JP3100832B2 - Device to compensate for rotational shock - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an engine having at least two masses which are rotatable relative to each other via rolling bearings against the action of shock absorbing means. The invention relates to a device for compensating for rotational shocks, in particular torque fluctuations, in which one mass can be connected to the engine and the other to the input of the power transmission. 2. Description of the Related Art Conventionally, in this type of torque transmitting device, a bearing device for supporting both mass members is provided directly between the two mass members. Therefore, a rolling bearing is used as the bearing device. In this case, one bearing race inside or outside the bearing is non-rotatably connected to one mass and the other bearing race is connected to the other mass. According to such a torque transmission device, the vibration generated between the internal combustion engine of the automobile and the drive system is very well damped. [0003] The object of the present invention is therefore to provide an improved function and a longer service life compared to a conventional torque transmitting device of the type mentioned at the outset, as well as being particularly simple to manufacture. It is to provide a torque transmitting device that is economical. [0004] The gist of the present invention to solve the above-mentioned problem is that at least two mass bodies which can rotate relative to each other via a rolling bearing against the action of the buffer means. An apparatus for compensating for rotational shock of an engine, particularly torque fluctuation, wherein one mass body can be connected to an engine, the other mass body can be connected to an input portion of a power transmission device, and a shock absorbing means is arranged in series. A shock-absorbing device, in which case a disk-shaped structure is provided which is non-rotatable with respect to the mass supporting the friction clutch, said disk-shaped structure applying a load to the energy storage member. And it serves to axially fix the rolling bearing in the mass supporting the friction clutch. [0005] Numerous experiments have shown that the thermal energy released during the operation of the friction clutch causes an unacceptable thermal load on the bearing. Especially when a bearing having a small bearing play is used, a jamming phenomenon occurs in the bearing due to a difference in expansion and contraction generated between components due to rapid heating and cooling. The reason is that if a large temperature difference occurs between the parts of the bearing, the bearing play is lost. Due to the short life of the bearing provided between the two masses, the above-mentioned torque transmitting devices have not been widely used in automobiles in general. Since this bearing is used severely, its service life is short,
This is one of the problems of this type of torque transmission device.
Therefore, according to an advantageous embodiment of the present invention, the rolling bearing is assembled to the mass body by interposing heat insulating means for at least reducing the amount of heat flowing from one mass body supporting the friction clutch to the rolling bearing. As a result, overheating of the bearing lubricant, for example oil, grease, etc., is avoided, whereby sufficient bearing lubrication is always provided and the service life of the bearing is increased. It is particularly advantageous if the insulation is arranged between the bearing area of the second mass and the bearing. [0007] Such an arrangement of thermal insulation is particularly advantageous in a device in which the bearing mechanism comprises a rolling bearing. This is because thermal insulation can be provided between the race with the second mass, which is non-rotatably connected thereto, and the support portion of this mass, which forms the seat for accommodating the bearing. Because. [0008] Various materials are provided for the manufacture of thermal insulation to prevent overheating of the bearing mechanism. Particularly advantageously, the thermal insulation can consist of plastic, optionally fiber-reinforced plastic or ceramic material. Plastics used are duroplastics, especially phenoplastics, for example hard paper or thermoplastics, for example polytetrafluoroethylene, polyamide or polyamideimide. Furthermore, the insulation can be made of fiber-reinforced polycarbonate. In particular, one of the masses is provided with an axial projection, which projects axially into the central cutout of the other mass and which is connected to the cutout. If the bearing mechanism is arranged in between, it is advantageous if the insulation is arranged between the central recess and the bearing. One mass has a central projection, which projects axially into the central notch of the other mass,
In the case where a bearing mechanism is arranged between the protrusion and the notch, it is effective that the heat insulating material is arranged between the protrusion and the bearing. A second mass connected to the input of the power transmission has a central notch, and insulation is provided between the notch and a bearing race non-rotatably connected thereto. Is particularly advantageous. Advantageously, the inner race of the bearing is arranged on the protrusion, and the outer race is housed in the central notch and supports the second mass body through the heat insulating material. It is a target. There are various methods for fixing the heat insulating material to the race depending on the material selection. For example, the insulation is injection method,
It is fixed to the bearing by a sintering method or to the corresponding race or by means of a press when it consists of an insulating ring with a sleeve-like area. Another advantageous possibility of providing insulation between the bearing and the corresponding mass is that the outer race is accommodated in a notch having a diameter larger than its outer diameter, and the notch and the outer race The bearing is pre-mounted on one of the masses in such a way that the space between them is filled by injection or injection with plastic. [0013] It is particularly advantageous if the thermal insulation is also formed as a packing for the bearing. To this end, the thermal insulation integrally comprises the packing for the bearing. In this case, the thermal insulation is formed by at least one ring having an L-shaped cross section, one leg of which is connected to one of the bearing races.
