JPH0563650B2 - - Google Patents

Abstract

A torque-transmitting device has means for absorbing or compensating for rotary impulses by means of at least two gyratory masses (3,4) which are arranged coaxially with each other via a bearing (15) and are rotatable with respect to each other through a limited angle against the action of a damping device (13). One of the gyratory masses (4) has a friction surface which cooperates with a clutch disk (9). In order to increase the working life of the bearing (15) and consequently also to improve the operation of the torque- transmitting device, means (18) are provided between the friction surface of the gyratory mass (4) and the bearing (15) for reducing heat flow between the friction surface and the bearing. <IMAGE>

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention is a torque transmission device for an internal combustion engine, provided with a flywheel, in which the flywheel is rotatable via a rolling bearing against the action of a shock absorber. the first mass being fixedly connectable to the output shaft of the internal combustion engine and the second mass having a friction surface for engagement with the clutch disc. The invention further relates to a friction clutch which can be fixed to the second mass for connecting and disengaging the second mass with the transmission device.

[Prior Art] Conventionally, in this type of torque transmission device, a support mechanism is provided directly between both mass bodies, and therefore, 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.

[Problem to be Solved by the Invention] The object of the invention is therefore to provide an improved function and a longer service life compared to conventional torque transmission devices of the type mentioned at the outset, as well as to be 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 that solves the problems] The gist of the present invention that solves the above problems is that a heat insulating material is disposed between the friction surface and the bearing as a means for at least reducing the flow of heat from the friction surface to the bearing. Furthermore, an additional seal is provided which engages this insulation.

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 phenomena occur within the bearing due to differential expansion and contraction between the 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. According to the means of the present invention, a bearing lubricant,
For example, overheating of oils, greases, etc. is avoided, 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. This is because a thermal insulation can be provided between the race comprising the second mass and non-rotatably connected thereto, and the supporting part of this mass forming a seat for accommodating the bearing. It is from.

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.
The plastics used are duroplastics, especially phenoplastics, such as hard paper, or thermoplastics, such as polytetrafluoroethylene, polyamides or polyamidemides. 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 heat insulating material is advantageously arranged between this projection and the bearing.

A second mass coupled to the input of the power transmission device has a central notch, and a heat insulating material is disposed between the notch and a bearing race non-rotatably coupled thereto. It is particularly advantageous if

Advantageously, the inner race of the bearing is arranged in the protrusion, and the outer race is accommodated in the central notch and supports the second mass body 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 a corresponding race by injection or sintering, 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. The 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 L-shaped cross-section, one leg of which covers and grips one of the bearing races in the axial direction; Advantageously, the other leg extends radially towards the other bearing race. In that case, the radially extending leg of the L-shaped 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 be supported by this race in the direction.

Although it is advantageous in many applications for the insulation to be formed from a ring with an L-shaped cross-section, the axially extending legs of which extend at least approximately the full width of the race, It is particularly advantageous if it consists of two rings, each of which is mounted on one bearing race from one side.

In torque transmission devices in which the rolling bearing is housed in a central recess of a mass with friction surfaces, a ring of heat insulating material with an L-shaped 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, it is necessary that the radially extending legs of the ring made of insulation material be directed by the force storage element towards the bearing race, which is covered in half by the legs. It is particularly advantageous if it is loaded in the axial direction, so that the legs are pressed against the end faces of the races. A force storage element of this kind is advantageously formed by a disc spring.

When a ring of insulation with an L-shaped cross-section is installed in a bearing, the radial legs are elastically pre-shrunk, so that the race radially covered by these legs is compressed. Preferably, it is formed to be elastically supported.

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 area that is pressed into the recess of one of the masses, which 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. is effective. In a further embodiment, the sleeve-like regions of the insulation material gripping the bearings have different thicknesses or diameters in the axial direction, so that only the regions with the larger diameters or thicknesses are provided. is accommodated in the bearing receiving recess by a press fit.

When using bearings filled with lubricating medium,
It is particularly advantageous if a seal is provided between the leg of the ring with an L-shaped cross section, which axially covers and grips one of the bearing races, and this bearing race; This prevents lubricating media from penetrating between the insulation and the race, for example due to centrifugal forces. A seal of this type is preferably designed as an O-ring. In that case, the seal is supported on the inner circumferential surface of the leg extending in the axial direction of the insulation material and is provided with a chamfer or groove, for example.
It is housed within a notch in the outer race.

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 ensure simple assembly and problem-free positioning between the two masses with regard to 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. In order to automatically compensate for accidental wear and to securely position and retain the bearing in its receiving bore, an insulating ring with a conical or tapered cross section has an axial rebound in the direction of its narrowing. Advantageously, a force is applied, 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 storage element towards the end face of the race supporting it.

