JP2015165142A - Disc type shaft coupling and disc unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disc type shaft coupling capable of preventing abrasion and sectional defects caused by rubbing of discs against each other even upon repetitive bending deformation resulting from misalignment, preventing reduction in strength against torsional torque, ensuring high tolerance for misalignment and having excellent in durability, and to provide a disc unit used in the shaft coupling.SOLUTION: A disc unit comprises: a plurality of discs 10 (10A, 10B, 10C, and 10D) each of which is an annular polygonal element formed by connecting a plurality of linear side members on both end portions and is formed of fiber-reinforced plastic; and fixture members 12 arranged to hold corners of the discs 10 as connecting parts of the respective side members of the discs 10 therebetween while stacking the plurality of discs 10. Film abrasion prevention members 30 (30A, 30B, and 30C) are arranged between the stacked discs 10 to be located in a fixed part region pressed by the fixture members 12 and fixed part peripheral regions outward of the fixed part regions.

Description

  The present invention generally relates to a shaft coupling that connects rotating shafts in general rotary machines, wind power generation, and the like, and in particular, a disk-type shaft coupling that uses a flexible plate (disk) as a rotational torque transmission member, and the like. The present invention relates to a disk unit used for a shaft coupling.

  Conventionally, for example, in general rotary machines, wind power generation, etc., as a shaft coupling (coupling) that connects rotating shafts and transmits torque while absorbing misalignment between the shafts, it is mainly maintenance-free and rigid. From the point of view, a plate-type shaft coupling using a leaf spring, that is, a flexible plate (disc), is widely used.

  As a disk material of this disk type shaft coupling, stainless steel is generally used, and an allowable misalignment amount is about 1 ° in declination. However, it may be required to allow a larger misalignment of, for example, a deviation angle of about 3 ° for use in a place where the centering operation is difficult or a place where vibration is intense.

  In order to increase the allowable misalignment while ensuring the strength against the disc, the material used requires high physical properties such as high strength and low bending rigidity. However, as a material that satisfies this characteristic, fiber reinforced plastic ( FRP).

Therefore, a shaft coupling has been devised that uses a fiber reinforced plastic that is softer and stronger than stainless steel.
(1) A structure in which the outer shape is a polygon and a hole such as a polygon or a circle is formed in the inside (see Patent Document 1),
(2) A structure in which strip-shaped link members are combined (see Patent Document 2),
There are two types of discs. Note that Patent Document 1 also describes a structure in which strip-shaped link members are combined and combined together.

  In either case, the thickness of the disc and the direction of the reinforcing fiber are determined by appropriate design for the amount of deflection of the disc as a leaf spring due to misalignment of the shaft and the stress applied to the disc by the rotational torque. When the misalignment to be performed is large, a plurality of thin disks are used in a stacked manner, and the durability as a disk unit is improved by reducing the distortion generated in each disk.

  Each side of the polygonal disk incorporated as a disk unit is individually deformed as a leaf spring when misalignment occurs, and for torque load from the shaft, one is a tension member and the other is a compression member And the function of transmitting torque from one input shaft to the other output shaft. When the load torque is increased, the compression side will eventually buckle and the disk unit Loses its torque transmission ability.

  In general, when multiple discs are used in combination, a hole is made in the fixed part set at the corner of the polygonal disc (both ends in the case of a strip-shaped link member), and a rigid bolt and fixing member Then, each leaf spring member is fastened and fixed to form a disk unit, which is assembled into the shaft coupling.

  Cited Document 3 describes a disc type shaft joint having a disc unit using fiber reinforced plastic (FRP) as a disc, which is configured as described above. As can be understood with reference to FIGS. 25 and 26 attached to the present application, the disk unit 20 of the disk type shaft coupling 100 connects a plurality of linear side members 10a, 10b, 10c, and 10d to each other at both ends thereof. The disk 10 made of fiber reinforced plastic, which is an annular polygonal body, and the corners 10s, 10t, 10u, 10v of the disk 10 which is a connecting part of the side members 10a, 10b, 10c, 10d are sandwiched and arranged. Fixed plate 12. The disc-type shaft coupling 100 described in the cited document 3 including the disc unit 20 having such a configuration suppresses the occurrence of cracks and peeling on the disc 10 even when subjected to repeated bending deformation due to misalignment, and causes a decrease in strength. It is described that the tolerance of misalignment is large and the durability is excellent.

