JP3390152B2 - Device for damping rotational vibration - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention
Vibration damping devices located in the
You. [0002] The object of the present invention is to provide an apparatus
Easy, quick, inexpensive and reliable function assembly
It is an object of the present invention to provide such a device. Departure
Clearly another challenge is to improve the operation of this type of device and its
To increase life. [0003] The present invention has solved the above problems.
The gist of the light is that it is supported so that it can rotate
With at least two bounce masses, one bounce
Mass can be coupled to the engine and the other fly mass can be coupled to the transmission
Function and at least one flywheel mass
Partially filled with a stratified or viscous medium
Chamber, in which the relative mass between both
Especially vehicles of the type in which buffer means against rotation are accommodated
Device for damping rotational vibrations in the power train
And the viscous medium is at least partially filled,
A chamber that receives the damper device is provided inside,
After the chamber is filled with media, the device is balanced or
Before lancing, at least the bouncing material with the chamber
Position the medium as radially inward as possible in the chamber
Can be distributed to the bounce speed
It is manufactured by that. The advantages provided by the present invention arise.
No change in state over the temperature range
Minimal state change as possible, viscous
Chamber by a paste-like medium that does not cause significant changes in
When filling, distribute evenly or evenly around
Uniform filling height is adjusted and therefore the device is exactly balanced
Is made possible. DETAILED DESCRIPTION OF THE INVENTION At least partial filling of a chamber
In many constructions of the device, a bouncing mass with a chamber is
Before reaching the spinning speed that creates the distribution
This is advantageous. However, during filling of the chamber with a viscous medium,
At least the bounce mass of the person with the room
Rotating at a speed that produces a uniform distribution of the medium
Is particularly advantageous. However, in many applications, viscous media
When loading the body into the room, at least the person with the room
The bouncing mass first bounces off at a rotational speed lower than the rotational speed.
It is effective to rotate. To obtain a sufficient distribution of the viscous medium in the room
In addition, the number of revolutions
Advantageously it is between 2 and 15 times. Using this device
At least approximately at the critical speed of the internal combustion engine.
It is effective that the revolving speed is located in the range. At a high rotation speed as described above, there is no space between parts.
Centrifugal force that acts on the viscous medium
Air is forced out, leaving air in this free chamber.
Do not stay. This allows for long operating hours after the device has been operating.
After that, air may later enter through the viscous medium.
Does not occur. Precise balancing
As well as additional unbalanced later
In order to avoid occurrences, the device is brought before
The rotation speed is generally between 4000 and 7000 r.p.
m. advantageously between approximately 5000 and 6000 rpm.
In that case, a small amount is required for a sufficient distribution of the viscous medium
At least the bounce mass with chamber has 30 seconds to 3
It is effective that the number of revolutions is kept at the number of revolutions.
This bounce time depends on the viscosity of the medium used and the bounce rotation.
Depends on the number. [0009] In addition to reducing the bouncing time, indoor
In order to obtain a sufficient distribution of the viscous medium, at least
Heat the bounce mass or remove the viscous medium indoors
It is especially important to heat it before charging it, or both.
Is advantageous. According to such heating, the bounce
The number of turns can also be reduced. Bounce mass and (also
A) The target heating temperature of the viscous medium is 80 to 250 ° C.
You. In many embodiments of the present invention, a
Inside the chamber of the vibrating mass body
Inject or inject viscous media through chainable openings
It would be advantageous if you could. In that case, complete before filling
The device is pre-assembled. In another embodiment of the present invention, a chamber
Both the charging of the viscous medium into the room and the distribution of the viscous medium in the room
Before assembling or assembling
It is advantageous. For such at least partial filling of the chamber
According to this, it is easy to handle the bounce mass body with this chamber
As well as being closed by the combination of both masses.
A viscous medium can be charged through the chamber area to be filled.
The advantage of the latter is that additional filling ports and closing means or
There is no need for a sealing means. In many use cases,
After assembly of both flywheel masses forming the
It is advantageous if the training is performed. In that case, balance rotation
The number can be between 400 and 2000 rpm. Another use example or embodiment of the device of the present invention
Now, a flywheel mass with a chamber for the viscous medium and
The other bounce masses are each separately balanced and
It is also advantageous to combine them afterwards into one unit. Sticky
Media such as lubricants, greases or the like.
A medium in the form of a paste is suitable. FIG. 1, FIG. 2 and FIG.
