WO2004067357A1 - Boitier de direction a cremaillere pour vehicule automobile et module palier a cet effet - Google Patents

Boitier de direction a cremaillere pour vehicule automobile et module palier a cet effet Download PDF

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Publication number
WO2004067357A1
WO2004067357A1 PCT/EP2004/000736 EP2004000736W WO2004067357A1 WO 2004067357 A1 WO2004067357 A1 WO 2004067357A1 EP 2004000736 W EP2004000736 W EP 2004000736W WO 2004067357 A1 WO2004067357 A1 WO 2004067357A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
spring
bearing module
pressure
rack
Prior art date
Application number
PCT/EP2004/000736
Other languages
German (de)
English (en)
Inventor
Friedhelm GÜNTHER
Original Assignee
Schmitterchassis Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schmitterchassis Gmbh filed Critical Schmitterchassis Gmbh
Priority to DE112004000167T priority Critical patent/DE112004000167D2/de
Publication of WO2004067357A1 publication Critical patent/WO2004067357A1/fr

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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
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/34—Ring springs, i.e. annular bodies deformed radially due to axial load
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D3/00—Steering gears
    • B62D3/02—Steering gears mechanical
    • B62D3/12—Steering gears mechanical of rack-and-pinion 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/02—Sliding-contact 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/12—Arrangements for adjusting play
    • F16C29/126—Arrangements for adjusting play using tapered surfaces or wedges
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H57/022—Adjustment of gear shafts or bearings
    • F16H2057/0222—Lateral adjustment
    • F16H2057/0224—Lateral adjustment using eccentric bushes
    • 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/26—Racks
    • F16H55/28—Special devices for taking up backlash

