Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
  • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
  • B60K17/00—Arrangement or mounting of transmissions in vehicles
  • B60K17/22—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of main drive shafting, e.g. cardan shaft
  • B60K17/24—Arrangements of mountings for shafting
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
  • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
  • F16C27/066—Ball or roller bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F1/00—Springs
  • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
  • F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
  • F16F1/387—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type comprising means for modifying the rigidity in particular directions

Definitions

• the invention relates to an elastic mounting, in particular an intermediate bearing for the Antrieos joint wel le of motor vehicles, with a rigid outer sleeve, a radial inner sleeve lying at a radial distance from this, a rubber-elastic bearing body arranged between the two and with means for changing the damping and / or stiffness properties .
• the present invention has for its object to provide an intermediate storage in which the change of stiffness and / or damping properties in different vibration levels differently and can also take place in the assembled state of the intermediate storage.
• This object is achieved in that the bearing body itself is provided with recesses distributed over its circumference, in the filler body are optionally replaceable.
• the advantage here is that the packing elements can be inserted into the bearing elements in the planes in a simple manner, to which the properties are to be changed.
• the recesses are preferably designed as openings running axially through the bearing body, in particular as cylindrical bores.
• the bores and fillers can have any cross section, e.g. Have polygon or the like, only the mutual adjustment is important.
• the fillers which are provided with heads at the ends, can be inserted into these. Due to the elastic properties of the bearing body, the recesses are widened when the bolts are pushed through.
• the middle section of the bolt corresponds to the cross section of the bore. After completely pushing it through, the bolt rests with its two end heads on the end faces of the bearing body. As a result, it is axially secured relative to the bearing body.
• the bolt advantageously has a cross section in its central cross section which is slightly larger than the bore cross section, so that the bolt is received in the bore with tension.
• the recesses are designed as a bore with two steps, namely the shape that starting from an end face of the bearing body there is a first bore step which is smaller in the opening cross section than the insertion cross section of the filling body. This is then followed by the second bore step, which has a receiving cross-section which is in corresponds approximately to that of the packing or is slightly smaller than the insertion cross section of the packing.
• the receiving space of the second bore step is dimensioned so that it corresponds approximately to the volume of the packing.
• the first bore steps have insertion openings that have a smaller cross section than the insertion cross section of the filler body and are arranged open to both end faces of the bearing body.
• the bore step which serves to accommodate the packing, is then arranged centrally in the bearing body.
• the recesses are distributed uniformly over the circumference of the bearing body.
• the recesses can also be arranged at different radial distances from the axis of rotation or the axis of the intermediate storage.
• the fillers are preferably designed as cylindrical bolts or bolts of other cross-section. However, it is also possible to form these as balls.
• the filler bodies consist of a material that has different stiffness and / or damping properties than those of the bearing body.
• the packing may consist of metal, for example. However, it is also possible to provide a plastic or a rubber which has different properties from the bearing body.
• FIG. 3 shows a longitudinal section through an intermediate store according to FIG. 2,
• Fig. 4 shows a longitudinal section through a second embodiment of the intermediate storage with stepped bore
• Fig. 5 shows a longitudinal section through a third embodiment of the intermediate storage with balls as filler.
• the cardan shaft assembly shown in Figure 1 consists of three joints 2, which are designed as universal joints.
• An elastic mounting 6 is arranged between the first joint 2 that is shown on the left in the drawing figure 1 and the middle joint 2.
• the intermediate bearing 5 is held on the pin 3 by a sleeve 4 carrying a flange.
• the flange of the sleeve 4 is rotatably connected to the flange 5 of the central joint 2.
• a profile toothing that allows displacements is arranged.
• the intermediate storage 6 and its various alternatives are explained in more detail with reference to FIGS. 2 to 5.
• the intermediate storage 6 has a rigid outer sleeve 7, which can be connected to a chassis of a motor vehicle, for example, by means of a flange-like attachment.
• An inner sleeve 8 is arranged concentrically with the outer sleeve 7.
• Outer sleeve 7 and inner casing 8 are connected to one another by a bearing body 9 arranged between the two.
• the bearing body 9 consists of a rubber-elastic material. Its basic properties are selected in accordance with the respectively required basic properties of the intermediate storage for a specific stiffness and / or damping characteristic. This also essentially applies to the shape.
