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WO2017187947A1 - Joint homocinétique - Google Patents

Joint homocinétique Download PDF

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Publication number
WO2017187947A1
WO2017187947A1 PCT/JP2017/014595 JP2017014595W WO2017187947A1 WO 2017187947 A1 WO2017187947 A1 WO 2017187947A1 JP 2017014595 W JP2017014595 W JP 2017014595W WO 2017187947 A1 WO2017187947 A1 WO 2017187947A1
Authority
WO
WIPO (PCT)
Prior art keywords
power transmission
transmission shaft
constant velocity
velocity universal
annular
Prior art date
Application number
PCT/JP2017/014595
Other languages
English (en)
Japanese (ja)
Inventor
真 友上
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2017033370A external-priority patent/JP6879775B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to EP17789234.6A priority Critical patent/EP3450783B1/fr
Priority to US16/095,450 priority patent/US11512743B2/en
Publication of WO2017187947A1 publication Critical patent/WO2017187947A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B2/00—Friction-grip releasable fastenings
    • F16B2/02—Clamps, i.e. with gripping action effected by positive means other than the inherent resistance to deformation of the material of the fastening
    • F16B2/16—Clamps, i.e. with gripping action effected by positive means other than the inherent resistance to deformation of the material of the fastening using rollers or balls
    • 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
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B21/00—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings
    • F16B21/10—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts
    • F16B21/16—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft
    • F16B21/18—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft with circlips or like resilient retaining devices, i.e. resilient in the plane of the ring or the like; Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B7/00—Connections of rods or tubes, e.g. of non-circular section, mutually, including resilient connections
    • F16B7/20—Connections of rods or tubes, e.g. of non-circular section, mutually, including resilient connections using bayonet connections
    • 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
    • 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
    • F16D3/22—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/224—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 the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/50—Sealings between relatively-movable members, by means of a sealing without relatively-moving surfaces, e.g. fluid-tight sealings for transmitting motion through a wall
    • F16J15/52—Sealings between relatively-movable members, by means of a sealing without relatively-moving surfaces, e.g. fluid-tight sealings for transmitting motion through a wall by means of sealing bellows or diaphragms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J3/00—Diaphragms; Bellows; Bellows pistons
    • F16J3/04—Bellows

Definitions

  • the present invention relates to a constant velocity universal joint that is used in a power transmission system of automobiles and various industrial machines, and is particularly incorporated in a propeller shaft for automobiles.
  • constant velocity universal joints that are used as a means for transmitting rotational force from an automobile engine to wheels at a constant speed: a fixed constant velocity universal joint and a sliding constant velocity universal joint. Both of these constant velocity universal joints have a structure in which two shafts on the driving side and the driven side are connected so that rotational torque can be transmitted at a constant speed even if the two shafts have an operating angle.
  • the propeller shaft is generally a fixed type constant velocity universal joint that allows only angular displacement on the transmission side, and a sliding type constant velocity universal joint that allows both axial displacement and angular displacement on the differential side. Equipped with a structure where both constant velocity universal joints are connected by a propeller shaft.
  • the fixed type constant velocity universal joint includes an outer joint member, an inner joint member, a plurality of balls, and a cage.
  • a power transmission shaft which is an output shaft extending from the transmission, is coupled to the shaft hole of the inner joint member so that torque can be transmitted by spline fitting.
  • the power transmission shaft is prevented from coming off from the inner joint member by a retaining ring.
  • the inner joint member of the constant velocity universal joint is extended to the axial power transmission shaft side, and at a portion other than the spline fitting portion between the inner joint member and the power transmission shaft, The inner joint member and the power transmission shaft are fixed with a retaining ring.
  • the drive sleeve is connected to the inner joint member of the constant velocity universal joint so that torque can be transmitted by spline fitting, the drive nut is connected to the power transmission shaft, and the drive nut is connected to the drive sleeve.
  • the structure which fitted is comprised.
  • the constant velocity universal joint needs to be detachable with respect to the power transmission shaft of the transmission for parts replacement and maintenance inspection of the propeller shaft.
  • the connection structure between the power transmission shaft and the constant velocity universal joint disclosed in Patent Documents 1 and 2 has the following problems.
  • the drive nut of the power transmission shaft is fitted to the drive sleeve extending from the inner joint member of the constant velocity universal joint, so that the constant velocity universal joint can be securely attached to the power transmission shaft.
  • the constant velocity universal joint can be easily separated from the power transmission shaft.
  • the present invention has been proposed in view of the above-mentioned problems, and the object of the present invention is to securely fix the inner joint member and the power transmission shaft with a simple structure, and to easily separate them. It is to provide a quick universal joint.
  • the constant velocity universal joint includes an outer joint member and an inner joint member that transmits torque while allowing angular displacement between the outer joint member and the outer joint member via the torque transmission member.
  • the power transmission shaft is coupled so as to be able to transmit torque, and a structure is provided between the inner joint member and the power transmission shaft, and a detachment mechanism for attaching and detaching the power transmission shaft to and from the inner joint member is provided.
  • the detaching mechanism according to the present invention includes a cylindrical member that extends from the inner joint member and is extrapolated to the power transmission shaft, and is movable in the radial direction to the cylindrical member.
  • the power transmission shaft and the inner joint member are fixed and separated by the attachment / detachment mechanism including the cylindrical member, the fixing member, and the annular member in the following manner.
  • the power transmission shaft and the inner joint member are fixed and separated by a fixing member in a tubular member extending from the inner joint member.
  • the fixing of the power transmission shaft and the inner joint member is as follows.
