JPH028532A - Device for compensating rotational impact - Google Patents

Abstract

PURPOSE: To enhance the torque transmitting function and prolog the durable lifetime by holding a rolling bearing in such a way as not capable of moving in the axial direction on masses on which a friction clutch is supported through a disc-shaped constituent member. CONSTITUTION: Masses 3 and 4 are supported with possibility of relative rotation through a supporting mechanism 15 equipped with a single row ball bearing 16 and the inner race 19 of the ball bearing 16 is attached to a protrusion 20 on the mass 3 intruding into a notch 18 provided in the mass 4 upon extending in the axial direction from a crank shaft 5 while the outer race 17 of the ball bearing 16 is through a heat insulating material 24 into the notch 18. A coned disc spring 35 attaches a friction cylinder 37 by pressure to a disc- shaped constituent member 30, and the bearing 16 is fastened between the constituent member 30 and a shoulder 31 integrally formed with the mass 4 supporting a friction clutch and supported on the mass 4 in such a way as not capable of moving in the axial direction. This establishes improvement of the torque transmitting function and prolongation of the durable lifetime.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application 1] The present invention provides a method for absorbing rotational shocks of an engine by at least two masses rotatable relative to each other via rolling bearings against the action of a shock absorber. A device for compensating torque fluctuations, wherein one mass body is connectable to the engine and the other mass body is connectable to the input part of the power transmission device, and the damping device acts at least in the circumferential direction of a force storage member. and a friction device.

[Prior art 1] Conventionally, in this type of torque transmission device, a support mechanism is provided directly between both mass bodies, so that when a rolling bearing is used, one race is attached to one mass body, and The other race is non-rotatably coupled to the other mass.

When using this torque transmission device, the vibrations that occur between the vehicle engine and the drive system are very well damped, but because the life of the support mechanism arranged between both masses is short, this torque transmission device has not yet been widely used in automobiles. This support mechanism has a short service life due to severe use, and is the lifespan of this type of device.

C Problems to be Solved by the Invention J It is therefore an object of the invention to provide a torque transmission device which has an improved function and a longer service life compared to conventional torque transmission devices of the type mentioned at the outset, and which is particularly simple and economical to manufacture. The object of the present invention is to provide a torque transmitting device that is suitable for use.

[Means of the present invention for solving the problems] The gist of the present invention for solving the above problems is that the friction device is fixed unrotatably between the two mass bodies, also in the axial direction, to the mass body supporting the friction clutch. between the disc-shaped component and the mass connectable to the engine, the friction device comprising a friction ring and an axially preloaded force storage element; The force storage member presses the friction ring against the disk-shaped component, and the rolling bearing is tightened between the component and a shoulder integrally formed on the mass body supporting the friction clutch. Accordingly, the rolling bearing is secured in an axially immovable manner via a disc-shaped component on a mass body supporting the friction flange.

Numerous experiments have shown that the thermal energy released during operation of the friction clutch is the cause of unacceptable thermal loading of the bearing. Particularly when bearings with low bearing play are used, jamming occurs within the bearing due to differences in expansion and contraction between parts due to rapid heating and cooling. The reason for this is that when a large temperature difference occurs between the various parts of the bearing, there is no play in the bearing. The measure of the invention furthermore avoids overheating of the bearing lubricant, for example oil, grease, etc., which results in always sufficient bearing lubrication and thus increases the service life of the bearing.

It is particularly advantageous if the insulation is arranged between the support area of the second mass and the bearing.

Such an arrangement of the insulation is particularly advantageous in devices in which the support mechanism has rolling bearings. Because the second f
This is because a heat insulating material can be provided between the race, which is provided with the f11 body and is non-rotatably connected thereto, and the supporting part of this mass, which forms the seat for accommodating the bearing.

Various materials are available for fabricating insulation to prevent overheating of the support mechanism. Particularly advantageously, the insulation material can consist of plastic, optionally fiber-reinforced plastic, or ceramic material. As plastics used are duroplastics, especially phenoplastics, such as hard paper, or thermoplastics, such as polytetrafluoroethylene, polyamides or polyamides. Furthermore, the insulation material can also consist of fiber-reinforced polycarbonate.