Japanese Patent No. 3275289 JP 2006-250034 A JP 2013-241980 A

  However, according to the results of experimental studies by the present inventors, in the disc type shaft coupling 100 including the disc unit 20 having the configuration described in the cited document 3, a plurality of pieces made of fiber reinforced plastic as the disc 10 are used. When the discs 10A, 10B, 10C, and 10D are used in an overlapped manner, if bending deformation due to misalignment is applied to the disc unit 20, a fixing portion region (hatched portion region FA shown in FIG. 26) by the bolt 121 and the nut 131 is applied. The discs in the area immediately below and / or around the fixed part (the outer area ΔFA from the shaded area FA shown in FIG. 26) rub against each other, and a phenomenon similar to the so-called fretting phenomenon occurs in the metal material, It was found that the stacked disk surface was worn.

  As a result of further research and experiments, when the wear of the disks progresses as a result of repeated use, the bending rigidity of each side 10a to 10d decreases, and as a result, the breaking torque when the torsional torque is applied to the disk unit 20 It was confirmed that it also decreased. The rubbing mechanism of each disk will be described in detail later.

  As a result of further research and experiments in order to solve such a problem of rubbing, the present inventors have found that a disk is formed by interposing an anti-wear member such as a resin film between the disks to be overlapped. It has been found that wear due to mutual rubbing can be prevented, and the bending rigidity and the torsional breaking torque of the disk unit 20 can be prevented from decreasing.

  This invention is made | formed based on the said novel knowledge by the present inventors.

  The object of the present invention is to prevent wear and cross-sectional defects due to friction between discs even when subjected to repeated bending deformation due to misalignment, to prevent a decrease in strength against torsional torque, and to have good fatigue strength. A disc type shaft joint having a large allowable value and excellent in durability and a disc unit used for such a shaft joint are provided.

The above object is achieved by a disk type shaft coupling and a disk unit according to the present invention. In summary, according to the first aspect of the present invention, there is provided a disk unit that transmits rotational torque between a drive shaft and a driven shaft in a disk-type shaft coupling,
A plurality of discs made of fiber-reinforced plastic plates;
A fixing member disposed in a fixing portion of the disk to overlap and sandwich the plurality of disks integrally;
In a disk unit with
A film having a thickness of 10 to 200 μm located between the stacked discs and at least in a fixed portion region pressed by the fixing member and a fixed portion peripheral region outside the fixed portion region There is provided a disk unit characterized by disposing an anti-wear member in the shape of a disk.

  In the first aspect of the present invention, according to one embodiment, the disk is a holeless polygonal body or an annular polygonal body integrally formed with a plurality of side members, and the fixing portion is the polygon. It is formed at the corner of the feature. According to another embodiment, the disc is formed into an annular polygonal body integrally formed by a plurality of side members by integrally combining strip-shaped link members, and the fixing portion is the side members. It is formed in the connection part.

According to a second aspect of the present invention, there is provided a disk unit that performs rotational torque transmission between a drive shaft and a driven shaft in a disk-type shaft coupling,
A plurality of side members made of fiber-reinforced plastic plates connected to each other at both ends thereof to form an annular polygonal body; and
In a disk unit comprising: a fixing member disposed so as to sandwich the fixing part of the disk, which is a connection part of each side member of the disk,
A thickness of 10 to 200 μm located between adjacent side members of the disk and at least in a fixing portion region pressed by the fixing member and a fixing portion peripheral region outside the fixing portion region. There is provided a disk unit characterized in that a film-shaped wear preventing member is arranged.

  In the first and second aspects of the present invention, according to the first embodiment, the wear preventing member is a resin film or a metal film.

  According to another embodiment of each of the above inventions, the wear preventing member has the same shape as the disk, or an elongated band having a predetermined width extending between the fixed part of the disk. It is made into the shape, or it is made circular shape or polygonal shape made larger than the fixed part area | region pressed by the said fixing member.

  According to another embodiment of the present invention, the fixing member has a circular shape or a polygonal shape.

  According to another embodiment of the present invention, the fixing member is a metal material such as a steel material or an aluminum material, a resin plate, a fiber reinforced plastic material, or a ceramic material.

According to another embodiment of each of the present invention described above, the reinforcing fiber of the fiber-reinforced plastic is an inorganic fiber such as carbon fiber, glass fiber, or basalt fiber; metal fiber such as boron fiber, titanium fiber, or steel fiber; , Organic fibers such as PBO (polyparaphenylene benzbisoxazole), polyamide, polyarylate, and polyester; are used alone or in a hybrid mixed with multiple types,
Examples of the resin of the fiber reinforced plastic include a thermosetting resin such as a room temperature curing type or thermosetting type epoxy resin, vinyl ester resin, MMA resin, acrylic resin, unsaturated polyester resin, or phenol resin; or polyamide A thermoplastic resin such as a resin, a polycarbonate resin, a polyether ether ketone resin, or a polyphenylene sulfide resin is used.

