WO2019035395A1 - Power transmission shaft - Google Patents

Power transmission shaft Download PDF

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Publication number
WO2019035395A1
WO2019035395A1 PCT/JP2018/029687 JP2018029687W WO2019035395A1 WO 2019035395 A1 WO2019035395 A1 WO 2019035395A1 JP 2018029687 W JP2018029687 W JP 2018029687W WO 2019035395 A1 WO2019035395 A1 WO 2019035395A1
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WO
WIPO (PCT)
Prior art keywords
shaft member
metal
resin
convex
power transmission
Prior art date
Application number
PCT/JP2018/029687
Other languages
French (fr)
Japanese (ja)
Inventor
真 友上
卓 板垣
Original Assignee
Ntn株式会社
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Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2019035395A1 publication Critical patent/WO2019035395A1/en

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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
    • 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
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/064—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable
    • F16D1/068—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable involving gluing, welding or the like
    • 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
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members

Definitions

  • the present invention relates to a power transmission shaft, and more particularly to a power transmission shaft used in automobiles and various industrial machines.
  • the power transmission shaft used in automobiles and various industrial machines is generally made of steel.
  • steel products are heavy.
  • fiber reinforced plastics such as CFRP (carbon fiber reinforced plastic) may be used for weight reduction.
  • Patent Document 1 and Patent Document 2 there is one in which the bondability between the fiber reinforced plastic and the steel member is considered (Patent Document 1 and Patent Document 2).
  • Patent Document 1 at an end portion of a fiber reinforced plastic (FRP) tube body, a metal yoke is joined via a rivet. Further, in Patent Document 2, serrations are formed on the outer diameter surface and the inner diameter surface of the intermediate cylindrical member, and when the intermediate cylindrical member is pressed into the end of the FRP cylinder, the serration on the outer diameter surface is made of FRP. It bites into the inner diameter surface of the end of the cylinder. Further, by inserting the press-fit shaft portion of the metal yoke into the intermediate cylindrical member, the serration formed on the outer diameter surface of the press-fit shaft portion of the metal yoke is engaged with the serration of the inner diameter surface. As a result, the metal yoke is joined to the FRP cylinder.
  • FRP fiber reinforced plastic
  • the present invention can achieve weight reduction by using a resin-made shaft member made of fiber-reinforced plastic, and moreover, the metal-made shaft member and the resin-made shaft member can be joined stably. It is an object of the present invention to provide a power transmission shaft capable of maintaining a state and excellent in torque transmission.
  • the power transmission shaft of the present invention is a power transmission shaft including a metal shaft member and a resin shaft member connected to the metal shaft member along the axial direction, and the resin shaft member is
  • the metal shaft member and the resin shaft member are made of fiber reinforced plastic, and are joined to each other via a fastening structure formed by inflow solidification of the fiber reinforced plastic on the fine uneven surface.
  • the fine uneven surface can be formed by a chemical method such as etching, even if it is a method by physical processing such as shot blasting.
  • the fastening structure is formed by inflow solidification of the fiber reinforced plastic on the fine uneven surface
  • the metal shaft member and the resin shaft member are anchored by the anchoring effect (anchor effect) , Mechanical bonding.
  • the anchor effect is an effect of increasing the adhesive strength by the adhesive penetrating into the fine unevenness of the material surface like the root of a tree and curing in adhesion and painting.
  • the inflow solidification of the fiber-reinforced plastic causes this anchoring effect (anchor effect).
  • a fine asperity surface is formed on the outer surface of the metal shaft member, and the resin shaft member is externally fitted on the fine asperity surface, and a fastening structure is provided between the outer surface of the metal shaft member and the inner diameter surface of the resin shaft member.
  • the part may be formed.
  • a metal cylindrical body is externally fitted and fixed to a metal shaft member, the metal cylindrical body is formed with a fine asperity surface on the outer surface, and the resin shaft member is externally fitted with the fine asperity surface.
  • a fastening structure may be formed between the outer surface of the cylindrical body and the inner diameter surface of the resin shaft member.
  • the metallic shaft member and the metallic cylinder may be made of different materials. For this reason, a metal having a specific gravity smaller than that of the metal shaft member, for example, a metal such as aluminum can be used for the metal cylinder. For this reason, further weight reduction can be achieved as the whole power transmission shaft.
  • the metal shaft member and the metal cylinder be joined via a concavo-convex fitting structure in which the entire area of the fitting contact portion of the protrusion and the recess of the mating member fitting to the protrusion is in close contact .
  • a gap in which rattling occurs in the radial direction and the circumferential direction is not formed.
  • all of the fitting parts contribute to rotational torque transmission, enabling stable rotational torque transmission, and spline fatigue due to friction between spline tooth surfaces.
  • a decrease in strength can be avoided and durability is excellent.
  • no abnormal noise is generated.
  • the strength of the torque transmission portion can be improved, and the power transmission shaft can be made lightweight and compact.
  • the metal shaft member and the resin shaft member are mechanically joined by the anchor effect (anchor effect).
  • anchor effect anchor effect
  • FIG. 1 It is a principal part perspective view of a power transmission shaft of the present invention. It is sectional drawing which shows the joining area
  • FIG. 5 is an enlarged sectional view taken along line XX of FIG. 4; It is a principal part enlarged view of FIG. It is sectional drawing of another uneven
  • FIG. 9 shows a drive shaft using the power transmission shaft 1 according to the present invention, and the power transmission shaft 1 extends in the axial direction between the pair of metal shaft members 2, 2 and the metal shaft members 2, 2. And a resin-made shaft member 3 connected in series. That is, the resin-made shaft member 3 is arrange
  • the drive shaft is formed by connecting a fixed type constant velocity universal joint 31 and a sliding type constant velocity universal joint 32 by a power transmission shaft 1 according to the present invention.
  • a bar field constant velocity universal joint is used as the fixed constant velocity universal joint 31
  • a tripod constant velocity universal joint is used as the sliding constant velocity universal joint 32.
  • the fixed type constant velocity universal joint 31 has an outer joint member 35 in which a plurality of axially extending track grooves 33 are formed in the inner diameter surface 34 and a plurality of axially extending track grooves 36 in the outer diameter surface 37 in the circumferential direction.
  • Inner joint members 38 formed at equal intervals, a plurality of balls 39 transmitting torque by being interposed between the track groove 33 of the outer joint member 35 and the track grooves 36 of the inner joint member 38, and the outer joint member 35
  • a cage 40 for holding the ball 39 interposed between the inner diameter surface 34 of the inner joint member 38 and the outer diameter surface 37 of the inner joint member 38.
  • the sliding type constant velocity universal joint 32 has an outer joint member 52 in which three track grooves 51 extending in the axial direction are provided on the inner circumference and a roller guide surface 51 a facing each other is provided on the inner side wall of each track groove 51;
  • a tripod member 54 having three leg shafts 53 projecting in the radial direction, an inner roller 55 externally fitted to the leg shaft 53, and an outer roller inserted in the track groove 51 and externally fitted to the inner roller 55 56 and the like. That is, the sliding constant velocity universal joint 32 is a double roller type in which the outer roller 56 is rotatable with respect to the leg shaft 53 and movable along the roller guide surface 51a.
  • the tripod member 54 includes a boss 57 and the leg shaft 53. The leg shaft 53 protrudes radially from the circumferential three-way position of the boss 57.
  • the shaft end fitting portion of the power transmission shaft 1 is fitted into the shaft hole of the inner joint member 38 in the fixed type constant velocity universal joint 31 so that torque can be transmitted, and the shaft hole of the tripod member 54 in the sliding type constant velocity universal joint 32
  • the shaft end fitting portion of the power transmission shaft 1 is fitted so as to transmit torque.
  • the end portions of the both-shaft end fitting portion of the power transmission shaft 1 are prevented from coming off by snap rings 25 such as snap rings. That is, circumferential grooves 26, 26 are formed at the end of the shaft end fitting portion, and the snap rings 25, 25 are fitted in the circumferential grooves 26, 26.
  • Male splines 5 and 5 are formed on the outer diameter of the shaft end fitting portion of the power transmission shaft 1, and female splines 27 and 27 are formed in the axial holes of the inner joint member 38 and the tripod member 54 of both constant velocity universal joints. It is formed.
  • the male splines 5 and 5 and the female splines 27 and 27 are engaged by fitting the shaft end fitting portion of the power transmission shaft 1 into the axial hole of the inner joint member 38 and the tripod member 54 of the constant velocity universal joints 31 and 32. By combining them, torque transmission is enabled between the power transmission shaft 1 and the inner joint member 38 and the tripod member 54.
  • a boot 30 is mounted between the power transmission shaft 1 and each of the outer joint members 38 and 52 for preventing foreign matter from the outside and grease from the inside from leaking.
  • the boot 30 includes a large diameter end 30a, a small diameter end 30b, and a bellows 30c connecting the large diameter end 30a and the small diameter end 30b.
  • the large diameter end 30a of the boot 30 is fastened and fixed by the boot band 45 at the open end of the outer joint members 35 and 52, and the small diameter end 30b is fastened by the boot band 46 at the boot mounting portion 6c of the power transmission shaft 1 described later. It is fixed.
  • the metal shaft member 2 is provided with a large diameter boss 4 at one end and a male spline 5 at the other end. That is, the medium diameter portion 6a, the small diameter portion 6b, the boot mounting portion 6c, the small diameter portion 6d, and the medium diameter portion 6e are provided from the large diameter boss portion 4 toward the male spline 5.
  • the circumferential groove 7 is provided in the boot mounting portion 6c, and the small diameter end 30b (see FIG. 9) of the boot 30 is mounted on the boot mounting portion 6c, the inner diameter of the small diameter end 30b in the circumferential groove 7 Part of the face fits.
  • the resin shaft member 3 is made of an FRP (fiber reinforced plastic) cylinder.
  • the FRP cylinder is formed by a filament winding method or a sheet winding method.
  • the filament winding method is a method in which a resin-impregnated carbon fiber (fiber bundle) is wound around a mandrel, formed, heated and cured, and then the mandrel is removed. It is called "sheet winding" to wind a sheet instead of a bundle of fibers.
  • both open end portions 3a, 3a are externally fitted and joined to the large diameter boss portions 4, 4 of the metal shaft members 2, 2, as shown in FIG.
  • the fine uneven surface 8 as shown in FIGS. 3A, 3B, and 3C is formed.
  • the fine concavo-convex surface 8 shown in FIG. 3A is composed of a large number of concave portions 9a and a large number of convex portions 9b, and each concave portion 9a and the convex portions 9b differ in their cross-sectional shape from a circle, an ellipse, a rectangle, a polygon, etc. It is considered to be a different form.
  • the fine uneven surface 8 shown in FIG. 3B has a large number of concave portions 9c having a triangular shape whose cross-sectional shape has a rounded top, and a triangular shape whose cross-sectional shape has a rounded top. It consists of many convex parts 9d.
  • the micro uneven surface 8 shown in FIG. 3C is composed of a large number of convex portions 9 f having a flat triangular shape in cross section, and a large number of trapezoidal concave portions 9 e provided between the convex portions.
  • the fine uneven surface 8 as shown in FIGS. 3A, 3B, and 3C can be formed by a physical processing method such as shot blasting, a chemical method such as etching, or the like.
  • Shot blasting is a method of processing a work by causing particles called projection material to collide with a work (work).
  • Etching is a molding or surface processing technique that utilizes the corrosive action of a chemical or the like.
  • thermoplastic resin is a resin material that softens when heated and solidifies when cooled.
  • thermosetting resin a resin material which is solidified by heating and does not soften even by reheating.
  • the resin in fiber reinforced plastic using a thermoplastic resin for the resin shaft member 3, the resin is finely uneven if it is reheated when externally fitted to the large diameter bosses 4 of the metal shaft members 2, 2. It flows into 8 and solidifies. Further, in a fiber reinforced plastic using a thermosetting resin, it may be fitted outside the large diameter bosses 4 of the metal shaft members 2 before being solidified.
  • the resin of the fiber reinforced plastic flows in and solidifies on the micro uneven surface 8 to form the fastening structure 10.
  • the metal shaft member 2 and the resin shaft member 3 are mechanically joined by the anchoring effect (anchor effect).
  • the anchor effect is an effect of increasing the adhesive strength by the adhesive penetrating into the fine unevenness of the material surface like the root of a tree and curing in adhesion and painting. That the resin of the fiber reinforced plastic flows and solidifies will exhibit this anchoring effect (anchor effect).
  • the metal shaft member 2 and the resin shaft member 3 are mechanically joined by the anchoring effect (anchor effect). Therefore, stable rotational torque transmission is possible, the strength of the torque transmission portion is improved, and the power transmission shaft can be made light and compact.
  • the axial length of the fastening structure 10, that is, the bonding area H can be set arbitrarily, but the bonding force between the metal shaft member 2 and the resin shaft member 3, the large diameter of the metal shaft member 2 It can be set in consideration of the outer diameter of the boss portion 4 and the fiber reinforced plastic to be used.
  • the unevenness depth W see FIGS. 3A, 3B, and 3C
  • about 200 ⁇ m or less is desirable in consideration of formation by etching and shot blasting.
  • the metal cylinder 11 is externally fitted and fixed to the metal shaft member 2, and the open end 3 a of the resin shaft member 3 is externally fitted to the metal cylinder 11. It is fixed.
  • a fine uneven surface 8 as shown in FIGS. 3A, 3B and 3C is formed.
  • the fiber reinforced plastic flows into the fine uneven surface 8 to solidify, and the fastening structure 10 is formed.
  • Ru the anchoring effect
  • the outer diameter dimension of the large diameter boss portion 4 of the resin shaft member 3 can be set small, and the thickness dimension and the outer diameter dimension of the resin shaft member 3 are It can be set to the same size as the power transmission shaft 1 shown in FIG. 1 without using the metal cylinder 11.
  • the metal shaft member 2 and the metal cylinder 11 are joined via the concavo-convex fitting structure M.
  • the uneven fitting structure M is, for example, provided on an outer diameter surface of the large diameter boss portion 4 of the metal cylindrical body 11 and extends in the axial direction, as shown in FIGS.
  • the entire area of the fitting contact portion 18 between the convex portion 15 and the concave portion 16 of the metal cylindrical body 11 fitted to the convex portion 15 is in close contact with the concave portion 16 formed on the inner diameter surface of the cylindrical body 11 .
  • a plurality of convex portions 15 are disposed at a predetermined pitch along the circumferential direction, and a plurality of concave portions 16 in which the convex portions 15 are fitted are formed along the circumferential direction. That is, the convex portion 15 and the concave portion 16 fitted thereto are tightly fitted over the entire circumferential direction.
  • any part in the projecting direction of the projection corresponds to the position of the recess forming surface before the recess is formed. That is, each convex portion 15 is in a triangular shape (peak shape) having an apex in the form of a convex rounded cross section, and the fitting contact portion 18 between each convex portion 15 and each concave portion 16 is in the range shown in FIG. It is A, and it is the range from the middle part of the mountain shape to the summit in the cross section. Further, a gap 20 is formed on the inner diameter side of the inner diameter surface 11 b of the metal cylindrical body 11 between the convex portions 15 adjacent to each other in the circumferential direction.
  • a part (for example, a tip end part) may correspond to the intermediate part in the protrusion direction of the convex part 15 not corresponding to the position of the concave part forming surface before the concave part is formed.
  • the entire area of the fitting contact portion 18 between the convex portion 15 and the concave portion 16 is in close contact, so in this concavo-convex fitting structure M, a gap where rattle occurs in the radial direction and the circumferential direction Is not formed.
  • all the fitting parts contribute to rotational torque transmission, stable rotational torque transmission is possible, and deterioration of the fatigue strength of the spline due to rubbing of the spline tooth surface can be avoided, and the durability is excellent.
  • no abnormal noise is generated.
  • the strength of the torque transmission portion can be improved, and the constant velocity universal joint can be made lightweight and compact.
  • thermosetting process is applied to at least the outer diameter portion of the large diameter boss portion 4 of the metal shaft member 2 to form a spline including a convex portion and a concave portion along the axial direction on the hardened layer. Therefore, the convex portion of the spline is hardened, and the convex portion becomes the convex portion 15 of the concavo-convex fitting structure M. Under the present circumstances, in the internal-diameter surface 11b of the metal cylinder 11, it is set as the unhardened part which does not perform a thermosetting process. The difference in hardness between the hardened layer of the convex portion of the spline and the unhardened portion of the inner diameter surface 11b of the metal cylinder 11 is 30 points or more in HRC.
  • corresponds to the position of the recessed part formation surface (in this case, the internal diameter surface 11b of the metal cylinder 11) before recessed part formation.
  • the inner diameter D of the inner diameter surface 11b of the metal cylinder 11 is the maximum outer diameter of the projection 15, that is, the maximum diameter of the circle connecting the apexes of the projections 15 which are the projections of the spline (diameter of circumscribed circle ) Smaller than D1 and set larger than the minimum outer diameter dimension of the large diameter boss portion 4 of the metal shaft member 2 between the adjacent convex portions, that is, the maximum diameter dimension D2 of the circle connecting the bottoms of the spline recesses. That is, D2 ⁇ D ⁇ D1.
  • the spline can be formed by various processing methods such as rolling processing, cutting processing, press processing, drawing processing, and the like which are conventionally known and used means. Moreover, various heat treatments, such as induction hardening and carburizing hardening, are employable as a thermosetting process.
  • the metal shaft member 2 is inserted (pressed in) into the metal cylinder 11 in a state where the shaft center of the metal shaft member 2 and the shaft center of the metal cylinder 11 are aligned.
  • the diameter D of the inner diameter surface 11b of the metal cylindrical body 11, the maximum outer diameter D1 of the convex portion 15, and the maximum outer diameter D2 of the concave portion of the spline are as described above.
  • the hardness of the convex portion 15 is 30 points or more larger than the hardness of the inner diameter surface 11b of the metal cylindrical body 11, if the metal shaft member 2 is press-fit into the metal cylindrical body 11, the convex portion 15 is the inner diameter surface It will bite into 11b, and the convex part 15 will form the recessed part 16 which this convex part 15 fits along an axial direction.
  • the fitting state in which the entire area of the fitting contact portion 18 between the convex portion 15 of the metal shaft member 2 and the concave portion 16 of the metal cylindrical body 11 is in close contact can be configured. . That is, the shape of the convex portion 15 is transferred to the other concave portion forming surface (in this case, the inner diameter surface 11 b of the metal cylinder 11). Under the present circumstances, when the convex part 15 bites into the internal diameter surface 11b of the metal cylinder 11, it will be in the state which the hole part of the metal cylinder 11 diameter-expanded slightly, and the axial direction movement of the convex part 15 is carried out.
  • the diameter of the hole of the metal cylinder 11 is reduced as it returns to its original diameter.
  • the hole of the metal cylinder 11 is elastically deformed in the radial direction when the convex portion 15 is press-fitted, and a preload for this elastic deformation is applied to the tooth surface of the convex portion 15 (surface of the fitting contact portion 18) Ru.
  • a preload for this elastic deformation is applied to the tooth surface of the convex portion 15 (surface of the fitting contact portion 18) Ru.
  • this spline can also be formed by various processing methods such as broaching, cutting, pressing, and drawing which are publicly known means.
  • various heat treatments such as induction hardening and carburizing and quenching can be adopted as the heat hardening treatment.
  • the middle portion in the protrusion direction of the convex portion 15 corresponds to the position of the concave surface (the outer diameter surface of the large diameter boss portion 4 of the metal shaft member 2) before the concave portion is formed. That is, the minimum diameter (minimum inner diameter dimension of the convex portion 15) D4 of the circle connecting the apexes of the convex portions 15 which are the convex portions of the splines is smaller than the outer diameter dimension D3 of the large diameter boss portion 4 of the metallic shaft member 2, The maximum outer diameter dimension (inner diameter dimension of the shaft hole inner diameter surface between the convex portions) D5 of the circle connecting the bottoms of the concave portions of the splines is set larger than the outer diameter dimension D3 of the large diameter boss portion 4. That is, D4 ⁇ D3 ⁇ D5.
  • the convex portion 15 on the metal cylindrical body 11 side allows the outside of the large diameter boss portion 4 of the metal shaft member 2 to The recessed part 16 which the convex part 15 fits in a diameter surface can be formed.
  • the fitting state in which the entire area of the fitting contact portion 18 between the convex portion 15 and the concave portion 16 is in close contact can be configured.
  • the fitting contact portion 18 between the convex portion 15 and the concave portion 16 is the range B shown in FIG. 8, and is the range from the middle part of the mountain to the peak in the cross section. Further, a gap 22 is formed on the outer diameter side of the outer peripheral surface of the large diameter boss portion 4 between the convex portions 15 adjacent in the circumferential direction.
  • the metal cylinder 11 can be used. As described above, when the metal cylinder 11 is used, the metal shaft member 2 and the metal cylinder 11 can be made of different materials. As described above, when the metal shaft member 2 and the metal cylinder 11 are made of different materials, it is possible to apply to the metal cylinder 11 a material different from steel generally used for the shaft member such as aluminum. it can. Thereby, the further weight reduction of a power transmission shaft and the selection freedom of the formation method of the fine concavo-convex surface 8 improve.
  • the present invention can be variously modified without being limited to the above embodiment, and as the fiber reinforced plastic, glass fiber reinforced plastic (GFRP) or carbon fiber reinforced Plastic (CFRP) can be used, and furthermore, boron fiber reinforced plastic (BFRP), aramid fiber reinforced plastic (AFRP, KFRP), polyethylene fiber reinforced plastic (DFRP), etc. can be used. Moreover, as a short fiber to be impregnated, glass fiber, carbon fiber, etc. can be used, but carbon nanotube (CNT), cellulose nanofiber (CNF), etc. may be used.
  • GFRP glass fiber reinforced plastic
  • CFRP carbon fiber reinforced Plastic
  • BFRP boron fiber reinforced plastic
  • AFRP aramid fiber reinforced plastic
  • DFRP polyethylene fiber reinforced plastic
  • CNT carbon nanotube
  • CNF cellulose nanofiber
  • the fiber reinforced plastic may be hoop-wound or helically-wound.
  • the hoop winding is a method of winding a fiber so that an angle between the central axis and the winding direction of the fiber is substantially perpendicular.
  • substantially perpendicular includes both 90 ° and an angle of around 90 ° that can be generated by shifting the winding position of the fibers so that the fibers do not overlap with each other.
  • the helical winding is a method of winding the fiber such that the angle between the central axis and the winding direction of the fiber is a predetermined angle.
  • the thickness dimension and outer diameter dimension of the resin shaft member 3 can be arbitrarily set according to the portion used, the total length of the power transmission shaft, etc., but the torque transmission corresponds to the torque transmission, and the diameter and weight increase Various settings can be made within the range not
  • the fixed type constant velocity universal joint 31 is not limited to the illustrated one, and even if it is an undercut free type constant velocity universal joint, the sliding constant velocity universal joint 32 is a double offset type, cross groove type It may be a constant velocity universal joint. Moreover, in the said embodiment, although used as a drive shaft as a power transmission shaft, you may use for propeller shafts other than a drive shaft. When a tripod type is used as the sliding constant velocity universal joint 32, it may be a single roller type or a double roller type.
  • the shape of the convex portion 15 of the concavo-convex fitting structure various shapes such as a triangular cross section, a trapezoidal cross section, a semicircular shape, a semielliptical shape, and a rectangular shape can be adopted in the illustrated example.
  • the number, circumferential arrangement pitch, etc. can also be changed arbitrarily. That is, it is not necessary to form a spline, and the convex portion (convex tooth) of this spline need not be the convex portion 15 of the concavo-convex fitting structure M, and it may be a key or a curvilinear corrugated alignment It may form a surface.
  • the convex portion 15 disposed along the axial direction is press-fit to the other side, and the concave portion 16 closely fitted to the convex portion 15 can be formed on the other side by the convex portion 15, and thus the convex It suffices that the entire area of the fitting contact portion 18 between the portion 15 and the corresponding recess 16 be in close contact and that the rotational torque be transmitted between the metal shaft member 2 and the resin shaft member 3.
  • thermosetting treatment is performed on the convex portion 15 and the hardness of the convex portion 15 is made higher than the portion where the concave portion is formed, with the convex portion corresponding side being an uncured portion, but if hardness difference can be made, both Even if the heat treatment is performed, both may not be heat treated. Furthermore, since only the press-fit start end of the convex portion 15 needs to have a hardness higher than the portion where the concave portion 16 is formed when press-fitting, it is not necessary to increase the overall hardness of the convex portion 15. Furthermore, although the gap 20 is formed, it may be such that the recess between the projections 15 bites into the inner diameter surface 11 b.
  • the hardness difference between the convex portion 15 side and the concave portion forming surface side formed by the convex portion 15 is preferably 30 points or more in HRC as described above, but the convex portion 15 can be press-fit If there is, it may be less than 30 points.
  • Examples of the heat treatment method include induction hardening, carburizing, tempering, normalizing, and the like.
  • the inner diameter surface 11 b is subjected to a carbonization treatment to form a layer having hardness lower than that of the convex portion 15 Is easily formed on the inner diameter surface 11 b of the metal cylinder 11.
  • the metal shaft member 2 when forming the recess 16 in the metal shaft member 2 by the convex portion 15 of the inner diameter surface 11b of the metal cylindrical body 11 at the time of press-fitting, the metal shaft member 2 is subjected to normalizing treatment or tempering treatment
  • the hardness of the outer diameter surface of the metal shaft member 2 can be made lower than the convex portion 15 of the inner diameter surface 11 b of the metal cylinder 11 while securing the torsional strength of the shaft member 2.
  • the end face of the convex portion 15 (the press-in start end may be a plane orthogonal to the axial direction or may be inclined at a predetermined angle with respect to the axial direction. In this case, from the inner diameter side toward the outer diameter side) It may be inclined toward the non-convex part side or may be inclined toward the convex part Note that when the convex part 15 is press-fitted, the side where the concave part 16 is formed is fixed and the convex part 15 is formed Alternatively, the side on which the convex portion 15 is formed may be fixed, the side on which the concave portion 16 is formed may be moved, or both may be moved.
  • a power transmission shaft As a power transmission shaft, it can be suitably used not only for automotive applications but also for marine applications, various industrial machinery applications, and aircraft applications.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