Shows a torque transmission, which comprises two flywheel parts 3,
It has one flywheel 2 divided into 4
The car part 3 is fixed to the crankshaft 5 of an internal combustion engine (not shown).
It is fixed via a stitch 6. Cut the flywheel part 4
The replaceable friction clutch 7 is fixed. Friction club
Clutch plate between the pressure plate 8 of the switch 7 and the flywheel portion 4
9 is provided, which is an input of a transmission (not shown).
Attached to the shaft 10. Pressure plate 8 of friction clutch 7
Turn to clutch cover 11 in the direction of flywheel part 4
It is loaded by a possibly supported disc spring 12.
By the operation of the friction clutch 7, the flywheel portion 4 and, consequently,
Flywheel 2, ie, the internal combustion engine is connected to the input shaft 10 of the transmission
Connected and disconnected. With flywheel part 3 and flywheel part 4
Between the radially outer first damper 13 and the first damper 13
And a second radially inner damper 14 connected to the
And both flywheels by both dampers
Minute relative rotation is possible. The two flywheel parts 3, 4 are rotated relative to each other.
It is rotatably supported via a bearing 15. Bearing 1
5 comprises a rolling bearing in the form of a single row ball bearing. ball
Outer ring 17 of bearing 16 is inside notch 18 of flywheel part 4
The inner ring 19 extends axially in a direction away from the crankshaft 5.
Located on the cylindrical shaft 20 in the center of the flywheel 3
Have been. The inner ring 19 is fixed on the shaft by a press fit.
And the shoulder 21 of the shaft 20 or a flywheel
The part 3 is fixed to the end face of the shaft part 20 by the rivet 22a.
It is clamped between the safety plate 22 and the safety plate 22. As can be seen especially from FIG. 2, the ball bearing 14
Axial direction through two rings 23 and 24 having an L-shaped cross section
Then, through the shoulder 25 of the flywheel part 4 and the rivet 26
Ring plate 2 fixedly connected to second flywheel part 4
7 is tightened. Radially inward legs of rings 23, 24
23a, 24a partially extend in the radial direction to the inner ring 19;
And is supported by the inner ring 19 in the axial direction.
This also serves as a packing for the ball bearings 16
ing. To ensure a sufficient seal of the ball bearing 16
The legs 23a, 24a extending in the radial direction
An inner ring in the axial direction by means of a storage element in the form of springs 28, 29
19 is crimped to the end face. The inner ring 19 and the shaft portion 20 of the flywheel portion 3 are provided.
A packing ring 37 is provided between the girder and the step portion 20a.
This is the radial annular groove 3 provided in the step 20a.
7a. As can be seen from FIG. 1, the flywheel part 3 is a ring.
A casing for limiting the chamber 30 is formed.
Dampers 13 and 14 are housed in the chamber 30. Annular
The flywheel part 3 having the chamber 30 is generally composed of two housings.
Lacing portions 31 and 32. Restrict annular chamber 30
Casing portions 31, 32 are formed from a casting.
I have. The casing part 32 has an axial cylindrical shape around it.
Is provided, and through an inner peripheral surface 35 of the additional portion 32a.
The casing part 32 is the outer peripheral surface 34 of the casing part 31.
Is positioned on top. Of the casing parts 31, 32
Axial fixing is performed via radial pins 38.
And the pin 38 is arranged in the area of the outer peripheral surface 34 and the inner peripheral surface 35.
Have been. The casing part 32 has a starting tooth on its shoulder 39.
Supports crown 40, which partially extends pin 38
The pin 38 cannot move in the radial direction.
Noh. To seal the annular chamber 30 to the outside
In the area between the pin 38 and the chamber 30, the packing ring 3
6 are arranged. Both dampers 13 and 14 are provided with radial flags.
One common output in the form of a
It is located axially between the two casing parts 31, 32.
It is location. As can be seen from FIG.
Axial mating connection by its radially inner region
And is non-rotatably connected to the ring plate 27 through the portion 42.
The ring plate 27 should face the direction of the crankshaft 5,
Fixed to the end face of the additional part of the wheel part 4 via the rivet 26
Have been. The flange 41 has a radial arc on its outer periphery.
A coil 44 of the damper 13 on the outside.
Forming a load area for a storage element in the form of a spring 45
I have. When viewed in the circumferential direction, the coil
Arm 4 is located radially inward of notch 46 for
4, a curved window 47 is provided.
