WO1988005504A1 - Coussinet pour roues d'entrainement - Google Patents

Coussinet pour roues d'entrainement Download PDF

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Publication number
WO1988005504A1
WO1988005504A1 PCT/JP1988/000030 JP8800030W WO8805504A1 WO 1988005504 A1 WO1988005504 A1 WO 1988005504A1 JP 8800030 W JP8800030 W JP 8800030W WO 8805504 A1 WO8805504 A1 WO 8805504A1
Authority
WO
WIPO (PCT)
Prior art keywords
wheel
transmission
taper
bushing
screw
Prior art date
Application number
PCT/JP1988/000030
Other languages
English (en)
Japanese (ja)
Inventor
Kenkichi Onogi
Original Assignee
Tokyo Jido Kiko Kabushiki Kaisha
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 JP1987004999U external-priority patent/JPH0638200Y2/ja
Priority claimed from JP1987007048U external-priority patent/JPH0712738Y2/ja
Priority claimed from JP1987037498U external-priority patent/JPH0712739Y2/ja
Priority claimed from JP62336626A external-priority patent/JP2668791B2/ja
Application filed by Tokyo Jido Kiko Kabushiki Kaisha filed Critical Tokyo Jido Kiko Kabushiki Kaisha
Publication of WO1988005504A1 publication Critical patent/WO1988005504A1/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
    • 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
    • F16D1/08—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 with clamping hub; with hub and longitudinal key
    • F16D1/09—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 with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
    • F16D1/093—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 with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using one or more elastic segmented conical rings forming at least one of the conical surfaces, the rings being expanded or contracted to effect clamping
    • F16D1/095—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 with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using one or more elastic segmented conical rings forming at least one of the conical surfaces, the rings being expanded or contracted to effect clamping with clamping effected by ring contraction only
    • F16D1/096—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 with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using one or more elastic segmented conical rings forming at least one of the conical surfaces, the rings being expanded or contracted to effect clamping with clamping effected by ring contraction only the ring or rings being located between the shaft and the hub
    • 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
    • F16D1/076—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 by clamping together two faces perpendicular to the axis of rotation, e.g. with bolted flanges
    • 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
    • F16D1/08—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 with clamping hub; with hub and longitudinal key
    • F16D1/0805—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 with clamping hub; with hub and longitudinal key with radial clamping due to deformation of a resilient body or a body of fluid