In particular, one of the masses is provided with an axial projection which projects axially into a central recess of the other mass, and between this projection and the recess said If a bearing arrangement is provided, it is advantageous if a thermal insulation material is arranged between the central recess and the bearing. One of the masses has a central projection which projects axially into a central notch of the other mass, and a bearing mechanism is provided between the projection and the notch. If so, a second mass connected to the input of the power transmission device advantageously has a heat insulating material arranged between this projection and the bearing. It is particularly advantageous if the recess has a recess and a heat insulating material is arranged between the recess and the bearing ring which is connected non-rotatably thereto.

an inner race of the bearing is disposed on the protrusion, and
Advantageously, the outer ring is accommodated in the central recess and supports the second mass via a heat insulating material.

There are various methods for fixing the insulation to the lace, depending on the material selection. For example, the insulation material can be fixed to the bearing or the corresponding race by an injection method, a sintering method, or by pressing when it consists of a heat-insulating ring with a sleeve-like region. In another advantageous possibility of providing thermal insulation between the bearing and the corresponding mass, the outer ring is accommodated in a recess with a large diameter compared to its outer diameter, and the outer ring is connected to the recess. A bearing is premounted on one of the masses in such a way that the space between them is filled by injection or injection with plastic.

Particularly preferably, the insulation is also designed as a seal for the bearing. For this purpose, the insulation material is integrally provided with seals for the bearings.

In that case, the insulation is formed by at least one ring of cross-sectional shape, one leg of which covers and grips one of the bearing races in the axial direction,
It is also advantageous if the other leg of the ring extends radially towards the other bearing race. In that case, the radially extending leg of the cross-sectional insulation extends at least partially along the radial direction of the bearing race that is not axially covered by the insulation, and It is effective to have support from this race.

Although it is advantageous in many applications for the insulation to be formed from a cross-sectional ring whose axially extending legs extend at least approximately the full width of the race, it is advantageous in many applications when the insulation is formed from two cross-sectional rings. It is particularly advantageous if this ring is mounted on one bearing race from one side in each case.

In torque transmission devices in which the rolling bearing is accommodated in a central cutout of a mass with friction surfaces, a ring of insulating material with an angular cross-section has legs pointing radially inward in cross-section. It is particularly effective if it is held in place and housed in the outer lace.

In order to ensure an adequate sealing of the bearing, the radially extending legs of the ring made of insulation material must be loaded axially by the force storage element towards the bearing race, which is half-covered by the legs. It is particularly advantageous if the legs are crimped onto the end faces of the laces. A force storage element of this kind is advantageously formed by a spring.

When a ring of insulating material with an angular cross-section is installed in a bearing, the radial legs are elastically wired, 1 and thus the race covered radially by these legs is elastically wired. It is preferable that it be formed so that it is supported by.

When using a disc spring for loading the radially extending packing leg of the insulation, the disc spring is supported radially outwardly on a second mass connectable to the input of the power transmission device. It is particularly advantageous if the sealing ring is loaded radially inwards and axially loaded in the end region of the radial leg of the sealing ring.

For assembly, it is particularly advantageous if the insulation has a sleeve-like region that is press-fitted into the recess of the one mass that accommodates the bearing. Depending on the intended use, the insulation material is first press-fitted into the recess, or the insulation material is first attached to the bearing and then press-fitted together with it into the recess of one of the masses. It is effective to become In yet another aspect, gripping the bearing;
The sleeve-like regions of the insulation material have different thicknesses or diameters in the axial direction, so that only the regions with a larger diameter or thickness are accommodated in the bearing receiving recess by a press fit. .

When using a bearing filled with a lubricating medium, it is especially important if a seal is provided between the leg of the ring, which axially covers and grips one of the bearing races and has a cross-sectional shape, and this bearing race. Advantageously, this additional seal prevents lubricating medium from penetrating between the insulation and the raceway due to centrifugal forces, for example. A seal of this type is preferably designed as an O-ring. The seal is then supported on the inner circumferential surface of the axially extending leg of the insulation and is accommodated in a recess, for example a chamfer or groove, in the outer ring.

