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
  • 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
• • 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
  • F16F1/3842—Method of assembly, production or treatment; Mounting thereof
• • 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
  • F16F1/3863—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 characterised by the rigid sleeves or pin, e.g. of non-circular cross-section
• • 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
  • F16F1/393—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 with spherical or conical sleeves
• • 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
  • B60G2204/143—Mounting of suspension arms on the vehicle body or chassis
• • 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
  • B60G2204/41—Elastic mounts, e.g. bushings
• • 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
• • 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
  • Y10T403/32713—Elastomerically biased or backed components
• • 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
  • Y10T403/32737—Universal ball and socket including liner, shim, or discrete seat

Definitions

• the present invention relates to a joint for the elastic connection of two machine parts, in particular in vehicle construction.
• the invention relates in particular to two variants of a joint which has a claw and a housing, the claw having a central region which is encompassed by the housing and two end regions to which one of the machine parts to be connected is fastened.
• a mechanical connection In vehicle construction, it is necessary to couple all kinds of mechanical elements at an angle. Such a mechanical connection usually takes place by means of an elastic joint, in which, among other things, a spherical connecting part, which connects the corresponding mesh elements, is enclosed by a housing.
• the spherical part of the connecting piece is supported in the housing in an elastic intermediate layer.
• the housing itself is usually pressed into a bearing eye of a motor vehicle part.
• Such joints are maintenance-free because the mobility is not achieved by sliding surfaces, but by deformation of the elastic intermediate layer. Because of the spherical part of the connecting piece, such a joint is referred to as a "ball joint".
• the ball-and-socket joint consists of two metallic halves (half-shells) placed flat against one another with their flat sides, from which cap-shaped hemispherical or semi-ellipsoidal contours are embossed on opposite sides.
• the combination of these two halves results in a so-called ball piece in the middle and so-called nozzles at both ends Bores or grooves for fixing the parts to be connected elastically by means of screw connections.
• FIG. 8 shows one of these two halves, also called "claw". The possibility of attaching mechanical parts to these halves explains the term "claw" used for such a part.
• the ball piece is inserted according to FIG. 7 into a cylindrical housing and is elastically connected to it via an articulated body made of elastic material (rubber), which was introduced by means of vulcanization.
• an articulated body made of elastic material (rubber), which was introduced by means of vulcanization.
• both claws are rigidly connected to the chassis or frame parts of the motor vehicle.
• the fastening is carried out by means of screws which are inserted into the groove shown.
• the housing or housings are usually integrated in struts or handlebars which elastically connect the corresponding chassis and frame parts.
• the corresponding half-shells (claws with ball piece) must be manufactured for each length variant in accordance with the required length.
• the respective production of a length variant is complex, especially since the forged part (embossed part) has so-called stiffness jumps due to its shape, which requires high-strength steel. Machining the half-shells is not sensible for cost reasons (time-consuming, high waste, etc.).
• the object of the present invention is therefore to provide a joint according to the preamble of claim 1, which is easier to manufacture and more flexible to use.
• a joint for elastic mechanical connection of two machine parts comprising a claw and a housing, the claw having a central region which is encompassed by the housing and two end regions to each of which one of the machine parts to be connected is fastened is.
• the claw adjusts according to the invention
• the housing consists of at least two concentrically nested bushings which together define a hollow cylinder, the space between which is poured out with elastic material, so that the claw encompassed by the innermost bush relative to the other bushes of the housing is cardan, torsional and is radially and axially movable.
• the invention comprises two configurations:
• a first embodiment is that the housing consists of three concentrically nested bushings.
• Each bushing is advantageously cylindrical and as such represents a cylinder sleeve.
• the middle cylinder sleeve advantageously has openings, as a result of which the cavities between the inner and middle as well as middle and outer Cylinder sleeve are connected. It is therefore possible that the entire space between the innermost and outermost bushing can be filled with elastic material.
• a second embodiment is that the housing consists of two concentrically nested bushings.
• the outer bush is cylindrical and, as such, represents a cylindrical sleeve.
• the inner bush has two bumps in the shape of two adjacent, outwardly directed spherical segment surfaces and, as such, represents a double spherical sleeve.
• the double ball sleeve is simply a cast part and can be inexpensively e.g. made of spheroidal graphite cast iron.
• the machine parts are fixed to the claw in the area of the claw that is not covered by means of bores.
• the claw is milled planarly on both sides in the area of the claw that is not encompassed.
• (C) generating a prestress of the cooled elastic material.
• the elastic material is advantageously pressed in on the end face.
• a pretension and an exact fit for the housing to be pressed in are produced in the cooled elastic material by cold compression of the outer bush.
• the double ball sleeve is mechanically reworked to create an exact fit for the claw to be pressed in.
• FIG. 1 shows in axial and transverse cross section a first embodiment of the joint according to the invention in the non-installed state
• Figure 2 shows in axial cross section the housing of the first invention
• FIG. 3 shows an exploded perspective view of the first embodiment in the non-installed state
• FIG. 4 shows, in axial and transverse cross section, a second embodiment of the joint according to the invention in the non-installed state
• FIG. 5 shows in axial cross section the housing according to the invention of the second embodiment before calibration
• FIG. 6 shows an exploded perspective view of the second embodiment in the non-installed state
• FIG. 7 shows a perspective illustration of a joint according to the prior art in the non-installed state
• Figure 8 shows a perspective view of a half-shell of the joint shown in Figure 7.
• Figure 1 shows in axial A and transverse B cross-section a first embodiment of the joint according to the invention in the non-installed state.
• the joint is essentially rotationally symmetrical and consists of a housing 13 into which a claw 1 (connecting element) is pressed in the middle in a suitable fit 4.
• the claw 1 has no spherical surfaces, which is why it is referred to below as a cylinder piece 1.
• the term "ball joint" used in the prior art is not correct in this embodiment according to the invention.
• the joint according to the invention is therefore referred to as a cylindrical joint.
• the cylinder piece has 2 bores 3 in the non-pressed-in area, which make it possible to screw the parts to be connected elastically.
• both sides are milled at one end of the cylinder piece 10 transversely to the axis of the bore 3.
• the housing 13 consists of three concentrically nested cylinder sleeves 5, 6, 7 of different diameters. In the case of FIG. 1, the innermost cylinder sleeve 5 is the longest and the outer cylinder sleeve 7 is the shortest.