[Example] As can be seen from FIG. 1, the rotational shock absorber 1 includes a flywheel 2, and the flywheel 2 is divided into two mass bodies 3 and 4. The mass body 3 is fixed to a crankshaft 5 of an engine (not shown) via a fixing screw 6. A friction clutch 7 is fixed to the mass body 4 by means not shown. A clutch disk 9 is provided between the pressure plate 8 of the friction clutch 7 and the mass body 4, and this clutch disk 9 is connected to an input shaft 1 of a power transmission device (not shown).
It is attached to 0. The pressure plate 8 of the friction clutch 7 is biased towards the mass 4 by a disk spring 12 which is pivotably mounted on the clutch cover 11. By actuating the friction clutch 7, the mass 4 and thus the flywheel 2 of the input shaft 10 are switched on and off. Between the two masses 3, 4 there is provided a damping device 13 and in parallel thereto a sliding clutch 14, both of which permit relative movement between the two masses 3, 4 within certain limits.

Both mass bodies 3, 4 are supported via a support mechanism 15 so as to be rotatable relative to each other. Support mechanism 1
5 is equipped with 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 race 19 is attached to the protrusion 20 by press fit.
and is axially clamped between the projection 20 or the shoulder 21 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 clutch disc 9 to the ball bearing 16. or at least reduced. This prevents overheating of the bearing's grease filling as well as excessive thermal distortions or unacceptable stretching of the bearing. Otherwise,
Excessive thermal strain and unacceptable elongation can cause ball 16a to jam between the inner and outer races. For receiving the insulation 24, the recess 18 in the mass 4 has a larger diameter compared to the diameter of the outer ring 17, thereby creating a radial gap.

The heat insulating material 24 includes two rings 25 having an L-shaped cross section,
26, each of which is attached to the outer race 17 from one side. The legs 25a, 2 of the rings 25, 26 are L-shaped in cross section.
6a covers the outer race 17. The radially inwardly directed legs 25b, 26b partially extend radially along the inner race 19 and are supported axially on the inner race 19, thereby securing the ball bearing 1.
It is also useful as a pack for 6. In order to ensure sufficient sealing of the ball bearing 16, the radially extending legs 25b, 26b are each fitted with a disc spring 2.
A load is applied axially toward the end face of the inner race 19 by a force storage member 7, 28. The disc spring 27 rests radially outwardly on the shoulder of a plate 30 which is connected to the second mass 4 via a standoff bolt 29 and radially inwardly on the shoulder of the ring 25.
loading the end region of the radial leg 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 rings 25, 26 and the ball bearing 16, in the embodiment shown in FIG.
The ball bearing 16 with rings 25, 26 can then be press-fitted into the bore or recess 18 of the mass 4. The ball bearing 16 is immovably fixed to the mass body 4 in the axial direction by being tightened between the shoulder 31 and the plate 30 of the mass body 4 in the axial direction by interposing the rings 25 and 26. Ru.

The shock absorber 13 has two plates 30 and 33 arranged on both sides of the flange 32.
0 and 33 are non-rotatably connected to each other via a separating bolt 29 at an axial distance. The separating bolt 29 also serves to secure the two plates 30, 33 to the mass 4. Cutouts are provided in the plates 30, 33 and the flange 32, and a force storage member consisting of a coil spring 34 is housed in the cutout. This coil spring 34 acts against the relative rotation between the flange 32 and the two plates 30,33.

Furthermore, the damping device 13 has a friction device 13a, which is effective 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 disc spring 35, which is connected to the plate 30 and the pressure ring. 36, thereby tightening a friction ring 37 arranged between the pressure ring 36 and the mass body 3. The force exerted on plate 30 by disc spring 35 is supported by ball bearing 16.

The flange 32 forms the input for the shock absorber 13 and also the output of the slip clutch 14. The input part of the slip clutch 14 consists of two plates 3 spaced apart in the axial direction.
8, 39, and plates 38, 39
is immovable relative to the mass. circular 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 engages in the notch 41 of the plate 39 to prevent rotation of the plate 38 with respect to the plate 39. There is. Both plates 3 in the axial direction
A radial protrusion 42 of the flange 32 is fitted between 8 and 39. For this purpose, the two plates 38, 39 are compressed together by disk springs 43. For this purpose, a disc spring 43 is supported on the mass 3 and loads the plate 38 towards the plate 39. Projection 42 of flange 32 and projection 4
In the area between 2 and 3, a notch is provided in the plates 38, 39, which coincide in the axial direction and accommodate a force accumulating member 44.
serves as an end stop for the projection 42 of the flange 32, thereby limiting the rotation angle of the slip clutch 14.