According to the third aspect of the present invention, rotational torque transmission between the first hub attached to the drive shaft and the second hub attached to the driven shaft is performed between the drive shaft and the driven shaft. In a disc-type shaft coupling with a disc unit that performs
A disc type shaft coupling is provided, wherein the disc unit is a disc unit having any one of the configurations described above.

  According to the present invention, even when subjected to repeated bending deformation due to misalignment, there is no wear or cross-sectional defect due to friction between the disks. Therefore, it is possible to prevent a decrease in strength against torsional torque, to have good fatigue strength, a large misalignment tolerance, and excellent durability.

FIG. 1A is an exploded perspective view showing an embodiment of a disc type shaft coupling and disc unit according to the present invention, and FIG. 1B is an assembled perspective view. FIG. 2A is a diagram showing an example of the positional relationship between the disk and the fixing member, and FIG. 2B is a partially enlarged view showing the positional relationship between the disk and the fixing member. ) Is a diagram showing another embodiment of the positional relationship between the disk and the fixing member. FIG. 3A is a cross-sectional view for explaining an embodiment of a manner of fixing a disc unit including a disc and a fixing member to a shaft joint, and FIG. 3B is a perspective view of the fixing member. FIG. 4A is a cross-sectional view for explaining another embodiment of the manner of fixing the disk unit including the disk and the fixing member to the shaft coupling, and FIG. 4B is a perspective view of the fixing member. . FIG. 5A is a perspective view for explaining an embodiment of a fiber sheet, and FIG. 5B is a perspective view for explaining a prepreg sheet. It is a figure explaining one Example of the method of producing a disk. It is a figure explaining the side member in a disc, and the orientation direction of a reinforced fiber. FIG. 8A is a view showing one embodiment of the wear preventing member, and FIGS. 8B and 8C are views showing another embodiment of the wear preventing member. It is a schematic structure sectional view showing other examples of a disc type shaft coupling concerning the present invention. It is a schematic block diagram of the rotation bending fatigue testing machine of a disk test piece. It is a schematic block diagram of the torque holding type rotary bending tester of a disk test piece. FIG. 12A shows a schematic configuration of a testing machine for grasping a change in bending rigidity of a disk test piece. FIG. 12B is a view of the testing machine as viewed from above, and FIG. 12C is a view for explaining how to attach the disk unit having the disk test piece to the lower jig. FIG. 13A is a plan view showing a schematic configuration of a disk test piece destructive testing machine, and FIG. 13B is a front view. FIG. 14A is a photograph showing a deformed state when a load is applied to the disk test piece, and FIG. 14B is a photograph showing a broken state of the disk test piece. It is a graph which shows the change of the residual fracture torque with respect to the frequency | count of repeated rotation bending of a disk test piece. It is a graph which shows the change of the bending rigidity with respect to the frequency | count of repeated rotation bending of a disk test piece. 17 (a), 17 (b), and 17 (c) are diagrams for explaining a damaged portion of the disk test piece, FIG. 17 (a) is a perspective view of four disk test pieces, and FIG. ) Is a front view of a disk unit constituted by fixing a disk test piece integrally with a fixing member, and FIG. 17C is a perspective view showing four disk test pieces separated from each other. FIGS. 18A and 18B are photographs showing the internal state of the disk test piece after the fatigue test according to the conventional configuration. FIGS. 19A and 19B are photographs showing the internal state of the disk test piece after the fatigue test according to the configuration according to the present invention. 20 (a1) and (a2) are photographs showing the surface condition of the disk specimen before the fatigue test, and FIGS. 20 (b1) and (b2) show the surface condition of the disk specimen after the fatigue test according to the conventional configuration. It is a photograph shown. FIGS. 21 (a1) and (a2) are photographs showing the surface condition of a disk test piece after a fatigue test according to the configuration of the present invention. It is a figure explaining the mode of a deformation | transformation of the disk at the time of giving a declination to a coupling. FIGS. 23A, 23B, and 23C are diagrams showing another embodiment of a disk and a disk unit that can be used in the present invention. FIGS. 24A, 24B, and 24C are diagrams showing another embodiment of a disk and a disk unit that can be used in the present invention. FIG. 25A is an exploded perspective view showing an example of a conventional disk type shaft coupling and a disk unit, and FIG. 25B is an assembled perspective view. FIG. 26A is a diagram showing an example of the relationship between the disc and the fixing member in the conventional disc unit, and FIG. 26B is a partially enlarged view showing the arrangement relationship between the disc and the fixing member.