Definitions

  • the rotation center of the transmission wheel and the axis of the mounting rotation shaft are coaxially or eccentrically positioned.
  • the method of transmission and the pushing of the transmission vehicle used for this purpose.
  • FIG. 8 shows an installation diagram of a transmission vehicle using the above-mentioned tape-cleaning-type bushing.
  • a transmission wheel 4 is fixed to a shaft 2 via a key 3 and a taper pusher 1.
  • e- pushing 1 has a screw 5 attached to a transmission wheel opening 7 by operating a wrench 9. Pressed in and fixed.
  • the reason that the conventional pushing 1 is provided with a tapered surface la and the transmission wheel 4 is provided with a tapered surface 4a is that the wedge effect of the conical tapered surfaces is used to transmit the transmission wheel 4 to the shaft 2. This is to increase the strength of the fixing (fitting) due to friction. For this reason, the inclination L of the taper surfaces la and 4a is small, and the thickness L of the minimum outer diameter and inner diameter of the taper surface 1a is key. 3 is thin enough to exist.
  • the conventional pushing 1 shown in FIG. 8 when the transmission / removal operation of the bushing 1 is performed with the belt tension acting on the transmission wheel 4, the transmission wheel 4 is sealed to the shaft 2. It is dangerous because it cannot be maintained stably, and it is practically impossible, and conventional pushing cannot be used for the above-mentioned new technologies.
  • the present invention provides a bushing in which both mounting and dazing operations on a transmission vehicle can be performed easily and safely while the transmission vehicle is connected to another transmission means such as a belt.
  • another transmission means such as a belt.
  • the present invention is applied to a transmission wheel configured to be able to slide on a support provided on a rotating shaft, with a wheel having a power transmission portion for connecting to another transmission body.
  • a wheel for sliding the disk wheel so that its center of rotation is coaxial with the axis of the rotating shaft as it is fitted into the insertion opening provided in the disk wheel.
  • a bushing comprising an integral combination of a taper member having a taper portion and a detachable screw member for attaching and detaching the tapered member to and from an insertion port of the disk wheel.
  • the thickness (inclination amount) L of the tapered portion of the tipper member is a dimension required for shifting the connection between the disc wheel and the other transmission body from the hard connection to the soft connection.
  • FIG. 1 shows a pusher according to a first embodiment of the present invention and a transmission vehicle to which the pusher is applied, wherein FIG. 1 (A) is a perspective view of the pusher, and FIG. 1 (B) is a view of the pusher.
  • the cross-sectional view, Figure (C) is a cutaway view of the transmission vehicle, Figure (D) is a plan view of the transmission vehicle, and Figure (E) is the eccentric and coaxial transmission vehicle using the pushing of the present invention.
  • FIG. 3 is a diagram illustrating a positioning method.
  • FIG. 2 shows a pushing according to a second embodiment of the present invention
  • FIGS. (A) and (B) are cross-sectional views of a bushing using a male screw and a female screw, respectively
  • FIG. Fig. 2 shows a cross-sectional view of a transmission vehicle using the pushing shown in Fig. (A).
  • FIG. 3 shows a bushing suitable for a double-shaft support structure according to a third embodiment of the present invention.
  • FIG. 3 (A) is a cross-sectional view of a pushing
  • FIG. 3 (B) and FIG. Fig. 2 is a partial cross-sectional view of the transmission vehicle device to which the bushing is applied.
  • FIG. 4 shows a tapered inner / outer ring bushing according to a fourth embodiment of the present invention.
  • FIG. 4 (b) is a partial sectional view of a transmission wheel provided with the bushing
  • FIG. FIG. 3 is a cross-sectional view of the bushing when it is formed.
  • FIG. 5 shows a pusher according to a fifth embodiment of the present invention.
  • the pusher according to the fifth embodiment shown in FIG. 1 is used to perform not only the function of positioning (centering) the transmission wheel and the rotating shaft but also the power transmission.
  • the transmission vehicle with the function added is also shown.
  • Figure ( ⁇ ) is a cross-sectional view with the pusher assembled, and Figure ( ⁇ ) is a cross-sectional view with the pusher removed.
  • FIG. S shows a bushing according to a sixth embodiment of the present invention, in which FIG. ( ⁇ ) is a cross-sectional view of a bushing of the type screwed to a support as shown by a broken line, and FIG. The top view of a one-piece member is each shown.
  • FIG. 7 shows a bushing having a taper portion and a cylindrical portion in a seventh embodiment of the present invention.
  • FIG. 7 (B) shows an expansion medium pressurized type
  • FIG. 7 (B) shows a spiral taper type
  • FIG. FIGS. (C) and (D) show respective sectional views of the taper pressurization type.
  • FIG. 8 is a partial sectional view illustrating a conventional bushing.
  • the bushing of the present invention and the transmission vehicle that can be driven by the bushing are implemented mainly as a belt vehicle of a belt transmission device.
  • FIG. 1 (a) and 1 (b) are perspective and sectional views of a transmission wheel ffi bushing according to a first embodiment of the present invention.
  • Reference numeral 1 denotes a pushing according to the present invention, which comprises a tapered member or a wedge member 14 and a detachable screw 17 which is removably mounted thereto. It is configured as a body assembly.
