WO2004056638A1 - 車両ステアリング用伸縮軸 - Google Patents
車両ステアリング用伸縮軸 Download PDFInfo
- Publication number
- WO2004056638A1 WO2004056638A1 PCT/JP2003/016088 JP0316088W WO2004056638A1 WO 2004056638 A1 WO2004056638 A1 WO 2004056638A1 JP 0316088 W JP0316088 W JP 0316088W WO 2004056638 A1 WO2004056638 A1 WO 2004056638A1
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- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- female
- male
- spherical body
- torque
- Prior art date
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Classifications
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- 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
- B62D1/185—Steering columns yieldable or adjustable, e.g. tiltable adjustable by axial displacement, e.g. telescopically
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- 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
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- 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
- F16C29/007—Hybrid linear bearings, i.e. including more than one bearing type, e.g. sliding contact bearings as well as rolling contact bearings
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- 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
- F16C29/04—Ball or roller bearings
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- 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
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- 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
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- 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
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- 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 relates to a telescopic shaft for a vehicle steering which is assembled into a steering shaft of a vehicle, and a male shaft and a female shaft are fitted to each other so as to be non-rotatable and slidable.
- the telescopic shaft of the steering mechanism of an automobile must be capable of absorbing the axial displacement that occurs when the automobile runs and not transmitting the displacement and vibration to the steering wheel.
- the driver must be able to move the steering wheel in the axial direction and adjust its position in order to obtain the optimal position for driving the car.
- the telescopic shaft reduces rattling, reduces rattle on the steering wheel, and reduces sliding resistance during axial sliding operation. Is required.
- the wear of the coating film progresses due to the progress of use, and the rotational force may become larger. Also, under the conditions exposed to high temperatures in the engine room, the nylon membrane changes its volume, causing the sliding resistance to become extremely large and the wear to be greatly accelerated. There is.
- Japanese Patent Application Laid-Open No. 2001-520293 discloses that between a plurality of pairs of axial grooves formed on the outer peripheral surface of the male shaft and the inner peripheral surface of the female shaft, respectively. Axial relative of both shafts A torque transmitting member (spherical body) that rolls when moving is fitted.
- a torque transmission member (spherical body) is provided between a radially inner or outer side of a spherical body as a torque transmitting member and a pair of axial grooves, respectively.
- a plate panel which is an elastic body for preload, for applying a preload to the shaft and the female shaft is provided.
- the spherical body which is the torque transmitting member, is preloaded by the leaf spring to the extent that there is no play on the female shaft, so that there is no rattling between the male shaft and the female shaft.
- the male and female shafts can slide in the axial direction with a stable sliding load without play.
- the plate panel when transmitting torque, the plate panel allows the spherical body, which is the torque transmitting member, to be constrained in the circumferential direction, so that the male shaft and the female shaft prevent rattling in the rotation direction. Torque can be transmitted with high rigidity.
- the present invention has been made in view of the above-described circumstances, and realizes a stable sliding load, reliably prevents backlash in the rotational direction, and can transmit torque in a highly rigid state.
- a telescopic shaft for vehicle steering is used for a vehicle.
- the male shaft and the female shaft are fitted non-rotatably and slidably,
- a spherical body that rolls when the two shafts move relative to each other in the axial direction is disposed between at least a pair of axial grooves formed on the outer peripheral surface of the male shaft and the inner peripheral surface of the female shaft, respectively.
- An elastic body that applies a preload to the male shaft and the female shaft via the spherical body is interposed between the axial groove on the male shaft side or the female shaft side and the spherical body,
- a cylindrical body that slides when the two shafts are moved relative to each other in the axial direction is disposed between at least another pair of axial grooves formed on the outer peripheral surface of the male shaft and the inner peripheral surface of the female shaft, respectively.
- the radius of curvature of the cross section of the axial groove on the male shaft side or the female shaft side on which the spherical body rolls is set to 55% or less of the diameter of the spherical body.
- the radius of curvature of the cross section of the axial groove on the male or female shaft side on which the spherical body rolls is set to 55% or less of the diameter of the spherical body. Therefore, the contact pressure between the spherical body and the axial groove can be suppressed to 150 OMPa or less even at the assumed maximum torsional torque input.