Advantageously, the seal is clamped between the end face of the axially extending leg of the insulation and the shoulder of the outer race.

In order to be able to easily assemble and position the same masses without any problems in connection with manufacturing tolerances, a heat insulating material with a conical or tapered cross section is provided between the support area of the second mass and the bearing. Advantageously, a ring is arranged.

In that case, the bearing and/or the support area can have a conical or tapered circumferential surface adapted to the insulation ring. automatically compensates for accidental wear,
In addition, in order to sufficiently fix and retain the bearing in its receiving hole, it is effective for the insulating ring, which has a conical or tapered cross section, to be subjected to an axial elastic force in the direction in which it becomes narrower. , whereby the insulation ring is clamped between the receiving hole and the corresponding race. To ensure sufficient tightening of the insulation ring, the insulation ring can be provided with a slit and left open.

The conical or tapered insulation ring can also have a seal for the bearing.

This seal is formed as described above and is loaded axially by means of a force accumulator towards the end face of the race supporting it.

Embodiment As can be seen from FIG. 1, the rotational shock absorber l is equipped with a flywheel 2, which is divided into two masses 3.4. The mass body 3 is fixed to a crankshaft 5 of an engine (not shown) via a fixing screw 6. mass body 4
A friction clutch 7 is fixed by means not shown. A clutch disc 9 is provided between the pressure plate 8 of the friction clutch 7 and the mass body 4, and this clutch disc 9 is attached to an input shaft 10 of a power transmission device (not shown). The pressure plate 8 of the friction clutch 7 is loaded towards the mass 4 by a disk spring 12 which is pivotably mounted on the clutch cover 11 . By operating the friction clutch 7, the mass body 4 and thus the flywheel 2 of the input shaft 10 are switched on and off. A shock absorber 13 is provided between the two mass bodies 3 and 4, and a slide latch 14 is provided in parallel therewith, both of which permit relative movement between the same mass bodies 3 and 4 within certain limits.

Both masses 3, 4 are rotatably supported relative to each other via a support mechanism I5. The support mechanism 15 includes a single row ball bearing 16. The outer race 17 of the ball bearing 16 is inserted into the notch 18 or hole of the mass body 4, and the inner race 19 extends axially away from the crankshaft 5 and projects into the notch 18 of the mass body 3. It is attached to a cylindrical central protrusion 20.

The inner ring 19 is attached to the projection 20 by a press fit and is axially clamped between the shoulder 21 of the projection 20 or of the mass 3 and the safety disc 22. The safety disc 22 is fixed to the end surface 20a of the protrusion 20 by screws 23.

A heat insulator 24 is provided between the outer race 17 and the mass 4, which interrupts the flow of heat from the friction surface 4a of the mass 4 cooperating with the crassochi disk 9 to the ball bearing 16. Or at least reduced. by this,
Overheating of the grease filling of the bearing as well as excessive thermal strain or unacceptable elongation of the bearing is prevented. may cause jamming. For receiving the insulation 24, the recess 18 in the mass 4 has a large diameter compared to the diameter of the outer ring 17, thereby creating a radial gap.

The insulation 24 is formed by two rings 2526 of cross-sectional shape, which are each attached to the outer race 17 from one side. This ring 25 has a rectangular cross section.
．． 26 leg portions 25a, 26a cover the outer race 17. The radially inwardly directed legs 25b, 26b extend partially radially along the inner race 19 and are supported axially on the inner race 19, thereby supporting the ball bearing 16.
It is also useful as a padskin. To ensure sufficient sealing of the ball bearing 16, a radially extending leg 25b.

26b are loaded in the axial direction towards the end face of the inner ring 19 by force storage elements each consisting of a disk spring 27,28. Disc springs 27 rest radially outwardly on the shoulders of a plate 30 connected to second mass 4 via spacing ports 29 and radially inwardly on the radial legs of ring 25. Loading the end region of 25b. Similarly, disk springs 28 rest radially outwardly on the shoulders of mass 4 and radially inwardly load the end regions of radial legs 26b of ring 26.