Definitions

  • the invention relates to a bearing module for a motor vehicle steering gear with a rack and drive pinion in engagement therewith.
  • the bearing module has at least one pressure ring with a receiving bore, the bore wall of which runs eccentrically with respect to the outer circumference of the pressure ring and / or an imaginary central axis of the rack and surrounds a guide passage for axially guiding the rack. Starting from the bore wall, radial forces can be generated for the pressure of the rack received in the guide passage on the drive pinion engaging therein.
  • the invention relates to a motor vehicle steering gear with such a bearing module, the guide passage of which comprises the toothed rack which engages with the drive pinion within a gear housing.
  • the rack bearing from at least one annular element and at least one eccentric bearing shell.
  • the eccentric bearing shell is composed of two parts, of which at least one part has an elastomer layer or a spring element. Furthermore, the eccentric bearing shell is also intended to be a mechanical stop Form the limit of the insertion into the gearbox used for assembly.
  • the eccentric bearing shell is placed on a housing inner wall, which concentrically or symmetrically surrounds the rack passage with its central axis.
  • the invention has for its object to provide a robust, insensitive to external shocks rack mounting and guidance for steering gear, which is characterized by a simplified assembly without the need for additional, manual settings.
  • the bearing module specified in claim 1 and the motor vehicle steering gear specified in claim 27, provided with the specified bearing module are proposed.
  • a complementary pressure piece which can be integrated into the bearing module according to the invention as claimed in claim 20. Further advantageous configurations result from the dependent claims.
  • an elastic buffer can be created between the eccentric receiving bore of the pressure ring and the rack, which is exposed to impacts introduced via the roadway and the vehicle wheels.
  • the guide parts can be radially adjusted according to the invention, they can be displaced during assembly with simple handling and without the need for subsequent adjustment against the spring forces so that the wall of the bore of the eccentric pressure ring based on radial forces inward to push the rack onto the pinion.
  • the rack can be used during assembly as a means to radially adjust the guide parts according to the eccentricity and thus adjust the spring biasing force.
  • the spring constant or characteristic and the degree of eccentricity can be matched to one another in the sense of a specified preload so that further adjustments or adjustments are no longer required in the subsequent assembly in the steering gear housing.
  • the guide part or parts are arranged symmetrically or concentrically with respect to an imaginary line of symmetry or central axis (expediently running through the guide passage) or also symmetrically or are designed concentrically. It can thus be achieved that only symmetrical or regularly shaped and thus easier to manufacture components are required for the guide part (s), which reduces the manufacturing outlay.
  • at least one inner ring is arranged as a guide part within the eccentric receiving bore of the (outer) pressure ring and is resiliently supported on the bore wall thereof via one or more radially oriented, elastic pressure elements.
  • the inner guide ring can be made rotationally symmetrical and thus be easy to manufacture in terms of production technology.
  • the resilient support or the elastic pressure element or elements are realized by one or more, radially deflectable spring ring elements. These can then be arranged parallel to the eccentric inner circumference of the pressure ring and / or in contact with the wall of the bore around the guide part or parts.
  • the pressure ring on one or both end faces has a plurality of radially inwardly projecting holding shoulders or elements for axially holding the guide part or parts.
  • the bearing module to be manufactured as a compact, stable, self-contained component that can be assembled quickly and reliably and that can be easily stored and handled independently of the other steering gear.
  • the axial holding of the guide parts is expediently implemented with play in order to prevent jamming.
  • the assembly handling and safety can be facilitated by an advantageous embodiment of the invention, according to which the outer jacket of the pressure ring is designed with one or more axial or axially parallel stop shoulders or ramps.
  • these stop elements When such a bearing module is inserted axially into a steering housing, these stop elements then serve as insertion limits when they encounter counter-stop shoulders on the inner wall of the steering gear housing.
  • the eccentric pressure ring forming a wedge bearing must be rotatably mounted in the housing so that the eccentric section bears against the toothed rack side which lies opposite the teeth by means of a rotary setting.
  • This requires additional, time-consuming assembly and adjustment activities of high skill.
  • an advantageous embodiment of the invention is proposed, according to which the outer casing of the pressure ring is provided with one or more, axially parallel orientation projections and depressions. These can then come into engagement with complementary recesses or elevations in or on the inner wall of the transmission housing when it is inserted into a steering gear housing during assembly.
  • This mutually intermeshing, rail-like guide is positioned in the circumferential direction (with respect to the rack or housing center axis) such that when assembled with the rack and the drive pinion engaging in it Housing which are directed at the wall of the bore with eccentric thickening pressure forces on the outside of the rack or that rack outer shell section, which or which are diametrically opposed to the teeth of the rack meshing with the drive pinion.
  • the correct orientation of the eccentric section of the pressure ring namely opposite the tooth side of the rack, can be brought about quickly, easily and reliably.
  • the preassembled bearing module is expediently only axially pressed into the gearbox or main housing when the toothed / piston rod, expediently in engagement with the drive pinion, has already been inserted into the housing beforehand.