• the cylindrical cavities 8, 9 resulting from the installation geometry are filled with elastic material, preferably rubber (shown hatched).
• the middle cylinder sleeve 6 has bores 12 (openings) through which the interior of the middle cylinder sleeve 9 is connected to that of the outer cylinder sleeve 8.
• the openings 12 have a diameter of several millimeters (approx. 5 mm) and can also be oval in shape.
• the outer cylinder sleeve 7 is - like the housing of a joint according to the prior art 18 - in a bearing eye stable part of the vehicle.
• the installation consists of an HIO fit; the press-in force is approx. 60kN + 10kN.
• the cylinder piece 1 is gimbaled via which the parts to be connected which are movable can be flexibly coupled by means of the elasticity of the housing interior. With such a suspension there is radial mobility and cardanic up to 12 °. The maximum torsion of the cylinder joint is approximately 26 °.
• a cylinder joint according to the present invention requires a suitable manufacturing process which is briefly outlined below:
• the cooled elastic material After casting, the cooled elastic material must be mechanically pre-stressed so that a desired elastic behavior of the housing 13 is achieved in the cold state.
• a preload is achieved in that the outer cylinder sleeve 7 is cold-pressed from the outside in a suitable device (for example by means of press jaws), as a result of which the outer diameter is reduced by approximately 3 mm.
• the inner cylinder sleeve 5 is also cold expanded (for example by means of expanding jaws or mandrel) from the inside, as a result of which the inner diameter increases by approximately 2 mm.
• the elastic material in the interior of the housing is thus depressed, partially evades laterally and fills the recesses 11. Overall, however, the rubber receives a pretension that increases the rigidity or the elasticity of the
• Cylinder joint defined.
• the expansion and / or compression of a cylinder sleeve 5, 7 is referred to in this context as "calibration".
• FIG. 3 an exploded view of the cylinder joint is shown.
• the perspective view of the housing shows the staggering of the nested cylinder sleeves 5, 6, 7.
• the middle cylinder sleeve 6 has four bores 12 in FIG.
• the number of holes can vary. Except for the surfaces 10 milled transversely to the bores, the cylinder piece is clearly recognizable as a rotationally symmetrical component (in terms of production: as a turned part).
• the length of the cylinder piece and the spacing of the bores 3 from one another can be varied independently of the housing 13.
• the housing 13 in this embodiment is the same for all cylinder pieces 1. After the calibration of the housing 13, the cylinder piece 1 is pressed into the housing 13 with a fit and a defined press-in force. An h9 fit is used; the press-in force is approx. 60kN ⁇ 10kN.
• FIG. 4 shows in the axial C and transverse D cross section a second embodiment of the joint according to the invention in the non-installed state.
• the cylinder piece 1 is identical to the joint according to the first embodiment (ie according to the cylinder joint).
• the housing 14 into which the cylinder piece 1 is also pressed in the middle in a suitable fit 4 (h9 fit / press fit) is again rotationally symmetrical.
• the housing 14 of a joint of this embodiment has only a single outer cylinder sleeve 7, which comprises a double ball sleeve 15 made of strong material.
• the space 16 between the cylinder sleeve 7 and the double ball sleeve 15 is filled with elastic material (e.g. rubber).
• the double ball sleeve 15 has a thickness of several millimeters (approx. 6 mm) and has two bump-shaped two adjacent outwardly directed spherical segment surfaces 17.
• the double ball sleeve 15 is a cast part and, as such, does not have to have high-quality material properties, in contrast to the forged half-shell 24 according to the articulated joint.
• it makes sense to use spheroidal graphite cast iron, short name GGG-40.3.
• the outer cylinder sleeve 7 When installed, as with the cylinder joint, the outer cylinder sleeve 7 is pressed into a bearing eye with the same fit and press-in force.
• the cardanic suspension of the cylinder piece 1 takes place via the double ball sleeve 15 cast in rubber, which is why the joint according to the invention of this second embodiment is to be referred to as a "double ball joint".
• the manufacturing process is similar to that of the cylinder joint:
• the pipe socket, which represents the cylinder sleeve 7, and the cast double ball sleeve 15, which is cast on the inside and machined according to the fit, are introduced concentrically into a casting mold.
• the resulting cavity 16, which has annular recesses 11 on the end face due to the subsequent calibration, is cast under the same conditions with elastic material (eg rubber).
• a housing 14 produced in this way is shown in the uncalibrated state in FIG. 5. After cooling, only the cylinder sleeve 7 is calibrated and thus the rubber is pre-tensioned (the double ball sleeve 15 is too thick-walled to be able to widen on the inside).
• FIG. 6 shows an exploded view of the double ball joint according to the invention.
• the housing 14 consists of only two parts (cylinder sleeve 7 and double ball sleeve 15) which are elastically connected by means of the rubber compound.
• the double ball sleeve 15 as a cast part has to be reworked on the front but mainly on the inside so that the cylinder piece 1 can be fitted precisely and non-positively.
• the cylinder piece 1 itself is identical to that of the cylinder joint and, due to the construction of both joints according to the invention (cylinder joint and double ball joint), it can only be manufactured shortly before assembly in accordance with the latest structural dimensions.
• both joints Due to the different construction of the respective housing 13, 14 of the cylinder joint and double ball joint, both joints have different gimbal properties and, in this respect, cover a wide range of applications.
• the area of application is defined by the kinematic and stationary forces of the parts to be coupled in the transverse, torsional and axial directions.
• the field of application can be expanded according to the invention by producing the housing 13, 14 with different diameters of the outer cylinder sleeve 7.
• the cylinder joint can have more than three cylinder sleeves, the radii of which can additionally be varied.
• a housing with a larger diameter of the outer cylinder sleeve 7 is expected to be able to be used under higher loads.
• the present invention is characterized by the dissolution of claw 19, 24 and ball piece 20 of a joint according to the prior art into separate components.
• the claw 19, 24 is reduced to a simple cylinder piece 1; the ball piece 20 is received in a novel housing 13, 14 or its functionality is taken over or replaced by a housing 13, 14 of new construction.
• the ball joint in particular for pneumatic suspensions in commercial vehicles - is disclosed in EP 1 092 891 A2.
• the ball joint consists of two metallic halves (half-shells) 24 with their flat sides laid flat against one another, from which cap-shaped hemispherical or semi-ellipsoidal contours 20 are embossed on opposite sides.
• the combination of these two halves results in a so-called ball piece in the middle and so-called connecting pieces 19 with bores 21 or grooves 22 at both ends for fixing the parts to be connected elastically by means of
• FIG. 8 shows one of these two halves 24, also called “claw".
• the possibility of attaching 24 mechanical parts to these halves explains the term "claw" used for such a part.
• the ball piece is inserted according to FIG. 7 into a cylindrical housing 18 and is elastically connected to it via an articulated body made of elastic material (rubber) 23, which was introduced by means of vulcanization.
• Both claws are rigidly connected to the chassis or frame parts of the motor vehicle by means of the ends 19 of the two halves 24 projecting on both sides.
• the fastening is carried out by means of screws which are inserted into the illustrated groove 22.
• the housing or housings 18 are usually integrated into struts or (three-point, four-point, etc.) handlebars which elastically connect the corresponding chassis and frame parts. LIST OF REFERENCE NUMBERS