  • the annular member is moved in the direction approaching the fixed member in the cylindrical member. Due to the proximity movement of the annular member, the fixing member moves radially inward within the cylindrical member. At this time, the movement of the fixing member to the outside in the radial direction is restricted by the annular member. Thereby, a fixing member protrudes from the internal peripheral surface of a cylindrical member. By the protrusion of the fixing member, the fixing member is locked to the power transmission shaft.
  • the separation of the power transmission shaft and the inner joint member is as follows.
  • the annular member is moved away from the fixed member in the cylindrical member.
  • the separation movement of the annular member By the separation movement of the annular member, the movement restraining state of the fixing member toward the radially outer side is released, and the fixing member becomes movable toward the radially outer side.
  • the fixing member moves radially outward and retracts from the inner peripheral surface of the tubular member.
  • the locked state of the fixing member with respect to the power transmission shaft is released.
  • the detaching mechanism in the present invention is provided with a locking groove on one of the end of the inner joint member and the end of the cylindrical member, and a locking claw on the other, and the locking claw is fitted in the locking groove.
  • a structure in which the inner joint member and the tubular member are connected by combining them is desirable.
  • the cylindrical member can be formed separately from the inner joint member that is a component of the constant velocity universal joint, and the cylindrical member can be easily manufactured.
  • the cylindrical member of the detaching mechanism in the present invention preferably has a structure composed of a plurality of divided members divided in the circumferential direction.
  • the cylindrical member when the structure in which the cylindrical member is constituted by a plurality of divided members divided in the circumferential direction is employed, the cylindrical member can be easily assembled to the inner joint member.
  • the desorption mechanism in the present invention preferably has a structure in which an annular concave groove is formed on the outer peripheral surface of the power transmission shaft so that the concave groove of the power transmission shaft and the fixing member in the cylindrical member can be engaged and detached.
  • the fixing member when the structure in which the annular groove is formed on the outer peripheral surface of the power transmission shaft is employed, when the power transmission shaft and the inner joint member are fixed, the fixing member is fitted into the groove of the power transmission shaft. Thus, the fixing member can be reliably locked to the power transmission shaft. In addition, when the power transmission shaft and the inner joint member are separated, the fixing member can be reliably detached from the power transmission shaft by separating the fixing member from the concave groove of the power transmission shaft.
  • through holes are formed at a plurality of positions in the circumferential direction of the cylindrical member to be opened at the inner and outer circumferences of the cylindrical member, and a spherical fixing member is disposed in the through hole and the inner circumferential side opening portion thereof.
  • a spherical fixing member is disposed in the through hole and the inner circumferential side opening portion thereof.
  • the fixing member is moved inward in the radial direction when the power transmission shaft and the inner joint member are fixed. By protruding from the inner peripheral surface of the cylindrical member, it becomes easy to lock the fixing member to the power transmission shaft.
  • the fixing member retreats from the inner peripheral surface of the cylindrical member by moving the fixing member radially outward, so that the fixing member is detached from the power transmission shaft. It becomes easy to make.
  • the desorption mechanism in the present invention desirably has a structure in which at least one of the inner peripheral side opening and the outer peripheral side opening of the through hole of the cylindrical member is reduced in diameter so as to have an inner diameter smaller than the outer diameter of the fixing member.
  • the desorption mechanism in the present invention preferably has a structure in which an annular member is attached to the end of the boot that closes the opening of the outer joint member.
  • the annular member prevents the leakage of the lubricant enclosed in the joint and prevents the entry of foreign matter from the outside of the joint, the power transmission shaft, the inner joint member, Detachment function by a desorption mechanism that fixes and separates.
  • the desorption mechanism according to the present invention preferably has a structure in which a seal portion vulcanized and bonded is formed on the inner peripheral surface of the annular member, and the seal portion is unevenly fitted in an annular recess formed in the power transmission shaft.
  • the desorption mechanism according to the present invention preferably has a structure in which an annular groove is formed on the outer peripheral surface of the power transmission shaft, and a seal member that contacts the end of the annular member is fitted in the groove.
  • the detaching mechanism for attaching and detaching the power transmission shaft to and from the inner joint member is constituted by the cylindrical member, the fixing member, and the annular member, so that the inner joint member and the power transmission shaft can be configured with a simple structure. It can be securely fixed and easily separated. As a result, it is possible to improve the degree of design freedom in the detaching mechanism, and to reduce the cost of the constant velocity universal joint without increasing the number of parts.
  • FIG. 3 is a cross-sectional view showing a state before the power transmission shaft is inserted into the inner joint member in the desorption mechanism of FIG. 2.
  • FIG. 3 is a cross-sectional view showing a state in the middle of inserting a power transmission shaft into an inner joint member in the desorption mechanism of FIG. 2.
  • FIG. 3 is a cross-sectional view showing a state where insertion of a power transmission shaft into an inner joint member is completed in the detaching mechanism of FIG. 2.
  • FIG. 3 is a cross-sectional view showing a state after a power transmission shaft is fixed to an inner joint member in the desorption mechanism of FIG. 2. It is sectional drawing which shows the whole structure of the constant velocity universal joint in other embodiment of this invention. It is a perspective view which shows the cylindrical member of a division
  • a Rzeppa type constant velocity universal joint which is one of fixed type constant velocity universal joints incorporated in a propeller shaft for an automobile, is exemplified, but undercut-free as another fixed type constant velocity universal joint. It can also be applied to a constant velocity universal joint (UJ).
  • the present invention can also be applied to sliding type constant velocity universal joints such as a double offset type constant velocity universal joint (DOJ), a cross groove type constant velocity universal joint (LJ), and a tripod type constant velocity universal joint (TJ).