  • the arrangement according to the invention is characterized in that the central axis and / or the axis of symmetry of the guide part or parts of the bearing module coincide with that of the rack and / or the transmission housing tube and are offset eccentrically with respect to the central axis of the pressure ring receiving bore.
  • the guide part or parts, in particular the inner ring are radially displaced from their position concentric with respect to the receiving bore before assembly by approximately the amount of the eccentricity applied by means of the toothed rack to the eccentrically thickened section of the pressure ring.
  • a range between approximately 0.1 to 0.8 mm or 0.2 to 0.6 mm has proven to be a useful measure of eccentricity between the central axis of the toothed rack and the central axis of the pressure ring receiving bore.
  • the radially outer pressure ring which surrounds the guide parts, from several individual parts. This enables the advantage of increased application flexibility with regard to different requirements and operating conditions to be achieved. In the case of the ring-like configuration, its individual parts can then easily be replaced by other individual parts that are specially tailored to the specific application.
  • the pressure ring is provided with at least one cutout, opening and / or interruption, in which at least one complementary supplementary pressure piece can be used.
  • This is designed to bear against the or at least one of the guide parts in order to reduce its residual play.
  • the or at least one of the guide parts is provided with a contact surface which is assigned to the pressure piece and which runs obliquely in a wedge-like manner with respect to a central axis or axially parallel longitudinal direction or line of symmetry of the guide passage such that a self-locking or self-locking locking of the adjacent pressure piece occurs in the axial passage direction.
  • This effect is based on the effect of self-locking known per se in mechanical engineering if the wedge or pitch angle is smaller than the effective friction angle, that is to say if the wedge-like pressure gap cannot jump out of the notch, which in the present case is due to the oblique guide part - Contact surface is formed on the one hand and by the inner wall of the gear housing on the other.
  • an angle of inclination of 4 ° to 8 °, for example 6 °, in relation to the central axis or the longitudinal direction parallel to the axis or the line of symmetry of the guide passage has proven itself for the wedge-like contact surface.
  • the complementary pressure piece can rest on one or at least one of the elastic pressure pieces or spring elements.
  • a complementary pressure piece according to the invention is characterized by a shape with two side sections which follow one another at an obtuse angle and which can be used for bearing against the or one of the guide parts and / or against the or one of the elastic pressure elements.
  • the two side sections which adjoin one another at an obtuse angle, jointly lie opposite one side of the pressing piece, with which they each enclose acute angles. Areas between 15 ° and 45 ° (for example 30 °) or 4 ° and 8 ° (for example 6 °) have proven useful for the latter.
  • the complementary pressure piece according to the invention with orientation projections and / or is provided according to an advantageous option
  • edge-side projections or indentations lie in a plane or circumferential surface that is common to the opposite side.
  • a simple and inexpensive way of producing the complementary pressure piece is by plastic injection molding.
  • the spring ring elements mentioned above are radially and eccentrically compressed when the bearing module is installed in the gear housing via a circular piece or an arc which, seen in the radial direction, is congruent with the outside of the rack or the outer casing section and / or this outer side or this outer jacket section extends in parallel, which is diametrically opposite the teeth of the rack.
  • the bearing module is arranged in an end region of the gearbox housing in such a way that the pressure ring with an end face facing the housing end region has a stop surface for realizing a steering stroke. Limit can form, for example, with respect to an adjacent tie rod joint.
  • the end face mentioned it is expedient for the end face mentioned to be of the largest possible area. This can be done by means of an annular shoulder projecting radially inwards, which then engages behind the guide part or parts and fixes them axially, preferably with play.
  • the disadvantage is that the length in the circumferential direction of a helical or spiral spring could lengthen or shorten depending on the radial interaction or expansion. Accordingly, in the case of a closed ring shape, the circumference must lengthen or shorten or the diameter must widen or decrease.
  • the spring ring elements are enclosed between the pressure ring and the inner ring.
  • the spiral or helical turns of a screw spring ring element would rub and / or skew on the inner wall of the correspondingly formed annular chamber between the pressure ring and the inner ring during the radial compression or separation.
  • a helical or spiral spring closed in the manner of a ring can easily block in the bearing module according to the invention.
  • the linearity of the resulting spring characteristic would not be guaranteed.
  • the spring ring element specified in claim 42 is proposed, which is characterized by a design with a plurality of elastic spring members, which are ring-shaped and are connected in a ring to form the spring ring element.
  • the spring ring element is thus designed to form a spring ring chain with individual spring links.
  • Each of these, independently of adjacent circular spring members, can expand or decrease in circumference without the length in the circumferential direction of the spring ring element thereby changing. Protection of the invention is hereby reserved for such a specially designed spring ring element.
  • Advantageous, optional designs of this spring ring element according to the invention result from the dependent claims 43-53.
  • the ring-like basic shape is designed with an opening or ring interruption, in particular in the manner of a C-shape. Their opposite opening ends can be adjusted to or from each other depending on the radial load.
