorus coating layer as the insulating layer is particularly advantageous in that the coating layer is less likely to be worn and has self-lubricating properties.

The casing part 31 further has a fitting seat 39 on its outer periphery, on which a starter gear 40 is supported. The starter gear 40 is connected at least locally to the casing portion 31 by a weld 40a over the entire circumference. This is advantageous when the casing part 31 is made of a sheet metal part. This is because, in this case, the wall thickness of the casing part 31 is limited, so that the fitting seat 39 does not cover the entire width of the starter gear.

As can also be seen from FIG. 1, the casing part 31 on the internal combustion engine side has a greater wall thickness than the casing part 32.

As can be seen from FIG. 3, the circumferential stoppers 55, 5 shown in FIG.
Instead of 5a, a formed portion formed by stamping thin sheet formed members 31, 32, for example, concave portions 55c, 55d can be used. These recesses 55c, 55d can advantageously be used to position the two casing parts 31, 32 relative to each other during welding. To this end, the above-described recess 55c,
Corresponding projections are provided which conform to 55d. These projections can in this case form electrodes which direct the required welding current into the casing parts 31,32. With these projections, furthermore, the axial pressure required for welding can be applied to the casing parts 31, 32. These projections are especially provided in the welding device so that a certain distance is maintained at all times during the welding process, so that the two casing parts 31, 32 have a predetermined axial relative position after welding. It is advantageous. The fact that the two casing parts have a predetermined axial relative position after welding is that the spring 45 provided in the ring passage-shaped receiving portion 51 and, in particular, the two regions 60 and 61 and the flange 41 provided between these regions It is important for the function of the predetermined play to be maintained during this time, which play influences the hydraulic or viscous damping generated by the device.

The mode of operation of the device of FIGS. 1 and 2 is as follows.

When the flywheel element 4 is pivoted from the rest position shown in FIG. 2 with respect to the flywheel element 3, the flange 41 is driven via the plug-in connection 42, so that the spring 45 , 55a and the radial arm 44. When the two flywheel elements 3 and 4 rotate relatively, a friction buffering action occurs due to the friction of the spring 45 on the surfaces of the indentations 52 and 53.
In this case, the damping action increases with an increase in the rotational speed. Further, the viscous medium or the paste-like medium contained in the ring-shaped chamber 30 has a buffering action due to vortex or displacement. In particular, the viscous medium in the virtually closed ring channel-shaped receptacle 51 produces a hydraulic or viscous damping action. This is because the spring receiving cup 59 acts as a piston in a ring-shaped receiving part. When the spring 45 is compressed, the spring receiving cup 59, which is loaded by the arm 44, is provided with a circumferential stopper 55,5.
It moves towards the spring receiving cup supported by 5a, so that the viscous medium in the spring 45 is pushed out mainly through the gap 54, which acts like a throttle. Yet another portion of the viscous medium is extruded between the spring receiver cup 59 and the wall of the ring channel receiver 51. The viscous medium initially displaced inward is again distributed over the outer circumference by the centrifugal force acting on it. During the relaxation of the spring 45, the viscous medium on the opposite side of the spring receiving cup 59 from the spring 45 side is extruded in a similar manner through the spring receiving cup and through the gap 54, and The spring 45 is filled again due to the centrifugal force acting on the viscous medium. The damping effect produced by the viscous medium is related to the centrifugal force acting on the viscous medium, and therefore increases with increasing rotational speed.

By providing at least one spring receiving cup with an axial cutout and also by appropriately defining the gap 54 or the outer dimensions of the spring receiving cup, the damping effect produced by the viscous medium is changed or reduced. It can be adapted to the respective application. Further, the viscous or hydraulic damping effect is achieved by using a small number of the springs 45.
By providing the spring receiving cup 59 on only 45, it can be adapted to the respective application.