  • DOJ double offset type constant velocity universal joint
  • LJ cross groove type constant velocity universal joint
  • TJ tripod type constant velocity universal joint
  • the propeller shaft is generally a fixed type constant velocity universal joint that allows only angular displacement on the transmission side, and a sliding type constant velocity universal joint that allows both axial displacement and angular displacement on the differential side. Equipped with a structure in which both constant velocity universal joints are connected by a steel propeller shaft.
  • the fixed type constant velocity universal joint 11 (hereinafter, simply referred to as a constant velocity universal joint) of this embodiment includes a plurality of outer joint members 12, an inner joint member 13, and torque transmission members.
  • the ball 14 and the cage 15 constitute a main part.
  • arc-shaped track grooves 16 extending in the axial direction are formed at a plurality of positions in the circumferential direction of the spherical inner peripheral surface 17 at equal intervals.
  • a pipe-like propeller shaft 19 is coaxially coupled to one open end 18 of the outer joint member 12 so that torque can be transmitted by friction welding or the like.
  • a seal plate 20 is attached to the open end 18 by press-fitting so as to enclose a lubricant such as grease inside the outer joint member 12.
  • arc-shaped track grooves 21 extending in the axial direction in pairs with the track grooves 16 of the outer joint member 12 are formed at a plurality of positions in the circumferential direction of the spherical outer peripheral surface 22 at equal intervals.
  • a power transmission shaft 25, which is an output shaft extending from the transmission 24, is connected to the shaft hole 23 of the inner joint member 13 so that torque can be transmitted by spline fitting.
  • the power transmission shaft 25 can be attached to and detached from the inner joint member 13 by a detachment mechanism 33.
  • the ball 14 is interposed between the track groove 16 of the outer joint member 12 and the track groove 21 of the inner joint member 13.
  • the ball 14 transmits rotational torque between the outer joint member 12 and the inner joint member 13.
  • the number of balls 14 may be 6, 8, or any number, and the number is arbitrary.
  • the cage 15 is interposed between the inner peripheral surface 17 of the outer joint member 12 and the outer peripheral surface 22 of the inner joint member 13.
  • a plurality of pockets 26 for holding the balls 14 are formed at a plurality of positions in the circumferential direction at equal intervals.
  • the operating angle of the ball 14 held in the cage 15 is always set. In this case, the operating angle is maintained within the bisecting plane, and the constant velocity between the outer joint member 12 and the inner joint member 13 is ensured. Between the outer joint member 12 and the inner joint member 13, rotational torque is transmitted via the balls 14 in a state where constant velocity is ensured.
  • the constant velocity universal joint 11 is provided with a sealing mechanism between the outer joint member 12 and the power transmission shaft 25 in order to prevent leakage of the lubricant enclosed in the outer joint member 12 and prevent foreign matter from entering from the outside. 27 is provided.
  • the constant velocity universal joint 11 for the propeller shaft has a high rotation and a small operating angle.
  • the sealing mechanism 27 described above includes a rubber boot 28, a metal ring 29, and an annular member 37.
  • the boot 28 has a small-diameter end portion 30 and a large-diameter end portion 31 and has a U-shaped folded shape in the middle.
  • One end of the metal ring 29 is fixed to the outer peripheral surface of the open end 32 of the outer joint member 12 by press-fitting, and the other end is fixed to the large-diameter end 31 of the boot 28 by caulking.
  • the small diameter end portion 30 of the boot 28 is integrally fixed by vulcanization adhesion.
  • the annular member 37 constitutes a part of the seal mechanism 27 and a part of the detachment mechanism 33.
  • the constant velocity universal joint 11 of this embodiment includes a detaching mechanism 33 having the following structure.
  • the detaching mechanism 33 is provided between the inner joint member 13 of the constant velocity universal joint 11 and the power transmission shaft 25 of the transmission 24, and includes a cylindrical member 34, a fixing member 36, and the like.
  • the main part is composed of the annular member 37.
  • the cylindrical member 34 is extrapolated to the power transmission shaft 25 so as to extend in the axial direction toward the transmission 24 side of the inner joint member 13.
  • An annular locking groove 38 is provided on the outer peripheral surface of the protruding end portion located on the transmission 24 side of the inner joint member 13, and the annular engagement is provided on the inner peripheral surface of the end portion of the cylindrical member 34 located on the propeller shaft 19 side.
  • a pawl 39 is provided.
  • the inner joint member 13 and the cylindrical member 34 are connected by fitting the locking claw 39 of the cylindrical member 34 into the locking groove 38 of the inner joint member 13.
  • the cylindrical member 34 is axially restricted by the step surface 41 of the large-diameter portion 40 of the power transmission shaft 25 while being connected to the inner joint member 13.
  • the cylindrical member 34 is provided with a slit (not shown) so that the diameter can be increased.
  • a slit (not shown) so that the diameter can be increased.
  • the diameter of the cylindrical member 34 is increased using a slit, so that the locking claw 39 of the cylindrical member 34 and the locking groove 38 of the inner joint member 13 are formed. Mating is easy. Even if such a slit is provided, since the outer periphery of the cylindrical member 34 after assembly is restrained by the annular member 37, the cylindrical member 34 does not unnecessarily expand its diameter.
  • the cylindrical member 34 is illustrated as a separate member from the inner joint member 13 that is a component of the constant velocity universal joint 11, but the cylindrical member 34 is configured integrally with the inner joint member 13. It is also possible to do. In addition, by forming the cylindrical member 34 separately from the inner joint member 13, the cylindrical member 34 can be easily manufactured on the processing surface.
  • the cylindrical member 34 is made of, for example, low carbon steel, brass, aluminum, resin, or the like, and does not cause deformation or breakage of the locking claw 39 with a required axial strength (for example, about 2000 N at the maximum). If it is.