The energy storage member in the form of a coil spring 48 of the inner damper 14
Is housed. Between the notch 46 and the window 47 in the radial direction
Forms a web 49 in which the flange 41 extends in the circumferential direction.
This is a radial arm 44 or a circumferential window
47, a radial area 50 of the flange 41
Are connected to each other. The radial area 50 is carp
Forming the load area of the flange 41 for the spring 48
I have. The annular chamber 30 has an annular passage shape on the outside in the radial direction.
Alternatively, a receiving portion 51 similar to a torus is formed.
The arm 44 of the flange 41 is engaged in the radial direction in the receiving portion.
I agree. Annular channel-shaped receiving for the coil spring 45
The part 51 is substantially axially extending in the circumferential direction.
Are formed by concave portions 52 and 53 of
The part is formed in the radial area of the casing parts 31, 32
In this recessed portion, there are projections on both sides of the flange 41.
The region of the coil spring 45 protrudes in the axial direction.
The receiving portion 51 is formed so that the web 4 of the flange 41 faces inward in the radial direction.
9, apart from the slight gap 54, is closed
I have. As can be seen from FIG. 1, the recess 5 in the axial direction
The cross-section of 2,53 has at least approximation of its curved extension
To fit around the cross section of the coil spring 45
Has been established. Therefore, the concave portions 52 and 53 are
Forming a support or guide area for the spring 45
Thus, the coil spring 45 is supported in this area. Recessed part 5
The support area formed by the coil spring 45
Of the recesses 52, 53
Wear due to friction between the limiting surface and the coil of the coil spring 45 is reduced.
Significantly reduced. Because the coil spring 45 and recessed
This is because the support surface between the parts increases. Annular channel-shaped receiving for the coil spring 45
To prevent wear in the radial support area of the part 51
Steel band 81 with high hardness is provided to reduce
Which extends around the periphery of the receptacle 51
And surrounds the coil spring 45. Stee
The band 81 is formed in a cylindrical shape, and the notch 82
This notch has a radial cut
Or by a radial depression. apparatus
At the time of one rotation, the coil spring 45 is subjected to the centrifugal force acting on it.
Supported on the steel band 81 through its wire loop
It is. 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, which are coiled in the circumferential direction.
It forms a support area for the spring 45. Circumferential stop
The parts 55 and 55a are parts adapted to the concave parts 52 and 53, for example.
For example, it is formed by casting or press molding,
This is achieved through the integrally formed rivets 58 through the casing.
It is fixedly connected to the parts 31, 32. Circumferential strike
The end regions of the hoppers 55 and 55a in the circumferential direction are coiled.
It has a flat part to produce a good load
You. As can be seen from FIG.
Circumferential stoppers 55, 55a arranged on both sides of the
Is longer in the circumferential direction than the arm 44, and
In the embodiment, in the rest position of the device shown in FIG.
Centered with respect to the circumferential stoppers 55, 55a
Therefore, the circumferential stoppers 55 and 55a
Project the same amount on both sides. The casing portions 31 and 32 are
Forming annular surfaces facing each other on the radial inside
Regions 60 and 61 are provided.
An annular passage 62 for the flange 41 is formed. In the embodiment shown in FIG. 1 and FIG.
The width of the passage 62 is accommodated in the passage of the flange 41.
Slightly larger than the area of
At least a gap 54 is formed on one side. The casing portions 31 and 32 are formed as annular passages.
An axially recessed portion 63, 64 is provided radially inward of 62.
And protrudes into the recess on both sides of the flange 41.
The area of the inner coil spring 48 is at least partially
I'm rushing. As can be seen from FIG. 1, the recess 6 in the axial direction
3, 64 cross-sections whose arcuate extension is at least radial
In the area on the outside side, a suitable area around the cross section of the coil spring 48 is used.
So that the coil spring 48 is at least
Or guided by the recesses 63, 64 in the
You. As with the outer concave portions 52 and 53, the inner concave portions
The installation portions 63 and 64 also extend over the entire circumference of the device. This
This is for example the precast recesses 52, 53 and 63, 6
Advantageously, 4 can be machined by a rotating operation
It is. Due to the load of the coil spring 48, the recesses 63, 6
4 are provided with circumferential stoppers 65 and 66
The circumferential stoppers 65 and 66 are
5,55a and likewise
Rivet portions 31 and 32. Flange
Circumferential strikes disposed on both sides of a radial region
The wrappers 65 and 66 are provided in a region 5 serving for the load of the coil spring 48.