- the surface hardness of the telescopic shaft becomes a general hardness (for example, HV266 to HV30). (Approximately 0), it is possible to reliably prevent indentation.
- FIG. 1A is a side view of a telescopic shaft for vehicle steering according to a first embodiment of the present invention
- FIG. 1B is a perspective view thereof
- FIG. 2 is a cross-sectional view taken along line AA of FIG. 1A.
- FIG. 3 is a schematic diagram showing a calculation model of an analysis program for torsional rigidity of a telescopic shaft.
- Figure 4 is a graph showing the results of the torsional stiffness test of the prototype telescopic shaft as solid lines and the results of calculations by the analysis program as dashed lines.
- FIG. 5A is a longitudinal sectional view of a telescopic shaft for vehicle steering according to a second embodiment of the present invention
- FIG. 5B is a transverse sectional view taken along the line bb of FIG. 5A.
- FIG. 6 is an exploded perspective view of a telescopic shaft for vehicle steering according to a second embodiment.
- FIG. 7 is a graph showing a calculation result of the maximum contact pressure between the spherical body of the telescopic shaft and the female shaft side axial groove shown in FIGS. 5A, 5B and 6 according to the second embodiment. .
- FIG. 8 shows a spherical body of a telescopic shaft and a female shaft side axial direction disclosed in Japanese Patent Application Laid-Open No. 2001-520293 or German Patent Invention DE 3730309C2.
- 9 is a graph showing a calculation result of a maximum contact pressure with a groove.
- FIG. 9 is a side view of a steering mechanism of an automobile to which the telescopic shaft for vehicle steering according to the embodiment of the present invention is applied.
- FIG. 9 is a side view of a steering mechanism of an automobile to which the telescopic shaft for vehicle steering according to the embodiment of the present invention is applied.
- an upper steering shaft section 120 (a steering column 103, which is attached to a vehicle body member 100 via an upper bracket 101 and a lower bracket 102). (Including the steering shaft 104 rotatably held by the steering column 103) and the upper end of the steering shaft 104 Steering shafts are attached to the mounted steering wheel 105, the mouth steering shaft 107 connected to the lower end of the steering shaft 104 via the universal joint 106, and the lower steering shaft 107.
- a pinion shaft 109 connected via a joint 108, a steering rack shaft 111 connected to the pinion shaft 109, and another frame of the vehicle body supporting the steering rack shaft 112
- a steering mechanism is constituted by a steering rack support member 113 fixed to 110 via an elastic body 111.
- the telescopic shaft 107 uses a telescopic shaft for vehicle steering (hereinafter referred to as a telescopic shaft) according to the embodiment of the present invention.
- the lower steering shaft portion 107 is a combination of a male shaft and a female shaft.
- Such an opening steering shaft portion 107 is provided with an axial displacement generated when a vehicle travels. It is necessary to have a performance that absorbs and does not transmit the displacement and vibration on the steering wheel 105. This performance is due to the fact that the body has a sub-frame structure, and the member 100 that fixes the upper part of the steering mechanism and the frame 110 to which the steering rack support member 113 is fixed are separate bodies.
- the steering rack support member 113 is fastened and fixed to the frame 110 via an elastic body 111 such as rubber.
- the operator contracts the extension shaft once and then fits it to the pinion shaft 109 for expansion and contraction. May be required.
- the upper stem part 120 at the upper part of the steering mechanism also has a male shaft and a female shaft fitted to each other. In order to obtain the optimal position, the function of moving the position of the steering wheel 105 in the axial direction and adjusting the position is required, so that the function of expanding and contracting in the axial direction is required. In all of the above cases, reducing the rattling noise of the fitting part on the telescopic shaft, reducing the rattling feeling on the steering wheel 105, and reducing the axial sliding , It is required to reduce the sliding resistance.
- FIG. 1A is a side view of a telescopic shaft for vehicle steering according to a first embodiment of the present invention
- FIG. 1B is a perspective view thereof
- FIG. 2 is a cross-sectional view along the line A—A of FIG. 1A.