The invention is not restricted to the embodiment shown, but can be embodied in further different ways, for example with a plurality of spring dampers. Thus, for example, it is also possible for at least the individual arm portions 44 to have different lengths in the circumferential direction from the circumferential stoppers 55, 55a belonging thereto. Also, individual arm parts
44, when viewed in the circumferential direction,
It is also possible to extend over an angular range larger or smaller than 55, 55a. Furthermore, damper 13
It is also possible to provide a further damper having a power storage member, connected in parallel or in series with the damper 13, radially inward.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 shows an embodiment of the present invention. FIG. 1 is a sectional view of an embodiment of the apparatus of the present invention, and FIG. 2 is a sectional view taken along line II-II of FIG. FIG. 3 is a detailed view of one structural part of the device of the present invention, which can be used in the embodiment of FIGS. 1. Torque transmission device 2. Flywheel 3. 4, 4.
... Flywheel element, 5 ... Crankshaft of internal combustion engine, 7 ... Friction clutch, 8 ... Pressure plate, 9 ... Clutch disc, 10 ... Input shaft of transmission,
12 ... Diaphragm spring, 13 ... Damper device, 15 ... Bearing part, 16 ... Rolling bearing, 20 ... Additional part, 20b ... Mating seat part, 22 ... Fixed disk, 27 ... Disk part, 30…
… Casing (ring-shaped chamber), 31 ・ 32… Casing part (shell-shaped body), 34 ・ 35… Butted surface, 38… Welded part, 39… Fitting seat, 40… Starter ring gear, 41…
... Flange, 42 ... Plug-in joint, 43 ... Axial additional part, 44 ... Arm, 45 ... Power storage member (coil spring),
49 …… Range, 51 …… Ring passage-shaped receiving part, 52 ・ 53 ……
Bay entrance, 54 …… Gap, 55 ・ 55a …… Circumferential stopper, 59
... spring receiving cup, 60 ... area forming a circular ring-shaped surface, 62 ... circular ring-shaped space, 65, 66 ... recess,
67: Stopper, 71: Central opening, 72: Radial molded part, 73: Corresponding molded part, 74: Packing, 75: Disk, 81: Steel band, 82: Concave part.

Claims (33)

