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
  • F16C11/00—Pivots; Pivotal connections
  • F16C11/04—Pivotal connections
  • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
  • B62D—MOTOR VEHICLES; TRAILERS
  • B62D7/00—Steering linkage; Stub axles or their mountings
  • B62D7/16—Arrangement of linkage connections
  • B62D7/166—Arrangement of linkage connections substantially perpendicular, e.g. between tie-rod and steering knuckle
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G7/00—Pivoted suspension arms; Accessories thereof
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G7/00—Pivoted suspension arms; Accessories thereof
  • B60G7/005—Ball joints
• • 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
  • F16C11/00—Pivots; Pivotal connections
• • 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
  • F16C11/00—Pivots; Pivotal connections
  • F16C11/04—Pivotal connections
  • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
  • F16C11/0604—Construction of the male part
• • 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
  • F16C11/00—Pivots; Pivotal connections
  • F16C11/04—Pivotal connections
  • F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
  • F16C11/0695—Mounting of ball-joints, e.g. fixing them to a connecting rod
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
  • B60G2204/10—Mounting of suspension elements
  • B60G2204/14—Mounting of suspension arms
  • B60G2204/148—Mounting of suspension arms on the unsprung part of the vehicle, e.g. wheel knuckle or rigid axle
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60G—VEHICLE SUSPENSION ARRANGEMENTS
  • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
  • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
  • B60G2204/416—Ball or spherical joints
• • 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
  • F16C2326/00—Articles relating to transporting
  • F16C2326/01—Parts of vehicles in general
  • F16C2326/05—Vehicle suspensions, e.g. bearings, pivots or connecting rods used therein
• • 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
  • F16C2326/00—Articles relating to transporting
  • F16C2326/20—Land vehicles
  • F16C2326/24—Steering systems, e.g. steering rods or columns
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T403/00—Joints and connections
  • Y10T403/32—Articulated members
  • Y10T403/32606—Pivoted
  • Y10T403/32631—Universal ball and socket
  • Y10T403/32672—Swiveled ball parts or seat