  Hereinafter, the disc-type shaft coupling and disc unit according to the present invention will be described in more detail with reference to the drawings.

Example 1
1 (a) and 1 (b) show an embodiment of a disc type shaft coupling 100 according to the present invention. Referring to FIGS. 1A and 1B, in this embodiment, the shaft coupling 100 is provided with a first hub 101 to which an input shaft (drive shaft) 201 is attached and an output shaft (driven shaft) 202. The second hub 102 is disposed opposite to the second hub 102. A disk unit 20 is disposed between the first hub 101 and the second hub 102. The disk unit 20 includes a flexible plate (plate spring), that is, a disk 10 as a rotational torque transmission member, and a fixing member 12 for clamping the disk 10 when the disk 10 is fixed to the hubs 101 and 102 with bolts and nuts. have. In the present embodiment, the shaft coupling 100 is a single-type shaft coupling including one set of the disk units 20, but is not limited thereto. In the present invention, for example, as shown in FIG. 9, two sets (20A, 20B) of disk units 20 are provided, and the respective disk units 20A, 20B are fixed to the first hubs 101, 102 and the spacer (intermediate body) 200. Various types of shaft couplings known to those skilled in the art, such as a spacer-type shaft coupling having the above-described structure, can be realized.

  In the present invention, the disk 10 may have an arbitrary shape, but is usually a polygonal body having a triangular shape or more, and in the present embodiment, is a circular rectangular body. In the present specification and claims, a polygonal body in which the outer shape is rectangular and a rectangular hole is similarly formed inside is referred to as an “annular polygon”. That is, in this embodiment, as understood with reference also to FIG. 2, the outer shape of the disk 10 is rectangular (square), and a rectangular (square) hole is similarly formed inside. It is supposed to be configured. That is, the disk 10 has an annular rectangular shape in which four side members 10a, 10b, 10c, and 10d each having a substantially rectangular shape having a width W and a length L are connected to each other at 90 ° to each other. It is assumed to be a body. Further, in the present embodiment, each corner of the square body has a curved shape of R1.

  The disk 10 is formed of a thin plate (that is, a flexible plate) having a thickness (T0) (usually about T0 = 0.1 to 5 mm) made of fiber reinforced plastic molded into an annular square. As shown in FIG. 1, a plurality of, for example, four disks 10 (10A, 10B, 10C, 10D) in this embodiment are formed by a laminated body. At this time, the respective disks 10 (10A, 10B, 10C, 10D) are not bonded and are simply overlapped and stacked. Further, according to the present invention, the film-like wear preventing member 30 (30A, 30B, 30C) is disposed between the adjacent disks that are stacked. The wear preventing member 30 will be described in detail later.

  According to the present embodiment, as shown in FIGS. 2A and 2B, the four corners 10s, 10t, 10u, and 10v of the disk 10 forming the annular square body are connected to the four disks 10 by bolts 121. , A fixing portion for attaching to the first hub 101 and the second hub 102 by a nut 131, and a fixing portion region (a hatched portion shown in FIG. 2B) that is sandwiched and pressed by the fixing member 12 Area FA) is set. The corner portions 10s, 10t, 10u, and 10v in which the fixed portion area FA is set have mounting holes 13 to the first hub 101 that are positioned substantially at the center and are paired on the diagonal line of the annular rectangular disk. And the attachment hole 14 to the 2nd hub 102 is formed.

  Here, the first hub 101 and the second hub 102 will be described. The first and second hubs 101 and 102 are not limited, but in this embodiment, as shown in FIG. And disc-shaped flange portions 101a and 102a and cylindrical boss portions 101b and 102b integrally formed at the same center as the flange portions 101a and 102a. Center holes 111 and 112 are formed in the flange portions 101a and 102a and the boss portions 101b and 102b so as to pass through the centers and attach the rotation shafts (the input shaft 201 and the output shaft 202).