In the embodiment shown in FIG. 2, a ball bearing 116 is likewise used for supporting the mass 4 on the mass 3, which ball bearing 116 is arranged similarly to the ball bearing 16 shown in FIG. ing. The outer race 117 of the ball bearing 116 is provided with chamfered portions 117a and 117b, which allow the outer race 117 and the ring 12 made of a heat insulating material to cover it in the axial direction to
A space is formed between 5 and 126.
A gasket consisting of O-rings 145 and 146 is arranged within this space. This O-ring 14
5, 146 are rings 125, 126 with an L-shaped cross section
The bearing grease between the outer race 117 and the outer race 117 is protected from extrusion or seepage. Chamfered portions 117a, 117b and O-rings 145,1
46 are mutually defined so that the O-rings are elastically deformed between the rings 125, 126 each having an L-shaped cross section and the chamfered portions 117a, 117b of the ball bearing 116.

As can be seen from Figure 2, the ring 1 has an L-shaped cross section.
25, 126 radial legs 125b, 126
The thickness of the leg portions 125a and 12b extending in the axial direction is
The thickness is reduced compared to that of 6a. Legs 125
Seal nose 12 at the radially inner end of b, 126b.
5c and 126c are integrally molded.

In the embodiment shown in FIG. 3, a ring 225 made of a heat insulating material and having a conical or tapered cross section is arranged between the notch 218 of the mass body 4 containing the ball bearing 216 and the outer race 217. 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 formed on the conical outer peripheral surface of the ring 225, and the outer peripheral surface of the outer race 217 is formed on the outer peripheral surface of the ring 225.
It fits the inner circumferential surface of the conical shape. A ring 225 made of a heat insulating material is loaded in the axially tapering direction by a disc spring 227.
is a plate 23 fixed in the axial direction with respect to the mass body 4
It is supported by 0. The ring 225 has a radially inwardly extending region 225b which axially bears against the inner race 219 of the ball bearing 216 thereby sealing the ball bearing 216. In order to seal the other side of the ball bearing 216, a ring 226 of heat insulating material is provided, which, under the action of a disc spring 227, axially connects the outer ring 217 and the shoulder 231 of the mass 4. is locked between. Ring 226 has a seal nose 226b, which is connected to inner race 219.
is supported axially.

In the embodiment shown in FIGS. 1 and 2, the disk springs 27, 28 have a radially extending sealing area 2.
5, 26b, 125b, 126b are loaded toward the inner races 19, 119 in the axial direction. Depending on suitable material selection, rings 25, 26, 12
The rings 25, 26, 125, 12 are arranged such that the radial legs 25b, 26b, 125b, 126b are elastically deformed in the assembled state of the rings 25, 26, 125, 12.
6 may be formed. This allows the ring to move to the inner race 1 of the ball bearings 16, 116 under preload.
9,119 in the axial direction. According to this means, the disc springs 27 and 28 can be omitted.

In the embodiment described above, the insulation was formed by an additional ring placed between the second mass 4 and the ball bearings 16, 116, 216. However, in another embodiment (not shown), the heat insulating material may be used for the ball bearings 16, 116, 216 or
117, 217 by injection or sintering, in which case the insulation material becomes virtually integral with the ball bearing. Similarly, cut out the insulation material 1
It can also be attached to the peripheral surface of 8, 118, 218.

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

[Effects of the Present Invention] According to the present invention, the thermal load on the bearing is reduced by the heat insulating material, thereby increasing the useful life of the bearing.

[Brief explanation of the drawing]

FIG. 1 is a vertical sectional view of the first embodiment of the present invention, and the second
The figure is a partial sectional view of a second embodiment of the invention, and FIG. 3 is a partial sectional view of a third embodiment of the invention. 1... Rotating shock absorber, 2... Flywheel,
3, 4...Mass body, 4a...Friction surface, 5...Crankshaft, 6...Fixing screw, 7...Friction clutch,
8...Pressure plate, 9...Clutch disk, 10...
...Input shaft, 11...Clutch cover, 12...Disc spring, 13...Buffer device, 14...Slip clutch, 15...Support mechanism, 16...Ball bearing, 17...
...Outer race, 18...Hole, 19...Inner race, 2
0... Protrusion, 20a... End face, 21... Shoulder, 2
2...Safety disc, 23...Screw, 24...Insulating material, 25, 26...Ring, 25a, 26a, 2
5b, 26b... Leg portion, 27, 28... Belleville spring,
29...separation bolt, 30...plate, 31...shoulder,
32...flange, 33...plate, 34...coil spring, 35...disc spring, 36...pressure ring, 3
7...Friction ring, 38, 39...Plate, 40...
Rivet, 41...Notch, 42...Protrusion, 43
... disc spring, 44 ... force storage member, 117a, 11
7b... Chamfered portion, 145... O-ring.