  • a hook portion 35 is formed on the outer peripheral surface of the cylindrical member 34 so as to protrude outward in the radial direction.
  • Through holes 46 that open to the inner and outer peripheries of the cylindrical member 34 are formed at a plurality of locations in the circumferential direction of the cylindrical member 34 (four locations at intervals of 90 °), and a spherical fixing member 36 is radially attached to the through hole 46. It is movably accommodated. Due to the radial movement of the fixing member 36, the fixing member 36 can protrude and retract with respect to the outer peripheral side opening 47 and the inner peripheral side opening 48 of the through hole 46 of the cylindrical member 34.
  • the fixing member 36 a plurality of (four) spherical bodies (steel balls) are exemplified.
  • the fixing members 36 arranged at two positions above and below in the opposite direction of 180 ° are shown.
  • the number of the fixing members 36 may be appropriately set depending on the fixing force required for locking the cylindrical member 34 to the power transmission shaft 25.
  • the fixing member 36 moves inward in the radial direction. It becomes easy to restrain the power transmission shaft 25 by the fixing member 36. Further, when the power transmission shaft 25 and the inner joint member 13 are separated, it is easy to release the restraint of the power transmission shaft 25 by the fixing member 36 by the movement of the fixing member 36 radially outward.
  • the through hole 46 of the cylindrical member 34 has a diameter that is slightly smaller than the outer diameter of the fixing member 36 by reducing the diameter of the inner peripheral side opening 48 of the cylindrical member 34. Accordingly, when the annular member 37 is assembled to the cylindrical member 34 (in a state where the power transmission shaft 25 is not inserted into the cylindrical member 34), the fixing member 36 accommodated in the through hole 46 of the cylindrical member 34 is gravity-induced. Etc. to prevent the cylindrical member 34 from falling off to the inner diameter side (see FIG. 4).
  • annular groove 45 is formed in the outer peripheral surface between the spline fitting portion 44 and the large diameter portion 40 of the power transmission shaft 25.
  • the concave groove 45 coincides with the axial position of the through hole 46 provided in the cylindrical member 34 in a state where the cylindrical member 34 is in contact with the stepped surface 41 of the large-diameter portion 40 of the power transmission shaft 25. Is formed. In this state, the fixing member 36 is engaged with the groove 45 so that the fixing member 36 is locked to the power transmission shaft 25.
  • the annular member 37 is disposed on the outer peripheral surface of the large-diameter portion 40 of the power transmission shaft 25 and the outer peripheral surface of the cylindrical member 34 so as to be axially movable.
  • the annular member 37 is integrally attached to the small-diameter end 30 of the boot 28 constituting a part of the above-described seal mechanism 27 by vulcanization adhesion.
  • the annular member 37 has a cylindrical shape that is long in the axial direction, and is located on the transmission 24 side, and is a small-diameter cylindrical portion 49 that is in sliding contact with the outer peripheral surface of the large-diameter portion 40 of the power transmission shaft 25 and the outer peripheral surface of the cylindrical member 34. And a large-diameter cylindrical portion 50 that is located on the propeller shaft 19 side and has a gap with the outer peripheral surface of the cylindrical member 34.
  • the transmission side end portion 51 of the small diameter cylindrical portion 49 is bent outward in the radial direction.
  • the small-diameter cylindrical portion 49 restricts the movement of the fixing member 36 to the outside in the radial direction in a state where the fixing member 36 is accommodated in the through hole 46 of the cylindrical member 34. It protrudes from the inner peripheral surface.
  • an enlarged-diameter portion 52 that is inclined in a tapered shape from the small-diameter cylindrical portion 49 toward the large-diameter cylindrical portion 50 is provided.
  • the fixing member 36 can be smoothly moved radially inward along the enlarged diameter portion 52 by the axial movement of the annular member 37.
  • the large-diameter cylindrical portion 50 accommodates the fixing member 36 in which the restrained state of the radially outward movement is released when the power transmission shaft 25 and the inner joint member 13 are separated. Thereby, the fixing member 36 is prevented from falling off from the through hole 46 of the cylindrical member 34 radially outward.
  • the propeller shaft side end portion 43 of the large diameter cylindrical portion 50 is reduced in diameter and bent radially inward.
  • the inner diameter of the propeller shaft side end 43 reduced in diameter from the large diameter cylindrical portion 50 is larger than the outer diameter of the cylindrical member 34, and the hook portion 35 provided on the outer peripheral surface of the cylindrical member 34. It is set smaller than the outer diameter.
  • the annular member 37 can be smoothly moved in the axial direction with respect to the tubular member 34, and the propeller shaft side end portion 43 interferes with the catch portion 35 during the axial movement, so that the annular member 37 becomes the tubular member. This prevents the member 34 from being pulled out.
  • the fixing member 36 protrudes from the inner peripheral surface of the cylindrical member 34, and the small diameter cylindrical portion of the annular member 37.
  • the fixing member 36 is accommodated in the large-diameter cylindrical portion 50 of the annular member 37 and protrudes from the inner peripheral surface of the cylindrical member 34.
  • the size of the fixing member 36 is set so that it does not occur.
  • the fixing member 36 can be reliably locked and detached from the power transmission shaft 25.
  • annular groove 53 is formed on the transmission side of the outer peripheral surface of the large-diameter portion 40 of the power transmission shaft 25, and a retaining ring 54 is fitted in the groove 53.
  • the propeller shaft side end 43 of the annular member 37 is locked to the stepped portion 55 on the outer peripheral surface of the cylindrical member 34, and the transmission side end 51 of the annular member 37 is locked to the retaining ring 54.