  Further, a connecting bolt insertion hole 101c is formed in the flange portion 101a of the first hub 101 in a symmetric arrangement in the diameter direction, and the connecting bolt insertion hole of the first hub flange portion 101a is formed in the second hub 102a. A clearance hole 102d such as a nut 131 and a fixing member 12 that are screwed into the connecting bolt 121 is formed at a position corresponding to 101c. On the other hand, the flange portion 102a of the second hub 102 has a connecting bolt insertion hole 102c in a symmetric arrangement in the diametrical direction with a 90 ° spacing from the connecting bolt insertion hole 101c forming the pair of the first hub flange portion 101a. Is formed. The first hub 101 is formed with a relief hole 101d such as a nut 131 and a fixing member 12 that are screwed into the connection bolt 121 at a position corresponding to the connection bolt insertion hole 102c of the second hub flange portion 102a.

  Therefore, the disk 10 forming the annular square body disposed between the first hub flange portion 101a and the second hub flange portion 102a is inserted through the connection bolt insertion hole 101c and the first hub attachment hole 13 of the first hub. The nut 131 is screwed into the connecting bolt 121 to be fixed to the first hub 101. Further, the disk 10 is fixed to the second hub 102 by screwing a nut 131 into the connection bolt 121 inserted through the connection bolt insertion hole 102c and the second hub mounting hole 14 of the second hub. Each nut 131 will be located in the relief holes 101d and 102d of the flange part opposingly arranged.

  According to the present embodiment, the four discs 10 (10A, 10B, 10C, 10D) are provided with a film-like wear prevention member 30 between adjacent discs as shown in FIGS. Overlaid in the state. The fixing member 12 is brought into contact with the outermost surfaces of the disc stacks 10A to 10D, in this embodiment the disc 10A and the corners 10s to 10v of the disc 10D, and the four discs 10 (10A, 10A, 10B, 10C, and 10D) are fixed to the hubs 101 and 102 by bolts 121 and nuts 131 in a state where the fixing members 12 are sandwiched. The fixing member 12 will be described in detail later.

  Next, the disk 10, the wear preventing member 30, and the fixing member 12 constituting the disk unit 20 according to the present invention will be described.

(disk)
As described above, the disk 10 is made of a thin plate (flexible plate) made of fiber-reinforced plastic molded into an annular square body in the present embodiment, and four disks 10A, 10B, 10C, and 10D are stacked. Used together. However, according to the present invention, the wear preventing member 30 (30A, 30B, 30C) is disposed between the stacked disks.

  In the present embodiment, as described above, the four corners of the disk 10 forming the annular square body, that is, the corner portions 10s forming the connecting portions of the linear four sides (side members) 10a, 10b, 10c, and 10d arranged orthogonal to each other, Reference numerals 10t, 10u, and 10v denote bolt and nut fixing portions for the shaft coupling 100, and a fixing portion area FA (shaded area shown in FIG. 2B) is set in the fixing portion. In each of the disks 10A, 10B, 10C, and 10D, the fixed portion area FA is sandwiched between the fixed members 12, and the first and second hubs 101 are connected to the wear prevention members 30 (30A, 30B, and 30C) by bolts and nuts 121 and 131. , 102.

  The required area of the fixed portion region FA is appropriately determined depending on the transmission torque required for the shaft coupling 100, the configuration of the disk 10 to be used, and the like, and a predetermined fastening torque is applied by bolts and nuts 121 and 131.

  Each disk 10 is made by cutting or pressing a fiber reinforced plastic thin plate (fiber reinforced plastic plate) produced by impregnating a reinforced fiber with a resin and curing the resin, in this embodiment, by machining into an annular square. It is produced by molding.

  Therefore, first, a thin plate-like fiber-reinforced plastic that can be used to manufacture the disk 10, that is, the flexible plate member 11 (see FIG. 6) before being formed into a disk shape will be described.

If an example of the manufacturing method of a fiber reinforced plastic board, ie, the flexible board member 11, if shown, as shown to Fig.5 (a), (b), it will arrange | position the continuous reinforcing fiber f to one direction, and will comprise it in a sheet form. A resin sheet impregnated with resin 1A is impregnated with resin Re, and the resin is semi-cured to prepare prepreg sheet 1B. The design thickness (t) of each prepreg sheet 1B is about 0.05 to 1.0 mm (fiber basis weight 30 to 1000 g / m ² ).

  The required number of prepreg sheets 1B, four in this embodiment, as shown in FIG. 6, for example, 0.degree., 90.degree., 90.degree., 0.degree. Then, the resin is cured and the fiber-reinforced plastic plate 11 can be manufactured. In the example shown in FIG. 6, the fiber orientation direction of the prepreg sheet 1B to be overlapped has been described as two directions of 0 ° and 90 °. However, the fiber orientation direction should be oriented in a desired predetermined direction such as three directions of 0 ° and ± 60 °. Can do.