Claims (1)

[Scope of Claims] 1. A torque transmission device for an internal combustion engine equipped with a flywheel, in which the flywheel is divided into two mass bodies rotatable via rolling bearings against the action of a shock absorber. , a first mass is fixedly connectable to an output shaft of the internal combustion engine, a second mass includes a friction surface for engagement with a clutch disc, and a second mass includes a friction surface for engagement with a clutch disc. Furthermore, in a type in which a friction clutch is fixable for connecting and disengaging the transmission device with the transmission device, the friction clutch is used as means 24, 125, 126, 225, 226 for at least reducing the flow of heat from the friction surface 4a to the bearing 15. An intermediate layer of insulation is arranged between the surface 14a and the bearing 15, and additional packings 145, 146 are provided which engage this insulation, and the insulation has a second mass. Support area 1 of body 4
8,118,218 and bearing 16,116,216
is arranged between the packing 145,
146 is the bearing 16, 116, 216 and the insulation material 2
4, 125, 126, 225, 226. 2. The torque transmission device according to claim 1, wherein the heat insulators 24, 125, 225, 226 are made of plastic. 3. One mass body is provided with an axial protrusion, this protrusion protrudes axially into a notch in the center of the other mass body, and there is a bearing between the protrusion and the notch. is placed, and the insulation material 2
4,125,126,225,226 are central notches 18,118,218 and bearings 16,116,2
Claim 1 located between
Torque transmission device as described in . 4. One mass body is provided with a pin-shaped central protrusion, this protrusion protrudes into a central notch of the other mass body, and a bearing is disposed between the protrusion and the notch. 3. The torque transmission device according to claim 1, wherein the heat insulating material is arranged between the pin-shaped protrusion and the bearing. 5 Insulating material 24, 125, 126, 225, 22
5. Torque transmission device according to claim 1, wherein 6 also serves as a seal for the bearings 16, 116, 216. 6 Insulating material 24, 125, 126, 225, 22
6 is the packing 25b, 26b, 125b, 126b, 225 for the bearing 16, 116, 216
6. The torque transmission device according to claim 5, further comprising: b, 226b integrally. 7 The heat insulating material 24, 125, 126, 225 is formed by at least one ring 25, 26 having an L-shaped cross section, one leg 2 of this ring
5a, 26a, 125a, 126a, 225a axially covers and grips one of the bearing races 17, 117, 217, and the other leg 25b, 26b, 125b, 126b, 22 of the ring
5b is the other bearing race 19, 11 in the radial direction.
9,219. Torque transmission device according to any one of claims 1 to 6, extending towards No. 9,219. 8 L-shaped cross-section insulation material 24, 125, 126,
The other leg 25b, 2 extending in the radial direction of 225
6b, 125b, 126b, 225b radially overlie at least partially the bearing race 19, 119, 219 which is not axially covered by a heat insulating material and axially cover this bearing race 1.
The torque transmission device according to claim 7, which is supported by No. 9,119,219. 9 The rings 25, 26, 12 having an L-shaped cross section
The other leg 25b, 26b, 125b, 126b, 225 extending in the radial direction of 5, 126, 225
b is loaded in the axial direction by the force accumulating member 27, 28, 227 towards the bearing race 19, 119, 219 which is radially covered by the leg. The torque transmission device according to item 7 or 8. 10. The torque transmission device according to claim 9, wherein the force storage member comprises disc springs 27, 28, 227. 11 The disc springs 27, 28 are supported on the radially outer side by the other mass 4 connected to the input part 10 of the transmission device, and on the radially inner side by rings 25, 26 made of heat insulating material. 11. Torque transmission device according to claim 9, characterized in that the end regions of the radial legs 25b, 26b are axially loaded. 12 Legs 125a and 126a of the heat insulating material having an L-shaped cross section, which cover and engage with one bearing race 117 in the axial direction, and this bearing race 11
7. The torque transmission device according to any one of claims 1 to 11, wherein packings 145, 146 are provided between the torque transmitting device and the torque transmitting device. 13 The gaskets are O-rings 145, 146
A torque transmission device according to any one of claims 1 to 12 consisting of: 14 The gaskets 145 and 146 are the insulation material 12
5,126 axially extending leg portions 125a, 12
14. The torque transmission device according to claim 12 or 13, which is supported on the inner circumferential surface of the bearing race 6a and accommodated in a notch provided in the outer bearing race 117. 15. Claim 13 or 14, wherein the packing is tightened between the end surface of the leg portion extending in the axial direction of the heat insulating material and the shoulder portion of the outer bearing race.
Torque transmission device as described in .