It has a greater extension in the circumferential direction than 0. Radial direction
Of circumferential stoppers 65 and 66 in relation to the region 50
Protrudes on one side with respect to the area 50 in the rest position of the device 1,
On the other side is made to coincide with the radial area 50
You. Further, the circumferential stop associated with the radial region 50
The misalignment of the pars 65, 66 is arranged one after the other in the circumferential direction.
The circumferential stoppers 65 and 66 are in opposite directions to each other.
The flange 41 is opposed to the circumferential stoppers 65 and 66.
This is performed so as to be shifted with respect to the radial direction region 50. this
Depending on the configuration, the inner coil spring 48 acts stepwise.
Two coil springs 48a and 48b are formed. The web 49 of the flange 41 is an inner concave portion.
In connection with 63, 64, the coil spring 48 is at least
To be radially supported by web 49 under the action of force
Designed to. This means that the flange 41 must be at least
Made from surface-hardened steel and therefore coil spring
Advantageously, wear of the support for 48 is reduced.
You. As can be seen from FIG.
Circumferential stoppers 55, 55a and
A spring receiver 59 is arranged between the end of the oil spring 45 and
The outer periphery is suitable for the cross section of the annular passage-shaped receiving portion 51.
I agree. The spring receiver 59 has a slightly tapered projection 59.
a, which projects axially into the coil spring 45.
Yes. The end of the projection 59a is conical in the embodiment shown.
Although it is formed in a shape, it may be formed in a spherical shape.
With such a configuration of the spring receiver 59, the spring receiver is operated.
As long as it slides out of the spring end during rolling,
When reloading or reducing the load on the spring, the spring support is automatically coiled.
Coil spring or spring holder
Not damaged. The outer coil spring 45 is compressed and
When the device 1 rotates at a relatively high rotation speed, the spring receiver 59 slides.
Put out. In this operation state, the wire loop of the coil spring 45 is
Of the casing parts 31, 32 for the coil springs
The friction existing between the support area in
Il spring 45 is at least complete during sudden load alternation impact
The load cannot be reduced. Half load impact
Radial arm 44 allows outwards under the action of centrifugal force
Due to the pressure on the redistributed viscous medium,
The spring support 59 is provided for the coil spring 45 which has not been lightened.
We receive pressure from the end. In the annular chamber 30, a viscous medium or lubrication
There is a medium, for example grease. Viscous medium or moisture
The level of the lubricating medium should be at least in the center
Or the axis of the coil spring 45 outside the damper 13.
Reach with. In the illustrated embodiment, this level is at least
Reaching the area outside the wire loop of the inner coil spring 48
It is advantageous that at least this wire loop
Area in which it is supported in the radial direction, in this case franc
Lubrication to reduce wear is generated between the web 49 of the die 41 and the web 49.
I will. In the embodiment shown, the axis of the inner coil spring 48 is
Up to a viscous or lubricating medium.
You. Annular containing viscous or lubricating medium
Chamber 30 in flywheel section 3 connected to the engine
And the space from the flywheel part 4 supporting the slip wear clutch
Separation in the context of wear clutches
The effect of heat generated on the viscous or lubricating medium
Will be eliminated. Further, the annular chamber 30 or the casing
An outwardly open annular passage between portion 32 and flywheel portion 4
A channel or annular gap 68 is provided
Gap 68 provides cooling in relation to vent passage 69.
Further improve the use. The ventilation passage 69 is for the clutch plate 9
Provided radially inside the friction surface 4a of the flywheel portion 4
Have been. As can be seen particularly from FIG.
It has a central notch 71 whose contour is radial
Forming a shaped part 72 which engages with the opposing shaped part 73
And the opposite molded part is connected to the flywheel part 4.
It is provided on the outer peripheral portion of the annular plate portion 27. Axial direction
Molding 72 forming a mating connection 42
Due to the shape 73, the flange 41 is connected to both casing parts.
Positioned perfectly between minutes 31 and 32,
Gap existing between the annular passage 62 and the flange 41
54 may be made significantly smaller. Moreover, fit
Due to the connection, different contact surfaces or
Can increase the axial tolerance between support surfaces
You. As can be seen in particular from FIG.
Radial inner area of the casing part 32 for sealing
And the annular plate 27 or the flywheel part 4 in the axial direction
The packing 74 is arranged between the portion 43. Packing
74 has an annular plate 75 that is elastic in the axial direction.