  • the position of the annular member 37 is restricted on both sides in the axial direction with respect to the power transmission shaft 25 and the cylindrical member 34.
  • annular groove 56 is formed on the propeller shaft side of the outer peripheral surface of the large-diameter portion 40 of the power transmission shaft 25, and an O-ring 57 is fitted into the groove 56.
  • An annular member 37 is externally fitted to the outer peripheral surface of the large-diameter portion 40 of the power transmission shaft 25 and the outer peripheral surface of the cylindrical member 34 via the O-ring 57.
  • the annular member 37 not only has an attaching / detaching function by the attaching / detaching mechanism 33 that fixes and separates the power transmission shaft 25 and the inner joint member 13 but also prevents leakage of the lubricant encapsulated inside the joint and from the outside of the joint.
  • the seal function by the boot 28 of the seal mechanism 27 that prevents foreign matter from entering is also exhibited.
  • the fixing member 36 in the tubular member 34 is moved in the radial direction by the axial movement of the annular member 37, so that the fixing member 36 can be attached to and detached from the power transmission shaft 25. .
  • the detachment mechanism 33 including the cylindrical member 34, the fixing member 36, and the annular member 37 is used to connect the power transmission shaft 25 to the power transmission shaft 25 in the following manner shown in FIGS. Fixing and separation from the inner joint member 13 are performed. 4 to 7 show a state in which the fixing member 36 receives gravity from above to below.
  • FIG. 4 shows a state before the power transmission shaft 25 is inserted into the inner joint member 13
  • FIG. 5 shows a state in the middle of inserting the power transmission shaft 25 into the inner joint member 13 (see FIG. 3)
  • FIG. 7 shows a state in which the insertion of the power transmission shaft 25 into the inner joint member 13 is completed.
  • FIG. 7 shows a state after the power transmission shaft 25 is fixed to the inner joint member 13 (before the retaining ring 54 shown in FIGS. 1 and 2 is attached). State).
  • the cylindrical member 34 is locked in the locking groove 38 of the inner joint member 13.
  • the cylindrical member 34 is assembled to the inner joint member 13 by fitting the claw 39.
  • the annular member 37 is extrapolated to the outer peripheral surface of the cylindrical member 34.
  • the fixing member 36 is disposed in the through hole 46 of the cylindrical member 34, and the annular member 37 is extrapolated to the outer peripheral surface of the cylindrical member 34.
  • the propeller shaft side end portion 43 of the annular member 37 is inserted until it exceeds the catching portion 35 of the tubular member 34.
  • the large-diameter cylindrical portion 50 of the annular member 37 is disposed so as to close the outer peripheral opening 47 of the through hole 46 of the tubular member 34. Further, since the inner peripheral side opening 48 of the through hole 46 of the cylindrical member 34 is reduced in diameter, the fixing member 36 accommodated in the through hole 46 falls off from the inner peripheral side opening 48 of the through hole 46. None do. At this time, the propeller shaft side end portion 43 of the annular member 37 is locked to the catch portion 35 of the cylindrical member 34, so that the annular member 37 is prevented from coming off from the cylindrical member 34.
  • the power transmission shaft 25 is inserted into the shaft hole 23 of the inner joint member 13, and the inner joint member 13 and the power transmission shaft 25 are inserted. Are connected so that torque can be transmitted by spline fitting.
  • the power transmission shaft 25 is inserted until the stepped surface 41 of the large-diameter portion 40 of the power transmission shaft 25 contacts the cylindrical member 34 at the transmission-side end portion of the cylindrical member 34.
  • a jig 58 attached to the metal ring 29 of the seal mechanism 27 is used as shown in FIG.
  • the jig 58 has a locking portion 59 that restricts the annular member 37 of the detaching mechanism 33 from moving in the axial direction.
  • the locking portion 59 abuts on the inner side of the transmission-side end portion 51 of the annular member 37 so that the large-diameter cylindrical portion 50 of the annular member 37 closes the outer peripheral opening 47 of the through hole 46 of the tubular member 34.
  • the annular member 37 is positioned with respect to the cylindrical member 34.
  • the jig 58 is removed. Note that the above-described jig 58 is not necessarily required as long as the fixed state of the annular member 37 can be maintained.
  • the axial movement of the annular member 37 accompanying the insertion of the power transmission shaft 25 is prevented, and the annular member 37 is inserted into the outer peripheral side opening 47 of the through hole 46 of the cylindrical member 34.
  • the annular member 37 can be positioned so that the large-diameter cylindrical portion 50 corresponds.
  • the fixing member 36 can freely move in the radial direction within the through hole 46 of the cylindrical member 34, and the fixing member 36 can be accommodated in the large-diameter cylindrical portion 50 of the annular member 37.
  • the fixing member 36 does not protrude from the inner peripheral side opening 48 of the through hole 46 of the cylindrical member 34, so that the insertion of the power transmission shaft 25 is not hindered. Therefore, it becomes easy to assemble the inner joint member 13 to the power transmission shaft 25.
  • the large-diameter cylindrical portion 50 of the annular member 37 is disposed so as to correspond to the outer peripheral side opening 47 of the through hole 46 of the cylindrical member 34. Since the fixing member 36 can freely move in the radial direction within the through hole 46 of the cylindrical member 34, the fixing member 36 is pushed out radially outward by the outer peripheral surface of the power transmission shaft 25 inserted into the cylindrical member 34. It is.
  • the fixing member 36 is not accommodated in the large-diameter cylindrical portion 50 of the annular member 37 and protrudes radially inward from the inner peripheral side opening 48 of the through hole 46. As a result, the power transmission shaft 25 is smoothly inserted into the cylindrical member 34.