- a telescopic shaft for vehicle steering (hereinafter referred to as a telescopic shaft) is composed of a male shaft 1 and a female shaft 2 which are non-rotatably and slidably fitted to each other.
- three substantially arc-shaped grooves 3, 4, and 4 equally distributed at 120 ° intervals in the circumferential direction are formed to extend in the axial direction.
- three substantially arc-shaped grooves 5, 6, and 6 equally distributed at 120 ° intervals in the circumferential direction are formed on the inner circumferential surface of the female shaft 2 so as to extend in the axial direction. It is.
- the first interposed portion is formed by the axial grooves 3 and 5, and the second interposed portion is formed by the axial grooves 4, 6;
- a preload (described later) as an elastic body extending in the axial direction and having a substantially M-shaped cross section is provided between the axial groove 3 having a substantially circular cross section of the male shaft 1 and the axial groove 5 having a substantially circular cross section of the female shaft 2.
- a plate panel 9 is provided, and a plurality of rigid spherical bodies 7 are rotatably interposed between the central recess of the panel panel 9 and the axial groove 5 as a plurality of first torque transmitting members.
- a torque transmission device is configured.
- the two axial grooves 4, 4 of the male shaft 1 are substantially arc-shaped or gothic-shaped in cross-section, and the corresponding two axial grooves 6, 6, of the female shaft 2 are also substantially arc-shaped in cross-section. Or Gothic arch.
- a cylindrical member as a second torque transmitting member for transmitting the torque during rotation between the corresponding grooves 4 and 6 that allow the male shaft 1 and the female shaft 2 to move in the axial direction between the corresponding grooves 4 and 6. 8 is slidably disposed to constitute a second torque transmission device.
- grooves 3b, 3b are formed extending in the axial direction parallel to the groove 3, and between the axial groove 3 and the grooves 3b, 3b. Step extending axially in a ridge Parts 3a and 3a are formed.
- the panel panel 9 has a substantially M-shaped cross section, and both ends extend to the bottoms of the grooves 3b, 3b, respectively, and the tips contact the steps 3a, 3a so as to sandwich the steps 3a, 3a, respectively. ing.
- the plate panel 9 preloads the spherical body 7 and the cylindrical bodies 8 and 8 to the female shaft 2 so that there is no backlash when the torque is not transmitted, while the torque is transmitted to the spherical body 7 by elastic deformation.
- the male shaft 1 and the female shaft 2 serve to restrain in the circumferential direction.
- the plurality of spheres 7 are held by a retainer 12, and the sphere 7 and the retainer 12 are restricted from moving in the axial direction by a retaining ring 11 during sliding.
- the spherical body 7 and the cylindrical body 8 are interposed between the male shaft 1 and the female shaft 2, and the spherical body 7 and the cylindrical body 8 are connected to the female shaft 2 by the leaf spring 9.
- preload is applied to the extent that there is no looseness, when torque is not transmitted, looseness between the male shaft 1 and the female shaft 2 can be reliably prevented, and the male shaft 1 and the female shaft When the shaft 2 relatively moves in the axial direction, the shaft 2 can move with a stable sliding load without play.
- the preload can be increased without significantly increasing the sliding load.
- the plate panel 9 is elastically deformed and the spherical body 7 is deformed.
- the two shafts 8 interposed between the male shaft 1 and the female shaft 2 play a major role in transmitting torque, while being constrained in the circumferential direction between the male shaft 1 and the female shaft 2.
- the plate panel 9 when torque is input from the male shaft 1, in the initial stage, the plate panel 9 is preloaded, so there is no backlash, and the plate spring 9 generates a reaction force against the torque to transmit the torque. I do. At this time, when the torque transmission load between the male shaft 1 ⁇ leaf spring 9 ⁇ spherical body 7 ⁇ female shaft 2 and the torque transmission load between the male shaft 1 ⁇ cylindrical body 8 ⁇ female shaft 2 is balanced, the overall Torque is transmitted.