This is the area inside the radial direction,
43 and supported by an annular component 76 secured to
In the radially outer region of the casing part 32 in the radial direction
It is axially fixed to the inner area. Shaft similar to disc spring
Directionally deformable plate 75 has radially outer and inner
Coatings 75a, 75b, such as plastic coatings, in the area
This coating is applied, for example, by spraying.
It is. The coatings 75a and 75b have a small coefficient of friction and a low
If it has no elastic or plastic deformation
No. The radial outer edge area of the plate 75 is annular support
It is crimped tightly in the body 80. Area outside plate 75
This caulking is because the plate 75 can complete the conical deformation.
It is done to be able to. Surrounding the outer circumference of the plate 75
The area 80b of the support 80 is the radius of the casing part
Within the axial indentation 77 formed in the area inside
It is contained. For axial fixing of the outer area of the plate 75
In addition, the annular support 80 is provided inside the casing portion 32.
An edge bent area 80a that grabs the edge 32b in the radial direction
Have. The annular support 80 can be deformed into a disc spring shape
An annular pivot bearing is formed for the plate 75. An annular ring with a sealing surface cooperating with the plate 75
The component 76 is formed by connecting the end face of the additional portion 43 in the axial direction with the ring plate.
27 radially inner plate clamped axially between
Region 76a and an annular outer region 76b.
In this area 76b, a plate 75 is pressed in the axial direction.
We adhere by road. Area outside the annular component 76 in the radial direction
76b is axial to the radially inner region 76a,
Ring plate with opposed molding 73 of mating joint 42
Retracted from 27. As can be seen from FIG.
74 is the ring gear between the flywheel parts 3 and 4.
The annular chamber 30 is sealed toward the cap 68. Axial fit of both flywheel parts 3, 4
The inner diameter of the plate 75 should be radial to allow alignment
Larger than the outer diameter of the projection or the facing molding 73.
No. The annular component 7 supporting the plate 75 in the axial direction
The region 76 b of No. 6 is further outside in the radial direction than the facing molded portion 73.
Extends to the side. The fitting joint 42 and the packing 74 are
Special simple assembly of the Luc transmission device 1 is possible
You. That is, first, both flywheel parts 3,
4 is pre-assembled, and then a safety plate 2
2 by fitting in the axial direction and fixing
Are joined together. First of all, packing
74 is pre-assembled into flywheel section 3 and ball bearing 16
Is fitted to the flywheel portion 4. Both flywheel parts
When assembling 3 and 4, the inner ring 19 is
It is pressed into the step portion 20a of the shaft portion 20 in the axial direction, and
The shape part 73 is engaged with the molding part 72. In addition, both
The radius of the plate 75 when fitting the flywheel parts 3 and 4
The coating 75b of the area on the inner side faces the component 76 in the radial direction.
Abuts against the opposing sealing surface of the outer region 76b,
75 is swiveled like a disc spring and preloaded
76b. Both flywheel parts 3, 4
The final axial fixation, as already mentioned,
This is performed by fixing the safety plate 22. Next, the present invention will be described with reference to FIGS. 1, 2 and 3.
The operation of the device will be described. From the rest position shown in FIG.
When the flywheel portion 4 rotates, the flange 41 is disengaged.
It is driven via a mating connection 42, which
Inner spring 48b is between the circumferential stoppers 65 and 66
Compressed. One rotation direction or the other rotation direction
After relative rotation by the rotation angles 79, 80 at
Direction area 50 abuts end of inner coil spring 48
As a result, both additionally to the coil spring 48b
When the flywheel parts 3 and 4 rotate relatively,
The spring 48a is compressed. One rotation direction or the other
Relative rotation by rotation angles 79a, 90a in one rotation direction
Then, the outer coil spring 45 is connected to the radial arm 44.
And therefore, during subsequent relative rotation
The coil spring is radially aligned with the circumferential stoppers 55 and 55a.
And compressed between them. In the illustrated embodiment, the rotation angle
79 is the rotation angle 79a, and the rotation angle 90 is the rotation angle 90a.
Therefore, the coil spring 48a and the coil spring 48a
The spring 45 acts simultaneously. Thereby, FIG. 1 and FIG.
In the embodiment shown in FIG. 3, a two-stage spring characteristic curve results.
However, the rotation angles 79, 90, 79a, 90a are partially
Can only have the same value or have different values
You can also. Therefore, at least in both directions of rotation
Three-stage spring characteristic curve is possible or one-way rotation
Spring characteristic curve in at least two stages in the direction and the other direction of rotation
At least three stages of the spring characteristic curve are possible. As indicated by the alternate long and short dash line in FIG.
