Classifications

• • 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
  • F16C29/123—Arrangements for adjusting play using elastic means
• • 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
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/02—Parts of sliding-contact bearings
  • F16C33/04—Brasses; Bushes; Linings
  • F16C33/20—Sliding surface consisting mainly of plastics
• • 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
  • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
  • F16C2240/30—Angles, e.g. inclinations
• • 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

Definitions

• the invention relates to a support bearing for a steering of a motor vehicle and an associated steering gear.
• Steering gears have an essentially tubular steering housing, a steering rod displaceably guided in the steering housing by means of at least two support bearings, and a transmission in order to effect a rotating steering movement into an axial movement of the steering rod via its gear engagement.
• Steering gears are used in motor vehicles to convert the applied over the steering wheel rotating steering movement in a rectilinear movement for pivoting the vehicle wheels to be steered.
• a servo drive can be used, which can be arranged at suitable locations within the steering power flow.
• Conventional steering gear are designed as so-called rack and pinion steering.
• rack and pinion steering the end of the steering column is connected to a pinion, which engages in the teeth of the handlebar, which is also called rack, and this moves laterally when turning the steering.
• a tie rod is connected via a ball joint.
• Rack and pinion steering has good feedback and very good resilience. It is known to provide a thrust piece to bias the engagement of the transmission components so that wear-related play between these components is prevented.
• the pressure piece is screwed by spring force in a cylindrical pressure piece seat of the steering housing and it acts in the installed position under spring tension with its front contact surface on the outer surface of the handlebar so that the handlebar is pressed with its teeth against the pinion.
• Such plungers increase the design complexity of the steering gear, increase the effort in the assembly of the steering gear, increase the weight and the overall volume and can be disadvantageous cause of undesirable noise during steering.
• the gear engagement for example, the engagement between the pinion and the toothing of the handlebar, comparatively structurally simple can be set under bias and in particular can be adjusted, in particular at the same time advantageous removal of a pressure piece or the like.
• the object of the present invention is therefore to be able to reduce the assembly costs, the costs, the overall volume and also the weight for a steering gear while still causing a preloaded engagement of the associated transmission components and in particular to be able to adjust these, in particular by omission of a pressure piece, also called sliding block.
• This object is achieved by a support bearing according to claim 1.
• a correspondingly advantageous steering gear and its use in a motor vehicle are each subject of the independent claims.
• Advantageous embodiments are the subject of the dependent claims. It should be noted that the features listed individually in the claims can be combined with each other in any technologically meaningful manner and show further embodiments of the invention. The description, in particular in connection with the figures, additionally characterizes and specifies the invention.
• the support bearing according to the invention is provided for the storage of a handlebar in a steering housing.
• the support bearing comprises a support bearing body with an opening defining an inner wall for receiving the handlebar.
• the aperture is arranged to penetrate at least the geometric center of the support bearing.
• the support bearing body may have various configurations of the inner wall.
• the cross-sectional shape of the aperture defined by the inner wall is adapted to the cross section of the handlebar, for example, both have a circular cross section.
• the cross section defining the inner wall is drop-shaped, ie. partially V-shaped with a part-circular transition between the legs of the V.
• the breakthrough is provided in order to move the handlebar relative to the steering housing by means of a steering gear can.
• the outer wall of the support bearing body is generally positively against the steering housing to support the handlebar via the support bearing on the steering housing.
• the support bearing according to the invention is characterized in that, between the inner wall and the outer wall, at least one spring element for elastically restoring support of the handlebar is arranged in at least one of the inner wall, preferably radially. directed, main spring direction has.
• "Spring element” in the sense of the invention is to be interpreted broadly, and thus comprises a separate spring element inserted into the support bearing material and a spring element provided by a special shaping of the support bearing made of the material of the support bearing In addition, means for limiting the spring travel, such as beads or the like can be provided.
• the separate spring element is for example made of elastomer, rubber, such as synthetic or natural rubber, in particular vulcanized rubber. According to a preferred embodiment, the spring element is made of a spring steel.
• a plurality of spring elements per main spring direction are provided.
• two spring elements are provided. Due to the mating according to the invention, the total spring action per main spring direction is modulated by the spring retention of the individual spring elements. For example, we the overall spring behavior result from the mating of spring elements with a linear spring behavior but different elasticity in a non-linear spring behavior