- the clearance in the rotational direction of the male shaft 1 and the female shaft 2 via the cylindrical body 8 becomes larger than the male shaft 1 via the spherical body 7 ⁇ Panel panel 9 ⁇ Spherical body 7 ⁇ Female Since the clearance between the shafts 2 is set to be smaller, the cylinder 8 receives a stronger reaction force than the spherical body 7, and the cylinder 8 mainly transmits torque to the female shaft 2. Therefore, the rotation of the male shaft 1 and the female shaft 2 can be reliably prevented, and the torque can be transmitted in a highly rigid state.
- the spherical body 7 is preferably a rigid pole. Further, the rigid cylindrical body 8 is preferably a dollar dollar roller.
- the cylindrical body (hereinafter referred to as the needle port) 8 has various effects, such as being able to keep the contact pressure lower than a pole that receives a load by point contact because it receives the load by line contact. Therefore, the following items are superior to the case where all rows are pole-rolled.
- the needle roller can keep the contact pressure lower, so the axial length can be shortened and the space can be used effectively.
- the contact pressure can be kept lower by the needle roller, so that an additional process for hardening the axial groove surface of the female shaft by heat treatment or the like is unnecessary. • The number of parts can be reduced.
- the roller 21 serves as a key for transmitting torque between the male shaft 1 and the female shaft 2 and makes sliding contact with the inner peripheral surface of the female shaft 2.
- the advantages of using needle rollers compared to conventional spline fitting are as follows. ⁇ Needle rollers are mass-produced products and have very low cost.
- the needle roller is polished after heat treatment, so it has a high surface hardness and excellent wear resistance.
- the length and arrangement of the needle roller can be changed according to the conditions of use, making it possible to respond to various applications without changing the design concept.
- the coefficient of friction during sliding may need to be further reduced.At this time, if only the needle roller is surface-treated, its sliding characteristics can be changed, without changing the design concept It can respond to various applications.
- the insertion load can be kept low. • Preload can be increased by using poles, which can prevent long-term rattling and provide high rigidity at the same time.
- FIG. 3 is a schematic diagram showing a calculation model of an analysis program for torsional rigidity of a telescopic shaft.
- Figure 4 is a graph showing the results of the torsional rigidity test of the prototype telescopic shaft as solid lines and the results of calculations by the analysis program as broken lines.
- a program was created to analyze the torsional stiffness of the telescopic shaft using spherical and cylindrical bodies using a computer.
- the female shaft is fixed in space, and the cross-section (two-dimensional) of the telescopic shaft is balanced with the force applied to each sphere or cylinder, and the force applied to the male shaft (sphere Z cylinder / spring load and Solve the balance equation of the given torsional torque).
- the male shaft 1 and the female shaft 2 have three axial grooves 3, 4, 4; 5, 6, 6 respectively, and one axial groove 3, 5 has a plurality of spherical bodies 7, The remaining two axial grooves 4, 4; 6, 6 are provided with cylindrical bodies 8, 8.
- the spherical body 7 is preloaded by a plate spring 9 mounted on the male shaft 1.
- Figure 3 shows the calculation model.
- Figure 4 shows the results of the torsional stiffness test of the prototype telescopic shaft as solid lines, and the results of calculations by the analysis program as dashed lines. The calculated change in torsional rigidity is in good agreement with the measured values.
- FIG. 5A is a longitudinal sectional view of a telescopic shaft for vehicle steering according to a second embodiment of the present invention
- FIG. 5B is an enlarged transverse sectional view taken along the line bb of FIG. 5A
- FIG. 6 is an exploded perspective view of a telescopic shaft for vehicle steering according to a second embodiment.
- a first torque transmission device is configured by disposing a spherical body 7 as a first torque transmission member via a plate panel 9 as an elastic body.
- the second torque transmission device is configured by being arranged.
- the shapes and structures of the three pairs of axial grooves 3 and 5 and the leaf spring 9 are the same as the shapes and structures of the axial grooves 3 and 5 and the plate panel 9 of the first embodiment, respectively. It is. In the second embodiment, the shapes and structures of the three pairs of grooves 4 and 6 extending in the axial direction are the same as the shapes and structures of the axial grooves 4 and 6 in the first embodiment, respectively.