  In the above description, the fiber-reinforced plastic plate 11 is manufactured using a so-called unidirectional fiber-oriented prepreg sheet (UD prepreg sheet) 1B, which is prepared by aligning the reinforcing fibers f in one direction. As a method, a fiber sheet laminate is formed by laminating a so-called raw fiber sheet 1A, which is not impregnated with resin shown in FIG. The fiber reinforced plastic plate 11 can be manufactured by impregnating with resin and then curing.

For example, when carbon fibers are used as the reinforcing fibers f used in the fiber sheet 1A in the above-described production method, for example, 6000 to 24000 single fibers (carbon fiber monofilaments) f having an average diameter of 7 μm are converged and unimpregnated with resin. A plurality of single fiber bundles are used by being aligned in parallel in one direction. The fiber basis weight of the carbon fiber sheet 1A is usually 30 to 1000 g / m ² as described above.

  As the fiber sheet 1A, instead of the above-described unidirectional reinforcing fiber sheet in which the reinforcing fibers f are arranged in one direction, the so-called cloth (woven fabric, woven or knitted with the reinforcing fibers f in two axes and three axes is used. Knitted fabric) can also be used.

  Next, in this embodiment, as shown in FIGS. 2A and 2B, the length and width of each of the side members 10a to 10d are set to a predetermined length (L) and width (W). In other words, in this embodiment, cutting or press molding is performed by machining so as to form an annular square body. Further, in the present embodiment, the insertion holes 13 and 14 of the connecting bolt 121 are processed in the corner portions 10s to 10v in which the fixing portion areas FA of the respective disks 10A to 10D are set. Further, in the present embodiment, the protruding corner portion R1 and the entering corner portion R2 formed in the corner portions 10s to 10v of the respective disks 10 have curved shapes with radii R1 and R2, respectively.

  In this way, a flexible plate made of FRP molded into a predetermined shape constituting the disk 10 is produced. The thickness (T0) of the flexible plate member 11 is usually 0.1 to 5 mm.

  In the fiber sheet 1A (prepreg sheet 1B) described above, the reinforcing fiber f is not limited to carbon fiber, but is an inorganic fiber such as glass fiber or basalt fiber; metal such as boron fiber, titanium fiber, or steel fiber. Fibers; and organic fibers such as aramid, PBO (polyparaphenylene benzbisoxazole), polyamide, polyarylate, and polyester; can be used alone or in a mixture of plural kinds.

  In addition, as the resin Re in the case of the prepreg sheet 1B, a thermosetting resin or a thermoplastic resin can be used. As the thermosetting resin, a room temperature curing type or a thermosetting type epoxy resin, a vinyl ester resin can be used. MMA resin, acrylic resin, unsaturated polyester resin, phenol resin, etc. are preferably used. Also, as the thermoplastic resin, epoxy resin, polyamide resin, polycarbonate resin, polyether ether ketone resin, polyphenylene sulfide resin, etc. Can be suitably used. The fiber volume content (Vf) is 40 to 75%, preferably 50 to 60%.

(Abrasion prevention member)
Next, the film-like wear preventing member 30 (30A, 30B, 30C) disposed between the stacked disks will be described.

  As shown in FIG. 8A, the wear preventing member 30 is substantially the same as the shape of the disk 10 in this embodiment. That is, the wear preventing member 30 is formed into an annular rectangular body having the same shape as the disk 10 by using a film-like member 30 having a thickness (tf) of 10 to 200 μm. When the thickness (tf) is less than 10 μm, the effect as a wear preventing member is low. When the thickness (tf) exceeds 200 μm, there arises a problem that tightening of the tightened bolt is easily loosened. Preferably, it is 20-60 micrometers. Moreover, moderate intensity | strength is also required and an elastic modulus shall be 200-210000 MPa. If the elastic modulus is less than 200 MPa, there is a problem that it is crushed by bolt tightening, and if it exceeds 210000 MPa, there is a problem that the wear preventing function is impaired. Preferably, it is a resin film made 200-5000 MPa. The material of the wear preventing member 30 will be further described later.

  The corners 30s, 30t, 30u, and 30v that form the connection portions of the four corners of the wear preventing member 30 that forms the annular square body, that is, the linear four sides (side members) 30a, 30b, 30c, and 30d that are arranged orthogonal to each other, Similar to the disk 10, it has an exit corner R1 and an entrance corner R2, and the exit corner R1 and the entrance corner R2 have curved shapes with radii R1 and R2, respectively. Further, as shown in FIG. 8A, the wear preventing member 30 is paired diagonally at the four corners (corner portions) 30s, 30t, 30u, and 30v of the wear preventing member 30 forming an annular square body. A mounting hole 33 for the first hub 101 and a mounting hole 34 for the second hub 102 are formed.