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Manufacturing & Machinery (AREA)
• Pivots And Pivotal Connections (AREA)
• Support Of The Bearing (AREA)
• Component Parts Of Construction Machinery (AREA)
• Vibration Prevention Devices (AREA)
• Springs (AREA)

Applications Claiming Priority (3)

Publications (1)

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ID=32477716

Family Applications (1)

Country Status (9)

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Citations (1)

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• 2002
  • 2002-12-16 DE DE10258986A patent/DE10258986B4/de not_active Revoked
• 2003
  • 2003-12-15 WO PCT/DE2003/004126 patent/WO2004055406A1/de active Application Filing
  • 2003-12-15 KR KR1020047020236A patent/KR20050083573A/ko not_active Application Discontinuation
  • 2003-12-15 CN CNA2003801006471A patent/CN1692237A/zh active Pending
  • 2003-12-15 BR BR0312336-7A patent/BR0312336A/pt not_active IP Right Cessation
  • 2003-12-15 MX MXPA04012964A patent/MXPA04012964A/es active IP Right Grant
  • 2003-12-15 JP JP2004559609A patent/JP2006509976A/ja not_active Ceased
  • 2003-12-15 EP EP03785574A patent/EP1573222A1/de not_active Withdrawn
• 2005
  • 2005-02-17 US US11/060,698 patent/US7165909B2/en not_active Expired - Fee Related

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