- a product having a different outer diameter of the cylindrical body 8 can be manufactured at low cost in units of several microns, so that the diameter of the cylindrical body 8 can be appropriately selected or combined.
- the gap between male shaft 1 ⁇ cylindrical body 8 ⁇ female shaft 2 can be set arbitrarily. From the above, it is possible to meet various demands that differ depending on the characteristics of the vehicle at low cost without changing the basic structure and without increasing the number of parts.
- FIG. 7 is a graph showing the calculation result of the maximum contact pressure between the spherical body of the telescopic shaft and the female-side axial groove shown in the second embodiment (FIGS. 5A, 5B, and 6). .
- FIG. 8 shows a spherical body of a telescopic shaft and a female shaft side axial direction disclosed in Japanese Patent Application Laid-Open No. 2001-520293 or German Patent Invention DE 3730309C2.
- 9 is a graph showing a calculation result of a maximum contact pressure with a groove.
- the torque is transmitted mainly through the needle port 8 which is interposed between the female shaft 2 and the male shaft 1, but a part of the torque is also transmitted to the pole 7 which is preloaded by the spring. Be shared.
- the needle roller 8 is in line contact with the female shaft 2 and the male shaft 1 and has a wide contact area. Therefore, even if the contact load is large, the contact pressure is relatively small and does not pose a problem.
- the ball 7 makes point contact with the axial groove 5 on the female shaft 2 and the surface of the plate panel 9.
- the load supported by the ball 7 for transmitting the torque is smaller than that of the needle roller 8, but the contact pressure may be significantly higher due to the point contact where the contact area is narrow.
- Fig. 7 shows the results of calculating the maximum contact pressure between the pole 7 and the axial groove 5 of the female shaft 2 for the torsional torque of 10 O Nm using an analysis program.
- the cross-sectional shape of the axial groove 5 is a Gothic arch shape.
- the horizontal axis of the graph represents the radius of curvature of the cross section of the axial groove 5 on the female shaft 2 side as a ratio to the diameter of the pole 7. are doing.
- the maximum contact pressure between the ball 7 and the female shaft 2 increases, and the axial groove 5 on the female shaft 2 side has a V-groove (the groove surface is flat, When the radius is infinity), the pressure becomes close to 300 OMPa.
- the hardness required to prevent indentation can be considered as follows.
- the relationship between the yield stress Y and the Vickers hardness HV of a material is approximately expressed by the following equation (Toru Yoshida, Surface hardening technology for design engineers, Nikkan Kogyo Shimbun).
- HV-6 X Y (1) where, HV: Vickers hardness of the material, ⁇ Y: Yield shear stress of the material [kg f / mm 2 ],
- HV 0.6 X Y (2) where Y is the yield shear stress [MPa] of the material.
- Equation (5) Since the maximum shear stress occurs slightly inside the surface of the material, strictly speaking, the maximum contact pressure and the hardness at the depth where the maximum shear stress occurs must satisfy Equation (5). No. However, considering that the surface is hardest in the ordinary surface hardening treatment, and the hardness decreases toward the inside, the surface hardness also needs to satisfy Expression (5).
- the hardness is high, but the Brinell hardness is about 190 HB (for example, JIS Handbook [1] The Japan Standards Association), when converted to Pisces hardness, is about HV200 (same document).
- the maximum contact pressure Pmax cannot exceed 100 OMPa to prevent indentations due to permanent deformation of the surface.
- plastic working which can be manufactured at a lower cost, is preferable to machining such as cutting.
- plastic working due to work hardening, the surface hardness of the material is improved compared to before processing.
- the surface hardness of the telescopic shaft parts prototyped by the inventors through plastic working was about HV260 to HV300.
- the radius of curvature of the axial groove 5 can be adjusted to keep the maximum contact pressure Pmax at 150 OMPa or less even under a load of 10 ONm. It can be seen that it is better to make 55% or less of the diameter of the pole 7.