  • the opening forms a "mouth", so to speak, which can be opened and closed in an elastically deflectable manner.
  • This effect is further promoted in that, according to a further embodiment, the ring openings of the spring members resulting from the C-shape are aligned parallel to the central axis of the entire spring ring element, The radial compressive and tensile forces can then be directed completely to the C-shaped body of the spring element.
  • the last-mentioned point of view serves a further development of the invention, according to which connecting webs between two adjacent, connected spring members extend from the ends of the C-type spring member, which delimit the respective openings.
  • the openings can narrow or widen without the connecting webs having to be deformed in the spring ring element circumferential direction or axially parallel to the individual spring C spring members.
  • FIG. 1 shows a steering gear housing in a longitudinal view
  • FIG. 2 shows a sectional view along line A-A in FIG. 1, but in the fully assembled state
  • FIG. 3 shows a sectional view along line BB in FIG. 1
  • FIG. 4 shows the detail IV outlined in FIG. 2, namely the longitudinal section of the storage module according to the invention
  • FIG. 5 shows the bearing module according to the invention before assembly without a tube or main housing in cross section analogous to the section line VI-VI in FIG. 4,
  • FIG. 7 shows an end view of a blank for a steel spring ring according to the invention
  • FIG. 8 shows a sectional view along the line VIII-VIII in FIG. 7 after the blank has been formed in accordance with FIG. 8a
  • FIG. 8a shows a perspective illustration of the steel spring ring according to FIG. 8,
  • FIG. 9 shows a force-displacement diagram for O-rings (70
  • FIG. 10 shows a further embodiment of the bearing module or steering gear according to the invention in a section-wise, axial longitudinal section
  • FIG. 11 shows a sectional view along line XI-XI in FIG. 10,
  • FIG. 12 shows an enlarged illustration of detail XII in FIG. 10,
  • FIG. 13 shows a longitudinal view in the radial direction of the outer casing of the pressure ring with a complementary pressure piece with the gear housing cut open, Figure 14-18 each in an axial longitudinal view of the respective state of the steering gear housing after individual assembly steps
  • the steering gear has a tubular rack main housing 1, on the outer jacket of which a tubular pinion housing 2 is also attached obliquely or transversely. This is closed at one end with a bearing ring 3 like a lid.
  • the wall of the main housing 1 is penetrated by holes 10, to which connection pieces for hydraulic oil can be attached in the case of hydraulic steering.
  • the invention can also be used for electric steering.
  • the other end of the pinion housing 2 is expanded radially outwards to form a flange 4 for further connection purposes (for example connection or installation of a hydraulic valve).
  • fin-like fastening brackets 5 are connected to the outer casing of the main housing 1, through which sleeves 6 provide a passage for fastening means transversely to the axial or longitudinal direction.
  • a rack 11 penetrates within the main housing 1 at the left end of the drawing the bearing module 7 according to the invention, which is designed as a fully assembled combination part, in the central region where a molding is applied (cf. DE patent application 101 01 717.0), a seal holder 8 and in the right end area in FIG. 2, a toothed / piston rod guide bearing 9.
  • the respective end faces of the bearing module 7 and the guide bearing 9 facing the main housing ends are designed or used as stop faces 12 (so-called lockstop) in order to control the steering stroke in connection with the Limit tie rods 13.
  • the main housing end regions are designed with radial widenings 13a in order to form a stop shoulder 13b for the axial insertion limitation of the bearing module 7 and the guide bearing 9. Furthermore, the ends are covered in a manner known per se with bellows 14 through which the tie rods 13 are guided.
  • a drive pinion 15 extends obliquely or transversely to the toothed piston rod 11 (and to the plane of the drawing) and engages with the toothing region 16 of the toothed / piston rod 11.
  • the bearing module 7 is designed with a pressure ring 71, which is pressed into the main housing tube 1 up to the stop shoulder 13b.
  • the outer casing of the pressure ring 71 is designed with a radial extension 71a which is complementary to the shape of the stop shoulder 13b of the housing wall.
  • the pressure ring 71 forms a receiving bore 76, in which an inner ring 72 and two circumferential spring ring elements 74 are received.
  • the inner ring 72 serves as a guide component for the toothed rack 11 and is provided on its inner circumference with a guide bushing 75 attached to it for its sliding bearing.
  • the two spring washers 74 inserted axially one behind the other in outer grooves 77 of the inner ring 72 are circumferentially arranged between these outer grooves 77 or the inner ring 72 on the one hand and the pressure ring 71 or the bore wall 78 on the other hand.
  • the inner ring 72 is permanently axially fixed on the one hand by means of a locking ring 73 which is placed on a first end face of the inner ring 72.
  • the latter is permanently fixed axially by a front edge 79 of the pressure ring 71 which is bent by means of flanges. This engages behind the locking ring 73 on its end face facing away from the inner ring 72.
  • a holding shoulder 80 is used, which is formed on the end face of the pressure ring 71 facing the end of the main housing 1 and projects radially inward and engages behind the directly opposite end face of the inner ring 72.
  • a small axial play for example 0.05 to 0.1 mm.
  • the holding shoulder 80 of the pressure ring 71 also forms on its outside a stop surface or a fixed stop 80a for the steering stroke of the rack with a tie rod 13 attached to it via a joint 17.
  • the pressure ring 71 is designed to be eccentric to the extent that the central axis 81 of the receiving bore 76 does not coincide with the central axis 82 of the external pressure ring diameter 83.
  • the inner and outer diameters of the pressure ring 71 do not run concentrically to one another, rather there is an eccentricity between the two, the dimension e of which is between 0.2 mm and 0.6 mm, for example can be.