This power transmission shaft comprises a metal shaft member and a resin shaft member provided connected to the metal shaft member along the shaft direction. The resin shaft member is formed of a fiber-reinforced plastic. The metal shaft member and the resin shaft member are joined via a fastening structure part formed by causing the fiber-reinforced plastic to flow onto and solidify on a fine corrugated surface.

Description

[規則26に基づく補充 23.08.2018]　動力伝達シャフト[Refilling according to rule 26 23.08.2018] Power transmission shaft
　動力伝達シャフトに関し、特に、自動車や各種産業機械に用いられる動力伝達用シャフトに関する。 The present invention relates to a power transmission shaft, and more particularly to a power transmission shaft used in automobiles and various industrial machines.
　自動車や各種産業機械に用いられる動力伝達用シャフトは、一般的には鋼製である。しかしながら、このような鋼製では重量が大となる。このため、近年では、軽量化のためにＣＦＲＰ(炭素繊維強化プラスチック)等の繊維強化プラスチックを用いる場合がある。 The power transmission shaft used in automobiles and various industrial machines is generally made of steel. However, such steel products are heavy. For this reason, in recent years, fiber reinforced plastics, such as CFRP (carbon fiber reinforced plastic), may be used for weight reduction.
　このように、繊維強化プラスチックを用いる場合、強度劣化を防止するために、鉄鋼部材との併用となる。このため、繊維強化プラスチックと鉄鋼部材とを接合する必要が生じ、従来には、この繊維強化プラスチックと鉄鋼部材との接合性を考慮したものがある（特許文献１及び特許文献２）。 Thus, when using a fiber reinforced plastic, in order to prevent strength degradation, it becomes combined use with a steel member. For this reason, it is necessary to join a fiber reinforced plastic and a steel member, and in the related art, there is one in which the bondability between the fiber reinforced plastic and the steel member is considered (Patent Document 1 and Patent Document 2).
　特許文献１では、繊維強化プラスチック（ＦＲＰ）製のチューブ体の端部において、リベットを介して金属製ヨークと接合するものである。また、特許文献２では、中間円筒部材の外径面及び内径面にセレーションが形成され、中間円筒部材がＦＲＰ製筒体の端部に圧入された際に、外径面側のセレーションがＦＲＰ製筒体の端部の内径面に食い込ませるものである。また、中間円筒部材に、金属製ヨークの圧入軸部が嵌入されることによって、内径面のセレーションには金属製ヨークの圧入軸部の外径面に形成されたセレーションが噛合される。これらによって、ＦＲＰ製筒体に金属ヨークが接合されることになる。 In Patent Document 1, at an end portion of a fiber reinforced plastic (FRP) tube body, a metal yoke is joined via a rivet. Further, in Patent Document 2, serrations are formed on the outer diameter surface and the inner diameter surface of the intermediate cylindrical member, and when the intermediate cylindrical member is pressed into the end of the FRP cylinder, the serration on the outer diameter surface is made of FRP. It bites into the inner diameter surface of the end of the cylinder. Further, by inserting the press-fit shaft portion of the metal yoke into the intermediate cylindrical member, the serration formed on the outer diameter surface of the press-fit shaft portion of the metal yoke is engaged with the serration of the inner diameter surface. As a result, the metal yoke is joined to the FRP cylinder.
実開平１－９１１８号公報Japanese Utility Model Publication No. 1-9118 特開２００４－３０８７００号公報JP 2004-308700 A
  前記特許文献１では、前記したように、ＦＲＰ製のチューブ体の端部に金属製ヨークを嵌入し、リベットを用いてこれらを連結するものである。このため、トルク負荷時等に、リベット貫通部位に応力が集中し、比較的低トルク発生時に破損するおそれがある。また、リベットを用いるもので、組み立て性および接合性に優れると言えるものではない。 In the patent document 1, as described above, a metal yoke is inserted into the end portion of the FRP tube body, and these are connected using a rivet. For this reason, when torque is applied, stress concentrates on the rivet penetration site, and there is a risk of breakage when relatively low torque occurs. Moreover, it is a thing using a rivet and it can not be said that it is excellent in assemblability and bondability.
　特許文献２では、中間円筒部材の外径面側のセレーションをＦＲＰ製筒体の端部の内径面に食い込ませるものであり、この食い込みによって、ＦＲＰ製筒体の内径面側の繊維が切断されるおそれがある。このため、トルク負荷時にＦＲＰ（繊維強化プラスチック）層間で剥離が生じやすいものとなっている。 In Patent Document 2, the serration on the outer diameter surface side of the intermediate cylindrical member is made to bite into the inner diameter surface of the end portion of the FRP cylinder, and the fibers on the inner diameter surface side of the FRP cylinder are cut by this biting. There is a risk of For this reason, peeling is apt to occur between FRP (fiber reinforced plastic) layers when torque is applied.
　そこで、本発明は、上記課題に鑑みて、繊維強化プラスチックからなる樹脂製軸部材を用いることにより軽量化を図ることができ、しかも、金属製軸部材と樹脂製軸部材とは、安定した接合状態を維持でき、トルク伝達に優れた動力伝達シャフトを提供するものである。 Therefore, in view of the above problems, the present invention can achieve weight reduction by using a resin-made shaft member made of fiber-reinforced plastic, and moreover, the metal-made shaft member and the resin-made shaft member can be joined stably. It is an object of the present invention to provide a power transmission shaft capable of maintaining a state and excellent in torque transmission.
　本発明の動力伝達シャフトは、金属製軸部材と、この金属製軸部材に軸方向に沿って連設される樹脂製軸部材とを備えた動力伝達シャフトであって、前記樹脂製軸部材が繊維強化プラスチックで構成され、金属製軸部材と樹脂製軸部材とは、微細凹凸面に繊維強化プラスチックが流入固化してなる締結構造部を介して接合されているものである。微細凹凸面は、ショットブラストのような物理加工による方法であっても、エッチング等の化学的な方法等で成形することができる。 The power transmission shaft of the present invention is a power transmission shaft including a metal shaft member and a resin shaft member connected to the metal shaft member along the axial direction, and the resin shaft member is The metal shaft member and the resin shaft member are made of fiber reinforced plastic, and are joined to each other via a fastening structure formed by inflow solidification of the fiber reinforced plastic on the fine uneven surface. The fine uneven surface can be formed by a chemical method such as etching, even if it is a method by physical processing such as shot blasting.
　本発明の動力伝達シャフトによれば、締結構造部は微細凹凸面に繊維強化プラスチックが流入固化してなるものであるので、金属製軸部材と樹脂製軸部材とは投錨効果（アンカー効果）によって、機械的接合される。ここで、投錨効果（アンカー効果）とは、接着や塗装において、材料表面の微細な凹凸に接着剤が木の根のように入り込んで硬化することで接着力が高まる効果のことであり、微細凹凸面に繊維強化プラスチックが流入固化してなることは、この投錨効果（アンカー効果）を発揮することになる。 According to the power transmission shaft of the present invention, since the fastening structure is formed by inflow solidification of the fiber reinforced plastic on the fine uneven surface, the metal shaft member and the resin shaft member are anchored by the anchoring effect (anchor effect) , Mechanical bonding. Here, the anchor effect (anchor effect) is an effect of increasing the adhesive strength by the adhesive penetrating into the fine unevenness of the material surface like the root of a tree and curing in adhesion and painting. The inflow solidification of the fiber-reinforced plastic causes this anchoring effect (anchor effect).
　金属製軸部材の外表面に微細凹凸面が形成され、樹脂製軸部材が微細凹凸面に外嵌されて、金属製軸部材の外表面と樹脂製軸部材の内径面との間に締結構造部が形成されているものであってもよい。また、金属製軸部材に金属製筒体が外嵌固定され、この金属製筒体は外表面に微細凹凸面が形成され、樹脂製軸部材が微細凹凸面に外嵌されて、この金属製筒体の外表面と樹脂製軸部材の内径面との間に締結構造部が形成されているものであってもよい。 A fine asperity surface is formed on the outer surface of the metal shaft member, and the resin shaft member is externally fitted on the fine asperity surface, and a fastening structure is provided between the outer surface of the metal shaft member and the inner diameter surface of the resin shaft member. The part may be formed. In addition, a metal cylindrical body is externally fitted and fixed to a metal shaft member, the metal cylindrical body is formed with a fine asperity surface on the outer surface, and the resin shaft member is externally fitted with the fine asperity surface. A fastening structure may be formed between the outer surface of the cylindrical body and the inner diameter surface of the resin shaft member.
　金属製軸部材と金属製筒体とが異種材にて構成されていてもよい。このため、金属製筒体に、金属製軸部材よりも比重が小さい金属、例えば、アルミニウム等の金属を用いることができる。このため、動力伝達シャフト全体としてさらなる軽量化を図ることができる。 The metallic shaft member and the metallic cylinder may be made of different materials. For this reason, a metal having a specific gravity smaller than that of the metal shaft member, for example, a metal such as aluminum can be used for the metal cylinder. For this reason, further weight reduction can be achieved as the whole power transmission shaft.
　金属製軸部材と金属製筒体とが、凸部とその凸部に嵌合する相手部材の凹部との嵌合接触部位全域が密着する凹凸嵌合構造を介して接合されているのが好ましい。このように構成することによって、この嵌合構造において、径方向及び円周方向においてガタが生じる隙間が形成されない。径方向及び円周方向においてガタが生じる隙間が形成されないので、嵌合部位の全てが回転トルク伝達に寄与し、安定した回転トルク伝達が可能であり、スプラインの歯面の擦れ合いによるスプラインの疲労強度の低下を回避でき、耐久性に優れる。しかも、異音の発生も生じさせない。さらには、径方向及び円周方向において隙間無く密着しているため、トルク伝達部位の強度が向上し、動力伝達シャフトを軽量、コンパクトにすることができる。 It is preferable that the metal shaft member and the metal cylinder be joined via a concavo-convex fitting structure in which the entire area of the fitting contact portion of the protrusion and the recess of the mating member fitting to the protrusion is in close contact . By this configuration, in this fitting structure, a gap in which rattling occurs in the radial direction and the circumferential direction is not formed. There is no gap that causes rattling in the radial and circumferential directions, so all of the fitting parts contribute to rotational torque transmission, enabling stable rotational torque transmission, and spline fatigue due to friction between spline tooth surfaces. A decrease in strength can be avoided and durability is excellent. Moreover, no abnormal noise is generated. Furthermore, since they are in close contact with each other in the radial direction and the circumferential direction without any gap, the strength of the torque transmission portion can be improved, and the power transmission shaft can be made lightweight and compact.
　本発明では、金属製軸部材と樹脂製軸部材とは投錨効果（アンカー効果）によって、械的接合される。これにより、安定した回転トルク伝達が可能であり、トルク伝達部位の強度が向上し、動力伝達シャフトを軽量、コンパクトにすることができる。 In the present invention, the metal shaft member and the resin shaft member are mechanically joined by the anchor effect (anchor effect). Thereby, stable rotational torque transmission is possible, the strength of the torque transmission portion is improved, and the power transmission shaft can be made light and compact.