• a separate spring element and one integral with the support bearing body spring element is provided per main spring direction.
• the integrally formed with the support bearing body spring element is in the radial direction of the support bearing innermost of the at least two spring elements per main spring direction.
• the at least one spring element is arranged so that the elastically restoring support has a preferred direction with respect to the radial directions of the support bearing, for example, because the spring element does not extend fully around the inner wall. Due to the preferred direction, the direction of the elastic support can be preset or adjusted by turning the support bearing.
• the inner wall is arranged eccentrically to the outer wall. This means, for example, that the geometric center of the inner wall cross-section does not coincide with the geometric center of the Jardinwandungsqueritess. Due to the eccentricity a displacement possibility of the handlebar with respect to the steering housing by turning the support bearing is made possible to adjust the engagement of the transmission by the rotation of the support bearing and optionally the contact pressure by means of the spring element. By means of an eccentric breakthrough, it is possible to ensure manufacturing tolerances, dimensional tolerances by the different components and thus adjustability required for mounting in a steering gear, especially at the same time omitting a pressure piece or sliding block and its mounting means.
• the arrangement of the spring element in the circumferential direction is not necessarily fixed, for example, it is arranged so that its main spring direction is on the line connecting the two geometric centers so on the direction of eccentricity.
• the spring element is arranged offset according to a further variant about 90 ° to the eccentricity in the circumferential direction.
• the arrangement of the spring elements in the circumferential direction with respect to the eccentricity will be chosen according to a preferred variant, that results in an optimal variation of the contact pressure based on a statistically to be determined average rotational position of the support bearing, which is determined over several assembly and adjustment processes.
• the average position between maximum and minimum engagement between the handlebar and pinion is considered as the average rotational position.
• these are arranged so that their main spring direction by the connecting line of the two middle points defined axis (Exzentrizticiansraum) at an angle in the range of 45 ° to 90 ° intersects.
• the spring element defined according to a preferred embodiment, at least partially the inner wall. D.h. the spring element is thus arranged adjacent to the outer circumference of the handlebar, thus abuts against the handlebar.
• the spring element is preferably formed integrally with the support bearing body, which has the advantage that in the sliding relative movement between the support bearing and rack, the spring element can be separated from the support bearing difficult.
• this spring element as the support bearing body to improve the sliding properties between the support bearing and rack made of plastic.
• a cavity in the support bearing body is arranged between the spring element and outer wall to ensure a controlled, defined yielding of the spring element.
• this cavity may further be used a damping element to dampen the stop of the spring element to the boundary of the cavity.
• an inner wall of the opening at least partially defining sliding insert for example made of plastic, used.
• the support bearing body is at least partially made of plastic.
• the spring element is designed for example as a leaf spring, corrugated spring or plate spring.
• the spring element may be formed as a separate component which can be inserted into the support bearing body.
• the spring element and the support bearing body are integrally formed.
• the support bearing comprises at least two circumferentially offset spring elements. This can be done by Aligning the support bearing, in particular by rotating the support bearing of the support bearing used in the steering housing, the spring action can be adjusted.
• the main spring direction intersect at an angle of 90 °.
• the function of the support bearing according to the invention is not limited to the support function of the rack, but can also serve the impact (lock stop) of the sliding movement of the rack.
• the at least one spring elements additionally serves the elastic impact of the sliding movement of the rack.
• the invention further relates to a steering gear, which has a substantially tubular steering housing, a steering rod displaceably guided in the steering rod and a transmission in order to effect via its gear engagement a rotating steering movement in an axial movement of the handlebar.
• the steering gear according to the invention is characterized by at least one, for example one or two, support bearing for the mounting of the handlebar in the steering housing in one of the previously described embodiments.
• the transmission comprises a handlebar side toothing and a pinion meshing therewith.
• the steering gear according to the invention is not limited in terms of the technical design and the nature of the transmission, preferably the transmission comprises a pinion arranged in the so-called pinion tower of the steering housing and a toothing arranged on the handlebar side.
• the steering gear can have no as well as one, for example an electromechanical, power assistance.
• a hydraulic power assisting gear is provided.
• Steering gears with a hydraulic support have a mechanical range and a hydraulic range of the steering box.
