WO2006009230A1 - Arbre télescopique pour direction de véhicule - Google Patents

Arbre télescopique pour direction de véhicule Download PDF

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Publication number
WO2006009230A1
WO2006009230A1 PCT/JP2005/013428 JP2005013428W WO2006009230A1 WO 2006009230 A1 WO2006009230 A1 WO 2006009230A1 JP 2005013428 W JP2005013428 W JP 2005013428W WO 2006009230 A1 WO2006009230 A1 WO 2006009230A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
vehicle steering
bellows
seal
telescopic shaft
Prior art date
Application number
PCT/JP2005/013428
Other languages
English (en)
Japanese (ja)
Inventor
Takatsugu Yamada
Kiyoshi Sadakata
Original Assignee
Nsk Ltd.
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 Nsk Ltd. filed Critical Nsk Ltd.
Priority to JP2006529285A priority Critical patent/JPWO2006009230A1/ja
Publication of WO2006009230A1 publication Critical patent/WO2006009230A1/fr

Links

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
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/02—Shafts; Axles
    • F16C3/03—Shafts; Axles telescopic
    • F16C3/035—Shafts; Axles telescopic with built-in bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
    • B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
    • B62D1/16—Steering columns
    • B62D1/18—Steering columns yieldable or adjustable, e.g. tiltable
    • B62D1/187—Steering columns yieldable or adjustable, e.g. tiltable with tilt adjustment; with tilt and axial adjustment
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/06—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement
    • F16D3/065—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement by means of rolling elements
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/84—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor
    • F16D3/843—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers
    • F16D3/848—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers allowing relative movement of joint parts due to sliding between parts of the cover
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J3/00—Diaphragms; Bellows; Bellows pistons
    • F16J3/04—Bellows
    • F16J3/041—Non-metallic bellows
    • F16J3/042—Fastening details
    • 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 present invention is incorporated in a steering shaft of a vehicle, and a female shaft and a male shaft are fitted so as not to rotate relative to each other and slidable, and the fitting portion of the female / male shaft is sealed to allow rain into the fitting portion.
  • the present invention relates to a telescopic shaft for vehicle steering provided with a seal member that prevents intrusion of water or the like.
  • the intermediate shaft is composed of a telescopic shaft that is spline-fitted, etc., and absorbs axial displacement that occurs when the vehicle travels, and does not transmit the displacement or vibration to the steering wheel. It ’s like that.
  • FIG. 12 is a longitudinal sectional view of a telescopic shaft for vehicle steering according to a conventional example.
  • 13A is a cross-sectional view of the female / male shaft shown in FIG. 12, and
  • FIG. 13B is an enlarged vertical cross-sectional view of the end of the male shaft shown in FIG.
  • three axial grooves 43 are arranged so as to be evenly arranged at intervals of 120 degrees in the circumferential direction (phase).
  • three axial grooves 45 that are equally arranged at intervals of 120 degrees in the circumferential direction (phase) are formed to extend on the inner circumferential surface of the female shaft 10.
  • both shafts 1 0, 1 A plurality of rigid spherical bodies 47 (rolling bodies, poles) that roll during the relative axial movement of 1 are interposed so as to be freely rollable.
  • the axial groove 45 of the female shaft 10 has a substantially arc-shaped cross section or a Gothic arch shape.
  • the axial groove 4 3 of the male shaft 11 is composed of a pair of inclined flat side surfaces 4 3 a and a bottom surface 4 3 b formed flat between the pair of flat side surfaces 4 3 a. .
  • a leaf spring 49 for contacting and preloading the spherical body 47 is interposed between the axial groove 43 of the male shaft 11 and the spherical body 47.
  • the leaf spring 4 9 is separated from the spherical body side contact portion 4 9 a that contacts the spherical body 47 at two points, and is spaced apart from the spherical body side contact portion 4 9 a at a predetermined interval in the circumferential direction.