本発明の動力伝達シャフトの要部斜視図である。It is a principal part perspective view of a power transmission shaft of the present invention. 金属製軸部材と樹脂製軸部材の接合領域を示す断面図である。It is sectional drawing which shows the joining area | region of a metal-made axial member and a resin-made axial member. 金属製軸部材と樹脂製軸部材とが投錨効果（アンカー効果）によって機械的接合されている状態を示し、凹部の断面形状が異形である微細凹凸面の拡大断面図である。It is the enlarged sectional view of the fine concavo-convex surface which shows the state where the metal shaft member and the resin shaft member are mechanically joined by the anchoring effect (anchor effect), and the sectional shape of the recess is different. 金属製軸部材と樹脂製軸部材とが投錨効果（アンカー効果）によって機械的接合されている状態を示し、凹部の断面形状が山形である微細凹凸面の拡大断面図である。It is the enlarged sectional view of the fine concavo-convex surface which shows the state where the metal shaft member and the resin shaft member are mechanically joined by the anchor effect (anchor effect), and the cross section of the recess has a mountain shape. 金属製軸部材と樹脂製軸部材とが投錨効果（アンカー効果）によって機械的接合されている状態を示し、凹部の断面形状が台形状である微細凹凸面の拡大断面図である。It is the enlarged sectional view of the fine concavo-convex surface which shows the state where the metal shaft member and the resin shaft member are mechanically joined by the anchoring effect (anchor effect), and the sectional shape of the recess is trapezoidal. 金属製軸部材と樹脂製軸部材との間に他の金属製筒体が介在されている動力伝達シャフトの要部断面図である。It is principal part sectional drawing of the power transmission shaft by which another metal cylinder is interposed between metal shaft members and resin shaft members. 図４のＸ－Ｘ線拡大断面図である。FIG. 5 is an enlarged sectional view taken along line XX of FIG. 4; 図５の要部拡大図である。It is a principal part enlarged view of FIG. 他の凹凸嵌合構造の断面図である。It is sectional drawing of another uneven | corrugated fitting structure. 図７の要部拡大図である。It is a principal part enlarged view of FIG. 本発明に係る動力伝達シャフトを用いたドライブシャフトの断面図である。It is sectional drawing of the drive shaft using the power transmission shaft which concerns on this invention.
  以下本発明の実施の形態を図１～図９に基づいて説明する。図９は、本発明に係る動力伝達シャフト１を用いたドライブシャフトを示し、この動力伝達シャフト１は、一対の金属製軸部材２，２と、金属製軸部材２，２に軸方向に沿って連設される樹脂製軸部材３とを備える。すなわち、樹脂製軸部材３は、一対の金属製軸部材２，２間に配設されてこれらを連結する中間軸を構成する。 Hereinafter, an embodiment of the present invention will be described based on FIGS. 1 to 9. FIG. 9 shows a drive shaft using the power transmission shaft 1 according to the present invention, and the power transmission shaft 1 extends in the axial direction between the pair of metal shaft members 2, 2 and the metal shaft members 2, 2. And a resin-made shaft member 3 connected in series. That is, the resin-made shaft member 3 is arrange | positioned between a pair of metal-made shaft members 2 and 2, and comprises the intermediate shaft which connects these.
　このドライブシャフトは、固定式等速自在継手３１と摺動式等速自在継手３２とを、本発明に係る動力伝達シャフト１にて連結してなるものである。この図例では、固定式等速自在継手３１にバーフィールド型等速自在継手を用い、摺動式等速自在継手３２に、トリポード型等速自在継手を用いている。 The drive shaft is formed by connecting a fixed type constant velocity universal joint 31 and a sliding type constant velocity universal joint 32 by a power transmission shaft 1 according to the present invention. In this example, a bar field constant velocity universal joint is used as the fixed constant velocity universal joint 31, and a tripod constant velocity universal joint is used as the sliding constant velocity universal joint 32.
　固定式等速自在継手３１は、軸方向に延びる複数のトラック溝３３が内径面３４に形成された外側継手部材３５と、軸方向に延びる複数のトラック溝３６が外径面３７に円周方向等間隔に形成された内側継手部材３８と、外側継手部材３５のトラック溝３３と内側継手部材３８のトラック溝３６との間に介在してトルクを伝達する複数のボール３９と、外側継手部材３５の内径面３４と内側継手部材３８の外径面３７との間に介在してボール３９を保持するケージ４０とを備えている。 The fixed type constant velocity universal joint 31 has an outer joint member 35 in which a plurality of axially extending track grooves 33 are formed in the inner diameter surface 34 and a plurality of axially extending track grooves 36 in the outer diameter surface 37 in the circumferential direction. Inner joint members 38 formed at equal intervals, a plurality of balls 39 transmitting torque by being interposed between the track groove 33 of the outer joint member 35 and the track grooves 36 of the inner joint member 38, and the outer joint member 35 And a cage 40 for holding the ball 39 interposed between the inner diameter surface 34 of the inner joint member 38 and the outer diameter surface 37 of the inner joint member 38.
　摺動式等速自在継手３２は、内周に軸線方向に延びる三本のトラック溝５１を設けると共に各トラック溝５１の内側壁に互いに対向するローラ案内面５１ａを設けた外側継手部材５２と、半径方向に突出した３つの脚軸５３を備えたトリポード部材５４と、前記脚軸５３に外嵌する内側ローラ５５と、前記トラック溝５１に挿入されると共に前記内側ローラ５５に外嵌する外側ローラ５６とを備えたものである。すなわち、この摺動式等速自在継手３２は、外側ローラ５６が脚軸５３に対して回転自在であると共にローラ案内面５１ａに沿って移動可能なダブルローラタイプである。また、トリポード部材５４はボス５７と前記脚軸５３とを備える。脚軸５３はボス５７の円周方向三等分位置から半径方向に突出している。 The sliding type constant velocity universal joint 32 has an outer joint member 52 in which three track grooves 51 extending in the axial direction are provided on the inner circumference and a roller guide surface 51 a facing each other is provided on the inner side wall of each track groove 51; A tripod member 54 having three leg shafts 53 projecting in the radial direction, an inner roller 55 externally fitted to the leg shaft 53, and an outer roller inserted in the track groove 51 and externally fitted to the inner roller 55 56 and the like. That is, the sliding constant velocity universal joint 32 is a double roller type in which the outer roller 56 is rotatable with respect to the leg shaft 53 and movable along the roller guide surface 51a. Further, the tripod member 54 includes a boss 57 and the leg shaft 53. The leg shaft 53 protrudes radially from the circumferential three-way position of the boss 57.
　固定式等速自在継手３１における内側継手部材３８の軸孔にトルク伝達可能に動力伝達シャフト１の軸端嵌合部を嵌入し、摺動式等速自在継手３２におけるトリポード部材５４の軸孔にトルク伝達可能に動力伝達シャフト１の軸端嵌合部を嵌入している。なお、動力伝達シャフト１の両軸端嵌合部の端部は、スナップリング等の止め輪２５，２５によりそれぞれ抜け止めされている。すなわち、軸端嵌合部の端部に周方向溝２６、２６が形成され、この周方向溝２６、２６に止め輪２５，２５が嵌合している。 The shaft end fitting portion of the power transmission shaft 1 is fitted into the shaft hole of the inner joint member 38 in the fixed type constant velocity universal joint 31 so that torque can be transmitted, and the shaft hole of the tripod member 54 in the sliding type constant velocity universal joint 32 The shaft end fitting portion of the power transmission shaft 1 is fitted so as to transmit torque. The end portions of the both-shaft end fitting portion of the power transmission shaft 1 are prevented from coming off by snap rings 25 such as snap rings. That is, circumferential grooves 26, 26 are formed at the end of the shaft end fitting portion, and the snap rings 25, 25 are fitted in the circumferential grooves 26, 26.
　この動力伝達シャフト１の軸端嵌合部の外径には雄スプライン５，５が形成され、両等速自在継手の内側継手部材３８及びトリポード部材５４の軸孔には雌スプライン２７，２７が形成されている。動力伝達シャフト１の軸端嵌合部を等速自在継手３１，３２の内側継手部材３８及びトリポード部材５４の軸孔に嵌入することにより、雄スプライン５，５と雌スプライン２７，２７とを噛み合わせることで結合させ、動力伝達シャフト１と内側継手部材３８及びトリポード部材５４との間でトルク伝達を可能としている。 Male splines 5 and 5 are formed on the outer diameter of the shaft end fitting portion of the power transmission shaft 1, and female splines 27 and 27 are formed in the axial holes of the inner joint member 38 and the tripod member 54 of both constant velocity universal joints. It is formed. The male splines 5 and 5 and the female splines 27 and 27 are engaged by fitting the shaft end fitting portion of the power transmission shaft 1 into the axial hole of the inner joint member 38 and the tripod member 54 of the constant velocity universal joints 31 and 32. By combining them, torque transmission is enabled between the power transmission shaft 1 and the inner joint member 38 and the tripod member 54.
　動力伝達シャフト１と各外側継手部材３８，５２との間には、外部からの異物の侵入および内部からのグリースの漏洩を防止するためのブーツ３０がそれぞれ装着されている。ブーツ３０は、大径端部３０ａと、小径端部３０ｂと、大径端部３０ａと小径端部３０ｂとを連結する蛇腹部３０ｃとからなる。ブーツ３０の大径端部３０ａは外側継手部材３５，５２の開口端でブーツバンド４５により締め付け固定され、その小径端部３０ｂは動力伝達シャフト１の後述するブーツ装着部６ｃでブーツバンド４６により締め付け固定されている。 A boot 30 is mounted between the power transmission shaft 1 and each of the outer joint members 38 and 52 for preventing foreign matter from the outside and grease from the inside from leaking. The boot 30 includes a large diameter end 30a, a small diameter end 30b, and a bellows 30c connecting the large diameter end 30a and the small diameter end 30b. The large diameter end 30a of the boot 30 is fastened and fixed by the boot band 45 at the open end of the outer joint members 35 and 52, and the small diameter end 30b is fastened by the boot band 46 at the boot mounting portion 6c of the power transmission shaft 1 described later. It is fixed.
　金属製軸部材２は、図１と図２に示すように、一方の端部に大径ボス部４が設けられるとともに、他方の端部に雄スプライン５が設けられている。すなわち、大径ボス部４から雄スプライン５に向かって中径部６ａ、小径部６ｂ、ブーツ装着部６ｃ、小径部６ｄ、中径部６ｅが設けられている。ブーツ装着部６ｃに周方向凹溝７が設けられ、ブーツ３０の小径端部３０ｂ（図９参照）がブーツ装着部６ｃに装着された際に、周方向凹溝７に小径端部３０ｂの内径面の一部が嵌合する。 As shown in FIGS. 1 and 2, the metal shaft member 2 is provided with a large diameter boss 4 at one end and a male spline 5 at the other end. That is, the medium diameter portion 6a, the small diameter portion 6b, the boot mounting portion 6c, the small diameter portion 6d, and the medium diameter portion 6e are provided from the large diameter boss portion 4 toward the male spline 5. When the circumferential groove 7 is provided in the boot mounting portion 6c, and the small diameter end 30b (see FIG. 9) of the boot 30 is mounted on the boot mounting portion 6c, the inner diameter of the small diameter end 30b in the circumferential groove 7 Part of the face fits.
　樹脂製軸部材３は、ＦＲＰ（繊維強化プラスチック）製筒体からなる。ＦＲＰ製筒体としてはフィラメントワインディング法やシートワインディング法にて成形される。フィラメントワインディング法とは、樹脂を含浸した炭素繊維（繊維束）を心棒のまわりに巻いて成形し、加熱して硬化させた後に心棒を取り外す方法である。繊維の束でなく、シートを巻きつけるのが「シートワインディング」という。 The resin shaft member 3 is made of an FRP (fiber reinforced plastic) cylinder. The FRP cylinder is formed by a filament winding method or a sheet winding method. The filament winding method is a method in which a resin-impregnated carbon fiber (fiber bundle) is wound around a mandrel, formed, heated and cured, and then the mandrel is removed. It is called "sheet winding" to wind a sheet instead of a bundle of fibers.
　この場合、樹脂製軸部材３に両開口端部３ａ、３ａを、図２に示すように、金属製軸部材２，２の大径ボス部４、４に外嵌接合する。この場合、大径ボス部４の外表面４ａには、図３Ａ、図３Ｂ、及び図３Ｃに示すような微細凹凸面８が形成されている。 In this case, both open end portions 3a, 3a are externally fitted and joined to the large diameter boss portions 4, 4 of the metal shaft members 2, 2, as shown in FIG. In this case, on the outer surface 4 a of the large diameter boss portion 4, the fine uneven surface 8 as shown in FIGS. 3A, 3B, and 3C is formed.
　図３Ａに示す微細凹凸面８は、多数の凹部９ａと多数の凸部９ｂとからなり、各凹部９ａと凸部９ｂは、その断面形状を円形、楕円、矩形、及び多角形等とは相違する異形とされる。また、図３Ｂに示す微細凹凸面８は、その断面形状がその頂点がアール形状とされた三角形状をなす多数の凹部９ｃと、その断面形状がその頂点がアール形状とされた三角形状をなす多数の凸部９ｄとからなる。また、図３Ｃに示す微細凹凸面８は、断面扁平三角形状の多数の凸部９ｆと、凸部間に設けられる台形状の多数の凹部９ｅとからなる。 The fine concavo-convex surface 8 shown in FIG. 3A is composed of a large number of concave portions 9a and a large number of convex portions 9b, and each concave portion 9a and the convex portions 9b differ in their cross-sectional shape from a circle, an ellipse, a rectangle, a polygon, etc. It is considered to be a different form. Further, the fine uneven surface 8 shown in FIG. 3B has a large number of concave portions 9c having a triangular shape whose cross-sectional shape has a rounded top, and a triangular shape whose cross-sectional shape has a rounded top. It consists of many convex parts 9d. Further, the micro uneven surface 8 shown in FIG. 3C is composed of a large number of convex portions 9 f having a flat triangular shape in cross section, and a large number of trapezoidal concave portions 9 e provided between the convex portions.