  • the stepped surface 41 of the large diameter portion 40 of the power transmission shaft 25 is brought into contact with the transmission side end portion of the cylindrical member 34 as shown in FIG.
  • the concave groove 45 located on the outer peripheral surface of the power transmission shaft 25 is arranged at a position corresponding to the fixing member 36 exposed from the inner peripheral side opening 48 of the through hole 46 of the cylindrical member 34.
  • the fixing member 36 can freely move in the radial direction in the through hole 46 of the cylindrical member 34 between the concave groove 45 of the power transmission shaft 25 and the large-diameter cylindrical portion 50 of the annular member 37. is there.
  • the annular member 37 is slid in the direction close to the fixing member 36 (propeller shaft 19 side).
  • the fixing member 36 protruding from the outer peripheral side opening 47 of the through hole 46 of the cylindrical member 34 abuts on the enlarged diameter portion 52 of the annular member 37.
  • the annular member 37 pushes and moves the fixing member 36 radially inward.
  • the fixing member 36 is smoothly pushed along the enlarged diameter portion 52 of the annular member 37.
  • the propeller shaft side end portion 43 abuts on the stepped portion 55 on the outer peripheral surface of the cylindrical member 34 by the axial movement of the annular member 37.
  • the small-diameter cylindrical portion 49 of the annular member 37 restrains the movement of the fixing member 36 outward in the radial direction, the fixing member 36 moved radially inward within the through-hole 46 of the tubular member 34 is inserted into the through-hole 46. It protrudes from the inner peripheral side opening 48 of the power transmission shaft 25 and fits into the groove 45 of the power transmission shaft 25. In this way, the fixing member 36 pressed by the small-diameter cylindrical portion 49 of the annular member 37 is locked in the concave groove 45 of the power transmission shaft 25.
  • the fixing member 36 fixes the power transmission shaft 25 and the inner joint member 13 via the tubular member 34. Then, the retaining ring 54 is fitted in the concave groove 53 of the power transmission shaft 25 (see FIG. 2) to complete the fixing of the power transmission shaft 25 and the inner joint member 13.
  • the fixing member 36 can freely move in the radial direction in the through hole 46, and the state of being locked to the power transmission shaft 25 is released. From this state, when the spline fitting portion 44 of the power transmission shaft 25 is pulled out from the shaft hole 23 of the inner joint member 13, the fixing member 36 retreats from the inner peripheral side opening 48 of the through hole 46 of the cylindrical member 34. Then, it comes out of the concave groove 45 of the power transmission shaft 25 and comes into contact with the outer peripheral surface (see FIG. 5). Further, by pulling out the power transmission shaft 25, the separation of the power transmission shaft 25 and the inner joint member 13 is completed.
  • the concave groove 56 is formed on the outer peripheral surface of the large-diameter portion 40 of the power transmission shaft 25, and the O-ring 57 is fitted into the concave groove 56, thereby Although the structure in which the inner peripheral surface is in close contact with the O-ring 57 is illustrated, other structures may be used.
  • the seal portion 61 has a convex shape that matches the concave shape of the recess 60 of the power transmission shaft 25. As a result, it is possible to ensure sealing performance and restrict the axial position with respect to the power transmission shaft 25.
  • an integral cylindrical member 34 is illustrated.
  • the diameter of the cylindrical member 34 is increased using a slit, so that the locking claw 39 of the cylindrical member 34 and the locking groove 38 of the inner joint member 13 To fit.
  • the engaging claw 39 of the tubular member 34 and the engaging groove 38 of the inner joint member 13 can be fitted without expanding the diameter of the tubular member 34 (see FIGS. 1 to 8). . In this way, the cylindrical member 34 can be easily assembled to the inner joint member 13.
  • FIGS. 10 and 11 the same parts as those in FIG. 1 and FIG.
  • annular locking groove 62 is provided on the outer peripheral surface of the projecting end portion located on the propeller shaft 19 side of the tubular member 34, and the inner joint member 13 is located on the transmission 24 side.
  • An annular locking claw 63 is provided on the inner peripheral surface of the end portion.
  • the cylindrical member 34 is provided with a slit (not shown) so that the diameter can be reduced.
  • a slit (not shown) so that the diameter can be reduced.
  • the diameter of the tubular member 34 is reduced using a slit, so that the engagement claw 63 of the inner joint member 13 and the engagement groove 62 of the tubular member 34 are reduced. Mating is easy. Even if such a slit is provided, since the inner periphery of the cylindrical member 34 after assembly is restrained by the power transmission shaft 25, the cylindrical member 34 will not be unnecessarily reduced in diameter.
  • the propeller shaft side end portion 43 of the annular member 37 is locked to the end surface of the inner joint member 13, and the transmission side end portion 51 of the annular member 37 is locked to the retaining ring 54.
  • the position of the annular member 37 is restricted on both sides in the axial direction with respect to the power transmission shaft 25 and the cylindrical member 34.
  • a concave groove 56 is formed on the outer peripheral surface of the large-diameter portion 40 of the power transmission shaft 25, and an O-ring 57 is fitted into the concave groove 56.
  • an O-ring 57 is fitted into the concave groove 56.
  • annular recess 60 is formed in the outer peripheral surface of the large-diameter portion 40 of the power transmission shaft 25, and the rubber material of the boot 28 is used as the annular member 37.
  • the seal portion 61 is formed by vulcanizing and bonding also to the inner peripheral surface, and the annular member 37 is brought into close contact with the power transmission shaft 25 by the concave-convex fitting of the seal portion 61 and the recess 60.
  • an integral cylindrical member 34 is illustrated.