  • male shaft 1 1 axial groove 4 3 planar side surface 4 3 a groove surface side contact portion 4 9 b that contacts a, spherical body side contact portion 4 9 a and groove surface side contact portion 4 9 b And a bottom portion 4 9 d facing the bottom surface 4 3 b of the axial groove 4 3.
  • the urging portion 4 9 c is a substantially U-shaped bent shape that is bent in a substantially arc shape, and the bent-side urging portion 4 9 c causes the spherical body side contact portion 4 9 a and the groove surface to be bent.
  • the side contact portions 4 9 b can be elastically biased so as to be separated from each other.
  • the outer surface of the male shaft 1 1 is formed by extending three axial grooves 4 4 equally spaced at intervals of 120 degrees in the circumferential direction (phase). is there.
  • three axial grooves 46 are equally formed on the inner peripheral surface of the female shaft 10 so as to be evenly spaced at intervals of 120 degrees in the circumferential direction (phase).
  • a rigid cylindrical body that slides and slides between the axial groove 4 4 of the male shaft 1 1 and the axial groove 4 6 of the female shaft 1 0 when the two shafts 1 0 and 1 1 move in the axial direction.
  • 4 8 sliding body, Needle port-La
  • These axial grooves 4 4 and 4 6 have a substantially circular arc shape or a Gothic arch shape in cross section.
  • a small-diameter portion 1 1 b is formed at the end of the male shaft 1 1, and the small-diameter portion 1 1 b has an elastic plate 4 1 and A pair of flat plates 4 2, 4 2 and A stopper member consisting of is fitted and fixed by caulking.
  • This one stopper member is configured to apply an appropriate preload while being regulated in the axial direction of the needle roller 48, and serves as a stopper in the axial direction of the spherical body 47.
  • the spherical body 47 is interposed between the male shaft 11 and the female shaft 10, and the spherical body 47 is loosely separated from the female shaft 10 by the leaf spring 4 9. Since it is preloaded to the extent that there is no sticking, it is possible to reliably prevent backlash between the male shaft 1 1 and the female shaft 10 during low torque transmission, and the male shaft 1 1 and female shaft 1 0. When moving relatively in the axial direction, it can slide with a stable sliding load without rattling.
  • the plate panel 4 9 elastically deforms to restrain the spherical body 4 7 in the circumferential direction, and three rows of cylindrical bodies 4 8 interposed between the male shaft 11 and the female shaft 10 It plays the role of main torque transmission.
  • the substantially cap-shaped seal member 100 disclosed in Japanese Patent Laid-Open No. 6-2 4 1 2 3 8 is attached to the end of the female shaft 10. is there.
  • the seal member 100 is composed only of an elastic body such as rubber, and is fitted on the fitting portion 10 0 1 fitted on the end of the female shaft 10 and on the outer peripheral surface of the male shaft 11.
  • a slidable contact seal portion 102 that performs a sealing action by contacting with frictional force. This prevents rainwater, muddy water, dust, etc. from entering the fitting part of the female / male shaft.
  • the present invention has been made in view of the circumstances as described above, and reliably seals the fitting portion of the female / male shaft to prevent intrusion of rainwater, muddy water, dust, or the like into the fitting portion.
  • An object of the present invention is to provide a telescopic shaft for vehicle steering that can suppress fluctuations in sliding load.
  • the vehicle steering extension shaft according to the first aspect of the present invention is incorporated in a steering shaft of a vehicle, and a vehicle steering shaft in which a male shaft and a female shaft are fitted non-rotatably and slidably.
  • a male shaft and a female shaft are fitted non-rotatably and slidably.
  • the telescopic shaft is
  • a preload torque transmission unit that transmits the steering torque while preloading between the two shafts when the steering torque is a predetermined value or less;
  • the steering torque is A rigid torque transmitting portion for transmitting the torque
  • One end is fixed to the male shaft, the fitting portion of the male shaft and the two shafts is covered, and an axially expandable / contractible bellows-shaped dustproof boot having the other end fixed to the female shaft is provided.
  • the preload torque transmitting portion includes an elastic body between at least one row of axial grooves formed on the outer peripheral surface of the male shaft and the inner peripheral surface of the female shaft, respectively.
  • the rigid torque transmission part is a rigid torque transmission part