• the mechanical area is the area in which the area of the rack moves, which is provided with teeth and which engages with the pinion.
• the pinion engagement area is thus located in the mechanical area of the steering housing.
• the hydraulic region is the region in which the toothed rack also extends but usually has no toothing.
• the Rack connected to a displaceably mounted piston element, on whose end faces each have a cylinder chamber is formed.
• a control valve is actuated so that pressure oil flows into each one of the cylinder chambers, whereby the piston and thus the rack in the cylinder experiences a force that displaces the rack supportive.
• the displacement of the piston due to the pressure oil serves as a force reinforcement for the rack movement.
• the control valve and the rack housing are connected to each other via hydraulic lines, so that depending on the direction of rotation of the steering wheel one or the other cylinder chamber can be acted upon with pressure oil.
• the support bearing described above in one of the embodiments described above replaces a so-called sliding block, ie a biased, in sliding contact with the steering rod support of the steering rod in the engagement between the steering pinion and handlebar to bias the engagement.
• the invention further relates to an advantageous for the aforementioned reasons use of the steering gear in a motor vehicle.
• Fig. 1 is a sectional view of a first embodiment of the support bearing according to the invention
• Fig. 2 is a side view of a second embodiment of the support bearing according to the invention.
• FIG. 3 shows a side view of a third embodiment of the support bearing according to the invention.
• Fig. 4 is a sectional view of a steering gear (10) with the third embodiment of the support bearing of Fig. 3;
• FIG. 5 shows a perspective view of the third embodiment of the support bearing according to the invention from FIG. 3; 6a shows a side view of an insertable into the opening 9 of the support bearing 1 according to the figures 1 to 5, additional spring element 3 ⁇ ;
• Fig. 6b is a plan view of the additional spring element 3 ⁇ of FIG. 6a;
• FIG. 7 shows a side view of a fourth embodiment of the support bearing according to the invention.
• FIG. 8 shows a perspective view of the fourth embodiment of the support bearing according to the invention from FIG. 7;
• FIG. 9 shows a side view of a fifth embodiment of the support bearing according to the invention.
• Fig. 10 shows a curve of the rotational position-dependent contact force between the handlebar and pinion.
• Fig. 11 is a sectional view of an arrangement of a rack, a steering housing and a support bearing according to the invention in a sixth embodiment.
• FIG. 1 shows a first embodiment of the support bearing 1 according to the invention.
• This has a support bearing body 2 with a central opening 6.
• the support bearing body 2 is positively received in a steering housing, not shown, wherein the outer periphery 4 comes to rest on the inner wall of the steering housing.
• a sliding insert 7 for example made of a plastic, used to reduce friction.
• the defined by the sliding insert 7 of the support bearing body opening 6 serves to receive a handlebar, not shown, which is slidably received in the steering housing, not shown.
• the outer circumference 4 of the support bearing body 2 is adapted to the shape of the inner cross section of the steering housing, for example, the support bearing body 2 is elliptical or circular.
• the inner wall 5 is offset according to the figure 1 with a horizontal eccentric offset to the outer wall 4, wherein the eccentric offset refers to the geometric center of the outer wall 4 and the inner wall 5.
• a spring element 3 is arranged in the form of a leaf spring made of spring steel, whose main spring direction perpendicular to FIG. 1 runs.
• the support bearing body 2 shows a second embodiment of the support bearing 1 according to the invention, wherein the support bearing body 2 is annular and has an offset with respect to the outer wall 4 eccentric aperture 6.
• the spring element 3 is arranged laterally, ie offset in the circumferential direction by approximately 90 °.
• the leaf spring-shaped spring element 3 is formed integrally with the support bearing body 2 and results as an inner web, which is defined by the provided between the outer wall 4 and inner wall 5 opening 9.
• associated recesses 8 are provided on the support bearing body 2.
• a further separate spring element 3 ⁇ can be used, as shown for example in Figures 6a and 6b.
• FIG. 3 shows a third embodiment of the support bearing 1 according to the invention, which differs essentially only from the second embodiment described above, that the leaf spring-shaped spring element 3 has been replaced by two, one-sided with the support bearing body integrally connected, a free end having leaf springs. Again, in the opening 9 another, separate spring element, as shown for example in Figures 6a and 6b, if necessary, be used.
• a further description of functionally identically acting components is dispensed with and reference is hereby made to the above description in this regard.
• FIG. 4 shows the steering gear 10 according to the invention with a support bearing in the third embodiment according to the invention, as known from FIG.
• the support bearing body 2 is received positively in the steering housing 14, wherein the outer periphery 4 comes to rest on the inner wall of the steering housing 14.
• the defined by the support bearing body 2 opening 6 serves to receive a handlebar 13, which is slidably received on the support bearing body 2 in the steering housing 14.
• the outer circumference 4 of the support Bearing body 2 is adapted to the shape of the inner cross section of the steering housing 14.
• the inner wall 5 is offset according to the figure 4 with a horizontal eccentric offset relative to the outer wall 4, wherein the eccentric offset refers to the geometric centers of the outer wall 4 and the inner wall 5.