  • the tapered member or wedge member 14 has a tapered part or wedge part 14 a and a locking support part 14 d formed with a through-hole 14 b for rotatably receiving the screw 17.
  • this embodiment also has a shaft insertion opening 14c for receiving a rotating shaft 11 (see FIG. 1 (C)) described later.
  • This click finely portion 14a bottom surface 14e of the opening end or approach end thickness side L 2 of is made form.
  • the radial length (inclination amount) L of the wedge portion 14a is long enough to move the transmission wheel 10 [see FIG. 1 (E)] which is subjected to the biasing force as described later. Stipulated.
  • the attachment / detachment screw 17 has a bolt shape, and is a first locking portion for combining a screw portion 17a for coupling with the shaft 1] and a locking portion 14d of the taper member 14. 19, a second locking portion 18, and an intermediate portion 17d.
  • the locking portion 19 is formed of a rotatable nut, is screwed to the screw 17b above the screw 17 and is welded at the welded portion 17e, whereby the screw is screwed.
  • the tool 17 is combined with the wedge member 14 so as not to come out of the wedge member 14 so that the tool 17 can be pressed and rotated.
  • the first locking portion 19 abuts on the upper surface of the locking support portion 14d of the bushing 14 via a bushing to form a push-in locking portion when the screw portion 17a is inserted into the shaft. I do.
  • the second locking portion 18 locks and presses the inner wall of the holding portion 14d, and the locking portion for removing the entire pushing 14 from the disc wheel 15 is formed.
  • the intermediate portion 17d of the first and second locking portions 18 and 19 is rotatably fitted.
  • the rotary shaft 11 or the rotary shaft equivalent 11 is inserted into the inlet 14c [see FIG. 4 (A). Is inserted, two types of slits are used to improve the coaxial (centering) accuracy between the rotation center C of the disk wheel 15 and the rotation axis ⁇ . Is applied to the bushing, ie.
  • the wedge member 14 is provided with a different slit 14f from the outer wall (taper portion) 14a to the through hole 14b, and the slit 14 ⁇ reduces the outer circumference of the member 14 by the thickness thereof. You can do it.
  • the other slit 14g is a bending slit provided at equal intervals in the circumferential direction so that the member 14 can be bent in the circumferential direction. Three tribute holes 14h penetrating in the direction are connected to each other. If the centering accuracy may be low, the slits 14i and 14g and the prize hole 14h are unnecessary.
  • FIGS. 1 (C) and 1 (D) show a transmission vehicle coaxially or centered on a rotating shaft 11 using the bushing 1 of the first embodiment shown in FIGS. 1 (A) and 1 (B).
  • FIG. 10 is a sectional view and a plan view showing 10;
  • a support 13 is installed on the rotating shaft 11 via a key 12.
  • the support 13 may be integrally formed with the rotating shaft 11.
  • the support base 13 is provided with a screw 6a at a position distant from the rotation axis, and the upper part is formed as a plane 13b.
  • the coaxial holding bushing 1 according to the present invention comprises a tapered member 13 ⁇ 4 and a detachable screw 17.
  • Reference numeral 15 denotes a disk wheel or a rotating wheel, which is formed by three portions, namely, a belt groove portion 15a, a flat surface portion 15b, and a pushing receiving portion 15c, and a groove portion 15a has an engagement groove for a V-belt.
  • the flat portion 15b has a plurality of elongated holes 15e oriented in the same direction as each other, and the boxing receiving portion 15c has a conical opening 15 ⁇ coaxial with the rotary shaft 11.
  • a bolt 16 for fixing the disk wheel 15 between the screw hole 13a of the support base 13 is installed.
  • FIG. 2 shows a state where the rotary shaft 11 is coaxially arranged on the support base 13.
  • FIG. 1 (D) shows the arrangement of four bolts ⁇ 6a and ⁇ 6b.
  • the pressing 1 has a coaxial holding function so that the center axis of the disk wheel 15 always coincides with the axis of the rotating shaft 11. It does not function as a clamp for fixing to the surface.
  • the clamp function is achieved by the four bolts 16a and 16b being connected to the support 13 and the support 13 being connected to the rotating shaft 11 via the key 12.
  • FIG. 1 (E) shows a coaxial or non-coaxial cable for exchanging a belt transmission of a pulley transmission vehicle using the bushing 1 of the present invention shown in FIGS. 1 (B) and 1 (B).
  • FIG. 4 is an explanatory diagram showing an eccentric positioning method.
  • Fig. 1 (E) (E-1) shows the movement of bushing 1 to release the pressurized state from belt 20 to disc wheel 15. ing .
  • Fig. 1 (E) and (E-2) show the release of the rebel by removing the pushing 1.
  • the input / output shafts 11 and 22 are fixed to each other while the shafts are fixed, and the belt is wound around the input / output shafts 11 and 22.
  • the transmission wheel is eccentric with the rotating shaft while keeping the vehicle 15 stable without falling off; the belt can be replaced and then the transmission wheel can be positioned coaxially again.
  • connection between the belts and the belt for transmitting the main power is defined as a hard connection and the other connections are defined as a soft connection
  • the length of the tapered portion 14a of the bushing 1 By the movement corresponding to L, the connection between the disk wheel 15 and the belt 20 shifts from the hard connection to the soft connection. In this state, the bushing 1 can be easily removed since the external pressure is already acting on the bushing 1. Then, as shown in FIGS.
  • the disk wheel 15 can be moved at least by an amount corresponding to the thickness L z of the bushing 1 and the belt Since a gap 20 having a length is formed between the disc 20 and the outer periphery of the disc wheel 15, the disc wheel 15 or the belt 20 can be easily replaced using the gap.