The toppers 65 and 66 are further provided with flanges of the coil spring 48.
Retracted against the spring end held in 41
In this case, between the two flywheel parts 3 and 4
The spring force over a predetermined angle around the zero position of the relative motion
Do not produce, and in some cases,
Sexual and / or frictional cushioning
Absent. In the illustrated embodiment, the coil springs 48a, 48
The common compression of b, 45 is at least the inner coil spring
48a is compressed to the contact height, so that both
It is performed until the relative rotation between the flywheel parts 3 and 4 is limited.
You. When the two flywheel parts 3 and 4 rotate relative to each other, the recess 5
2,53 face or outer core with steel band 81
The friction of the il spring 45 and the friction of the plate 75 in the region 76b
Causes frictional cushioning. Radial inner coil spring 4
8 and its radial support area also provide friction damping.
I will. Between the coil spring 45 and the radial support area.
The frictional damping depends on the rotation speed, and increases with the rotation speed.
The buffering action increases. Furthermore, it exists in the annular chamber 30
Disturbing viscous or pasty media
The compression also provides a buffering effect. In particular, it was actually closed
The viscous medium existing in the annular passage-shaped receiving portion 51 is hydraulically
This produces a viscous or viscous buffer. Because the ring
The spring receiver 59 in the channel-shaped receiving part is similar to a piston.
This is because it is used. When the outer coil spring 45 is compressed
The spring receiver 59 loaded by the arm 44 is
Toward the spring receiver that has contacted the direction stoppers 55 and 55a.
Move, thereby causing the viscous medium present in the coil spring
The body is extruded primarily through the gap 54, which resembles an iris
You. The other part of the viscous medium includes a spring receiver 59 and an annular passage.
It is pressed between the receiving parts 51 in the shape of a circle. At first push inward
The dislodged viscous medium is centrifugally acting on it.
Again, it is evenly distributed over the circumferential direction. Outer coil
What is the spring 45 of the spring receiver 59 when the load of the spring 45 is reduced?
The viscous medium on the opposite side is likewise at the spring receiver
Compressed and displaced through gap 54, acting on it
Due to the centrifugal force, the coil spring is filled again. Sticky
The buffer created by a viscous medium is a centrifugal force acting on a viscous medium.
Depends on. In other words, as the rotational speed increases, the buffer action
Increase. The viscous medium of the radially inner coil spring 48
Similarly, areas immersed in the body may become viscous or
Causes hydraulic buffering. Axial cutout in at least one spring receiver
By providing a gap 54 or a spring support
By appropriately designing the outer circumference, the viscous medium
The resulting buffering action can be varied or
It can be adapted to the respective use conditions. In addition, young
By providing a spring receiver only on the dry coil spring 45,
To adapt viscous or hydraulic buffering.
Can be. At least one inner coil spring 48
Between the spring end and the radial region 50 of the flange 44
A catch can also be provided. In particular, as can be seen from FIG.
Has a radial arm 86 on its outer periphery.
The friction clutch 7 is fixed to each arm.
There is a screw hole for fixing. Some arms 8
6 has holes for receiving pins, which are
Accurate attachment of clutch cover to component 3a during assembly
Guarantee positioning. The radial arm 86 is attached to the flywheel portion 3
Make simple structures possible. In addition, the radial
The recesses 86a between the members 86 cause the component 3
a and the cooling effect of the clutch attached to it
Be improved. Because the clutch cover and the dent 86
This is because air circulation occurs between the air circulation system and a. Further, the presence of the radial arm 86
Thus, the component 3a has an area of the friction surface 4a with a given mass.
Relatively thick, thus avoiding overheating of this area.
It is. Change in buffer action caused by viscous medium
The annular passage-shaped receiving portion 51 has at least one coil.
Constant traversal over at least a partial range of the length of the spring
Surface, which can result in areas with large cross-sections.
Slight buffering action occurs, large in areas with small cross sections
It is obtained by producing a buffer action. Of the receiving part 51
This change in cross section may be provided at any location or at multiple locations.
The end of the coil spring 45 that is not compressed
If a cross section change section or a cross section enlargement section like
Especially effective. In that case, the cross-section changes suddenly or
It may be progressive. In that case, the enlarged cross section is received
Advantageously provided in the radially inner half area of the part 51
It is. This type of cross section enlargement is indicated by reference numeral 89 in FIG.