- Japanese Patent Application Laid-Open No. 2001-50293 and German Patent Application DE 3730393 C2 disclose a plurality of poles interposed in axial grooves formed in a male shaft and a female shaft. A structure preloaded by an elastic body is disclosed.
- the contact pressure of the pole contact part was calculated using an analysis program.
- Fig. 8 shows the results of calculating the maximum contact pressure between the pole and the female shaft with respect to the torsional torque of 100 ONm using an analysis program.
- the horizontal axis of the graph represents the radius of curvature of the axial groove (Gothic approach shape) on the female shaft side in the cross section perpendicular to the axis as a ratio to the pole diameter, as in FIG.
- the maximum contact pressure between the pole and the female shaft increases.
- the pressure becomes higher than 0 0 OMPa.
- the treatment may cause deformation of the raceway surface, and a uniform sliding load may not be obtained.
- performing surface hardening treatment such as heat treatment will increase the cost itself, but if machining or other treatment is required to remove deformation after treatment, the production cost will further increase.
- German Patent DE 37 03 093 3 C2 in order to avoid such a problem relating to a large contact pressure between the pole and the mating member, the surface in contact with the pole has a high hardness.
- a structure formed of a plate material for example, a heat-treated spring steel plate. Arranging plates at all contact points requires preparing multiple parts with complicated shapes, which is costly.
- the present invention By applying the present invention to the second embodiment (FIGS. 5A, 5B, and 6), the axial direction in which the pole 7 rolls can be obtained without performing any surface hardening treatment such as heat treatment. Indentation of the track portion of the groove 5 can be prevented.
- Japanese Patent Application Laid-Open Publication No. 2000-520293 and German Patent Invention DE 37 30 393 C2 it has a low cost, a compact structure, and a smooth structure. It is possible to provide a telescopic shaft for steering which has excellent sliding characteristics, has no torque, and has high torque transmission capability.
- the cross-sectional shape of the track of the axial groove 5 that contacts the pole 7 is a Gothic arch shape.
- the present invention can be similarly applied to other curves such as a parabola with respect to the cross-sectional radius of curvature near the contact point where the pole contacts the pole.
- the present invention is also effective for an axial groove having a cross-sectional shape obtained by combining a Gothic arch and a straight line, since the pole mainly contacts the Gothic arch cross-section when a large torsional torque is applied.
- the radius of curvature of the cross section of the orbital groove of the female shaft 2 or the male shaft 1 on which the spherical body 7 rolls is 55% or less of the diameter of the spherical body 7.
- the present invention is not limited to the above-described embodiment, and can be variously modified.
- the radius of curvature of the cross section of the axial groove on the male or female shaft side on which the spherical body rolls is set to 55% or less of the diameter of the spherical body. Therefore, the contact pressure between the spherical body and the axial groove can be suppressed to 150 OMPa or less even at the assumed maximum torsional torque input.
- the contact pressure between the spherical body and the axial groove is suppressed to 150 OMPa or less, the surface hardness of the telescopic shaft becomes a general hardness (HV260 to HV300). ), The occurrence of indentation can be reliably prevented.
- a stable sliding load can be realized, and the torque can be transmitted in a highly rigid state by reliably preventing rotation in the rotational direction.