  • a second torque transmission member is interposed between at least one other groove direction formed on the outer peripheral surface of the male shaft and the inner peripheral surface of the female shaft.
  • the first torque transmission member is a rolling element that rolls in the axial relative movement of the two shafts.
  • the second torque transmitting member is preferably a sliding body that slides when the two wheels move in the axial direction relative to each other.
  • the rigid torque transmitting portion is provided on each of the outer peripheral portion of the male shaft and the inner peripheral portion of the female shaft, and transmits torque by contacting each other during rotation.
  • the preload torque transmission unit is
  • the rolling element includes: an elastic body that is disposed adjacent to the rolling element in a radial direction, and applies a preload to the male shaft and the female shaft via the rolling element.
  • the telescopic shaft for vehicle steering is incorporated in a steering shaft of a vehicle, and a male shaft and a female shaft are fitted in a non-rotatable and slidable manner, and the fitting portions of both shafts are sealed.
  • the sealing member is:
  • a bellows-like portion that covers the fitting portion of both shafts and is extendable in the axial direction;
  • the other end of the bellows-like portion is fixed to the outer peripheral surface of the female shaft
  • seal portion contacts the outer peripheral surface of the male shaft with an appropriate margin.
  • the seal portion has a pair of lip portions between which a grease reservoir portion is formed.
  • the seal portion preferably has a metal ring embedded therein.
  • a solid lubricating film is coated on the lip portion of the seal portion.
  • the outer peripheral surface of the male shaft that is in contact with the seal portion is coated with a solid lubricating film.
  • the seal portion has a grease ring exposed to the seal surface and adjacent to the lip portion.
  • the seal portion includes a metal ring embedded in the interior thereof, and is exposed to the seal surface and adjacent to the lip portion, and is press-fitted into the metal ring. It is preferable to have a certain resin ring.
  • the seal portion includes a metal ring embedded in the seal portion and a metal ring exposed to the seal surface and pressed against the metal ring. It is preferable to have a resin ring or a coasting ring that is inserted or fixed.
  • the relationship between the axial displacement resistance of the bellows-like portion and the sliding resistance of the seal portion is:
  • the axial displacement resistance of the bellows-shaped part is smaller than the sliding resistance of the seal part
  • the seal portion slides while the internal space of the bellows-like portion becomes a positive pressure.
  • an axially expandable / contractible bellows-shaped dustproof boot that fixes one end to the male shaft, covers the fitting portion between the male shaft and both shafts, and fixes the other end to the female shaft.
  • the seal member is formed on the one end of the bellows-shaped portion that covers the fitting portions of both shafts and is extendable in the axial direction, and is appropriately formed on the outer peripheral surface of either shaft. And a seal portion that comes into contact with a tight margin.
  • the fitting part of the female / male shaft is securely sealed to prevent intrusion of rainwater, muddy water, dust, etc. into the fitting part, and in the internal space of the dustproof boot or seal member, air compression, etc. There is no change in volume, and fluctuations in sliding load can be suppressed.
  • FIG. 1A is a side view of a vehicle steering apparatus according to the present invention
  • FIG. 1B is a cross-sectional view of an accordion-shaped portion according to an example
  • FIG. 1C is a cross-section of an accordion-shaped portion according to another example.
  • FIG. 2 is a longitudinal sectional view of the telescopic shaft for vehicle steering according to the first embodiment of the present invention.
  • FIG. 3A is a longitudinal sectional view of a telescopic shaft for vehicle steering according to a second embodiment of the present invention
  • FIG. 3B is an enlarged sectional view of the seal member shown in FIG. 3A.
  • FIG. 4A and FIG. 4B relate to a third embodiment of the present invention, and are longitudinal sectional views according to modifications of the female / male shaft, respectively.
  • FIG. 5 is an enlarged cross-sectional view of the female / male shaft shown in FIG. 4A.