  • the spring ring 74 resting against the bore wall 78 of the pressure ring 71 is in the undeflected or in the relaxed initial state if, according to FIG. 5, the bearing module 7 has not yet been pressed into the steering gear main housing 1.
  • the spring ring 74 extends with its outer and inner circumference concentrically to the central axis 81 of the pressure ring receiving bore 76 and eccentrically to the central axis 82 of the outer diameter of the pressure ring 83.
  • the inner ring 72 and the guide bushing 75 fastened to its inner jacket because this circular connection 72, 75 is centered by the spring ring or rings 74 on the receiving bore central axis 81.
  • the bearing module 7 is mounted in the main housing 1 of the steering gear, the rack 11 being pressed against the drive pinion 15 by the bearing module 7.
  • the assembly is facilitated by an orientation groove 84 which is formed in the outer circumference of the pressure ring 71. According to the example shown, it is diametrically opposite that part of the pressure ring wall which has the greatest wall thickness.
  • the orientation groove 84 runs parallel to the central axes 81, 82 (ie perpendicular to the drawing planes of FIGS. 5 and 6).
  • Complementary to the orientation groove 84 is formed on the inner wall of the main tube 1, for example by stamping, a radially inwardly projecting orientation cam 18 which also runs axially parallel.
  • FIG. 5 shows that the assembly of the inner ring 72 and guide bushing 75 and thus the guide passage 87 delimited by them is radially displaced in the direction of the location by mounting the bearing module 7 in the steering gear main housing 1 with the maximum pressure ring thickness 88.
  • the self-contained bearing module 7 is pushed over the toothed / piston rod 11 protruding from the main housing 1 and then into the main housing 1.
  • orientation cam 18 on the inner wall of the housing and the orientation groove 84 on the outer circumference of the pressure ring 71 move into one another.
  • the orientation groove 84 is positioned in the circumferential direction in such a way that when this enables the bearing module 7 to be inserted, the point with the maximum pressure ring thickness 88 (indirectly via spring washers 74 and composite guide ring 72, 75) on the side or the circumferential section of the toothed / piston rod for contact or comes into effect, which or which of the side or the peripheral portion with the toothing 16 are diametrically and optionally axially offset.
  • the guide part consisting of the inner ring 72 and the guide bush 75 increasingly moves to the spot with the maximum pressure ring thickness 88, because the space and installation conditions within the Main tube for the toothed / piston rod 11 meshing with the drive pinion 15 do not allow another path or a different evasion for the guide part 72, 75.
  • the guide part 72, 75 is countered by the increasing pressing of the bearing module 7 up to the stop shoulder 13b the spring force and thus prestressed by the spring washers 74 is radially displaced to the point with the maximum pressure ring thickness 88.
  • the offset corresponds approximately to the eccentricity measure e given above.
  • the point with the minimum spring ring thickness 85 results in the spring force which is directed to the side or the peripheral section of the toothed rack which is diametrically or axially offset from the toothing region 16.
  • the toothed / piston rod 11 is pressed against the drive pinion 15, any play during steering movements being largely avoided for the toothing engagement.
  • the spring constant of the spring ring (s) 74 is expediently dimensioned such that a deflection force of 200-300 Newtons arises when deflected by the eccentricity measure e mentioned, which is particularly suitable for car steering systems.
  • the toothed / piston rod 11 automatically and radially or eccentrically displaces the guide part assembly 72, 75 with spring deflection or with the generation of the spring preload without the need for further adjustment steps because the toothed / piston rod 11 is in the middle Seal holder 8 and in the end guide bearing 9 is positively guided and passes through the guide passage 87 delimited by the guide part assembly 72, 75.
  • the force with which the toothed / piston rod 11 is pressed against the drive pinion 15 is thus automatically generated without the need for further adjustment steps, the magnitude of the force being able to be influenced beforehand by the selection of the spring constant.
  • a flat or flat blank 19 for example made of sheet steel, is provided for producing the steel spring washer, which was first provided with a circular ring shape, for example by stamping. Furthermore, recesses 19a are provided both from the radially outside and from the inside radially Recesses 19b made. Both can also be created by punching. Seen in the circumferential direction 19c of the spring ring, the outer and inner recesses 19a, 19b alternate with one another.
  • the steel spring ring 19i consists of a plurality of individual C spring members 19f, which are connected to one another alternately via inner connecting webs 19d and outer connecting webs 19e. These form a spring ring chain around the central axis 19h.
  • an object for example, rack 11 above
  • the effect of the force is due to the mechanical tension under which the C-spring elements stand.
  • the respective connecting webs 19d, 19e start from the opposite ends of the individual C spring members 19f.
  • the inner connecting webs 19d, which each start from first ends of the C-spring links 19f, have mutually identical or congruent angular positions.
  • the outer connecting webs 19e, which each start from the opposite second ends of the C-spring links 19f If elastomer rings (O-rings) known per se are used, according to the diagram in FIG. 9, with a deflection path between 0.2 mm and 0.4 mm (which corresponds to the range of the eccentricity measure e given above), the spring force specified above of 200- 300 Newtons.
  • the inner ring 72 is displaced radially by the amount of the previously applied eccentricity e of, for example, 0.3 mm (cf. FIGS. 5 and 6) and thereby generates the spring characteristic of the spring ring element or elements 74 a pressure force (rack against pinion) of 200 - 300 Newtons.
  • a pressure force rack against pinion