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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)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2003289114A AU2003289114A1 (en) | 2002-12-20 | 2003-12-16 | Telescopic shaft for motor vehicle steering |
EP03778959A EP1584538A4 (en) | 2002-12-20 | 2003-12-16 | TELESCOPIC COLUMN FOR A MOTOR VEHICLE |
US10/538,728 US20060082120A1 (en) | 2002-12-20 | 2003-12-16 | Telescopic shaft for motor vehicle steering |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002-370654 | 2002-12-20 | ||
JP2002370654A JP2004196261A (ja) | 2002-12-20 | 2002-12-20 | 車両ステアリング用伸縮軸 |
Publications (1)
Publication Number | Publication Date |
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WO2004056638A1 true WO2004056638A1 (ja) | 2004-07-08 |
Family
ID=32677176
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/016088 WO2004056638A1 (ja) | 2002-12-20 | 2003-12-16 | 車両ステアリング用伸縮軸 |
Country Status (6)
Country | Link |
---|---|
US (1) | US20060082120A1 (ja) |
EP (1) | EP1584538A4 (ja) |
JP (1) | JP2004196261A (ja) |
CN (1) | CN1741931A (ja) |
AU (1) | AU2003289114A1 (ja) |
WO (1) | WO2004056638A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1650452A3 (en) * | 2004-10-25 | 2006-05-03 | Nsk Ltd. | Steering device |
EP1693579A3 (en) * | 2005-02-16 | 2009-04-08 | NSK Ltd., | Telescopic shaft |
Families Citing this family (21)
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DE102005037528B4 (de) * | 2005-08-09 | 2014-01-09 | Schaeffler Technologies AG & Co. KG | Wellenkupplung zur Drehmomentübertragung |
JP4271176B2 (ja) * | 2005-09-15 | 2009-06-03 | 本田技研工業株式会社 | 車両用ステアリング装置 |
JP4921762B2 (ja) * | 2005-09-30 | 2012-04-25 | 株式会社ジェイテクト | 伸縮自在シャフトおよび車両操舵用伸縮自在シャフト |
KR100708876B1 (ko) | 2005-10-10 | 2007-04-18 | 주식회사 만도 | 조향장치의 슬립 조인트 |
JP5152548B2 (ja) | 2006-11-10 | 2013-02-27 | 株式会社ジェイテクト | 車両用操舵装置 |
DE102007048208B4 (de) * | 2007-10-08 | 2009-07-09 | Thyssenkrupp Presta Ag | Lenksäule für ein Kraftfahrzeug |
KR100995851B1 (ko) | 2008-09-02 | 2010-11-22 | 덕창기계주식회사 | 신축 샤프트 |
CN101570213B (zh) * | 2009-06-16 | 2012-09-05 | 奇瑞汽车股份有限公司 | 一种吸能式汽车转向管柱 |
WO2012024719A1 (en) * | 2010-08-24 | 2012-03-01 | David Stuckey Investments Pty Ltd | Locking arrangement |
US9561817B2 (en) * | 2012-10-31 | 2017-02-07 | Austlen Baby Co. | Stroller with telescopic and locking members |
CN107444471B (zh) * | 2017-07-31 | 2019-05-07 | 安徽江淮汽车集团股份有限公司 | 转向传动轴连接结构 |
CN113483957B (zh) * | 2021-08-16 | 2023-03-21 | 上汽通用五菱汽车股份有限公司 | 一种汽车转向器密封性能耐久试验检测装置 |
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EP1106851B1 (de) * | 1999-12-10 | 2001-08-01 | SKF LINEARSYSTEME GmbH | Wälzlager für Längsbewegungen |
US6761503B2 (en) * | 2002-04-24 | 2004-07-13 | Torque-Traction Technologies, Inc. | Splined member for use in a slip joint and method of manufacturing the same |
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2003
- 2003-12-16 WO PCT/JP2003/016088 patent/WO2004056638A1/ja not_active Application Discontinuation
- 2003-12-16 US US10/538,728 patent/US20060082120A1/en not_active Abandoned
- 2003-12-16 EP EP03778959A patent/EP1584538A4/en not_active Withdrawn
- 2003-12-16 AU AU2003289114A patent/AU2003289114A1/en not_active Abandoned
- 2003-12-16 CN CNA2003801090518A patent/CN1741931A/zh active Pending
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1650452A3 (en) * | 2004-10-25 | 2006-05-03 | Nsk Ltd. | Steering device |
EP1693579A3 (en) * | 2005-02-16 | 2009-04-08 | NSK Ltd., | Telescopic shaft |
Also Published As
Publication number | Publication date |
---|---|
AU2003289114A8 (en) | 2004-07-14 |
EP1584538A1 (en) | 2005-10-12 |
AU2003289114A1 (en) | 2004-07-14 |
US20060082120A1 (en) | 2006-04-20 |
JP2004196261A (ja) | 2004-07-15 |
EP1584538A4 (en) | 2006-11-29 |
CN1741931A (zh) | 2006-03-01 |
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