  Here, the center distance L0 between the mounting holes 33 and 34 formed at the four corners of the wear preventing member 30 is the same as that of the disk 10, but the lengths of the side members 30a to 30d of the wear preventing member 30 are the same. Lf and width wf may be substantially the same as, or preferably slightly larger than, the length L and width w of each side member 10a-10d of the disk 10, respectively.

  As shown in FIGS. 1 and 3, the wear preventing member 30 is interposed between the disks 10 together with the disks 10 together with the bolts 121, nuts 131, and the fixing members 12. , 102.

  The wear preventing member 30 is made of a material that reduces the friction between the disc 10 and the wear preventing member 30 from the friction between the disc 10 and the disc 10. In other words, the coefficient of friction is such that the coefficient of static friction between the same materials is 0.1 to 0.9, preferably 0.1 to 0.4.

  As the film-like wear preventing member 30 having the above characteristics, a thermoplastic resin or a thermosetting resin is preferably used. For example, polyethylene terephthalate resin, polyamide resin, polyethylene resin, fluororesin, polycarbonate resin, polyacetal resin, silicone resin, vinyl chloride resin, polyphenylene sulfide resin, polyimide resin, polyester resin, cellophane, synthetic rubber (for example, low friction type silicon) Resin films made of various resins such as rubber, nitrile rubber, etc. can be suitably used. Further, for example, a metal film made of aluminum, stainless steel or the like can be used.

  The wear preventing member 30 is usually formed in the same shape as the disk 10 and has been described as an annular polygon having the same shape as the disk 10 in the above embodiment. Therefore, as illustrated in FIG. 8A, the description has been made assuming that the outer shape is a rectangular (quadrangular) shape, and a rectangular (rectangular) hole is similarly formed inside. However, the wear preventing member 30 according to the present invention is interposed between the adjacent disks 10 and 10 and is fixed in the fixing portion area FA and the peripheral area ΔFA defined by the fixing member 12 used for bolt fastening. It has a function of preventing wear due to rubbing. Therefore, the wear preventing member 30 is located between the stacked disks, and as shown in FIG. 8B, at least the fixing portion area FA pressed by the fixing member 12 and the fixing portion area FA. It is important to locate the outer periphery of the fixed portion peripheral area ΔFA.

  In other words, the wear preventing member 30 may have a shape located up to the fixed portion peripheral region ΔFA extending outward from the fixed portion region FA by the fixing member 12 in contact with the disk 10. Therefore, as shown in FIG. 8B, for example, if the region where the fixing member 12 contacts the disk 10 is a hatched portion in the region indicated by the diameter D12, the hatched portion is the fixed portion region FA. A region that is larger than the diameter D12 by ΔE is a fixed portion peripheral region ΔFA. Therefore, the wear preventing member 30 may be a circular wear preventing member 30 having a diameter D30 (that is, D30 ≧ D12 + 2ΔE) including at least the fixed portion peripheral region ΔFA. ΔE needs to be equal to or greater than the influence range of the tightening compression force by the fixing member 12.

  Therefore, the present inventors examined the influence range of the tightening compression force by the fixing member 12 by FEM analysis. As a result, the influence range of the tightening compression force by the fixing member 12 is the number of stacked disks (n) having the thickness (T0) constituting the deflecting plate (disk) 10, that is, the total thickness of the disks 10A to 10D. Although it fluctuates according to (n · T0), it has been found that it is substantially constant and substantially (n · T0 / 2) regardless of the magnitude of the tightening compression force by the fixing member 12. As described above, ΔE needs to be larger than the influence range of the tightening compression force by the fixing member 12, and therefore ΔE ≧ (n · T0 / 2). Specifically, when the thickness of one disk (T0) is 0.7 mm, when the flexure plate (disk) 10 is composed of one disk (total thickness 0.7 mm), four sheets ΔE is 0.35 mm, 1.4 mm, and 2 mm (total thickness 2.8 mm) and 8 disks (total thickness 5.6 mm), respectively. .8 mm or more.

  In the above description, the friction preventing member 30 has been described as being circular, but of course, the wear preventing member 30 is not limited to a circular shape, and may have various shapes such as a quadrangle, a pentagon, and a hexagon.