• the steering housing 14 has a pinion tower 11.
• pinion tower 11 which is rotatably driven by the steering column pinion 12 is arranged, which is in gear engagement with the not shown in Figure 4 toothing of the handlebar 13.
• FIG 5 shows the third embodiment of the support bearing 1 according to the invention in a perspective view.
• the defined by a cross-sectional expansion of the outer peripheral surface bead 18 can be seen, which ensures a positional fixation in the axial direction of the support bearing 1 in the steering housing, not shown.
• FIG. 7 shows a further, fourth embodiment of the support bearing 1 according to the invention that differs from the embodiment shown in FIG. 2 in that a plurality of spring elements 3 arranged offset by approximately 90 ° are provided whose main spring directions are at an angle of 90 ° to cut.
• the openings 9 between the spring elements 3 and the outer wall 4 can in turn, if necessary, be equipped with additional, separate, not shown in Figure 7 spring elements, as shown for example in Figures 6a and 6b. 8 shows the fourth embodiment in associated perspective view.
• FIG. 1 A fifth embodiment of the support bearing 1 according to the invention is shown in FIG. This is based on the fourth embodiment and takes up the specific embodiment of the spring elements of Figures 3 to 5.
• the fifth embodiment thus comprises two spring element pairs 3, each pair, two integrally formed with the support bearing body 2, each having a free end on includes pointing leaf springs.
• the pairs are arranged offset by about 90 ° to each other, wherein the main spring direction intersect the direction defined by the eccentricity at an angle of 45 °.
• the curve of the contact pressure more precisely its normal component, the handlebar in the direction of pinion in dependence on the rotational position of the support bearing is applied.
• the dotted line corresponds to the force curve of the third embodiment, wherein the O-degree representation corresponds to the middle position between maximum and minimum engagement due to the eccentric mounting of the rack.
• the dashed line shows this in comparison the course of the contact pressure, more precisely its normal component (based on the engagement between the handlebar and pinion), the handlebar in the direction of pinion in dependence of the rotational position of the fifth embodiment of the support bearing. Due to the two offset by 90 ° spring elements results in relation to the dotted graphs an overall flatter course with a higher angle of rotation shifted maximum. By using the two circumferentially offset spring elements thus results in a wider range of adjustment for the contact force with almost constant maximum force. By dividing the force in two directions, this can be adjusted so that the Normalkompenente is reduced, so as to reduce the frictional forces during the sliding movement of the handlebar in the support bearing over a spring elementless support bearing.
• An oblique force acting on the engagement between the handlebar and the pinion also has the advantage that when external impulse action on the handlebar this no longer removed in the normal direction from the engagement with the pinion, but along the resulting direction of force, ie obliquely. A part of the acting force is therefore absorbed by the other force component, which is vertical to the normal direction, and thus reduces the rebounding momentum. ment and thus also the impact sound at reunion of the components rack and pinion.
• FIG. 11 shows an arrangement of a steering housing 14, a steering rod 13 and a further embodiment of the support bearing 1.
• This support bearing 1 comprises a support bearing body 2 made of plastic and two pairs of spring elements 3, 3 "f ..
• the support bearing body 2 is in the steering housing 14
• the central opening 5 serves to receive and slide the steering rod 13.
• the steering rod 13 is mounted eccentrically in the steering housing 14 by the support bearing 1.
• Means are provided for relative rotatability of the support bearing 1 in the steering housing 14, wherein the support bearing 1 remains fixed at least in the axial direction of the steering housing 14.
• Means may also be provided for preventing the support bearing 1 from rotating in the steering housing 14.
• Each pair of spring elements 3, 3 “comprises an inner fitting to and integral with the rack 13 Support bearing body 2 formed spring element.
• the inner spring element 21 has a region 21 which is adapted to the contour of the outer circumference of the steering rod 13 in each case in the area of contact with the steering rod 13.
• the main spring direction of each pair 3, 3" intersects the axial course of the steering rod perpendicularly, with the main spring directions of the pairs relative to each other stand vertically. With rotation of the support bearing body 1, the direction of the resultant is rotated from the two main spring direction.
• the direction of the resultant varies with respect to the engagement between the handlebar 13 and pinion. Due to the eccentric arrangement of the handlebar 13 in the steering housing 14 varies simultaneously with the rotation of the support bearing 2, the engagement or the bias of the engagement between the handlebar 13 and pinion.

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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)
• Support Of The Bearing (AREA)

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Citations (5)

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• 2012
  • 2012-02-14 DE DE102012101147A patent/DE102012101147A1/de not_active Ceased
• 2013
  • 2013-02-14 WO PCT/EP2013/053019 patent/WO2013120969A1/fr not_active Ceased

Patent Citations (5)

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