It is advantageous if the one is axially covered and gripped by one and the other leg of the ring extends radially towards the other bearing race. In that case, the radially extending legs of the insulation having an L-shaped cross-section at least partially extend along the radial direction of the bearing race which is not axially covered by the insulation, and It is effective to be supported by this race. In many applications it is advantageous if the insulation is formed from an L-shaped ring and its axially extending legs extend at least approximately over the entire width of the race, but the insulation is L-shaped in cross section. It is particularly advantageous if it consists of two rings, each of which is mounted on one bearing race from one side. In a torque transmitting device in which a rolling bearing is accommodated in a central notch of a mass having a friction surface,
It is particularly advantageous if the ring of insulation with an L-shaped cross section has radially inwardly directed legs in cross section and is housed in an outer race. In order to ensure a sufficient sealing of the bearing, the radially extending legs of the ring of insulating material are axially moved by a storage element towards the bearing race which is half-covered by the legs. It is particularly advantageous if the load is applied in the direction, whereby the legs are pressed against the end face of the race. Such a storage element is advantageously formed by a disc spring. When the ring of L-shaped insulation is mounted on the bearing, the radial legs are elastically pre-shrunk, so that they are elastically supported by the race radially covered by the legs. It is good to be formed so that it may be performed. If a disc spring is used for loading the radially extending packing legs of the insulation, the disc spring is attached to a second mass which can be connected to the input of the drive train in a radially outward manner. It is particularly advantageous if the bearing is oriented and is radially inwardly applied axially to the end regions of the radial legs of the seal ring. For the assembly, it is particularly advantageous if the insulation has a sleeve-shaped area, which is pressed into a cutout in one of the masses which houses the bearing. Depending on the intended use, the insulation is first pressed into the notch, or the insulation is first mounted on the bearing and then pressed together with it into the notch of one of the masses. Is effective. In yet another aspect, the sleeve-like region of the insulation, which holds the bearing, has different thicknesses or diameters in the axial direction, so that only the region with the larger diameter or thickness is pressed. It is accommodated in the bearing accommodation notch by a fit. When using a bearing filled with a lubricating medium, one bearing race is axially covered and gripped,
It is particularly advantageous if a gasket is provided between the legs of the L-shaped ring and the bearing race, with this additional gasket the lubricating medium being separated from the insulation and the race by, for example, centrifugal forces. Is prevented from invading. Such packings are preferably formed as O-rings. In that case the packing is supported on the inner peripheral surface of the axially extending leg of the insulation and is, for example, a chamfer or a groove.