  • an interference force of more than 300 Newtons this can have an effect on the rack play, that is, the rack 11 lifts off the pinion 15 by this amount.
  • the pressure ring 71 is designed according to FIG. 10 with an opening 90 (cf. also FIG. 13), in which an additional complementary pressure piece 91, for example made of plastic, is used.
  • This is pressed by the inner wall of the main housing 1 via its axially parallel sides 92 into contact with the inner ring 72.
  • the common contact surfaces 93 of the pressure piece 91 and the inner ring 72 are wedge-like, for example at an angle of 6 °, relative to the (parallel) central axes 81, 82.
  • a further pressure piece side section 95 adjoins the aforementioned 6 ° contact surface 93 of the pressure piece 91 via an obtuse angle 94 and bears against one of the spring ring elements 74.
  • This side section 95 of the pressure piece 91 also has a wedge-like inclination of, for example, 30 ° with respect to the central axes 81, 82.
  • a beading 96 is provided in the wall of the main housing 1 from outside, which only extends over a partial circumference of the tubular main housing 1.
  • the bead formation 96 results in an axial fixing of the bearing module 7.
  • the pressure piece 91 is curved or curved in accordance with the circumference of the main housing 1, the concave side resting on the inner ring 72.
  • the pressure piece 91 seen in the assembly insertion direction 99 (see FIGS. 14-19), has front and rear sides 97, 98 which form a right angle with the axially parallel side 92.
  • FIG. 10 For the rest, reference can be made to the comments on FIG. 10.
  • the pressure piece 91 is inserted into the contour of the opening 90 of the pressure ring 71 already mentioned, with two orientation tabs 100 projecting rearward, as seen in the mounting insertion direction 99.
  • the underside of the latter are provided with the 30 ° side sections 95 which are assigned to one of the spring ring elements 74.
  • other geometrical orientation means can also be used to ensure that the pressure piece 91 is used in a functionally correct manner, for example indentations at the edge or recesses in the inner region of the pressure piece 91 that the pressure piece cannot be inserted incorrectly into the opening 90 of the pressure ring due to the orientation means.
  • the pinion 15 and the rack 11 are already installed in the main housing 1.
  • the bearing module 7 with the pressure ring 71, inner ring 72 etc. is pushed onto the rack 11 in the insertion direction 99.
  • the pressure piece 91 is inserted into the opening 90 with a self-checking shape.
  • the bearing module 7 is preferably advanced by hand so that the above-mentioned orientation groove 84 in the outer jacket of the pressure ring 71 engages with the orientation cam 18 on the inner wall of the main housing 1.
  • the further displacement of the bearing module 7 with the pressure piece 91 inserted is expediently supported by a mechanical, power-operated tappet 101.
  • the main housing 1 After leaving the radial expansion 13a of the main housing 1, the main housing 1 forms an internal press-in passage 102 with respect to the outer circumference of the bearing module 7. This is dimensioned such that the spring ring elements 74 are loaded on one side and, due to the eccentricity e described above, the radial displacement of the inner ring 72 takes place. This results in the spring preload for pressing the rack 11 against the pinion 15.
  • the complementary pressure piece 91 also enters the press-in passage 102 with increasing displacement. In the process, it rubs against the inner wall of the main housing 1 after the radial expansion 13a, so that it moves rearward relative to the inner ring 72 against the insertion direction 99 , This causes the 6 ° contact surfaces 93 of the pressure piece 91 and inner ring 72 to slide against one another. As a result of the displacement of the pressure piece 91 to the rear, the 30 ° side section 95 of the pressure piece 91 comes into contact with the spring element 74 in the insertion direction 99. In response to the corresponding pressure, the ring spring element 74 generates a corresponding counterforce on the pressure piece 91 over its 30 ° -Side section 95. The pressure piece 91 is held by a balance of forces. This process continues until the pressure ring 71 with its radial extension 71a abuts the inner stop shoulder 13b of the housing 1 corresponding to the radial housing expansion 13a.
  • the pressure of the pressure piece 91 on the spring ring element 74 generates a low counter-spring force, which holds the pressure piece 91 in connection with the 6 ° ramp of the contact surfaces 93 in a play-free block position.
  • the 6 ° inclination angle of the contact surfaces 93 lies in the area of self-locking, so that even with strong ones Bumps no noticeable rack play is effective. Due to the aforementioned equilibrium of forces for the pressure piece 91, it is locked in the axial direction and cannot slip. Due to the 6 ° inclination of the contact surfaces 93, a frictional force arises which, in combination with the spring force, prevents slipping due to the spring ring element 74 slightly deflected by the 30 ° side section 95.
  • the pressure piece 91 is locked in the axial direction.
  • the slightly deflected spring ring element 74 generates a force component parallel to the longitudinal axis (securing force).
  • the complementary pressure piece 91 is, as it were, locked in the opening 90 between the 6 ° contact surfaces 93 and the spring ring element 74 resting on the 30 ° side section 95. Its slight deflection by the axially displaced pressure piece 91 ensures its axial positioning and locking.
  • FIG. 18 illustrates the form-fitting securing of the bearing module 7 against axial displacement by means of the partial beading 96 already mentioned.
  • tie rod a radial expansion b stop shoulder bellows drive pinion toothing area joint orientation cam steel cut a outer recess b inner recess c spring ring circumferential direction d inner connecting web e outer connecting web f C-spring link g opening h central axis i steel spring ring k spring link circumferential direction 1 spring link central axis racks - / Housing center axis thrust ring a radial extension inner ring retaining ring spring ring element guide bush locating hole outer groove hole wall edge retaining shoulder a fixed stop center axis of the locating hole center axis of the outer diameter of the thrust ring 83 pressure ring outer diameter