　このため、樹脂製軸部材３の両開口端部３ａ、３ａが図２に示すように、金属製軸部材２，２の大径ボス部４、４に外嵌された際には、図３Ａ、図３Ｂ、及び図３Ｃに示すように微細凹凸面８に樹脂が流入することになる。すなわち、微細凹凸面８の凹部９ａ、９ｃ，９ｅに樹脂が嵌入することになる。 For this reason, as shown in FIG. 2, when both open end portions 3a, 3a of the resin shaft member 3 are externally fitted to the large diameter bosses 4, 4 of the metal shaft members 2, 2, FIG. 3A. As shown in FIG. 3B and FIG. 3C, the resin flows into the micro uneven surface 8. That is, the resin is inserted into the concave portions 9a, 9c, 9e of the micro uneven surface 8.
　図３Ａ、図３Ｂ、及び図３Ｃに示すような微細凹凸面８は、ショットブラストのような物理加工による方法、エッチング等による化学的な方法等で成形することができる。ショットブラストとは、投射材と呼ばれる粒体を加工物（ワーク）に衝突させ、ワークの加工等を行う手法である。エッチングとは、化学薬品などの腐食作用を利用した塑形ないし表面加工の技法である。 The fine uneven surface 8 as shown in FIGS. 3A, 3B, and 3C can be formed by a physical processing method such as shot blasting, a chemical method such as etching, or the like. Shot blasting is a method of processing a work by causing particles called projection material to collide with a work (work). Etching is a molding or surface processing technique that utilizes the corrosive action of a chemical or the like.
　ところで、繊維強化プラスチックには、熱可塑性樹脂を用いる場合と、熱硬化性樹脂を用いる場合とがある。熱可塑性樹脂は加熱をすると軟化し、冷却すると固化する樹脂材料である。一方、加熱することで固化し、再加熱しても軟化しない樹脂材料を熱硬化性樹脂という。 By the way, as fiber reinforced plastics, there are cases where a thermoplastic resin is used and cases where a thermosetting resin is used. A thermoplastic resin is a resin material that softens when heated and solidifies when cooled. On the other hand, a resin material which is solidified by heating and does not soften even by reheating is called a thermosetting resin.
　従って、樹脂製軸部材３に熱可塑性樹脂を用いる繊維強化プラスチックでは、金属製軸部材２，２の大径ボス部４、４に外嵌した際に再加熱をすれば、樹脂が微細凹凸面８に流入して固化することになる。また、熱硬化性樹脂を用いる繊維強化プラスチックでは、固化する前に、金属製軸部材２，２の大径ボス部４、４に外嵌するようにすればよい。 Therefore, in fiber reinforced plastic using a thermoplastic resin for the resin shaft member 3, the resin is finely uneven if it is reheated when externally fitted to the large diameter bosses 4 of the metal shaft members 2, 2. It flows into 8 and solidifies. Further, in a fiber reinforced plastic using a thermosetting resin, it may be fitted outside the large diameter bosses 4 of the metal shaft members 2 before being solidified.
　このため、微細凹凸面８に繊維強化プラスチックの樹脂が流入固化して締結構造部１０が形成される。このように、微細凹凸面８に繊維強化プラスチックの樹脂が流入固化すれば、金属製軸部材２と樹脂製軸部材３とは投錨効果（アンカー効果）によって、機械的接合される。ここで、投錨効果（アンカー効果）とは、接着や塗装において、材料表面の微細な凹凸に接着剤が木の根のように入り込んで硬化することで接着力が高まる効果のことであり、微細凹凸面に繊維強化プラスチックの樹脂が流入固化してなることは、この投錨効果（アンカー効果）を発揮することになる。 For this reason, the resin of the fiber reinforced plastic flows in and solidifies on the micro uneven surface 8 to form the fastening structure 10. As described above, when the resin of fiber reinforced plastic flows and solidifies on the fine uneven surface 8, the metal shaft member 2 and the resin shaft member 3 are mechanically joined by the anchoring effect (anchor effect). Here, the anchor effect (anchor effect) is an effect of increasing the adhesive strength by the adhesive penetrating into the fine unevenness of the material surface like the root of a tree and curing in adhesion and painting. That the resin of the fiber reinforced plastic flows and solidifies will exhibit this anchoring effect (anchor effect).
　従って、本発明に係る動力伝達シャフトでは、金属製軸部材２と樹脂製軸部材３とは投錨効果（アンカー効果）によって、機械的接合される。これにより、安定した回転トルク伝達が可能であり、トルク伝達部位の強度が向上し、動力伝達シャフトを軽量、コンパクトにすることができる。 Therefore, in the power transmission shaft according to the present invention, the metal shaft member 2 and the resin shaft member 3 are mechanically joined by the anchoring effect (anchor effect). Thereby, stable rotational torque transmission is possible, the strength of the torque transmission portion is improved, and the power transmission shaft can be made light and compact.
　ところで、締結構造部１０の軸方向長さ、すなわち、接合領域Ｈとしては、任意に設定できるが、金属製軸部材２と樹脂製軸部材３との接合力、金属製軸部材２の大径ボス部４の外径寸法、および使用する繊維強化プラスチック等を考慮して、設定することができる。また、微細凹凸面８の凹凸深さＷ（図３Ａ、図３Ｂ、及び図３Ｃ参照）としては、投錨効果（アンカー効果）を発揮して、安定した接合力を得るための寸法とする必要があるが、エッチングやショットブラストでの生成を考慮して約２００μｍ以下が望ましい。具体的には、微細凹凸面８の各凹部９ａ、９ｃ、９ｅの断面積を、２５μｍ2～４００００μｍ2程度と、凹凸深さＷを５μｍ～２００μｍ程度とするのが好ましい。 The axial length of the fastening structure 10, that is, the bonding area H can be set arbitrarily, but the bonding force between the metal shaft member 2 and the resin shaft member 3, the large diameter of the metal shaft member 2 It can be set in consideration of the outer diameter of the boss portion 4 and the fiber reinforced plastic to be used. In addition, as the unevenness depth W (see FIGS. 3A, 3B, and 3C) of the fine uneven surface 8, it is necessary to exhibit the anchoring effect (anchor effect) and have a dimension for obtaining a stable bonding strength. Although it is present, about 200 μm or less is desirable in consideration of formation by etching and shot blasting. Specifically, each recess 9a of the fine uneven surface 8, 9c, the cross-sectional area of 9e, and 25μm 2 ~ 40000μm 2 degrees, preferably an uneven depth W of about 5 [mu] m ~ 200 [mu] m.
　次に、図４に示す動力伝達シャフトは、金属製軸部材２に金属製筒体１１が外嵌固定され、この金属製筒体１１に、樹脂製軸部材３の開口端部３ａが外嵌固定されるものである。金属製筒体１１の外径面１１ａに、図３Ａ、図３Ｂ、及び図３Ｃに示すような微細凹凸面８が形成されている。このため、金属製筒体１１の外径面１１ａと、樹脂製軸部材３の開口端部３ａとの間に、微細凹凸面８に繊維強化プラスチックが流入固化して締結構造部１０が形成される。これによって、金属製筒体１１と樹脂製軸部材３とは、投錨効果（アンカー効果）によって、機械的接合され、図１に示す動力伝達シャフトと同様な作用効果を奏することになる。なお、このような金属製筒体１１を用いれば、樹脂製軸部材３の大径ボス部４の外径寸法を小さく設定でき、樹脂製軸部材３の肉厚寸法、及び外径寸法を、金属製筒体１１を用いない図１に示す動力伝達シャフト１と同様寸法に設定できる。 Next, in the power transmission shaft shown in FIG. 4, the metal cylinder 11 is externally fitted and fixed to the metal shaft member 2, and the open end 3 a of the resin shaft member 3 is externally fitted to the metal cylinder 11. It is fixed. On the outer diameter surface 11 a of the metal cylinder 11, a fine uneven surface 8 as shown in FIGS. 3A, 3B and 3C is formed. For this reason, between the outer diameter surface 11a of the metal cylindrical body 11 and the opening end 3a of the resin shaft member 3, the fiber reinforced plastic flows into the fine uneven surface 8 to solidify, and the fastening structure 10 is formed. Ru. Thereby, the metal cylinder 11 and the resin shaft member 3 are mechanically joined by the anchoring effect (anchor effect), and the same function and effect as the power transmission shaft shown in FIG. 1 can be obtained. In addition, if such a metal cylinder 11 is used, the outer diameter dimension of the large diameter boss portion 4 of the resin shaft member 3 can be set small, and the thickness dimension and the outer diameter dimension of the resin shaft member 3 are It can be set to the same size as the power transmission shaft 1 shown in FIG. 1 without using the metal cylinder 11.
　金属製軸部材２と金属製筒体１１とは凹凸嵌合構造Ｍを介して接合されている。凹凸嵌合構造Ｍは、図５及び図６に示すに示すように、例えば、金属製筒体１１の大径ボス部４の外径面に設けられて軸方向に延びる凸部１５と、金属製筒体１１の内径面に形成される凹部１６とからなり、凸部１５とその凸部１５に嵌合する金属製筒体１１の凹部１６との嵌合接触部位１８全域が密着している。複数の凸部１５が周方向に沿って所定ピッチで配設され、凸部１５が嵌合する複数の凹部１６が周方向に沿って形成されている。つまり、周方向全周にわたって、凸部１５とこれに嵌合する凹部１６とがタイトフィットしている。 The metal shaft member 2 and the metal cylinder 11 are joined via the concavo-convex fitting structure M. The uneven fitting structure M is, for example, provided on an outer diameter surface of the large diameter boss portion 4 of the metal cylindrical body 11 and extends in the axial direction, as shown in FIGS. The entire area of the fitting contact portion 18 between the convex portion 15 and the concave portion 16 of the metal cylindrical body 11 fitted to the convex portion 15 is in close contact with the concave portion 16 formed on the inner diameter surface of the cylindrical body 11 . A plurality of convex portions 15 are disposed at a predetermined pitch along the circumferential direction, and a plurality of concave portions 16 in which the convex portions 15 are fitted are formed along the circumferential direction. That is, the convex portion 15 and the concave portion 16 fitted thereto are tightly fitted over the entire circumferential direction.
　この場合、凸部の突出方向のいずれかの部位（図例では、突出方向中間部）が、凹部形成前の凹部形成面の位置に対応するものである。すなわち、各凸部１５は、その断面が凸アール状の頂点を有する三角形状（山形状）であり、各凸部１５と各凹部１６との嵌合接触部位１８とは、図６に示す範囲Ａであり、断面における山形の中腹部から山頂に至る範囲である。また、周方向の隣合う凸部１５間において、金属製筒体１１の内径面１１ｂよりも内径側に隙間２０が形成されている。なお、図例のように、凸部１５の突出方向中間部が凹部形成前の凹部形成面の位置に対応せずに、一部（例えば先端部位）が対応するものであってもよい。 In this case, any part in the projecting direction of the projection (in the illustrated example, the projection direction middle part) corresponds to the position of the recess forming surface before the recess is formed. That is, each convex portion 15 is in a triangular shape (peak shape) having an apex in the form of a convex rounded cross section, and the fitting contact portion 18 between each convex portion 15 and each concave portion 16 is in the range shown in FIG. It is A, and it is the range from the middle part of the mountain shape to the summit in the cross section. Further, a gap 20 is formed on the inner diameter side of the inner diameter surface 11 b of the metal cylindrical body 11 between the convex portions 15 adjacent to each other in the circumferential direction. As shown in the example of the drawing, a part (for example, a tip end part) may correspond to the intermediate part in the protrusion direction of the convex part 15 not corresponding to the position of the concave part forming surface before the concave part is formed.
　このため、凹凸嵌合構造Ｍは、凸部１５と凹部１６との嵌合接触部位１８全域が密着しているので、この凹凸嵌合構造Ｍにおいて、径方向及び円周方向においてガタが生じる隙間が形成されない。このため、嵌合部位の全てが回転トルク伝達に寄与し、安定した回転トルク伝達が可能であり、スプラインの歯面の擦れ合いによるスプラインの疲労強度の低下を回避でき、耐久性に優れる。しかも、異音の発生も生じさせない。さらには、径方向及び円周方向において隙間無く密着しているため、トルク伝達部位の強度が向上し、等速自在継手を軽量、コンパクトにすることができる。 For this reason, in the concavo-convex fitting structure M, the entire area of the fitting contact portion 18 between the convex portion 15 and the concave portion 16 is in close contact, so in this concavo-convex fitting structure M, a gap where rattle occurs in the radial direction and the circumferential direction Is not formed. For this reason, all the fitting parts contribute to rotational torque transmission, stable rotational torque transmission is possible, and deterioration of the fatigue strength of the spline due to rubbing of the spline tooth surface can be avoided, and the durability is excellent. Moreover, no abnormal noise is generated. Furthermore, since they are in close contact without gaps in the radial direction and the circumferential direction, the strength of the torque transmission portion can be improved, and the constant velocity universal joint can be made lightweight and compact.