(57) [Claims] 1. A vibration damping device comprising a flywheel mounted between a prime mover and a power transmission, wherein the flywheel is rotatably supported relative to one another and includes a spring. The flywheel element is divided into flywheel elements that are drivably connected to each other via the first flywheel element.
The other second flywheel element is connected or connectable to a power transmission device, and the vibration damping device has a chamber, at least a part of which is filled with a viscous medium. And at least part of a spring is received in the chamber, the chamber (3
0) are formed by at least two shells (31, 32) joined together by welding, forming one of the first flywheel elements (3), and defining a chamber (30). At least one of the at least two shells (31, 32) to be formed supports a starter gear (40),
Vibration damper. 2. The vibration damping device according to claim 1, wherein the shell-like body is formed from a thin plate. 3. The vibration damping device according to claim 1, wherein the shell-like members are welded to each other in their outer peripheral regions. 4. The vibration damping device according to claim 1, wherein the two shell-shaped members have end surfaces or abutting surfaces which are welded against each other. 5. The vibration damping device according to claim 1, wherein the two thin-plate shells are connected to each other by a pulsation resistance weld. 6. The vibration damping device according to claim 1, wherein the two thin-plate shells are connected to each other by a butt resistance weld. 7. The method according to claim 1, wherein the two thin-plate shells are connected to each other by a capacitor spot weld.
Item 5. The vibration damping device according to any one of items 1 to 4. 8. The vibration according to claim 1, wherein the butting surfaces of the two thin-plate shells heated to the welding temperature are joined by the action of pressure. Shock absorber. 9. An electrical insulation is provided at least between the shell part and the structural part of the device which is in contact with the shell body before welding and is movable with respect to the shell body.
The vibration damping device according to any one of claims 1 to 8, wherein 10. A structural part in which at least one of the thin-plate shells is received or assembled in a casing, such as a boss flange, a torsion spring, a spring-receiving cup or any other. The vibration damping device according to any one of claims 1 to 9, further comprising an insulating coating in a contact area with the structural part. 11. At least some structural parts in contact with at least one of the shells before welding.
For example, the boss flange, the torsion spring, and the spring receiving cup have an insulating coating.
Item 11. The vibration damping device according to any one of items 10 to 10. 12. The vibration damping device according to claim 1, further comprising a spring receiving cup made of a non-conductive material. 13. The method according to claim 1, wherein an insulating portion between the thin shell and at least some of the structural parts in contact with the thin shell is formed by a phosphor coating layer. Item 13. The vibration damping device according to any one of items 12 to 12. 14. The vibration damping device according to claim 1, wherein at least some of the components have a phosphorus coating layer. 15. The vibration damping device according to claim 1, wherein at least some of the components, in particular the compression springs, have a lacquer coating. 16. An electrical insulation between the shell-like body and at least some of the other structural parts may be provided with a ceramic coating, at least one of the parts in contact with each other.
The vibration damping device according to any one of claims 1 to 15, wherein the vibration damping device is provided by providing a coating such as a plastic coating or a grease coating. 17. A method according to claim 1, further comprising an axial stopper provided between said thin-plate shells and acting only in the step of welding said shells. A vibration damper as described. 18. The vibration damping device according to claim 1, wherein the thin-plate shells have no coating in their welding area. 19. The method according to claim 1, wherein the welding area and the power supply contact area of the thin-plate shell are made conductive by removing an insulating coating layer provided earlier in the area. Item 19. The vibration damping device according to any one of Items 1 to 18. 20. The vibration damping device according to claim 19, wherein the removal of the insulating coating layer is performed by mechanical processing. 21. A spring having a passage-like receiving portion extending in the circumferential direction, wherein the thin-plate shell-like body has a circumferential support region for an end portion of the spring receiving portion. Is formed by an axially embossed recess formed in the thin-plate shell body, and in order to accurately position the thin-shell members with each other during the welding process, 21. The vibration damping device according to any one of claims 1 to 20, wherein a body is supported by the embossed recess. 22. The method according to claim 1, wherein the thin-plate shell has positioning means for accurately fixing the position during the welding process. Vibration damper. 23. The vibration damping device according to claim 22, wherein said thin-plate shell-shaped body has a stamping portion as said positioning means. 24. The method according to claim 1, wherein the flywheel element connectable to the prime mover has a chamber formed by a shell.
The vibration damping device according to the above item. 25. A thin shell on the prime mover side having a radially inwardly extending additional portion extending toward the other flywheel element which can be coupled to a power transmission device. 25. The device according to claim 1, wherein the other flywheel element is rotatably supported on the additional portion via a rolling bearing with respect to the one flywheel element. Any one of
The vibration damping device according to the above item. 26. The vibration damping device according to claim 25, wherein the axial direction additional portion and the prime mover-side shell-like body are welded to each other. 27. The axially additional portion and the prime mover-side shell-like body are rivet-connected to each other.
Item 27. The vibration damping device according to Item 25. 28. The vibration damping device according to claim 25, wherein the rolling bearing on the axial addition portion is fixed in the axial direction by a disk fixed to an end face of the axial addition portion. 29. The vibration damping device according to claim 28, wherein the cover disk is riveted to the axial addition portion. 30. A passage-shaped receptacle formed by a thin-plate shell for the spring is adapted to the outer periphery of the spring,
22. The method according to claim 21, wherein the passage-shaped receiving parts forming the individual annular sectors are sealed, with a slight spacing, by a flange body forming a support area for the spring.
Item 30. The vibration damping device according to any one of items up to item 29. 31. The vibration damper according to claim 30, wherein the flange body is connected to the other flywheel element so as to transmit torque, but is not fixed to the flywheel element in the axial direction. apparatus. 32. A spring according to claim 30, wherein the spring is supported on a radial arm formed by the flange body and extending into a radial area of the passage-shaped receiving part. A vibration damper as described. 33. The thin shell structure on the prime mover side supports a Stirling gear that is at least locally welded to the thin shell structure.
33. The vibration damping device according to any one of the items up to 32.