  • FIG. 6A and FIG. 6B are enlarged sectional views of the seal member according to the fourth embodiment of the present invention.
  • FIG. 7A and FIG. 7B are enlarged cross-sectional views of the seal member according to the fourth embodiment of the present invention.
  • FIG. 8A is a longitudinal sectional view of a telescopic shaft for vehicle steering according to a fifth embodiment of the present invention.
  • FIGS. 8B and 8C are enlarged sectional views of the seal member shown in FIG. 8A, respectively. It is. ⁇
  • FIG. 9A is a longitudinal sectional view of a telescopic shaft for vehicle steering according to a sixth embodiment of the present invention.
  • FIGS. 9B and 9C are enlarged sectional views of the seal member shown in FIG. 9A, respectively. It is.
  • FIG. 10A, FIG. 10B, and FIG. 10C are longitudinal sectional views of the telescopic shaft for vehicle steering according to the seventh embodiment of the present invention.
  • FIGS. 11A and 11B are longitudinal sectional views of a telescopic shaft for vehicle steering according to a seventh embodiment of the present invention.
  • FIG. 12 is a longitudinal sectional view of a telescopic shaft for vehicle steering according to a conventional example.
  • FIG. 13A is an enlarged cross-sectional view of the female / male shaft shown in FIG. 12 and FIG. 13B is an enlarged vertical cross-sectional view of the end of the male shaft shown in FIG. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIG. 1A is a side view of a vehicle steering apparatus according to the present invention
  • FIG. 1B is a cross-sectional view of an accordion-shaped portion according to an example
  • FIG. 1C is a cross-section of an accordion-shaped portion according to another example. It is a figure.
  • a steering shaft 3 having a steering wheel 2 mounted on one side of the upper is rotatably supported.
  • a telescopic intermediate shaft 5 is connected to the lower side of the steering shaft 3 via a universal joint 4.
  • a rack and pinion type steering gear 7 is connected to the lower end of the intermediate shaft 5 via a universal joint 6, and a wheel (not shown) is connected to the steering gear 7 via a tie rod (not shown). ) Are connected so that the wheels can be steered.
  • the intermediate shaft 5 has a female shaft 10 and a male shaft 11 that are non-rotatable and slidably fitted.
  • the female shaft 10 is on the upper side of the vehicle, and the male shaft 11 is on the lower side of the vehicle. It is set to be. Thereby, as will be described later, it is possible to effectively prevent water or the like from entering the intermediate shaft 5.
  • both shafts 10 and 11 is formed with an accordion-like portion 20 that is extendable in the axial direction, and an outer peripheral surface of the male shaft 11 1 formed at one end of the accordion-like portion 20.
  • a seal member S composed of a seal portion 30 that comes into contact with a moderate tightening margin is attached.
  • a dustproof boot B shown in FIG. 2 may be attached.
  • the bellows-shaped portion 20 of the seal member S or dustproof block B may have a plurality of corrugated shapes as shown in FIG. 1B, or a single chevron shape as shown in FIG. 1C. It may be in shape.
  • FIG. 2 is a longitudinal sectional view of the telescopic shaft for vehicle steering according to the first embodiment of the present invention.
  • the telescopic shaft itself has the same configuration as the telescopic shaft shown in FIGS. 12 and 13 A and 13 B, and the description thereof is omitted.
  • the cylindrical body 48 shown in Fig. 1 2 and Fig. 1 3 A, 1 3 B it has a convex strip shape such as a circular arc section formed directly on the male shaft 1 1 like spline fitting. It may be.
  • An elastic bellows-shaped dustproof boot B is provided.
  • the dustproof boot B is formed of an elastic body such as rubber, and has an accordion-like bellows-like portion 20 that is freely stretchable in the axial direction, and a concave step portion of the female shaft 10 that is formed at one end of the bellows-like portion 20.
  • the telescopic shaft shown in Fig. 2 slides using rolling, so the sliding load is very light and stable.
  • the slide load varies little within the sliding range and is characterized by a low sliding load.
  • the dustproof boot B having the bellows-shaped part 20 is mounted on the telescopic shaft of such a low sliding load, the volume change such as air compression occurs in the internal space of the dustproof boot B. No fluctuation in sliding load on the telescopic shaft can be suppressed. Accordingly, it is possible to use the telescopic shaft outdoors while maintaining the characteristics of the telescopic shaft with a low sliding load as described above.