Housed in the cutout of the outer race. Advantageously, the packing is tightened 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 position without difficulty between the two masses in connection with simple assembly and manufacturing errors, the conical or tapered cross section between the bearing area of the second mass and the bearing. Is advantageously arranged. In that case, at least one of the bearing and the support area may have a conical or tapered peripheral surface adapted to the insulating ring. In order to automatically compensate for accidental wear and to fully fix and hold the bearing in its receiving bore, a conical or tapered insulating ring with axial rebound in its narrowing direction It is effective to be affected by force,
The insulating ring is clamped between the receiving hole and the corresponding race. In order to ensure a sufficient tightening of the insulation ring, the insulation ring can be slit open. The conical or tapered insulation ring can also have a packing for the bearing. This packing is formed as described above and is axially loaded by the energy storage element towards the end face of the race supporting the packing. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS As can be seen from FIG. 1, the rotary shock absorber 1 comprises 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. A friction clutch 7 is fixed to the mass body 4 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,
The clutch disk 9 is attached to an input shaft 10 of a power transmission (not shown). The pressure plate 8 of the friction clutch 7 is loaded towards the mass 4 by a disc spring 12 pivotally mounted on the clutch cover 11. By operating the friction clutch 7, the mass body 4 and thus the input shaft 1
The flywheel 2 of 0 is intermittent. A damping device 13 and a slip clutch 14 are provided between the two masses 3 and 4 in parallel with each other, and both allow relative movement between the masses 3 and 4 to a certain extent. The mass members 3 and 4 are supported by a support mechanism 15 so as to be rotatable relative to each other. Bearing mechanism 15
Is provided with a single row ball bearing 16. The outer race 17 of the ball bearing 16 extends into the notch 18 or hole of the mass 4 and the inner race 19 extends axially away from the crankshaft 5 and projects into the notch 18. It is mounted on a cylindrical central projection 20. The inner race 19 is attached to the projection 20 by a press fit and is axially clamped between the projection 20 or the shoulder 21 of the mass 3 and the safety disk 22. The safety disk 22 is fixed to the end face 20 a of the projection 20 by screws 23. The heat insulating material 2 is provided between the outer race 17 and the mass body 4.
4 is provided, whereby the flow of heat from the friction surface 4a of the mass 4 cooperating with the clutch disc 9 to the ball bearing 16 is interrupted or at least reduced. This prevents overheating of the grease filling of the bearing as well as excessive thermal strain or unacceptable elongation of the bearing. Otherwise, excessive thermal strain as well as unacceptable elongation will cause the ball 16a to move between the inner and outer races.
May cause jamming. For receiving the thermal insulation 24, the cutout 18 of the mass 4 has a diameter which is larger than the diameter of the outer race 17, which forms a radial gap. The heat insulating material 24 is composed of two rings 2 having an L-shaped cross section.
5 and 26, each of which is attached to the outer race 17 from one side. The legs 25 a, 26 a of the rings 25, 26 having an L-shaped cross section cover the outer race 17. Radial inward legs 25b, 26
b extends partially radially along the inner race 19 and is axially supported by the inner race 19, thereby also serving as packing for the ball bearing 16. In order to ensure a sufficient seal of the ball bearing 16, the radially extending legs 25b, 26b are
8 is loaded axially toward the end face of the inner race 19. The disc spring 27 is supported radially outwardly on the shoulder of a plate 30 connected to the second mass 4 via a bolt 29 and radially inwardly on the radial leg of the ring 25. The end area of 25b is loaded. Similarly, a disc spring 28 is supported radially outward on the shoulder of the mass 4 and loads radially inward on the end region of the radial leg 26 b of the ring 26. For the mounting of the rings 25, 26 and the ball bearings 16, in the embodiment shown in FIG. 1, the sleeve-like region of the ring is first pressed into the outer race 17 and then the ball with the rings 25, 26. The bearing 16 may be press-fit into a hole or notch 18 in the mass 4. The ball bearing 16
The ring 25, 26 is inserted axially between the shoulder 31 and the plate 30 of the mass 4 so as to be fixed axially immovably to the mass 4. The shock absorber 13 has two plates 30, 33 arranged on both sides of the flange 32.