  • FIG. 2 (C) is a cross-sectional view of a transmission car using the screwed pusher shown in Fig. (A).
  • the bushing 1 in FIG. 2 (A) also comprises a wedge member or a tapered member 14 (thickness and a detachable screw member ⁇ (length or more) rotatably combined with the wedge member or the tapered member 14.
  • the difference from the first embodiment is that the shaft insertion opening 14c does not exist, and the rotating shaft 11 or the equivalent shaft 1 does not have the function of the insertion guide. It also has the function of the guide body.
  • the bushing 1 in FIG. 2 (B) is an example in which a detachable screw 17 provided with a female screw 17a 'is combined with the wedge member 14, and in this case, a guide shaft such as the rotating shaft 11. Applicable when a thread groove is provided directly on
  • Fig. 2 (C) is an example in which a plurality of pushers 1 are not located coaxially with the shaft 11 but are installed radially around it. In this case, the wheel 15 should be removed with all pushers 1 removed.
  • the amount of movement L 2 is regulated by the periphery 13c of FIG shown in ⁇ rather support 13.
  • FIG. 3 (A), 3 (B) and 3 (C) show the pushing of the third embodiment of the present invention
  • FIG. 3 (A) is a sectional view of the pushing
  • FIGS. Part C) shows a partial cross-sectional view and a plan view of a speed reducer that supports the transmission vehicle using the same bushing on the rain shaft.
  • This embodiment is different from the first embodiment in that the bearing 8 is fitted around the outer periphery of the support portion of the wedge member 14 and the transmission wheel is supported on both shafts.
  • Shi outer diameter r 2 of the bearing 8a in Nodea Ru here was also improved power sale by Ru can apply in g, the maximum diameter r 3 good Ri also rather large structure of Te Ichipa member 14 Has been established.
  • the first locking member 19 and the screw 17 are fixed by passing the roll pin 22 through the cutout hole 21.
  • the housing 30 is of a semi-closed type because the belt can be replaced while keeping the distance between the input and output shafts fixed.
  • the maintenance opening 34 is closed by a lid 31 having an opening 33.
  • Transmission wheel 10 a bearing positioned in a direction to release the rotation shaft 11 and extended engagement supporting portion 14d and the two bearings 8a and in particular the wedge member 14 sigma is supported rain shaft by 8b from the pulley disc 15 8a is supported by a shaft support device 50, which includes three support arms 51, a cylinder portion 56 having an opening 53 and a taper 56a as shown in FIG. 3 (C). Further, it is formed by the bolt 55 and the seat 54, and the whole is integrally formed with the housing 30.
  • a guide port 16b for guiding the horizontal movement of the rotary wheel 15 is provided between the slot 15e of the rotary wheel 15 and the screw 6 13a of the support 13 as shown in FIG.
  • Four fixed bolts ⁇ 6a are provided to fix the pulley disk wheel 15 to the support base 13 separately.-
  • the maintenance lid 31 is opened, and First, as shown in Fig. 3 (C), turn the pulley disc wheel 15 so that the direction of the long hole 15e faces the direction of the mating shaft as shown by the arrow A. Second, remove the four fixed bolts 16a.
  • FIGS. 4 (A) and 4 (B) show a transmission vehicle bushing of still another embodiment of the present invention.
  • the same reference numerals as in the first embodiment denote the same or corresponding parts as in the first embodiment.
  • FIG. 4 (A) The difference between the embodiment of FIG. 4 (A) and the first embodiment is that a tapered ring 14k provided with a slit 14J2 is interposed between the disk wheel 15 and the bushing 1. And that the guide shaft 1 ⁇ is formed so as to protrude coaxially with the rotation shaft 11 from the support base 13. Since the shaft 1 has substantially the same function as the rotating shaft 11, it is referred to as a rotating shaft here. According to this embodiment, since the possible and removable also Li in g 14k and both pushing 1 the thickness L 3, the displacement amount is eccentric by pair disc wheel 15 to the rotation axis 0 L . This has the advantage that it can be greatly increased.
  • the power transmission between the transmission wheel 15 and the rotating shaft 11 is performed via the bolt 16a, and the pusher 1 and the ring 14k are provided with a positioning function and a disc-shaped cover. It has only sliding function. Therefore, also in this case, the car 15 and the shaft 11 are soft-coupled.
  • FIG. 4 (B) is essentially the same as FIG. 4 (A), and is formed by an inner ring 14 of an outer taper and an outer ring 14k of an inner taper.
  • the inner and outer rings 14, 14k may be integrated as shown in Fig. 4 (B).
  • Warped Thin grayed first member 14 is moved, the transmission wheel 15 with for eccentrically Tsu by the belts tension, flop Tsu sheet in g 1 at the locking end 14m in displacement of the length L 4 are
  • the outer ring 4k engages and can be attached and detached integrally.
  • bolts 16 are shown, and if the plurality of bolts 16 are interposed between the inner and outer rings, the disc wheel 15 is hard-coupled to the shaft 11 via the bushing '1 to enable power transmission. .
  • FIG. 5 differs from that of FIG. 1 in that firstly, a fastening screw 16a 'for fastening or removing between the pushing 1 and the rotary wheel 15 is provided. Second, a length P between the first and second locking means 19 and 18. This is the point that a dead zone is provided. Further, in this embodiment, in order to prevent the rotary wheel 15 as a timing pulley from separating and falling off the shaft 11, four falling-off preventing means are provided. That is, on the back surface of the disk wheel 15, a locking body 41 also serving as a belt locking member is attached so that the rain surface of the peripheral portion 13 d of the support 13 is sandwiched between the wheel and the wheel 15. Can be