  • FIG. 3A is a longitudinal sectional view of a telescopic shaft for vehicle steering according to a second embodiment of the present invention
  • FIG. 3B is an enlarged sectional view of the seal member shown in FIG. 3A.
  • the fitting portions of both shafts 10 and 11 are formed at the end of the bellows-like portion 20 and the bellows-like portion 20 that are extendable in the axial direction.
  • a seal member S composed of a seal portion 30 that contacts the outer peripheral surface of the male shaft 11 with an appropriate tightening margin is attached.
  • the seal member S is formed of an elastic body such as rubber, and has a bellows-like portion 20 that can be expanded and contracted in the axial direction. 1 0 a A bellows-like part 20 for fixing the bellows-like part 20 and a seal formed on the other end of the bellows-like part 20 and contacting the outer peripheral surface of the male shaft 11 with an appropriate tightening margin Part 30. Further, as shown in FIG. 3B, the seal portion 30 includes a plurality of lip portions 31, 31, and 31.
  • the internal space of the bellows-shaped portion 20 does not cause a volume change such as air compression, and the telescopic shaft The fluctuation of the sliding load can be suppressed.
  • the seal portion 30 is configured to slidably contact the outer peripheral surface of the male shaft 11. .
  • the volume of the internal space of the bellows-shaped part 20 can be increased, and the normal use area (small displacement area such as vibration absorption) can be increased or decreased.
  • the bellows-like portion 20 is made an optimum size, it is possible to improve the mountability as compared with the first embodiment described above.
  • FIG. 4A and FIG. 4B relate to a third embodiment of the present invention, and are longitudinal sectional views according to modifications of the female / male shaft, respectively.
  • FIG. 5 is an enlarged cross-sectional view of the female / male shaft shown in FIG. 4A. 4A and 4B is the same as that of the second embodiment described above in the modification of the female and male shafts. (Screw adjustable slider)
  • the end of the male shaft 11 is formed in a hollow or cylindrical shape, and a plurality of (in the illustrated example, four) slits 51 are formed in the axial direction. It is extended. As a result, the end of the male shaft 11 can be reduced or expanded.
  • a screw-type diameter adjusting mechanism is provided at the hollow end of the male shaft 11. That is, as shown in FIG. 5, a nut member 52 having a female screw on its inner peripheral surface is erected in the radial direction, and an adjusting bolt 53 is screwed into the nut member 52. .
  • a support member 54 is provided opposite to the nut member 52, and the tip of the adjustment port 53 is brought into contact with the support member 54 so that it can be pressed.
  • the adjustment port 53 is adjusted to reduce the pressing force from the adjustment port 53 to the support member 54, the hollow end portion of the male shaft 11 provided with the slit 51 is reduced in diameter. . As a result, the sliding resistance of the female and male shafts 10 and 11 can be reduced.
  • the adjustment bolt 53 When the adjustment bolt 53 is adjusted to increase the pressing force from the adjustment bolt 53 to the support member 54, the hollow end portion of the male shaft 11 provided with the slit 51 expands. As a result, the sliding resistance of the female / male shafts 10 and 11 can be increased.
  • the intermediate shaft 5 includes a female shaft 10 and a male shaft 11 that are spline-fitted.
  • a female spline portion 10 c is formed on the inner peripheral surface of the female shaft 10
  • a male spline portion 1 1 c is formed on the outer peripheral surface of the male shaft 1 1.
  • 0 and 11 are configured to be slidable and not rotatable relative to each other.
  • the male spline portion 1 1 c of the male shaft 1 1, the female spline portion 1 0 c of the female shaft 1 0, or both the shafts 1 0 and 1 1 are coated with resin or a solid lubricant film. May be.
  • the sliding resistance can be reduced when the female / male shafts 10 and 11 are rocked.
  • FIG. 6A, FIG. 6B, FIG. 7A, and FIG. 7B are enlarged cross-sectional views of the seal member according to the fourth embodiment of the present invention.
  • the basic structure of this embodiment is the same as that of the second embodiment described above, and only different points will be described.
  • the seal portion 30 is formed with a pair of lip portions 3 1 and 3 1, and a grease reservoir portion 3 2 is formed between the pair of lip portions 3 1 and 3 1. It is formed.