　次に、この凹凸嵌合構造Ｍの嵌合方法を説明する。少なくとも金属製軸部材２の大径ボス部４の外径部に熱硬化処理を施し、この硬化層に軸方向に沿う凸部と凹部とからなるスプラインを形成する。このため、スプラインの凸部が硬化処理されて、この凸部が凹凸嵌合構造Ｍの凸部１５となる。この際、金属製筒体１１の内径面１１ｂにおいては熱硬化処理を行わない未硬化部とする。なお、スプラインの凸部の硬化層と金属製筒体１１の内径面１１ｂの未硬化部との硬度差は、ＨＲＣで３０ポイント以上とする。 Next, the fitting method of this uneven | corrugated fitting structure M is demonstrated. A thermosetting process is applied to at least the outer diameter portion of the large diameter boss portion 4 of the metal shaft member 2 to form a spline including a convex portion and a concave portion along the axial direction on the hardened layer. Therefore, the convex portion of the spline is hardened, and the convex portion becomes the convex portion 15 of the concavo-convex fitting structure M. Under the present circumstances, in the internal-diameter surface 11b of the metal cylinder 11, it is set as the unhardened part which does not perform a thermosetting process. The difference in hardness between the hardened layer of the convex portion of the spline and the unhardened portion of the inner diameter surface 11b of the metal cylinder 11 is 30 points or more in HRC.
　この際、凸部１５の突出方向のいずれかの部位が、凹部形成前の凹部形成面（この場合、金属製筒体１１の内径面１１ｂ）の位置に対応している。すなわち、金属製筒体１１の内径面１１ｂの内径寸法Ｄを、凸部１５の最大外径寸法、つまりスプラインの凸部である前記凸部１５の頂点を結ぶ円の最大直径寸法（外接円直径）Ｄ１よりも小さく、隣合う凸部間の金属製軸部材２の大径ボス部４の最小外径寸法、つまりスプラインの凹部の底を結ぶ円の最大直径寸法Ｄ２よりも大きく設定される。すなわち、Ｄ２＜Ｄ＜Ｄ１とされる。 Under the present circumstances, the site | part of the protrusion direction of the convex part 15 respond | corresponds to the position of the recessed part formation surface (in this case, the internal diameter surface 11b of the metal cylinder 11) before recessed part formation. That is, the inner diameter D of the inner diameter surface 11b of the metal cylinder 11 is the maximum outer diameter of the projection 15, that is, the maximum diameter of the circle connecting the apexes of the projections 15 which are the projections of the spline (diameter of circumscribed circle ) Smaller than D1 and set larger than the minimum outer diameter dimension of the large diameter boss portion 4 of the metal shaft member 2 between the adjacent convex portions, that is, the maximum diameter dimension D2 of the circle connecting the bottoms of the spline recesses. That is, D2 <D <D1.
　スプラインは、従来からの公知公用の手段である転造加工、切削加工、プレス加工、引き抜き加工等の種々の加工方法によって、形成することがきる。また、熱硬化処理としては、高周波焼入れ、浸炭焼入れ等の種々の熱処理を採用することができる。 The spline can be formed by various processing methods such as rolling processing, cutting processing, press processing, drawing processing, and the like which are conventionally known and used means. Moreover, various heat treatments, such as induction hardening and carburizing hardening, are employable as a thermosetting process.
　そして、金属製軸部材２の軸心と金属製筒体１１の軸心とを合わせた状態で、金属製筒体１１に対して、金属製軸部材２を挿入（圧入）していく。この際、金属製筒体１１の内径面１１ｂの径寸法Ｄと、凸部１５の最大外径寸法Ｄ１と、スプラインの凹部の最大外径寸法Ｄ２とが前記のような関係であり、しかも、凸部１５の硬度が金属製筒体１１の内径面１１ｂの硬度よりも３０ポイント以上大きいので、金属製軸部材２を金属製筒体１１に圧入していけば、この凸部１５が内径面１１ｂに食い込んでいき、凸部１５が、この凸部１５が嵌合する凹部１６を軸方向に沿って形成していくことになる。 Then, the metal shaft member 2 is inserted (pressed in) into the metal cylinder 11 in a state where the shaft center of the metal shaft member 2 and the shaft center of the metal cylinder 11 are aligned. At this time, the diameter D of the inner diameter surface 11b of the metal cylindrical body 11, the maximum outer diameter D1 of the convex portion 15, and the maximum outer diameter D2 of the concave portion of the spline are as described above. Since the hardness of the convex portion 15 is 30 points or more larger than the hardness of the inner diameter surface 11b of the metal cylindrical body 11, if the metal shaft member 2 is press-fit into the metal cylindrical body 11, the convex portion 15 is the inner diameter surface It will bite into 11b, and the convex part 15 will form the recessed part 16 which this convex part 15 fits along an axial direction.
　これによって、図６に示すように、金属製軸部材２の凸部１５と金属製筒体１１の凹部１６との嵌合接触部位１８全域が密着している嵌合状態を構成することができる。すなわち、相手側の凹部形成面（この場合、金属製筒体１１の内径面１１ｂ）に凸部１５の形状の転写を行うことになる。この際、凸部１５が金属製筒体１１の内径面１１ｂに食い込んでいくことによって、金属製筒体１１の孔部が僅かに拡径した状態となって、凸部１５の軸方向の移動を許容し、軸方向の移動が停止すれば、金属製筒体１１の孔部が元の径に戻ろうとして縮径することになる。言い換えれば、凸部１５の圧入時に金属製筒体１１の孔部が径方向に弾性変形し、この弾性変形分の予圧が凸部１５の歯面（嵌合接触部位１８の表面）に付与される。このため、凸部１５と凹部１６との嵌合接触部位１８全域が密着する凹凸嵌合構造Ｍを確実に形成することができる。しかも、凹部１６が形成される部材には、スプライン部等を形成しておく必要がなく、生産性に優れ、しかもスプライン同士の位相合わせを必要とせず、組立性の向上を図るとともに、圧入時の歯面の損傷を回避することができ、安定した嵌合状態を維持できる。金属製軸部材２側の硬度を高くでき、また、金属製軸部材２の捩り強度を向上させることができる。 By this, as shown in FIG. 6, the fitting state in which the entire area of the fitting contact portion 18 between the convex portion 15 of the metal shaft member 2 and the concave portion 16 of the metal cylindrical body 11 is in close contact can be configured. . That is, the shape of the convex portion 15 is transferred to the other concave portion forming surface (in this case, the inner diameter surface 11 b of the metal cylinder 11). Under the present circumstances, when the convex part 15 bites into the internal diameter surface 11b of the metal cylinder 11, it will be in the state which the hole part of the metal cylinder 11 diameter-expanded slightly, and the axial direction movement of the convex part 15 is carried out. When the axial movement is stopped, the diameter of the hole of the metal cylinder 11 is reduced as it returns to its original diameter. In other words, the hole of the metal cylinder 11 is elastically deformed in the radial direction when the convex portion 15 is press-fitted, and a preload for this elastic deformation is applied to the tooth surface of the convex portion 15 (surface of the fitting contact portion 18) Ru. For this reason, it is possible to reliably form the concavo-convex fitting structure M in which the entire area of the fitting contact portion 18 between the convex portion 15 and the concave portion 16 is in close contact. Moreover, it is not necessary to form a spline portion or the like in the member in which the concave portion 16 is formed, which is excellent in productivity and does not require the phase alignment of the splines, and improves the assemblability. Damage to the tooth flanks can be avoided, and a stable fit can be maintained. The hardness on the metal shaft member 2 side can be increased, and the torsional strength of the metal shaft member 2 can be improved.
　図５及び図６に示す凹凸嵌合構造Ｍでは、金属製軸部材２の大径ボス部４側に凸部１５を構成するスプラインを形成するとともに、この金属製軸部材２のスプラインに対して硬化処理を施し、金属製筒体１１の内径面１１ｂを未硬化（生材）としている。これに対して、図７及び図８に示す凹凸嵌合構造Ｍでは、金属製筒体１１の内径面１１ｂに硬化処理を施されたスプライン（このスプラインに凸部が凹凸嵌合構造Ｍの凸部となる）を形成するとともに、金属製軸部材２の大径ボス部４には硬化処理を施さないものである。なお、このスプラインも公知公用の手段であるブローチ加工、切削加工、プレス加工、引き抜き加工等の種々の加工方法によって、形成することができる。また、熱硬化処理としても、高周波焼入れ、浸炭焼入れ等の種々の熱処理を採用することができる。 In the concavo-convex fitting structure M shown in FIG. 5 and FIG. 6, while forming the spline which comprises the convex part 15 in the large diameter boss part 4 side of the metal shaft member 2, the spline of the metal shaft member 2 is Hardening treatment is performed, and the inner diameter surface 11b of the metal cylindrical body 11 is uncured (green material). On the other hand, in the concavo-convex fitting structure M shown in FIG. 7 and FIG. 8, a spline in which the inner diameter surface 11 b of the metal cylindrical body 11 is hardened (a convex portion of this spline is the convex of the concavo-convex fitting structure M And the large diameter boss 4 of the metal shaft member 2 is not cured. In addition, this spline can also be formed by various processing methods such as broaching, cutting, pressing, and drawing which are publicly known means. In addition, various heat treatments such as induction hardening and carburizing and quenching can be adopted as the heat hardening treatment.
　この場合、凸部１５の突出方向中間部位が、凹部形成前の凹部形成面（金属製軸部材２の大径ボス部４の外径面）の位置に対応する。すなわち、スプラインの凸部である凸部１５の頂点を結ぶ円の最小直径（凸部１５の最小内径寸法）Ｄ４を金属製軸部材２の大径ボス部４の外径寸法Ｄ３よりも小さく、スプラインの凹部の底を結ぶ円の最大外径寸法（凸部間の軸孔内径面の内径寸法）Ｄ５を大径ボス部４の外径寸法Ｄ３よりも大きく設定する。すなわち、Ｄ４＜Ｄ３＜Ｄ５とされる。 In this case, the middle portion in the protrusion direction of the convex portion 15 corresponds to the position of the concave surface (the outer diameter surface of the large diameter boss portion 4 of the metal shaft member 2) before the concave portion is formed. That is, the minimum diameter (minimum inner diameter dimension of the convex portion 15) D4 of the circle connecting the apexes of the convex portions 15 which are the convex portions of the splines is smaller than the outer diameter dimension D3 of the large diameter boss portion 4 of the metallic shaft member 2, The maximum outer diameter dimension (inner diameter dimension of the shaft hole inner diameter surface between the convex portions) D5 of the circle connecting the bottoms of the concave portions of the splines is set larger than the outer diameter dimension D3 of the large diameter boss portion 4. That is, D4 <D3 <D5.
　この場合、金属製軸部材２の大径ボス部４を金属製筒体１１に圧入すれば、金属製筒体１１側の凸部１５によって、金属製軸部材２の大径ボス部４の外径面に凸部１５が嵌合する凹部１６を形成することができる。これによって、凸部１５と凹部１６との嵌合接触部位１８全域が密着している嵌合状態を構成することができる。 In this case, if the large diameter boss portion 4 of the metal shaft member 2 is press-fit into the metal cylindrical body 11, the convex portion 15 on the metal cylindrical body 11 side allows the outside of the large diameter boss portion 4 of the metal shaft member 2 to The recessed part 16 which the convex part 15 fits in a diameter surface can be formed. By this, the fitting state in which the entire area of the fitting contact portion 18 between the convex portion 15 and the concave portion 16 is in close contact can be configured.
　ここで、凸部１５と凹部１６との嵌合接触部位１８とは、図８に示す範囲Ｂであり、断面における山形の中腹部から山頂にいたる範囲である。また、周方向の隣合う凸部１５間において、大径ボス部４の外周面よりも外径側に隙間２２が形成される。 Here, the fitting contact portion 18 between the convex portion 15 and the concave portion 16 is the range B shown in FIG. 8, and is the range from the middle part of the mountain to the peak in the cross section. Further, a gap 22 is formed on the outer diameter side of the outer peripheral surface of the large diameter boss portion 4 between the convex portions 15 adjacent in the circumferential direction.