• a roller bearing 10 is received in the inner sleeve 8 of the intermediate bearing 6.
• the roller bearing 10 is secured axially immovably with its roller bearing outer ring 11 in the inner sleeve 8.
• the rolling bearing 10 furthermore has a rolling bearing inner ring 12 and rolling elements arranged in between in the form of balls 13. With the rolling bearing inner ring 12, the rolling bearing 10 and thus the intermediate bearing 6 is arranged on the pin 3.
• the bearing body 9 has recesses 15 arranged distributed over its circumference. In the present example, two rows running concentrically to one another are arranged distributed over the circumference. Ie the recesses are arranged on different radii with respect to the axis of the intermediate storage. These are cylindrical through bores 15a. However, the holes can take any other shape in cross section. Bolts 14a are inserted in the bores 15a.
• the cross section of the bolts 14a has a shape which is adapted to that of the recesses 15a.
• the bolts 14a are designed as cylinder rollers and they have heads 16 at the ends.
• the axial extent of the central cylindrical region of the bolt 14a corresponds to the axial extent of the bearing body 9.
• the bolts 14a can be inserted into the corresponding recesses 15a. The selection can be made so that the damping properties in the vertical and / or horizontal plane differ from each other! are. This difference can be achieved in that either the receiving bores 15a remain free or are filled with the fillers 14a.
• fillers 14a of different characteristics can be inserting fillers 14a of different characteristics into the different bores 15a.
• a filler 14a made of metal can be used in a row of bores, while those made of a different material, for example a rubber with a harder characteristic than that of the bearing body 9, are used in another row of bores.
• the filler 14a designed as a bolt 14a with heads 16 is inserted from one end, for example from the end 17 of the bearing body 9. Such insertion can take place due to the deformability of the bearing body 9.
• the bearing body 9 can expand again and secures the filler body 14a in the bore 15a, so that it is axially immovable relative to the bearing body 9.
• the central region of the bolt 14a preferably has a cross section which is slightly larger than the opening cross section of the through hole 15a. As a result, the bolt lies with tension in the through hole 15a.
• the spring identification can thus be changed in the vertical and horizontal direction or else in any direction resulting in any direction.
• the vibration amplitude of the bearing body 9 can be limited by the choice of the assignment of the filler body 14, in particular in the plane that would show the greatest deflection due to the resulting flexion angle.
• a stepped bore is provided as a recess 15.
• the stepped bore consists of a first bore step 15b and a second bore step 15c.
• the opening cross section of the bore step 15, that is the bore step, which starts from an end face 17 or 18, is provided with a cross section which is smaller than the insertion cross section of the filler body 14b, which is designed as a cylindrical roller according to FIG.
• the central cross section, ie the cross section of the recess intended for the final reception of the filler body 14b, is designated 15c and is adapted to the cross section of the filler body 14b.
• the fillers 14b can be inserted axially from one end 17,18.
• the filling bodies 14b are pressed in by widening the first bore step 15b due to the elastic behavior of the bearing body 9.
• the bearing body 9 deforms back again.
• the filler 14b is imprisoned.
• the length of the second bore step 15c and also its cross section is matched to that of the filler 14b.
• the filler body 14b or the bore step 15c intended to accommodate it is arranged centrally.
• a radially offset arrangement is also possible, as is shown, for example, in FIG. 1.
• An advantage with regard to the provision of insertion bores 15b on both sides, that is to say those which are open to both end faces 17, 18 of the bearing body 9, is that dirt which may settle in the bores 15b, 15c during operation when inserting the filler body 14b The deposited dirt is pressed out from one end face 17 in the direction of the receiving bore 15c toward the other end face 18.
• the embodiment according to FIG. 5 differs from that according to FIG. 4 essentially only in that balls 14c are provided as packing elements.
• the bore steps 15c are correspondingly adapted to the balls 14c, so that shell-shaped seating surfaces are formed.
• the insertion bores 15b are cylindrical. From Figure 5 it can be seen that in the axial direction of the intermediate bearing 6 in the bearing body 3 receiving points 15c are provided in the form of receiving bores, one of which is centrally, i.e. in the central plane of the camp and two are offset.

Applications Claiming Priority (2)

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• 1987
  • 1987-01-23 DE DE19873701887 patent/DE3701887A1/de not_active Withdrawn
  • 1987-12-31 WO PCT/DE1987/000612 patent/WO1988005503A1/de not_active Application Discontinuation
  • 1987-12-31 EP EP88900453A patent/EP0299003A1/de not_active Withdrawn
  • 1987-12-31 BR BR8707640A patent/BR8707640A/pt unknown
  • 1987-12-31 JP JP63500832A patent/JPH02501325A/ja active Pending
• 1988
  • 1988-09-22 KR KR1019880701148A patent/KR890700763A/ko not_active Application Discontinuation

Non-Patent Citations (1)

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