  • This grease reservoir 3 2 can improve waterproofness, and can reduce wear caused by the lip portions 31 and 31 when a large peristaltic load is required.
  • a metal ring 33 is embedded in the seal part 30.
  • the solid lubricant film SLM is coated on the seal surface of the seal part 30 on which the lip parts 31, 31 and 31 are formed. Thereby, wear of the lip portions 31 can be reduced, and sliding resistance can be reduced when the male shaft 11 and the lip portion 31 slide.
  • the solid lubricating film S L M is coated on the outer peripheral surface of the male shaft 11.
  • FIG. 8A is a longitudinal sectional view of a telescopic shaft for vehicle steering according to a fifth embodiment of the present invention
  • FIGS. 8B and 8C are enlarged sectional views of the seal member shown in FIG. 8A, respectively. It is.
  • the seal portion 30 has a resin ring 34 that is exposed to the seal surface and adjacent to the lip portion 31.
  • This resin ring 3 4 has low friction and excellent wear resistance such as dry bearings. It is. Thereby, the followability to the inclination of the male shaft 11 can be increased, and the sealing performance can be improved. Further, since the lip portion 3 1 only needs to bear the gap between the resin ring 3 4 and the male shaft 11 1, the friction caused by the lip portion 3 1 can be minimized.
  • a metal ring 3 3 is embedded in the seal portion 30, and a resin ring 3 4 is press-fitted into the metal ring 33.
  • FIG. 9A is a longitudinal sectional view of a telescopic shaft for vehicle steering according to a sixth embodiment of the present invention
  • FIG. 9B and FIG. 9C are enlarged sectional views of the seal member shown in FIG. 9A, respectively. It is.
  • the metal ring 3 3 is embedded in the seal part 30, and the resin ring 35 having the lip parts 3 5a and 3 5a is press-fitted into the metal ring 3 3. .
  • This resin ring 35 is a resin such as an elastomer material.
  • a metal ring 3 3 is embedded in the seal part 30, and an elastic ring 36 having lip parts 3 6a and 3 6a is fixed to the metal ring 3 3. .
  • This elastic ring 36 is made of rubber with high hardness.
  • FIG. 10A, FIG. 10B, and FIG. 10C are longitudinal sectional views of the telescopic shaft for vehicle steering according to the seventh embodiment of the present invention.
  • FIGS. 11A and 11B are also longitudinal sectional views of the telescopic shaft for vehicle steering according to the seventh embodiment of the present invention.
  • the fitting portion of the male shaft 11 with the female shaft 10 is enlarged in diameter to form a stepped portion 11a.
  • Fig. 1 OA is a basic set state, and the seal part 30 is located at a distance A from the step part 1 1 a of the male shaft 11 1.
  • Fig. 10B shows a state where both shafts 10, 11 are extended by a minute distance (1)
  • Fig. 10C shows a state where both shafts 10, 11 are contracted by a minute distance (1).
  • the seal portion 30 is a force at distances B and C from the step portion 11a.
  • ABC is a small displacement. In other words, the distance from the stepped portion 1 1 a to the seal 30 does not change much at the minute displacement (1).
  • Fig. 11A shows a state in which both shafts 10 and 11 are greatly extended from each other by a distance (L)
  • Fig. 11B shows a state in which both shafts 10 and 11 are contracted from each other by a distance (L). . Where 1 ⁇ L.
  • the relationship between the axial displacement resistance of the bellows-shaped portion 20 and the sliding resistance of the seal portion 30 is as follows.
  • the resistance is set to be smaller than the sliding resistance of the seal portion 30.
  • the sliding resistance of the seal part 30 is set to be smaller than the axial displacement resistance of the bellows-like part 20 when it becomes larger than that at the time of slight displacement.
  • the inflection point between the axial displacement resistance of the bellows-like part 20 and the sliding resistance of the seal part 30 is set to be less than the maximum relative displacement (about ⁇ 2.5 mm) during actual vehicle travel.
  • the axial displacement resistance of the bellows-shaped part 20 is smaller than the sliding resistance of the seal part 30, and if a large displacement such as a collision occurs, the sliding resistance of the seal part 30 Is smaller than the axial displacement resistance of the bellows-like portion 20.
  • the female shaft 10 is set on the upper side of the vehicle, and the male shaft 11 is set on the lower side of the vehicle. As a result, it is possible to effectively prevent water and the like from entering the intermediate shaft 5.