　このため、図７及び図８に示す凹凸嵌合構造Ｍであっても、図５と図６に示す凹凸嵌合構造Ｍと同様の作用効果を奏することができる。 For this reason, even in the concavo-convex fitting structure M shown in FIGS. 7 and 8, the same function and effect as the concavo-convex fitting structure M shown in FIGS. 5 and 6 can be obtained.
　微細凹凸面８は、物理的、化学的、さらにはこれらの組み合わせで成形されるものであるので、繊維強化プラスチックに接合する部位を金属製軸部材２とは別部材として処理したほうが、製造上有利になる場合がある。このため、図４に示すように、金属製筒体１１を用いることができる。このように、金属製筒体１１を用いる場合、金属製軸部材２と金属製筒体１１とを異種材にて構成することができる。このように、金属製軸部材２と金属製筒体１１とを異種材にて構成する場合、金属製筒体１１にアルミニウム等の軸部材に一般に用いられる鋼とは異なる材質を適用することができる。これにより、動力伝達シャフトの更なる軽量化や、微細凹凸面８の成形方法の選択自由度が向上する。 Since the micro uneven surface 8 is formed by physical, chemical, or a combination of these, it is better to process the portion to be bonded to the fiber reinforced plastic as a separate member from the metal shaft member 2 It may be advantageous. For this reason, as shown in FIG. 4, the metal cylinder 11 can be used. As described above, when the metal cylinder 11 is used, the metal shaft member 2 and the metal cylinder 11 can be made of different materials. As described above, when the metal shaft member 2 and the metal cylinder 11 are made of different materials, it is possible to apply to the metal cylinder 11 a material different from steel generally used for the shaft member such as aluminum. it can. Thereby, the further weight reduction of a power transmission shaft and the selection freedom of the formation method of the fine concavo-convex surface 8 improve.
　以上、本発明の実施形態につき説明したが、本発明は前記実施形態に限定されることなく種々の変形が可能であって、繊維強化プラスチックとしては、ガラス繊維強化プラスチック（ＧＦＲＰ）や炭素繊維強化プラスチック（ＣＦＲＰ）を用いることができ、さらには、ボロン繊維強化プラスチック（ＢＦＲＰ）、アラミド繊維強化プラスチック（ＡＦＲＰ, ＫＦＲＰ）やポリエチレン繊維強化プラスチック（ＤＦＲＰ）等も用いることができる。また、含浸させる短繊維としては、ガラス繊維や炭素繊維等を用いることができるが、カーボンナノチューブ（ＣＮＴ）やセルロースナノファイバー（ＣＮＦ）等であってもよい。 The embodiment of the present invention has been described above, but the present invention can be variously modified without being limited to the above embodiment, and as the fiber reinforced plastic, glass fiber reinforced plastic (GFRP) or carbon fiber reinforced Plastic (CFRP) can be used, and furthermore, boron fiber reinforced plastic (BFRP), aramid fiber reinforced plastic (AFRP, KFRP), polyethylene fiber reinforced plastic (DFRP), etc. can be used. Moreover, as a short fiber to be impregnated, glass fiber, carbon fiber, etc. can be used, but carbon nanotube (CNT), cellulose nanofiber (CNF), etc. may be used.
　繊維強化プラスチックとしては、フープ巻きであってもヘリカル巻きであってもよい。フープ巻きとは、中心軸と繊維の巻き付け方向とがなす角度が略垂直となるように、繊維を巻回する方法である。ここで「略垂直」とは、９０°と、繊維同士が重ならないように繊維の巻き付け位置をずらすことによって生じ得る９０°前後の角度と、の両方を含む。また、ヘリカル巻きとは、中心軸と繊維の巻き付け方向とがなす角度が所定の角度となるように、繊維を巻回する方法である。 The fiber reinforced plastic may be hoop-wound or helically-wound. The hoop winding is a method of winding a fiber so that an angle between the central axis and the winding direction of the fiber is substantially perpendicular. Here, “substantially perpendicular” includes both 90 ° and an angle of around 90 ° that can be generated by shifting the winding position of the fibers so that the fibers do not overlap with each other. The helical winding is a method of winding the fiber such that the angle between the central axis and the winding direction of the fiber is a predetermined angle.
　樹脂製軸部材３の肉厚寸法及び外径寸法として、用いる部位や、動力伝達シャフト全長等に応じて任意に設定できるが、トルク伝達に動力伝達シャフトに対応し、かつ大径化及び重量化しない範囲で種々設定できる。 The thickness dimension and outer diameter dimension of the resin shaft member 3 can be arbitrarily set according to the portion used, the total length of the power transmission shaft, etc., but the torque transmission corresponds to the torque transmission, and the diameter and weight increase Various settings can be made within the range not
　固定式等速自在継手３１として、図例のものに限らず、アンダーカットフリータイプの等速自在継手であっても、摺動式等速自在継手３２としては、ダブルオフセットタイプ、クロスグルーブタイプの等速自在継手であってもよい。また、前記実施形態では、動力伝達シャフトとしてはドライブシャフトに用いたが、ドライブシャフト以外のプロペラシャフトに用いてもよい。なお、摺動式等速自在継手３２としてトリポードタイプを用いる場合、シングルローラタイプであっても、ダブルローラタイプであってもよい。 The fixed type constant velocity universal joint 31 is not limited to the illustrated one, and even if it is an undercut free type constant velocity universal joint, the sliding constant velocity universal joint 32 is a double offset type, cross groove type It may be a constant velocity universal joint. Moreover, in the said embodiment, although used as a drive shaft as a power transmission shaft, you may use for propeller shafts other than a drive shaft. When a tripod type is used as the sliding constant velocity universal joint 32, it may be a single roller type or a double roller type.
  凹凸嵌合構造の凸部１５の形状として、図例では、断面三角形状、断面台形、半円形状、半楕円形状、矩形形状等の種々の形状のものを採用でき、凸部１５の面積、数、周方向配設ピッチ等も任意に変更できる。すなわち、スプラインを形成し、このスプラインの凸部（凸歯）をもって凹凸嵌合構造Ｍの凸部１５とする必要はなく、キーのようなものであってもよく、曲線状の波型の合わせ面を形成するものであってもよい。要は、軸方向に沿って配設される凸部１５を相手側に圧入し、この凸部１５にて凸部１５に密着嵌合する凹部１６を相手側に形成することができて、凸部１５とそれに対応する凹部１６との嵌合接触部位１８全域が密着し、しかも、金属製軸部材２と樹脂製軸部材３との間で回転トルクの伝達ができればよい。 As the shape of the convex portion 15 of the concavo-convex fitting structure, various shapes such as a triangular cross section, a trapezoidal cross section, a semicircular shape, a semielliptical shape, and a rectangular shape can be adopted in the illustrated example. The number, circumferential arrangement pitch, etc. can also be changed arbitrarily. That is, it is not necessary to form a spline, and the convex portion (convex tooth) of this spline need not be the convex portion 15 of the concavo-convex fitting structure M, and it may be a key or a curvilinear corrugated alignment It may form a surface. The point is that the convex portion 15 disposed along the axial direction is press-fit to the other side, and the concave portion 16 closely fitted to the convex portion 15 can be formed on the other side by the convex portion 15, and thus the convex It suffices that the entire area of the fitting contact portion 18 between the portion 15 and the corresponding recess 16 be in close contact and that the rotational torque be transmitted between the metal shaft member 2 and the resin shaft member 3.
　凸部１５に対して熱硬化処理を行い、凸部対応側を未硬化部位として、凸部１５の硬度を凹部が形成される部位よりも高くしたが、硬度差をつけることができれば、両者を熱処理しても、両者を熱処理しなくてもよい。さらに、圧入する際に凸部１５の圧入始端部のみが、凹部１６が形成される部位より硬度が高ければよいので、凸部１５の全体の硬度を高くする必要がない。さらに、隙間２０が形成されるが、凸部１５間の凹部まで、内径面１１ｂに食い込むようなものであってもよい。なお、凸部１５側と、凸部１５にて形成される凹部形成面側との硬度差としては、前記したようにＨＲＣで３０ポイント以上とするのが好ましいが、凸部１５が圧入可能であれば３０ポイント未満であってもよい。上記熱処理方法としては、例えば高周波焼入れ、浸炭焼入れ、調質、焼準などが上げられる。圧入時に凸部１５で凹部１６を形成する場合において、金属製筒体１１に浸炭焼入れを行う場合、内径面１１ｂを防炭処理することで、金属製軸部材の凸部１５より硬度の低い層を金属製筒体１１の内径面１１ｂに形成し易くなる。また、圧入時に金属製筒体１１の内径面１１ｂの凸部１５で金属製軸部材２に凹部１６を形成する場合、金属製軸部材２に焼準処理や調質処理を施すことで、金属製軸部材２の捩り強度を確保しつつ金属製軸部材２の外径面の硬度を金属製筒体１１の内径面１１ｂの凸部１５より低くすることができる。 The thermosetting treatment is performed on the convex portion 15 and the hardness of the convex portion 15 is made higher than the portion where the concave portion is formed, with the convex portion corresponding side being an uncured portion, but if hardness difference can be made, both Even if the heat treatment is performed, both may not be heat treated. Furthermore, since only the press-fit start end of the convex portion 15 needs to have a hardness higher than the portion where the concave portion 16 is formed when press-fitting, it is not necessary to increase the overall hardness of the convex portion 15. Furthermore, although the gap 20 is formed, it may be such that the recess between the projections 15 bites into the inner diameter surface 11 b. The hardness difference between the convex portion 15 side and the concave portion forming surface side formed by the convex portion 15 is preferably 30 points or more in HRC as described above, but the convex portion 15 can be press-fit If there is, it may be less than 30 points. Examples of the heat treatment method include induction hardening, carburizing, tempering, normalizing, and the like. In the case of forming the concave portion 16 by the convex portion 15 at the time of press-fitting, when the metal cylindrical body 11 is carburized and quenched, the inner diameter surface 11 b is subjected to a carbonization treatment to form a layer having hardness lower than that of the convex portion 15 Is easily formed on the inner diameter surface 11 b of the metal cylinder 11. Further, when forming the recess 16 in the metal shaft member 2 by the convex portion 15 of the inner diameter surface 11b of the metal cylindrical body 11 at the time of press-fitting, the metal shaft member 2 is subjected to normalizing treatment or tempering treatment The hardness of the outer diameter surface of the metal shaft member 2 can be made lower than the convex portion 15 of the inner diameter surface 11 b of the metal cylinder 11 while securing the torsional strength of the shaft member 2.
　凸部１５の端面（圧入始端を軸方向に対して直交する面としても、軸方向に対して、所定角度で傾斜するものであってもよい。この場合、内径側から外径側に向かって反凸部側に傾斜しても凸部側に傾斜してもよい。なお、凸部１５を圧入する場合、凹部１６が形成される側を固定して、凸部１５を形成している側を移動させても、逆に、凸部１５を形成している側を固定して、凹部１６が形成される側を移動させても、両者を移動させてもよい。 The end face of the convex portion 15 (the press-in start end may be a plane orthogonal to the axial direction or may be inclined at a predetermined angle with respect to the axial direction. In this case, from the inner diameter side toward the outer diameter side) It may be inclined toward the non-convex part side or may be inclined toward the convex part Note that when the convex part 15 is press-fitted, the side where the concave part 16 is formed is fixed and the convex part 15 is formed Alternatively, the side on which the convex portion 15 is formed may be fixed, the side on which the concave portion 16 is formed may be moved, or both may be moved.
　動力伝達シャフトとして、自動車用途のみならず船舶用途、各種産業機械用途および航空機用途などに好適に用いることができる。 As a power transmission shaft, it can be suitably used not only for automotive applications but also for marine applications, various industrial machinery applications, and aircraft applications.
２     金属製軸部材
３     樹脂製軸部材
８     微細凹凸面
１０   締結構造部
１１   金属製筒体
１５   凸部
１６   凹部
１８   嵌合接触部位
Ｍ     凹凸嵌合構造 2 Metal shaft member 3 Resin shaft member 8 Fine asperity surface 10 Fastening structure 11 Metal cylinder 15 Convex part 16 Concave part 18 Mating contact site M Corrugated fitting structure