  • Pushing 1 by press-fitting is slightly reduced dead area P Q, finally again clamped work screw member 17 is completed.
  • Pushing 1 can be removed in the reverse order.
  • a key 12 ' may be interposed between them.
  • the belt 20 wound in this manner as shown in the same figure) separates from the groove 15a, so that a gap L is formed between the belt and the locking member 15g or 41. If it is removed in the direction of arrow B, it will be easy to replace Zhang Dy and other connected parts such as levers.
  • the falling-off prevention means 40 may be another type.
  • FIG. 6 (A) is a partial modification of the bushing 1 shown in FIGS. 5 (A) and 5 (B).
  • the pushing 1 instead, it is screwed and fixed to the support 13 through the screw hole 14i and the through hole 14h by the fastening screw 16a.
  • the shape of the tapered member 14 is almost the same as that of the first embodiment shown in FIG. 1 (A).
  • the function is the same as in the fifth embodiment.
  • a groove 14 ⁇ for the key 12 ′ may be provided as shown by a broken line in FIG.
  • FIGS. 7 ( ⁇ ) and ( ⁇ ) are cross-sectional views of a bushing according to another embodiment of the present invention in a loaded state.
  • the expansion medium 36 sealed in the pushing 1 is pressurized and expanded by winding up the press-fit screw 16a to enlarge the thickness L s of the cylindrical portion 14 ⁇ , thereby forming the disc wheel 15 It is to be crimped to the shaft 11.
  • the dead area Pu is unnecessary.
  • the taper member 14 is provided with only the tipper portion 14a at the tip, and after centering at the tapered portion 14a, the shaft of the transmission wheel 15 is actually supported by this taper. This is performed in a flexi-n due to the expansion of the cylindrical portion 14 ⁇ that is connected to the lip portion 14a.
  • FIG. 7 ( ⁇ ) is almost the same as the embodiment of FIG. 7 ( ⁇ ), except that the shaft support is expanded. Regardless by Zhang medium, Te Ichipa portions 14q and 14r made from Oneji shaped and female screw shape decorated with the inner ring 14 0 and the outer exports 14P 2 Tsunote - by changing the radius by the force tl pressure between path member The centering and flexion support of the disk car 15 is performed.
  • This operation principle of Sri Tsu inner and outer races 14 bets are facilities 0, 14P is substantially equivalent to the action of the inner ring 14 and outer ring 14k embodiment of FIG. 4 (B), intermediate cylindrical portion 14 ⁇ is facilities Therefore, the actual treatment is completely the same as that in Fig. 7 ( ⁇ ).
  • the pusher 1 having the tapered portion 14a and the cylindrical portion 14 ⁇ adjacent to each other as in this embodiment is extremely effective for a transmission vehicle in which the rate at which a large belt tension is applied is small, such as a timing pulley. .
  • the press-fit screw 16a is also used as the detachable screw 17 and only a single screw means is used. It is also possible to attach / detach and press-fit.
  • FIGS. 7 (C) and 7 (D) depict left side sectional views of still another embodiment bushing.
  • the function of Pushing 1 is exactly the same as in FIGS. 7 (A) and (B).
  • Fig. 7 (B) there are many fine taper parts 14g and 14r
  • Fig. 7 (C) inner rings 14u, 14v having a slit by two opposing wedges 14s, 14t. ⁇ Of the inner and outer rings is expanded, and the shaft is supported by frictional force.
  • -Fig. 7 (D) is an example where there is only one tapered portion 14q, 14r. The operation of this embodiment is the same as that of FIG. 7 (B).
  • the pushing of the transmission wheel has been manufactured on the principle that once the rotating wheel is firmly supported on the rotating shaft, the attaching and detaching operations are not performed frequently in principle. Singing is not only suitable for frequent maintenance such as belt replacement, but is also suitable for repeated attachment / detachment operations.In addition, the acting force of the belt etc. is applied to the transmission vehicle. Since the pusher can be attached and detached as it is, a new industrial innovation can be expected if the concept of the present invention is applied to the field of belt transmissions.
  • a tape publishing is used in order to obtain a power coupling function or a hard coupling between the transmission wheel and the rotating shaft, but in the present invention, the power coupling is used. It is not necessary to have the aggressive function positively.Rather, to obtain a centering function between the transmission vehicle and the rotating shaft, it is necessary to softly couple at least the rainy people. This is intended to be used in some cases, and in some cases, a hard bond is further added.
  • the center of rotation of the transmission wheel and the axis of the rotating shaft maintain the coaxial state during normal operation only by attaching and detaching the pushing from the circular wheel, and the belt There is a method of positioning so that it will be eccentric when replacing You get it.
  • the bushing of the transmission wheel according to the present invention has mainly been described with reference to the transmission wheel for rotational power by Belt Zhangdi.
  • the bushing is not limited to the belt and chinin and other gears.
  • the present invention can be effectively applied to a case in which a roller, an idler wheel, and a friction-transmitting disk wheel are in pressure contact with another transmitting body.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Pulleys (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