Definitions

• the invention relates to a joint and / or bearing assembly according to the preamble of claim 1 and a motor vehicle with one or more such joint and / or bearing assembly (s), in particular in suspension and / or steering parts.
• the pin has a parallel-walled section onto which the conical disk is pressed in such a way that a conical section of the pin can be clamped by axial tension in relation to an inclined surface of the conical disk.
• the effective for transmitting power inclined contact surface of the pin to the conical disk is very small, also results in the transition between the conical journal portion to the axial portion of the pin weakening, especially when bending stress occurs.
• the invention has for its object to achieve an improvement of the holder of the pin in the receiving opening.
• the pivot pin remains free in the power transmission area of a weak point and no pressing a sleeve must be performed in the receiving opening.
• the surrounding support is therefore only minimally stressed and can be made very thin and made of relatively soft and lightweight material, for example, a light metal casting.
• the ring body does not have to be pressed onto the pin.
• the tapered portion may have a pitch angle with respect to the axis of the pin of 15 ° to 20 ° at least in part of its axial extent and thus also allow a high axial preload.
• a pressing of the ring body on the pin or an intimate, self-locking connection is still possible if the tapered portion is stepped and formed at its end remote from the pin end an axially parallel, cylindrical portion or portion of lesser pitch.
• the region of the journal supported on the annular body, in particular a conical disk can nevertheless carry out a maximum force transmission to the conical disk without being influenced.
• a gradation on the side facing away from the journal end is harmless insofar.
• the tapered region has a variable pitch which reduces towards the end of the pin, a particularly good support against bending stress can be ensured with a simultaneous high axial prestressing.
• the slope can go without a kink in a subsequent end of the pin and, for example, parallel-walled, cylindrical area.
• annular body consists of a material of approximately the same strength as the pivot pin, the risk of plastic deformation of one of the two parts is reliably prevented.
• the acting forces and tensions can be distributed evenly between them.
• Such joint or bearing arrangements can be subjected to the axial prestress both axially and because of the large area support intense bending.
• the pin can have a thread at the end of the pin and can be prestressed defined by a corresponding nut.
• a joint arrangement according to the invention is therefore also used on highly loaded yet weight-optimized brackets of firmer parts in receiving openings softer parts, for example within chassis and / or steering parts of motor vehicles, such as in the support of parts of the suspension.
• FIG. 1 is a schematic overview drawing of a joint and / or bearing arrangement according to the invention with a pin held in a control arm and upwardly pointing pin end,
• FIG. 2 is a detail view, approximately corresponding to the section II in Fig. 1,
• FIG. 3 is a view similar to FIG. 2 before assembly of the joint shell and seal and additionally with a gradation in the conical journal section on its side facing away from the journal end, 4 shows the detail IV in Fig. 3,
• FIG. 5 is a view similar to FIG. 3, but with a continuous pitch in the conical region of the pin and with a pin end projecting beyond this section,
• FIG. 6 is a view similar to FIG. 5, but with a concave configuration of the section supported in the conical disk, FIG.
• FIG. 7 is a view similar to FIG. 6 but with the convexity of the portion supported in the cone pulley;
• Fig. 8 is a similar view as Fig. 2, but with a pin end towards greater slope in the transition to the narrower section.
• the joint assembly 1 shown in the first embodiment according to Figures 1 and 2 comprises an axially extending and here a total peg-like joint body 2 with a formed for example by a substantially spherical shape condyle 3. This can be held in a - often slotted - joint shell 4 movable , An additional seal 5 for the contact area between joint head 3 and joint shell 4 may be provided to avoid external contamination and to hold a lubricant reservoir.
• joint and / or bearing arrangements 1, 101, 201, 301, 401 according to the invention can be designed in many different ways. In any case, they include for connection between an opening 6 in a relatively soft material and a more solid body 2 an at least partially peg-shaped design of the joint or bearing body 2, 102, 202, 302, 402, in a receiving opening, here a press-in opening 6 of a control arm 7, is firmly halterbar.
• the wishbone 7 consists for example of a relatively soft aluminum, magnesium or cast iron or Schmieden material and may have around the opening 6 only a small amount of material, for example, in a thickness of only two to five millimeters, so as to extent and weight of To keep assembly as low as possible.
• Such a joint arrangement 1, 101, 201, 301, 401 can be pressed in axially with a press fit.
• the joint can be manufactured with diameter tolerances in the range of a few hundredths of a millimeter, as well as the internal dimension of the opening 6 of the female body 7.
• the joint body 2 For its firm support in the opening 6 of the particular chassis or steering part 7 of the joint body 2 according to FIG. 1 comprises at least one in the direction of the condyle 3 opposite pin end 9 tapered section 8. About this, the joint body 2 is indirectly opposite the opening. 6 supported. Since the joint body 2 can be formed considerably harder with respect to the material surrounding the opening 6, for example made of a chromium molybdenum steel, this and the opening 6 an intermediate or closed annular body 10, in particular a conical disk, interposed, both with the edge of the opening 6 and with the tapered portion 8 is in contact.
• the annular body 10 consists of a material of approximately the same strength as the pivot pin 2.