Shown. 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 is a concave portion that limits the receiving portion 51.
It can also be obtained by appropriate shaping of the parts 52, 53
You. The charging of the viscous medium into the chamber 30 should be both.
Before assembling or fitting wheel parts 3, 4
be able to. Such at least partial of the chamber 30
Filling is done by fitting both flywheel parts 3,4.
The viscous medium through the area of the chamber 30, which is closed
It is possible by doing. In the embodiment shown in FIGS. 1, 2 and 3,
An area exists between the plate 75 and the shank 20. Pace of lubricant, grease or the like
Chamber 3 by viscous medium, which can consist of
The centrifugal force acting on the viscous medium is
That can evenly distribute it over the circumference
The flywheel parts 3, 4 are rotated up to a number. like this
According to the best method, it is possible to
Paste-like medium without or little change in state
At least with a medium without significant change in viscosity.
Filling the inside of the chamber will provide uniform distribution around the chamber 30
Or a uniform filling height is obtained,
A very accurate balancing of the device 1 to be performed is possible. The number of revolutions is 4000 to 700.
0 rpm, preferably at about 5000-6000 rpm
is there. The flywheel section 3 with the chamber is the other flywheel section
It can be balanced before assembly with minute 4. That
If the other flywheel part 4 is likewise balanced by itself
So that both flywheel parts 3 and 4 fit together
After the set, the device 1 is balanced. Both momentum
It is effective even if you balance after attaching the car part
is there. Cause sufficient distribution of the viscous medium in the room
The revolving speed is almost 4000 to 7000 r.p.
m., preferably 5000 to 6000 rpm. Jump
The skipping time is 30 seconds to 3 minutes, preferably about 1 minute
is there. Before filling the room with a flywheel or viscous medium
If heated, the number of spins and the time
Can be reduced. According to such heating, the chamber 30
The distribution of the viscous medium in the inside becomes good. The flywheel portions 3 and 4 or the entire device 1
Balancing at 400 to 2000 rpm
May be. In the apparatus 101 of the embodiment shown in FIG.
There is less on the side wall 103a of the wheel portion 103 facing the engine.
And one hole 191 is provided, and through this hole
A viscous medium such as grease may be charged into the chamber 130.
it can. After charging the viscous medium, the hole 191 is
Closed by The seal plug 192 is pressed into the hole 191.
Is entered. In the embodiment shown in FIG.
193, and a packing ring is provided in the groove 193.
194 is accommodated, and this packing ring
91 is sealed. Cover 13 for restricting chamber 130
2 is formed by a thin plate forming part,
End of the axial projection 131 by the socket coupling member 138
It is fixed to the surface. Viscosity from the chamber 130 due to centrifugal force
Rivet connection to prevent escaping media
A packing 136 is arranged radially inside the material 138.
I have. It should be the area inside the cover 132 in the radial direction.
Disc spring-like packing member 1 between the shoulder of wheel portion 104
75 is tensioned in the axial direction, and this packing member
The inside of 130 is sealed to the outside. Both flywheel portions 103 and 104 are rolled.
It is rotatably supported by a bearing 116. Mark
Reference numeral 174 indicates a disc spring.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a 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. [Description of Signs] 1 Torque transmission device, 2 flywheel, 3, 4 flywheel portion, 3a constituent members, 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 protrusion, 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

────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Wolfgang Like Baden-Buhl-Zonharde 8 Germany (56) References JP-A-63-72918 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , (DB name) F16F 15/16 F16D 3/12

Claims (1)

(57) [Claims] At least two flywheel masses mounted rotatably opposite the damping means, one flywheel mass being connectable to the engine, the other flywheel mass being connectable to the transmission, and at least one flywheel being provided. A power train, especially for vehicles, of the type in which the mass comprises a chamber partially filled with a pasty or viscous medium, in which a damping means against the relative rotation between the two flywheel masses is accommodated. In a device for damping rotational vibrations in a device, a chamber is provided which is at least partially filled with a viscous medium and receives a damper device therein. 101) before the balancing or balancing of at least the chambers (30; 13).