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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)
  • Ocean & Marine Engineering (AREA)
  • Steering Controls (AREA)
  • Sealing Devices (AREA)

Abstract

L’invention porte sur un arbre télescopique pour direction de véhicule, où une section à laquelle sont raccordés un arbre femelle et un arbre mâle est scellée hermétiquement pour empêcher la pénétration d’eau de pluie, d’eau boueuse et de poussière dans la section de raccord et limite toute variation de la contrainte de glissement. Un élément d’étanchéité (S) est formé à partir d’un corps élastique comme du caoutchouc et se compose d’une section télescopable axialement en forme de soufflet (20), une section de fixation (21) formée en une extrémité de la section en forme de soufflet (20) et fixant la section en forme de soufflet (20) à une section échelonnée rétreinte (10a) d’un arbre femelle (10), et une section hermétique (30) formée à l’autre extrémité de la section en forme de soufflet (20) et au contact, avec une interférence appropriée, de la surface périphérique externe d’un arbre mâle (11). Dans une zone d’utilisation normale (zone de très faible déplacement comme une absorption de vibrations), aucun changement de volume, comme la compression d’air, ne se produit dans l‘espace interne de la section en forme de soufflet (20), pour limiter toute variation de contrainte de glissement sur l’arbre télescopique. Par ailleurs, au moment de l’installation de l’arbre télescopique sur un véhicule ou bien si l’arbre télescopique coulisse nettement comme en cas de collision, la section hermétique (30) glisse sur la surface périphérique externe de l’arbre mâle (11).
PCT/JP2005/013428 2004-07-21 2005-07-14 Arbre télescopique pour direction de véhicule WO2006009230A1 (fr)

Priority Applications (1)

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JP2006529285A JPWO2006009230A1 (ja) 2004-07-21 2005-07-14 車両ステアリング用伸縮軸

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JP2004-213398 2004-07-21
JP2004213398 2004-07-21

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WO2006009230A1 true WO2006009230A1 (fr) 2006-01-26

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PCT/JP2005/013428 WO2006009230A1 (fr) 2004-07-21 2005-07-14 Arbre télescopique pour direction de véhicule

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JP (1) JPWO2006009230A1 (fr)
WO (1) WO2006009230A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008261371A (ja) * 2007-04-10 2008-10-30 Ntn Corp シール構造
DE102007031186A1 (de) * 2007-07-04 2009-01-08 Mtu Friedrichshafen Gmbh Antriebswelle
EP2167830A1 (fr) * 2007-06-25 2010-03-31 GKN Driveline North America, Inc. Soufflet de protection à volume variable
EP2551060A1 (fr) * 2011-07-26 2013-01-30 Black & Decker Inc. Marteau perforateur
JP2013142437A (ja) * 2012-01-10 2013-07-22 Nsk Ltd 伸縮軸
JP2020157887A (ja) * 2019-03-26 2020-10-01 株式会社山田製作所 ステアリングシャフト