For mounting the ring 25.26 and the ball bearing 16, in the embodiment shown in FIG.
A ball bearing 16 with 6 is preferably press-fitted into the bore or recess 18 of the mass 4 . The ball bearing 16 is a ring 25
Shoulder 31 of mass body 4 and plate 30 in axial direction by interposition of 26
It is fixed immovably in the axial direction with respect to the mass body 4 by being tightened between the two.

The shock absorber 13 has two plates 30.33 arranged on either side of the flange 32, which plates 30.33 are non-rotatably connected to each other at an axial distance via a separating port 29. There is.

The separating ports 29 also serve to secure the two plates 30,33 to the mass 4. A notch is provided in the plate 30.33 and the seven flange 32, and a coil spring 34 is inserted into this notch.
A force storage member consisting of is housed. This coil spring 3
4 acts against the relative rotation between the flange 32 and both plates 30.33.

Furthermore, is the shock absorber 113 a friction device? It is equipped with 3a,
This is valid over the possible relative rotation angles between the two masses 3, 4. The friction device 13a is arranged axially between the plate 30 and the mass body 3 and has a force storage member formed by a disk spring 35, which is connected to the plate 30 and the pressure ring 36. As a result, a friction ring 37 arranged between the pressure ring 36 and the mass body 3 is tightened. Plate 3 by disc spring 35
The force acting on 0 is supported by ball bearings 16.

The flange 32 forms the input for the shock absorber 13 and also the output of the slip clutch 14. The input of the slip clutch 14 is formed by two axially spaced plates 38.39, which are non-rotatable relative to the mass. The annular plate 39 is fixed to the mass body via rivets 40. An axial tongue piece 38a is integrally formed on the outer periphery of the plate 38, and this tongue piece 38a moves the plate 3 to the plate 39.
8 is engaged in the notch 41 of the plate 39 to prevent rotation of the plate 39. A radial projection 42 of the flange 32 is clamped axially between the two plates 38,39.

For this purpose, the two plates 38, 39 are compressed together by disc springs 43. For this purpose, a disc spring 43 is supported on the mass 3 and loads the plate 38 towards the plate 39. 7. In the area between the projections 42 of the flange 32, a cutout is provided in the plate 38, 39,
This recess coincides axially and accommodates a force accumulator 44 which serves as an end stop for the projection 42 of the seven flange 32 and thereby prevents rotation of the slip clutch 14. Movement angle is limited.

In the embodiment shown in FIG. 2, ball bearings 116 are likewise used for supporting the mass 4 relative to the mass 3;
This ball bearing is arranged similarly to the ball bearing 16 shown in FIG. The outer race 117 of the ball bearing I16 has a chamfered portion 117.
a, 117b, whereby the outer race l
17 and rings 125, 126 made of heat insulating material that cover it in the axial direction.

A seal consisting of an O-ring 145, 146 is arranged in this space. The O-rings 145, 146 protect the bearing grease between the cross-sectional rings 125, 126 and the outer race 117 from extrusion or seepage. The chamfered portions 117a, 117b and the O-rings 145.146 are a ring 125.1 with a cross-sectional shape.
26 and the chamfered portions 117a, 117b of the ball bearing 116 are mutually defined so that the O-ring is elastically deformed.

As can be seen from Fig. 2, the ring 125.1 has a cross section
The thickness of the 26 radial legs 125b, 126b is reduced compared to the thickness of the axially extending legs 125a126a. In the embodiment shown in FIG. 3 in which seal noses 125c and 126c are integrally molded on the radially inner ends of the legs 125b and 126b, the seal noses 125c and 126c are formed between the notch 218 of the mass body 4 housing the ball bearing 216 and the outer race 217. A ring 225 made of a heat insulating material and having a conical or tapered cross section is disposed at. In this embodiment, both the outer circumferential surface and the inner circumferential surface of the ring 225 extend conically in the axial direction. It is also possible to form it so that only one peripheral surface extends conically.

The notch 218 is adapted to the conical outer circumferential surface of the ring 225, and the outer circumferential surface of the outer race 217 is adapted to the conical inner circumferential surface of the ring 225. The ring 225 of insulation material is loaded in the axial tapering direction by a plate spring 227, which is supported on a plate 230 which is fixed axially to the mass 4. The ring 225 has a radially inwardly extending region 225b which is axially supported by the inner race 219 of the ball bearing 216 to seal the ball bearing 2I6. Ball bearing 21
6 is provided with a ring 226 of thermal insulation material, which is connected to the disc spring 227.
The ring 226, which is axially clamped between the outer ring 217 and the shoulder 231 of the mass 4, is provided with a sealing nose 226b, which is supported axially on the inner ring 219.