0) is produced by rotating the flywheel mass (3; 103) to a flipping speed capable of distributing the medium to a location as radially inward as possible of the chamber (30; 130). A device for damping rotational vibration. 2. The apparatus of claim 1, wherein the chamber is ring-shaped. 3. 3. The device according to claim 1, wherein the chamber consists essentially of a ring-shaped chamber formed by a structural part of one of the fly masses. 4. The ring chamber is formed by an outer wall surrounding the damper device and a plurality of side walls extending radially inward from the outer wall to receive the damper device therebetween. The device according to any one of the preceding claims. 5. 5. The device according to claim 1, wherein the first flywheel mass has a ring chamber. 6. One of the side walls of the ring chamber extends radially between the first and second fly masses, one between the radially inner region of the side wall and one of the fly masses. 6. The device according to claim 1, wherein a sealing member is provided. 7. One of the fly masses has an axially extending ring-shaped projection which forms the outer wall of the ring chamber and extends radially between the two fly masses of the ring chamber. The side wall portion is fixed to the protrusion,
Apparatus according to any one of the preceding claims. 8. 8. The device according to claim 7, wherein the wall is fixed to an end face of the axial projection. 9. A seal member is provided between the end face and the wall,
An apparatus according to claim 7. 10. The wall comprises a generally rigid structural member, the radially inner region of which cooperates with one sealing member provided between this region and one of the flywheel masses. Apparatus according to any one of claims 6 to 9 operative. 11. 11. The device as claimed in claim 10, wherein the sealing element comprises a single disc spring-like element fixed in the axial direction. 12. 11. An additional sealing element is provided between the axially fixed disc spring-like element and / or one of the flywheel mass and / or the rigid structural element. The apparatus according to claim 11, 13. 13. The device according to claim 1, wherein the sealing member is made of a friction material or a sliding material. 14． 14. The device according to claim 1, wherein one of the side walls of the ring chamber is formed at least in large part by a radial flange of one of the fly masses. 15. 15. Apparatus according to any of the preceding claims, wherein at least one second sealing member sealing the chamber is provided between the first and second fly masses. 16. One of the fly masses has a central pin-shaped projection in the center, which extends axially into the abutment of the other fly mass, between the projection and the abutment. 16. The device as claimed in claim 1, further comprising a bearing for the two flywheels and a second sealing member for sealing the chamber. 17． 17. The device according to claim 1, wherein the damper device acting between the two fly masses comprises a coil spring and friction means. 18. 18. The device according to claim 1, wherein the chamber is only partially filled. 19. 19. The filling amount of the viscous medium is set such that the energy storage member at least partially enters the viscous medium under the influence of the centrifugal force in the rotating state of the rotary shock reduction device. The apparatus according to claim 1. 20. 20. The device according to claim 1, wherein a damper device is provided between the flywheel mass and the viscous medium in addition to the energy storage member. 21. 3. The damper device is one fluid damper.
The apparatus of claim 0. 22. The damper device is one hydraulic damper.
The device according to 0 or 21. 23. 23. Apparatus according to any one of claims 20 to 22, wherein the damper device is a damper acting in shear. 24. 24. The device according to claim 1, wherein the viscous medium is a grease-like or paste-like medium. 25. 25. The device according to claim 1, wherein a ring-shaped gap is provided between the flywheel mass holding the friction clutch and the wall of the chamber. 26. 2. A ventilation passage is provided in the flywheel body holding the friction clutch, the ventilation passage leading to the ring chamber or being directed to the wall forming the chamber. 26. The apparatus according to any one of up to 25. 27. On the side of the bearing opposite to the grease chamber side, a seal member acting between the radially outer bearing outer ring and the radially inner bearing inner ring is provided, and the seal member is provided on one of the inner and outer bearing rings. 27. The device according to claim 1, wherein the device is non-rotatable and is initially tensioned axially toward the other of the inner and outer bearing rings. 28. The seal member cannot rotate with respect to the bearing outer ring,
And is in contact with the bearing inner ring under initial tension in the axial direction.
28. The device according to claim 27. 29. The device according to any one of claims 1 to 28, wherein a seal member is provided between at least one of the inner and outer wheels of the bearing and a structural part supporting the same. 30. 30. The seal member according to claim 29, wherein a seal member is provided between the bearing inner ring and a pin-shaped protrusion of the flywheel mass fixedly connected to the crankshaft of the internal combustion engine, which is surrounded by the bearing inner ring. apparatus. 31. 31. The device according to claim 29 or 30, wherein the sealing member is provided in the groove of the pin-shaped protrusion. 32. 32. Apparatus according to any one of the preceding claims, wherein one of the fly masses has a closable opening leading into a chamber partially filled with a viscous medium.