Claims (5)

  1.   金属製軸部材と、この金属製軸部材に軸方向に沿って連設される樹脂製軸部材とを備えた動力伝達シャフトであって、
    　前記樹脂製軸部材が繊維強化プラスチックで構成され、前記金属製軸部材と前記樹脂製軸部材とは、微細凹凸面に繊維強化プラスチックが流入固化してなる締結構造部を介して接合されていることを特徴とする動力伝達シャフト。     A power transmission shaft comprising: a metal shaft member; and a resin shaft member connected to the metal shaft member in the axial direction,
    The resin shaft member is made of fiber reinforced plastic, and the metal shaft member and the resin shaft member are joined to a fine uneven surface through a fastening structure formed by inflow solidification of the fiber reinforced plastic. Power transmission shaft characterized by
  2. 　前記金属製軸部材の外表面に前記微細凹凸面が形成され、前記樹脂製軸部材が前記微細凹凸面に外嵌されて、前記金属製軸部材の外表面と前記樹脂製軸部材の内径面との間に前記締結構造部が形成されていることを特徴とする請求項１に記載の等速自在継手。 The fine uneven surface is formed on the outer surface of the metal shaft member, and the resin shaft member is externally fitted to the fine uneven surface, and the outer surface of the metal shaft member and the inner diameter surface of the resin shaft member The constant velocity universal joint according to claim 1, wherein the fastening structure portion is formed therebetween.
  3. 　前記金属製軸部材に金属製筒体が外嵌固定され、この金属製筒体は外表面に前記微細凹凸面が形成され、前記樹脂製軸部材が前記微細凹凸面に外嵌されて、前記金属製筒体の外表面と前記樹脂製軸部材の内径面との間に締前記結構造部が形成されていることを特徴とする請求項１に記載の等速自在継手。 A metal cylinder is externally fitted and fixed to the metal shaft member, and the metal cylinder is formed with the fine uneven surface on the outer surface, and the resin shaft member is externally fitted to the fine uneven surface, The constant velocity universal joint according to claim 1, wherein a fastening and connecting portion is formed between an outer surface of a metal cylinder and an inner diameter surface of the resin shaft member.
  4. 　前記金属製軸部材と前記金属製筒体とが異種材にて構成されていることを特徴とする請求項３に記載の等速自在継手。 The constant velocity universal joint according to claim 3, wherein the metal shaft member and the metal cylinder are made of different materials.
  5. 　前記金属製軸部材と前記金属製筒体とが、凸部とその凸部に嵌合する相手部材の凹部との嵌合接触部位全域が密着する凹凸嵌合構造を介して接合されていることを特徴とする請求項３又は請求項４に記載の等速自在継手。 The metal shaft member and the metal cylindrical body are joined via a concavo-convex fitting structure in which the entire area of the fitting contact portion of the protrusion and the recess of the mating member fitting to the protrusion is in close contact with each other. The constant velocity universal joint according to claim 3 or 4, characterized in that
PCT/JP2018/029687 2017-08-18 2018-08-07 Power transmission shaft WO2019035395A1 (en)