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Power Steering Mechanism (AREA)

Abstract

L'invention concerne un module palier (7) pour un boîtier de direction de véhicule automobile comprenant une crémaillère (11) et un pignon d'attaque (15) en prise avec la crémaillère. Selon la présente invention, ce module palier (7) comprend au moins une bague de serrage (71) pourvue d'un alésage (76) dont la paroi (78) s'étend de manière excentrique par rapport à la périphérie extérieure (83) de la bague de serrage (71) et/ou à une ligne médiane imaginaire (19) de la crémaillère (11) et entoure un passage de guidage (87) destiné au guidage axial de la crémaillère (11). De plus, des forces radiales provenant de la paroi (78) de l'alésage peuvent être produites pour serrer la crémaillère (11), logée dans le passage de guidage (87), contre le pignon d'attaque (15) en prise dans la crémaillère. Ce passage de guidage (87) est directement délimité par une ou plusieurs parties de guidage séparées (72, 75) situées à l'intérieur de l'alésage (76), appuyées de façon élastique et/ou flexible contre la paroi (78) de cet alésage et, ainsi, pouvant être déplacées radialement à l'encontre de la force élastique au moins de la grandeur de l'excentricité de la bague de serrage (71) et/ou de façon à compenser cette excentricité.
PCT/EP2004/000736 2003-01-28 2004-01-28 Boitier de direction a cremaillere pour vehicule automobile et module palier a cet effet WO2004067357A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112004000167T DE112004000167D2 (de) 2003-01-28 2004-01-28 Kraftfahrzeug-Lenkgetriebe mit Zahnstange und Lagermodul dafür