Un coussinet (1) est utilisé avec une roue d'entraînement (10) ayant un disque (15) susceptible de glisser entre une position excentrique et une position coaxiale sur un support (13) monté sur un arbre rotatif (11). Le coussinet comprend un élément conique (14) ayant une partie conique ou en coin (14a) qui s'adapte dans le disque (15) et un élément à vis (17) de montage et de démontage de l'élément conique qui forme une seule pièce avec celui-ci, de sorte que l'élément à vis peut être mis en rotation indépendamment de l'élément conique, montant et démontant l'élément conique contre la force excentrique du disque. L'épaisseur (degré d'inclinaison) L1 de l'élément conique est fixée à un niveau approprié permettant de connecter de façon plus ou moins serrée la roue d'entraînement (10) avec un autre organe d'entraînement, tel qu'une courroie. L'invention concerne également un procédé de placement de l'axe (C) de rotation du disque dans une position coaxiale ou excentrique par rapport à l'axe (O) de l'arbre rotatif en montant le coussinet (1) sur le disque (15) ou en enlevant le coussinet (1) du disque (15).
PCT/JP1988/000030 1987-01-16 1988-01-16 Coussinet pour roues d'entrainement WO1988005504A1 (fr)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP1987004999U JPH0638200Y2 (ja) 1987-01-16 1987-01-16 プ−リの軸芯調整装置
JP62/004999U 1987-01-16
JP1987007048U JPH0712738Y2 (ja) 1987-01-21 1987-01-21 同軸保持ブッシュ
JP62/007048U 1987-01-21
JP62/037498U 1987-03-15
JP1987037498U JPH0712739Y2 (ja) 1987-03-15 1987-03-15 被軸支体取付装置
JP62/336626 1987-12-29
JP62336626A JP2668791B2 (ja) 1987-12-29 1987-12-29 伝達車のブッシング