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JP2017157963A JP2019035482A (en) 2017-08-18 2017-08-18 Power transmission shaft

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US20220242555A1 (en) * 2019-05-22 2022-08-04 Moog Inc. Preloaded torque shaft and the flight control driveline made therewith

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JP7414787B2 (en) * 2021-10-28 2024-01-16 中央可鍛工業株式会社 Joining joint to be joined to resin and method for manufacturing joining joint

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JPS6251694B2 (en) * 1978-06-21 1987-10-31 Hitachi Ltd
JP2004144269A (en) * 2002-10-28 2004-05-20 Hitachi Unisia Automotive Ltd Connecting structure for power transmission
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JP2014222069A (en) * 2013-05-13 2014-11-27 本田技研工業株式会社 Torque transfer device
JP2015100967A (en) * 2013-11-22 2015-06-04 株式会社ジェイテクト Method for manufacturing bar shaped component and bar shaped component
JP2015113359A (en) * 2013-12-09 2015-06-22 株式会社ジェイテクト Manufacturing method of bar-like component, and bar-like component

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JPS6251694B2 (en) * 1978-06-21 1987-10-31 Hitachi Ltd
JPS62101911A (en) * 1985-10-29 1987-05-12 Honda Motor Co Ltd Driving shaft for vehicle
JP2004144269A (en) * 2002-10-28 2004-05-20 Hitachi Unisia Automotive Ltd Connecting structure for power transmission
JP2012062013A (en) * 2010-09-17 2012-03-29 Ntn Corp Vehicle-wheel bearing device
JP2014222069A (en) * 2013-05-13 2014-11-27 本田技研工業株式会社 Torque transfer device
JP2015100967A (en) * 2013-11-22 2015-06-04 株式会社ジェイテクト Method for manufacturing bar shaped component and bar shaped component
JP2015113359A (en) * 2013-12-09 2015-06-22 株式会社ジェイテクト Manufacturing method of bar-like component, and bar-like component

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220242555A1 (en) * 2019-05-22 2022-08-04 Moog Inc. Preloaded torque shaft and the flight control driveline made therewith

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