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6075168U (ja) * 1983-10-29 1985-05-27 いすゞ自動車株式会社 チルトキヤブのステアリングシヤフト防塵装置
JPS6117373U (ja) * 1984-07-07 1986-01-31 マツダ株式会社 ステアリングシヤフト
JPH06241238A (ja) * 1993-02-19 1994-08-30 Nippon Seiko Kk 伸縮軸用シール装置
JPH1148991A (ja) * 1997-08-08 1999-02-23 Nippon Seiko Kk ステアリング中間軸継手
JPH11334607A (ja) * 1998-05-29 1999-12-07 Nippon Seiko Kk ステアリング装置のシャフト用シール装置
JP2000052360A (ja) * 1998-08-11 2000-02-22 Marugo Rubber Ind Co Ltd 自動車のステアリング用ダストシール及びその製造方法
JP2001221245A (ja) * 1999-12-02 2001-08-17 Koyo Seiko Co Ltd 伸縮自在シャフト
JP2002193117A (ja) * 2000-09-26 2002-07-10 Torrington Co:The ステアリングコラム・スライダ組立体
JP2004122938A (ja) * 2002-10-02 2004-04-22 Nsk Ltd 車両ステアリング用伸縮軸

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6075168U (ja) * 1983-10-29 1985-05-27 いすゞ自動車株式会社 チルトキヤブのステアリングシヤフト防塵装置
JPS6117373U (ja) * 1984-07-07 1986-01-31 マツダ株式会社 ステアリングシヤフト
JPH06241238A (ja) * 1993-02-19 1994-08-30 Nippon Seiko Kk 伸縮軸用シール装置
JPH1148991A (ja) * 1997-08-08 1999-02-23 Nippon Seiko Kk ステアリング中間軸継手
JPH11334607A (ja) * 1998-05-29 1999-12-07 Nippon Seiko Kk ステアリング装置のシャフト用シール装置
JP2000052360A (ja) * 1998-08-11 2000-02-22 Marugo Rubber Ind Co Ltd 自動車のステアリング用ダストシール及びその製造方法
JP2001221245A (ja) * 1999-12-02 2001-08-17 Koyo Seiko Co Ltd 伸縮自在シャフト
JP2002193117A (ja) * 2000-09-26 2002-07-10 Torrington Co:The ステアリングコラム・スライダ組立体
JP2004122938A (ja) * 2002-10-02 2004-04-22 Nsk Ltd 車両ステアリング用伸縮軸

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008261371A (ja) * 2007-04-10 2008-10-30 Ntn Corp シール構造
EP2167830A1 (fr) * 2007-06-25 2010-03-31 GKN Driveline North America, Inc. Soufflet de protection à volume variable
EP2167830A4 (fr) * 2007-06-25 2011-12-28 Gkn Driveline North America Soufflet de protection à volume variable
DE102007031186A1 (de) * 2007-07-04 2009-01-08 Mtu Friedrichshafen Gmbh Antriebswelle
DE102007031186B4 (de) * 2007-07-04 2013-08-08 Ifa-Technologies Gmbh Antriebswelle
EP2551060A1 (fr) * 2011-07-26 2013-01-30 Black & Decker Inc. Marteau perforateur
JP2013142437A (ja) * 2012-01-10 2013-07-22 Nsk Ltd 伸縮軸
JP2020157887A (ja) * 2019-03-26 2020-10-01 株式会社山田製作所 ステアリングシャフト
JP7254575B2 (ja) 2019-03-26 2023-04-10 株式会社山田製作所 ステアリングシャフト

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