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10303300.9 2003-01-28
DE10303300 2003-01-28
DE10334642.2 2003-07-28
DE10334642 2003-07-28

Publications (1)

Publication Number Publication Date
WO2004067357A1 true WO2004067357A1 (fr) 2004-08-12

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DE (1) DE112004000167D2 (fr)
WO (1) WO2004067357A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005070745A1 (fr) 2004-01-26 2005-08-04 Schmitterchassis Gmbh Palier reglable par clavette pour mecanisme de direction de vehicule automobile
EP1787890A1 (fr) * 2005-11-21 2007-05-23 TRW ITALIA S.p.A. Ensemble de direction
EP2072372A1 (fr) 2007-12-20 2009-06-24 Renault Palier de crémaillère de direction pour véhicule automobile
CN101844582A (zh) * 2009-03-27 2010-09-29 蒂森克鲁伯普雷斯塔股份公司 低成本的齿条式转向传动机构
DE102012100185A1 (de) * 2012-01-11 2013-07-11 Tedrive Steering Systems Gmbh Verformung des Lenkgehäuses zur Festlegung des Stützlagers
WO2013120969A1 (fr) * 2012-02-14 2013-08-22 Tedrive Steering Systems Gmbh Palier d'appui muni d'un élément élastique
US8555741B2 (en) 2005-06-30 2013-10-15 Steering Solutions Ip Holding Corporation Power steering apparatus with adjustment device
WO2014202656A1 (fr) * 2013-06-21 2014-12-24 Thyssenkrupp Presta Ag Compensation de jeu pour un palier de pignon

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1046569A1 (fr) * 1999-04-23 2000-10-25 TRW Inc. Appareil pour tourner les roues directrices de véhicules
US6435050B1 (en) * 2001-03-28 2002-08-20 Delphi Technologies, Inc. Steering gear for motor vehicle

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1046569A1 (fr) * 1999-04-23 2000-10-25 TRW Inc. Appareil pour tourner les roues directrices de véhicules
US6435050B1 (en) * 2001-03-28 2002-08-20 Delphi Technologies, Inc. Steering gear for motor vehicle

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005070745A1 (fr) 2004-01-26 2005-08-04 Schmitterchassis Gmbh Palier reglable par clavette pour mecanisme de direction de vehicule automobile
US8555741B2 (en) 2005-06-30 2013-10-15 Steering Solutions Ip Holding Corporation Power steering apparatus with adjustment device
EP1787890A1 (fr) * 2005-11-21 2007-05-23 TRW ITALIA S.p.A. Ensemble de direction
EP2072372A1 (fr) 2007-12-20 2009-06-24 Renault Palier de crémaillère de direction pour véhicule automobile
FR2925632A1 (fr) * 2007-12-20 2009-06-26 Renault Sas Palier de cremaillere de direction pour vehicule automobile
CN101844582A (zh) * 2009-03-27 2010-09-29 蒂森克鲁伯普雷斯塔股份公司 低成本的齿条式转向传动机构
EP2233381A1 (fr) * 2009-03-27 2010-09-29 ThyssenKrupp Presta AG Direction à crémaillère économique
DE102012100185A1 (de) * 2012-01-11 2013-07-11 Tedrive Steering Systems Gmbh Verformung des Lenkgehäuses zur Festlegung des Stützlagers
WO2013120969A1 (fr) * 2012-02-14 2013-08-22 Tedrive Steering Systems Gmbh Palier d'appui muni d'un élément élastique
WO2014202656A1 (fr) * 2013-06-21 2014-12-24 Thyssenkrupp Presta Ag Compensation de jeu pour un palier de pignon

Also Published As

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