  • the diameter of the cylindrical member 34 is reduced using a slit, so that the locking claw 63 of the inner joint member 13 and the locking groove 62 of the cylindrical member 34 To fit.
  • the number of the division members 65 may be other than three, and the number is arbitrary.
  • the engaging claw 63 of the inner joint member 13 and the engaging groove 62 of the tubular member 34 can be fitted without reducing the diameter of the tubular member 34. In this way, the cylindrical member 34 can be easily assembled to the inner joint member 13.
  • a simple core material such as sponge or plastic may be inserted into the inner periphery of the cylindrical member 34 during handling. That is, the cylindrical member 34 is assembled to the inner joint member 13, the fixing member 36 is accommodated in the through hole 46, the annular member 37 is extrapolated to the cylindrical member 34, and the core is inserted immediately before the power transmission shaft 25 is assembled. If the material is removed, the dividing member 65 of the cylindrical member 34 can be prevented from moving and separating.
  • the cylindrical member 34 in which the inner peripheral side opening 48 of the through hole 46 is reduced in diameter is illustrated.
  • the fixing member 36 accommodated in the through hole 46 is prevented from falling off to the inner peripheral side of the cylindrical member 34 when the annular member 37 is assembled to the cylindrical member 34.
  • the present invention is not limited to this, and may have a structure as shown in FIG.
  • FIG. 13 is an embodiment applied to the cylindrical member 34 shown in FIG. 10, and the same parts as those in FIG.
  • FIG. 14 is an enlarged cross-sectional view of the main part of FIG.
  • the structure shown in FIGS. 13 and 14 can be applied to the other embodiments shown in FIGS. 1, 8, and 11.
  • FIGS. 1, 8, and 11 Hereinafter, a case where the structure is applied to the cylindrical member 34 of FIG. 10 will be described.
  • the diameter of the outer peripheral side opening 47 of the through hole 46 of the cylindrical member 34 is reduced to an inner diameter slightly smaller than the outer diameter of the fixing member 36.
  • the annular member 37 can be connected to the cylindrical member 34 as in the embodiment shown in FIG. At the time of assembly, it is not necessary to prevent the fixing member 36 from falling off by covering the outer peripheral surface of the cylindrical member 34 with the annular member 37.
  • the fixing member 36 does not fall off to the outer diameter side of the cylindrical member 34 without the annular member 37 in the state where the fixing member 36 is incorporated in the cylindrical member 34. Assembling of the detaching mechanism 33 is facilitated.
  • the large-diameter cylindrical portion 50 or the reduced diameter portion is added to the annular member 37 as in the embodiment of FIG. There is no need to provide the end portion 43) or the hooking portion 35 to the cylindrical member 34. That is, the shapes of the annular member 37 and the cylindrical member 34 can be simplified, and the manufacturing process is simplified.
  • the cylindrical member 34 in the embodiment shown in FIG. 13 can be manufactured by either resin molding or metal machining. However, in consideration of ease of assembly of the fixing member 36, ease of manufacture, and processing cost, the cylindrical member 34 is elastic. A molded product of thermoplastic resin such as nylon having a large size is most preferable.
  • the inner peripheral side opening 48 and the outer peripheral side opening 47 of the through hole 46 of the cylindrical member 34 are reduced in diameter over the entire circumference, but the reduced diameter portion is the inner peripheral side opening.
  • the part 48 and the outer peripheral opening 47 may be formed in a protruding shape by partially reducing the diameter at a plurality of locations along the circumferential direction.
  • the inner diameter of the through hole 46 is set to the outer diameter of the fixing member 36.
  • the fixing member 36 can be prevented from falling out of the through hole 46 by making it slightly smaller and tightening.
  • the O-ring 57 is fitted into the concave groove 56 of the power transmission shaft 25 to prevent leakage of the lubricant sealed inside the joint between the annular member 37 and the power transmission shaft 25. At the same time, a sealing property for preventing foreign matter from entering from the outside of the joint is ensured.
  • the retaining ring 54 is fitted in the concave groove 53 of the power transmission shaft 25, and the transmission side end portion 51 of the annular member 37 is engaged with the retaining ring 54, so that the transmission side of the annular member 37 with respect to the power transmission shaft 25 is engaged. Is restricted from moving in the axial direction.
  • annular groove 66 is formed on the outer peripheral surface of the power transmission shaft 25, and the seal member 67 that contacts the transmission side end 51 of the annular member 37 is provided. It has a structure fitted in the concave groove 66.
  • the seal member 67 is made of rubber or resin, and the axial force acting on the annular member 37 during operation of the constant velocity universal joint is about the reaction force when the boot 28 is deformed. If it is fitted in the groove 66, it will not be pulled out of the groove 66 even if it receives an axial load.
  • the seal member 67 interferes with the transmission-side end portion 51 of the annular member 37 and restricts the axial movement thereof, and the seal lip that contacts the transmission-side end portion 51 of the annular member 37 and performs a sealing function. 69.
  • the seal lip 69 is flexible so as to follow even a slight axial relative movement between the seal member 67 and the annular member 37.
  • the power transmission shaft 25 can be provided with a single concave groove 66 and a seal member 67 to ensure sealing performance and to restrict the axial movement of the annular member 37 relative to the power transmission shaft 25 to the transmission side. .
  • the processing of the concave groove 56 of the power transmission shaft 25 and the retaining ring 54 can be omitted, the processing cost and the number of parts can be easily reduced.
  • the seal member 67 When assembling the constant velocity universal joint and the detaching mechanism 33 to the power transmission shaft 25, the seal member 67 is preliminarily attached to the power transmission shaft 25 and moved closer to the transmission side than the concave groove 66, and the annular member 37. After the assembling is completed, the seal member 67 may be fitted into the concave groove 66.