• the conical disk 10a can move in the direction of the journal end 9 over the region 8 supported on the conical disk 10a protrude or, as shown in Fig. 1, completely above its end facing the spigot end 9 17 lie. In both cases, the supported conical region 8 is only in contact with the inner walls of the opening 6 via the conical disk 10, 10a.
• a narrower and at least partially parallel and thus cylindrical or weaker tapering region 11 can adjoin the end 17 of the tapering section 8, which has a sufficiently small diameter to pass through the opening 6 even at its narrowest point and into to be able to open a thread 12 for cooperation with a nut 13 or other clamping element.
• the pin 2 can be axially biased.
• Such a joint and / or bearing arrangement 1 can counteract both radial loads, for example in guide joints, as well as axial and radial loads, for example in support joints.
• a transition 14 between the tapered portion 8 supported on the ring body and the thinner portion 11 adjoining the pin end 9 is located outside the axial extent of the ring body 10 in the direction of the pin end 9.
• the ring body 10 on its inner side can be in complete contact with the tapered section 8, resulting in a large force introduction surface which is not weakened by a bend or similar transition 14, since this transition 14 is outside the Contact surface between the annular body 10 and supported tapered portion 8 of the pin 2 is located.
• the joint arrangement 401 according to FIG. 8 it becomes clear that at the transition 14 from the supported area 8 to the narrower area 11 of the pin 402 there may also be a greater pitch, so that the area 11 does not have to taper slightly overall than the supported area 8.
• the supported in the mounted position on the annular body 10 and tapered region 8 has in a part 8a, which occupies the entire axial extent of the region 8 in the first embodiment of Figure 1 and Figure 2, a uniform pitch angle here relative to the axis 15 of the pin 2 of 15 ° to 20 °.
• the slope of the region 8 is therefore evenly rectilinear in the first embodiment, which is not mandatory, as is carried out in further embodiments.
• the joint arrangement 101 according to the second embodiment according to FIGS. 3 and 4 that, for an intimate, self-locking connection with the conical disk 110, the area 8 of the pin 102 supported thereon is graduated in a section 8a and 8b clamped axially with the conical disk at its end facing away from the pin end 9 an axially parallel portion or portion 8b lesser pitch.
• the region 8a of the pin 2 supported on the ring body 10 in particular a conical disk, can nevertheless carry out a maximum force transmission to the conical disk 10 without being influenced.
• the annular body 10 can be pressed onto the region 8b.
• a gradation 16 on the side facing away from the pin end 9 of the area 8 is harmless for the support of the pin end 9 facing region 8a.
• the tapering region 8 can also have a variable incline, as shown in FIG. 6, which reduces the end of the spigot 9, or a pitch according to FIG. 7 which increases the spigot end 9.
• the pin 302 of the joint or bearing assembly 301 is provided with a convex portion 8, correspondingly, the inner wall of the ring body 310 is formed concave in adaptation thereto.
• a sufficiently large pitch must be present in order to achieve an axial biasing on the clamping element 13 can.
• the shape of the section 8 can therefore be formed both overall hyperbolic and parabolic, with or without gradations, or in other ways, in each case a pin end-side transition 14 to the other, narrower portion 11 outside the support area 8 on the ring body 10, 110, 210, 310 is located.
• connection between the support region 8 and annular body 10, 110, 210, 310 may be formed differently, in addition to the pressing, for example, an adhesive bond may be possible. Also, the connection can be effected at loose concern solely by a seal 5.
• the outer contour of the annular body 10, 10a, 110, 210, 310 facing the inner wall of the receiving opening 6 can be shaped differently and, for example, be parabolic, hyperbolic or conical.
• the annular body 10, 10a, 110, 210, 310 need not be rotationally symmetrical in each case to the journal axis, but can, for example, in a bending stress of the joint or bearing assembly with a preferred direction of force, such as a recurrent bending only in one plane, also be elliptical or otherwise elongated designed to counteract this stress.
• the pin 2, 102, 202, 302, 402 itself can then have an adapted, for example elliptical, cross-section.
• the outer surfaces 18 of the conical disk 10, 10a, 110, 210, 310, which bear directly on the softer component 7, are conceivable in various shape, which should be given an axial and radial support depending on the requirement.
• a large contact surface is also helpful in order to selectively avoid excessive loads on the relatively soft component 7 and the risk of plastic deformation.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Transportation (AREA)
• Pivots And Pivotal Connections (AREA)
• Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
• Vehicle Body Suspensions (AREA)
• Bolts, Nuts, And Washers (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=37027726

Family Applications (1)

Country Status (10)

Families Citing this family (15)

Family Cites Families (7)

• 2005
  • 2005-06-01 DE DE102005025551.5A patent/DE102005025551C5/de active Active
• 2006
  • 2006-05-31 MX MX2007014893A patent/MX2007014893A/es not_active Application Discontinuation
  • 2006-05-31 WO PCT/DE2006/000935 patent/WO2006128436A1/de active Application Filing
  • 2006-05-31 EP EP06753217A patent/EP1886034A1/de not_active Withdrawn
  • 2006-05-31 KR KR1020077024890A patent/KR20080018864A/ko not_active Application Discontinuation
  • 2006-05-31 JP JP2008513919A patent/JP2008545929A/ja not_active Withdrawn
  • 2006-05-31 BR BRPI0611317-6A patent/BRPI0611317A2/pt not_active IP Right Cessation
  • 2006-05-31 ZA ZA200709818A patent/ZA200709818B/xx unknown
  • 2006-05-31 US US11/916,060 patent/US20080213035A1/en not_active Abandoned
  • 2006-05-31 CN CN200680019240XA patent/CN101203683B/zh not_active Expired - Fee Related

Non-Patent Citations (1)

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