In the embodiment shown in FIGS. 1 and 2, the disc spring 27,
28 is a radially extending sealing area 25.26b, 12
5b, 126b are loaded axially towards the inner race 19.119.

Depending on suitable material selection, rings 25, 26; 125
．． 126 is installed in its radial leg 25 in the state
The rings 25, 26; 125, 126 may be formed such that b, 26b; 125b, 126b are elastically deformed. This ensures that the ring is under preload in the ball bearing 16,
Race 19 out of 116. '119 is axially supported. According to this means, the disc springs 27 and 28 can be omitted.

In the embodiment described above, the heat insulating material is connected to the second mass body 4 and the ball bearing 1.
6,116,216 by an additional ring placed between them. However, in other embodiments not shown, the insulation material can also be attached to the ball bearings 16, 116, 216 or the outer races 17, 117, 217 by injection or sintering methods, in which case the insulation material It is virtually integrated with the ball bearing. Similarly, a heat insulating material can also be attached to the circumferential surface of the cutout 18, 118, 218.

When using the bearing with a packing ring, such as that provided by the bearing manufacturer, the outer ring 17 is centered and inserted into and held in the notch 18, which has a diameter larger than the outer diameter of the outer ring. It is also possible to pre-mount the ball bearing 16 on the mass body 4 in such a way that the space between it and the outer race 17 is filled with plastic or artificial resin.

[Brief explanation of the drawing]

FIG. 1 is a vertical sectional view of a first embodiment of the present invention, FIG. 2 is a partial sectional view of a second embodiment of the present invention, and FIG. 3 is a partial sectional view of a third embodiment of the present invention.
Clutch cover 12 is a partial sectional view of the embodiment.
... disk spring, 13 ... shock absorber, 14 ... slip clutch, 15 ... support mechanism 16 ... ball bearing, 17
...outer race, 18...hole, I9...inner race,
20...Protrusion, 2Qa...End face 21...Shoulder, 2
2...Safety disc, 23...Screw, 24...Insulating material, 25.26...Ring, 25a, 26a, 25b,
26b-leg, 27.28...disk spring, 29...separation bolt, 30...plate, 3J...shoulder 32...7 lunge, 33...plate, 34...coil Spring, 35...
・Disc spring, 36...Pressure ring, 37...Friction ring, 38.39...Plate, 40...Rivet 41...
・Notch, 42... Protrusion, 43... Belleville spring, 44.
... Force storage member, 117a, 117b... Chamfered portion 145
・・・○Ring

Claims (1)

[Claims] 1. A device for compensating engine rotational shocks, in particular torque fluctuations, by at least two mass bodies rotatable relative to each other via rolling bearings against the action of a shock absorber, comprising: In a type in which one mass body is connectable to the engine and the other mass body is connectable to the input part of the power transmission device, and the shock absorbing device consists of at least a force storage member acting in the circumferential direction and a friction device. , a disc-shaped component (30) in which the friction device (13a) is fixed non-rotatably between the two masses (3, 4), also in the axial direction, to the mass (4) supporting the friction clutch. and a mass body (3) connectable to the engine, the friction device comprising a friction ring (37) and an axially preloaded force storage member (35). The force storage member (35) presses the friction ring (37) onto the disk-shaped component (30), and the rolling bearing (16) connects the component (30) with the friction clutch. Supported mass body (4
), the rolling bearing (16) is tightened between the shoulder (31) integrally formed with the mass body (
4) A device for compensating rotational shocks, characterized in that it is secured immovably in the axial direction on the top. 2. The device according to claim 1, wherein the axial force generated from the force storage member (35) is received by the rolling bearing (16). 3. The friction device (13a) engages at least substantially in the radial region of the component, in which the disc-shaped component (30) axially secures the rolling bearing (16);
An apparatus according to claim 1 or 2.