  • the structure in which the annular member 37 is integrally attached to the small diameter end portion 30 of the boot 28 constituting a part of the seal mechanism 27 by vulcanization bonding is illustrated, but as shown in FIGS.
  • the annular member 37 and the small diameter end portion 30 of the boot 28 may be separated. That is, the seal mechanism 27 of the embodiment shown in FIGS. 16 and 17 has a structure in which the small-diameter end 30 of the boot 28 is fixed to the annular member 37 with the boot clamp 70.
  • the seal lip 69 of the seal member 67 is brought into contact with the small diameter end portion 30 of the boot 28. Further, the contact surface 68 of the seal member 67 is brought into contact with the transmission side end portion 51 of the annular member 37. Thereby, the sealing performance is ensured and the axial movement of the annular member 37 toward the transmission 24 with respect to the power transmission shaft 25 is restricted.
  • an O-ring 71 is used as a seal member.
  • a tapered surface 72 is formed on the transmission-side end portion 51 of the annular member 37, and the O-ring 71 is sandwiched between the tapered surface 72 and the concave groove 66 of the power transmission shaft 25. Accordingly, the O-ring 71 is elastically deformed to ensure sealing performance and to restrict the axial movement of the annular member 37 relative to the power transmission shaft 25 toward the transmission 24.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Motor Power Transmission Devices (AREA)

Abstract

L'invention concerne un joint homocinétique (11), lequel joint comprend un élément de joint externe (12) et un élément de joint interne (13) qui transmet un couple entre l'élément de joint interne (13) et l'élément de joint externe (12) par l'intermédiaire de billes (14) tout en permettant un déplacement angulaire, et dans lequel : un arbre de transmission de puissance (25) est relié à l'élément de joint interne (13) de telle sorte qu'un couple peut être transmis ; et un mécanisme de montage et de démontage (33) pour monter et démonter l'arbre de transmission de puissance (25) vers et à partir de l'élément de joint interne (13) est disposé entre l'élément de joint interne (13) et l'arbre de transmission de puissance (25). Le mécanisme de montage et de démontage (33) comporte : un élément cylindrique (34) s'étendant jusqu'à l'élément de joint interne (13) et adapté sur l'arbre de transmission de puissance (25) ; un élément de fixation (36) reçu à l'intérieur de l'élément cylindrique (34) de façon à être mobile radialement ; et un élément annulaire (37) disposé sur la périphérie externe de l'élément cylindrique (34) de façon à pouvoir se déplacer axialement. L'élément de fixation (36) peut être monté sur l'arbre de transmission de puissance (25) et démonté à partir de ce dernier par déplacement axial de l'élément annulaire (37) afin de déplacer radialement l'élément de fixation (36) à l'intérieur de l'élément cylindrique (34).
PCT/JP2017/014595 2016-04-25 2017-04-07 Joint homocinétique WO2017187947A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP17789234.6A EP3450783B1 (fr) 2016-04-25 2017-04-07 Joint homocinétique
US16/095,450 US11512743B2 (en) 2016-04-25 2017-04-07 Constant velocity universal joint

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2016-086961 2016-04-25
JP2016086961 2016-04-25
JP2016-168141 2016-08-30
JP2016168141 2016-08-30
JP2017-033370 2017-02-24
JP2017033370A JP6879775B2 (ja) 2016-04-25 2017-02-24 等速自在継手

Publications (1)

Publication Number Publication Date
WO2017187947A1 true WO2017187947A1 (fr) 2017-11-02

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PCT/JP2017/014595 WO2017187947A1 (fr) 2016-04-25 2017-04-07 Joint homocinétique

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WO (1) WO2017187947A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59144223U (ja) * 1983-03-17 1984-09-27 日産ディーゼル工業株式会社 回転軸の継手装置
JPS6099387U (ja) * 1984-10-11 1985-07-06 日東工器株式会社 管継手のソケツト
JPS62102027U (fr) * 1985-12-18 1987-06-29
JPH0196515U (fr) * 1983-08-19 1989-06-27
JP2005351348A (ja) * 2004-06-09 2005-12-22 Nitto Kohki Co Ltd プラグ／ソケットアセンブリ
JP2008267517A (ja) * 2007-04-23 2008-11-06 Nippon Steel & Sumikin Metal Products Co Ltd 軸継手着脱機構、及びこれを用いたロール成形機の伝動機構
JP2013194895A (ja) * 2012-03-22 2013-09-30 Hitachi Automotive Systems Kyushu Ltd プロペラシャフト及びこのプロペラシャフトに用いられる等速ジョイント

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59144223U (ja) * 1983-03-17 1984-09-27 日産ディーゼル工業株式会社 回転軸の継手装置
JPH0196515U (fr) * 1983-08-19 1989-06-27
JPS6099387U (ja) * 1984-10-11 1985-07-06 日東工器株式会社 管継手のソケツト
JPS62102027U (fr) * 1985-12-18 1987-06-29
JP2005351348A (ja) * 2004-06-09 2005-12-22 Nitto Kohki Co Ltd プラグ／ソケットアセンブリ
JP2008267517A (ja) * 2007-04-23 2008-11-06 Nippon Steel & Sumikin Metal Products Co Ltd 軸継手着脱機構、及びこれを用いたロール成形機の伝動機構
JP2013194895A (ja) * 2012-03-22 2013-09-30 Hitachi Automotive Systems Kyushu Ltd プロペラシャフト及びこのプロペラシャフトに用いられる等速ジョイント

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3450783A4 *

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