Reference numerals 33 are non-rotatably connected to each other via bolts 29 at axial intervals. Separating bolts 29 also serve to fix both plates 30, 33 to mass 4. Board 3
A notch is provided in each of the flanges 0 and 33 and the flange 32, and a power storage member including a coil spring 34 is accommodated in the notch. This coil spring 34 acts against the relative rotation between the flange 32 and the two plates 30,33. Furthermore, the shock absorber 13 is provided with 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 3 and comprises a power storage element formed by a disc spring 35, which , Whereby the friction ring 37 arranged between the pressure ring 36 and the mass 3 is tightened. Disc spring 35
The force acting on the plate 30 is supported by the ball bearing 16. The flange 32 forms an input for the shock absorber 13 and also forms an output for the slip clutch 14. The input portion of the slip clutch 14 is formed by two plates 38, 39 provided at an axial interval, and the plates 38, 39 cannot rotate with respect to the mass body. The annular plate 39 is fixed to the mass body via rivets 40. An axial tongue 3 is provided on the outer periphery of the plate 38.
8a are integrally formed, and the tongue piece 38a is
Notch 4 in plate 39 to prevent rotation of plate 38 relative to
1 is engaged. A radial projection 42 of the flange 32 is fastened between the two plates 38, 39 in the axial direction. For this purpose, both plates 38, 39 are compressed together by a disc spring 43. The disc spring 43 bears against this by the mass 3 and loads the plate 38 towards the plate 39. In the area between the projections 42 of the flange 32, notches are provided in the plates 38, 39, which notches are aligned in the axial direction and the storage elements 4
4, and the energy storage member 44 serves as a terminal stopper of the protrusion 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 with respect to the mass 3, which is arranged in the same way as the ball bearing 16 shown in FIG. Have been. The outer race 117 of the ball bearing 116 is provided with chamfers 117a, 117b, so that a space is formed between the outer race 117 and the rings 125, 126 of insulating material which cover the outer race 117 in the axial direction. Have been. In this space, a packing composed of O-rings 145 and 146 is arranged. This O-ring 145,
146 protects the bearing grease between the L-shaped rings 125, 126 and the outer race 117 from extruding or seeping out. Chamfers 117a, 117b
And O-rings 145 and 146 are ring 1 having an L-shaped cross section.
25, 126 and chamfered portions 117a, 117 of the ball bearing 116
b and the O-ring are mutually defined so that the O-ring is elastically deformed. As can be seen from FIG. 2, the thickness of the radial legs 125b, 126b of the rings 125, 126 having an L-shaped cross section is smaller than the thickness of the legs 125a, 126a extending in the axial direction. are doing. Seal nose 125c, 126c is integrally formed at the radial inner end of the leg 125b, 126b. In the embodiment shown in FIG. 3, a ring 225 made of a heat insulating material 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, the ring 2
Both the outer peripheral surface and the inner peripheral surface of 25 extend in a conical shape in the axial direction. It is also possible for only one of the peripheral surfaces to be formed so as to extend conically. The notch 218 fits the conical outer surface of the ring 225 and the outer surface of the outer race 217 fits the conical inner surface of the ring 225. Ring 2 made of heat insulating material
25 is loaded by a disc spring 227 in the direction of narrowing in the axial direction, and the disc spring 227 is supported by a plate 230 fixed in the axial direction to the mass body 4. Ring 22
5 is provided with a region 225b extending radially inward, which region extends axially in 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 thermal insulation is provided which is axially acted on by an outer race 217 by the action of a disc spring 227.
And the shoulder 231 of the mass 4. The ring 226 has a seal nose 226 b which is axially supported by an inner race 219. In the embodiment shown in FIGS. 1 and 2, the disc springs 27, 28 are provided with radially extending sealing regions 25, 26.
b, 125b, 126b in the axial direction with inner races 19, 11
It is loading towards 9. Depending on the appropriate material selection,
When the rings 25, 26; 125, 126 are assembled, their radial legs 25b, 26b;
6b are elastically deformed so that the rings 25, 26;
126 may be formed. This allows the rings to move under preload to the inner races 19, 119 of the ball bearings 16, 116.
Is supported in the axial direction. According to this means, the disc spring 27,
28 can be omitted. In the embodiment described above, the thermal insulation was formed by an additional ring arranged between the second mass 4 and the ball bearings 16, 116, 216. But,
In another embodiment, not shown, the heat insulating material is provided by ball bearings 16 and 11.