Publications (1)

Publication Number Publication Date
WO1988005504A1 true WO1988005504A1 (fr) 1988-07-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1988/000030 WO1988005504A1 (fr) 1987-01-16 1988-01-16 Coussinet pour roues d'entrainement

Country Status (1)

Country Link
WO (1) WO1988005504A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2647516A1 (fr) * 1989-05-24 1990-11-30 Peugeot Dispositif d'accouplement entre un arbre a cames et son pignon de commande
CN101865215A (zh) * 2010-07-14 2010-10-20 哈尔滨工业大学 一种高精度的同轴联接机构

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4862479U (fr) * 1971-11-19 1973-08-08
JPS50106064A (fr) * 1974-01-28 1975-08-21
JPS5131972Y2 (fr) * 1972-03-21 1976-08-10
JPS5246176U (fr) * 1975-09-27 1977-04-01
JPS52124375U (fr) * 1976-03-17 1977-09-21
JPS58109721A (ja) * 1981-12-09 1983-06-30 フルト・フエルヴアルツングス−ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング 軸・ボス用の摩擦継手
JPS5915814U (ja) * 1982-07-23 1984-01-31 磯川産業株式会社 揺動板付ねじ
JPS60152834U (ja) * 1984-03-23 1985-10-11 株式会社日立製作所 トルク伝達機構
JPS6126672Y2 (fr) * 1982-10-15 1986-08-09

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4862479U (fr) * 1971-11-19 1973-08-08
JPS5131972Y2 (fr) * 1972-03-21 1976-08-10
JPS50106064A (fr) * 1974-01-28 1975-08-21
JPS5246176U (fr) * 1975-09-27 1977-04-01
JPS52124375U (fr) * 1976-03-17 1977-09-21
JPS58109721A (ja) * 1981-12-09 1983-06-30 フルト・フエルヴアルツングス−ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング 軸・ボス用の摩擦継手
JPS5915814U (ja) * 1982-07-23 1984-01-31 磯川産業株式会社 揺動板付ねじ
JPS6126672Y2 (fr) * 1982-10-15 1986-08-09
JPS60152834U (ja) * 1984-03-23 1985-10-11 株式会社日立製作所 トルク伝達機構

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2647516A1 (fr) * 1989-05-24 1990-11-30 Peugeot Dispositif d'accouplement entre un arbre a cames et son pignon de commande
CN101865215A (zh) * 2010-07-14 2010-10-20 哈尔滨工业大学 一种高精度的同轴联接机构

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