6,216 or outer races 17, 117, 217 by injection or sintering, so that the thermal insulation is virtually integral with the ball bearing. Similarly, a heat insulating material can be attached to the peripheral surfaces of the notches 18, 118, 218. When using a bearing with a packing ring, as provided by the bearing manufacturer, the outer race 1
7 is inserted and held in a notch 18 having a diameter larger than the outer diameter of the outer race 17.
It is also possible to pre-attach the ball bearing 16 to the mass body 4 such that the space between them is filled with plastic or artificial resin.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal 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. FIG. 3 is a partial sectional view of a third embodiment of the present invention. [Description of Signs] 1 Rotary 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 shock absorber, 14 slip clutch, 15 bearing mechanism, 16 ball bearing, 17
Outer race, 18 holes, 19 Inner race, 20
Projection, 20a end face, 21 shoulder, 22 disk, 23 screw, 24 insulation, 25, 26 ring, 25a, 26a, 25b, 26b leg, 2
7,28 disc spring, 29 bolt, 30 disc-shaped structural part, 31 shoulder, 32 flange, 33
Plate, 34 coil spring, 35 disc spring, 36 pressure ring, 37 friction ring, 38, 39 plate,
40 rivets, 41 notches, 42 protrusions, 4
3 disc spring, 44 energy storage member, 117a, 117b
Chamfer, 145 O-ring

──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Wolfgang Like Baden-Buhl Amalie-Muller-Strasse 20 Germany (56) References JP-A-2-8532 (JP, A) JP-A 10-227335 (JP, A) (58) Field surveyed (Int. Cl. ⁷ , DB name) F16F 15/131 F16F 15/134 F16F 15/139 F16F 15/30

Claims (1)

(57) [Claims] A device for compensating for rotational impact of an engine, particularly torque fluctuations, by at least two masses which can rotate relative to each other via rolling bearings against the action of a shock absorbing means, wherein one mass is attached to the engine. , The other mass body can be connected to the input portion of the power transmission device via a friction clutch , and two shock absorbers (1) in which shock absorbers are arranged in series.
3,14) includes a, so as not to rotate the disk-shaped structural part (30) is provided on the mass body support this case friction clutch (4), the disc-shaped structural parts (30 ) Is a power storage member as a shock absorber (13, 14)
With loading the fixed rolling and have contact to the mass supporting the friction clutch (7) (4) bearing (16) in the axial direction
And wherein the are, apparatus for compensating a rotational shock. 2. The rolling bearing (16) is a disk-shaped structural member (3
2. The device as claimed in claim 1, wherein the friction clutch is clamped between a shoulder and a shoulder provided on the mass supporting the friction clutch. 3. Rolling bearing (16) has its inner race (19)
Through a shoulder (21) of a pin-shaped projection (20) provided on a mass body (3) connected to the engine and an end face (20a) of the projection (20). Characterized in that it is fixed between the disk (22).
3. An apparatus for compensating for rotational impact according to claim 1. 4. 4. The rolling bearing according to claim 1, wherein the rolling bearing is interposed with heat insulating means for reducing at least the amount of heat flowing from the mass supporting the friction clutch to the rolling bearing. An apparatus for compensating for rotational impact according to any one of claims 1 to 7. 5. Insulating means and rolling bearings, disc-shaped structure portion (30), the friction equipment is provided on the opposite side, and is made of a heat insulating ring it said insulating means has an L-shaped cross section, heat insulating The ring is a disc-shaped structural part (3
0), mass (4) in Ri Contact is written clamped between the formed shoulder (31), each one of the legs of the adiabatic ring (2
5a, 26a) is bearing surrounds the bearing outer race (17)
The other extending outer race (17) to engage with and and radially inwardly, respectively, characterized in that the legs (25b, 26b) are for the race in the bearing (19), according to claim An apparatus for compensating for rotational shock according to any one of claims 1 to 4. 6. Legs facing inward in the radial direction (25b, 26b)
6. The device for compensating for rotational shocks according to claim 5, characterized in that the bearings are in airtight contact with the inner race (19). 7. A device for compensating for rotational impact of an engine, particularly torque fluctuation, by at least two masses that can rotate relative to each other via rolling bearings against the action of a shock absorber, wherein one mass is attached to the engine. And the other mass body is connectable to an input portion of a power transmission device via a friction clutch , and the shock absorbing device comprises a power storage member acting at least in a circumferential direction.
In order fixed in the axial direction to the mass body 6) supports the friction clutch (4), the mass body for supporting the friction clutch (the shoulder provided 4) (31), the mass for supporting the friction clutch Inability to rotate with respect to body (4) via shape connection
Bearing outer rail between the disc-shaped structural part (30) is
The engine is tightened and the mass connected to the engine
Et al., The driven shaft of the engine (5) and Ri Contact with the race in the bearing is received in the shoulder <br/> protrusion protruding in the opposite direction (20),
Metals sheet (22) screwed portion (23) Ri Contact is coupled to one of the mass body (3) via, in edge region of the outer said sheet metal (22) extends in the radial direction, The inner race (19) is connected to the protrusion (2) of the one mass body (3).
0), characterized in that you are fixed on an apparatus for compensating a rotational shock. 8. A device for compensating for rotational impact of an engine, particularly torque fluctuation, by at least two masses that can rotate relative to each other via rolling bearings against the action of a shock absorber, wherein one mass is attached to the engine. And the other mass body is connectable to an input portion of a power transmission device via a friction clutch , and the shock absorbing device comprises a power storage member acting at least in a circumferential direction.
In order fixed in the axial direction to the mass body 6) supports the friction clutch (4), the friction and mass body provided with a shoulder for supporting the clutch (31), the shock absorber energy storing member (34) rolling bearing is characterized that you are written clamped between the radially inwardly through shape connection (29) non-rotatably fixed disk-like structure portion to the masses (30) A device that compensates for rotational shock. 9. 9. A rotary bearing according to claim 7, wherein the rolling bearing is interposed and fitted with heat insulating means for reducing at least the amount of heat flowing from the mass supporting the friction clutch to the rolling bearing. A device that compensates for impact. 10. A device for compensating for rotational shocks, in particular torque fluctuations, of an engine by means of at least two masses which can rotate with respect to each other via rolling bearings against the action of the damping means, one mass being provided to the engine and the other being provided to the other. A disk-shaped structural part (30) that can be connected to the input of the power transmission via a friction clutch and that cannot rotate with respect to one of the weights (4) supporting the friction clutch (7)
Are provided, and the disk-shaped structure portion (30) is loosened.
With loading the energy storing member (34) which forms the collision means, it has been fixed in the axial direction rolling the mass supporting the friction clutch (7) (4) bearing (16), rolling bearing (1
6) is characterized in that heat insulating means (25, 26) for reducing at least the amount of heat flowing from the mass body (4) supporting the friction clutch (7) to the rolling bearing (16) is interposed and assembled. A device that compensates for rotational shock. 11. Insulating means (25, 26) is a disk-shaped structural part (30), was written clamped between the shoulder formed in the mass body (31), at least one cross-sectional with a L-shaped cross-section <br The heat insulating ring (25, 2).
6), one of the legs (25a, 26a) surrounding the outer bearing race (17) and engaging with the outer bearing race , and the other leg (25b, 26) facing radially inward.
Device according to claim 9 or 10, characterized in that b) is directed to the inner race (19). 12. Legs facing inward in the radial direction (25b, 26
12. The device according to claim 11, wherein b) is in airtight contact with the inner race (19). 13. 13. The device according to claim 11, wherein the radially inwardly facing legs of the heat-insulating means apply a spring load to the bearing inner race. 14． 14. The device according to claim 13, wherein the spring load is provided by a disc spring. 15. 15. A ring packing is provided between the outer race and the heat insulating means.
An apparatus for compensating for rotational impact according to any one of the preceding claims.