  Further, as shown in FIG. 8C, the wear preventing member 30 is an elongated strip-like member extending between the corner portion (fixed portion) and the corner portion (fixed portion) of the side member of the disk 10. Can do. That is, in this embodiment, the strip 10 can be the same shape as one side member of the disk 10, both ends have a curved shape with a radius R30, and attachment holes 33 and 34 are formed at both ends. It is said. The outer length of the elongated strip member 30 is Lf, the width is wf, and the distance between the mounting hole centers is L0. The outer length Lf and the width wf can be substantially the same as the length L and the width w of the side member of the disk 10, respectively, or can be larger than the length L and the width w. it can. Further, the curved shape R30 at both ends can be the same as the curved shape R1 at the corner of the disk 10. The wear preventing member 30 configured as a belt-shaped member having such a configuration is disposed on the side member facing the disk 10 in accordance with, for example, the side members 30a and 30c or the side members 30b and 30d.

(Fixing member)
As shown in FIG. 1, the plurality of disks 10 (10A, 10B, 10C, 10D) and the wear prevention member 30 (30A, 30B, 30C) forming an annular square body are connected to the connecting bolt insertion hole 101c of the first hub 101. The nut 131 is screwed into the connecting bolt 121 inserted through the first hub mounting hole 13 of the disk 10 and the first hub mounting hole 33 of the wear preventing member 30 to be fixed to the first hub 101. In the disk 10, a nut 131 is screwed into a connection bolt 121 inserted through the connection bolt insertion hole 102 c of the second hub 102, the second hub attachment hole 14 of the disk 10 and the second hub attachment hole 34 of the wear prevention member 30. As a result, the second hub 102 is fixed.

  Thus, according to the present invention, as shown in FIGS. 1 (a) and 3 (a), the disk 10 has a fixed portion for the first hub 101 and the second hub, that is, a fixed portion area FA. The corner portions 10s to 10v of the respective disks 10A to 10D are sandwiched between the fixing members 12 and 12, and the first and second bolts 121 and nuts 131 are used together with the wear preventing member 30 via the fixing members 12 and 12. It is fixed to the hubs 101 and 102.

  As understood from the above, the fixing member 12 has an arbitrary shape. However, as shown in FIGS. 2A and 2B, the fixing member 12 is set at the corner portions 10 s to 10 v of the disk 10. The fixed portion area FA of the disk 10 and the wear preventing member 30 in the fixed portion is defined. Accordingly, the corners 10s to 10v may have a shape and dimensions that completely cover the protruding corner portion R1 and the entering corner portion R2, but as shown in FIG. It is not necessary to have a shape that completely covers the portions 10s to 10v, and the area may be smaller than the corner portions 10s to 10v as long as sufficient fastening torque by bolts and nuts for the shaft coupling 100 can be achieved.

  2 (a), (b), (c), and FIGS. 3 (a) and 3 (b), the fixing member 12 has been described as a circular circular plate. In the embodiment shown in FIG. 2B, the diameter D12 of the contacting surface is substantially the same size as the corner portions 10s to 10v, and includes the protruding corner portion R1 and the entering corner portion R2 formed in the corner portions 10s to 10v. Although it is set as the magnitude | size which contacts an area | region, in the Example shown in FIG.2 (c), it is set as the shape smaller than corner part 10s-10v. The shape and dimensions of the fixing member 12 can be any shape, and can be appropriately determined according to the shape of the disk, such as a circle, a rectangle, or a hexagon.

  The fixing member 12 is not a pair of circular fixing plates as described above, but as shown in FIGS. 4A and 4B, the fixing member 12a on one side is a circle that contacts the surface of the fixing portion of the disk. A plate 12a1 and a cylindrical body 12a2 that protrudes from the circular plate 12a1 and fits into the mounting holes 13, 14, 33, and 34 of the disk 10 and the wear preventing member 30 can be provided. According to the fixing member 12 of this example, when the cylindrical body 12a2 is fitted into the mounting holes 13, 14, 33, and 34 of the disk 10 and the wear preventing member 30, the tip of the cylindrical body 12a2 is overlapped. The disk 10 protrudes outward from the insertion side of the disk 10, and the other circular plate 12b is fitted into this part. As a result, the fixed portion area FA of the disk 10 provided with the wear preventing member 30 is sandwiched between the fixing members 12 (12a, 12b) and attached to the first and second hubs 101, 102.

  The material of the fixing member 12 is not particularly limited as long as sufficient bending rigidity can be obtained, but a steel material such as stainless steel, a metal material such as an aluminum material, a resin plate, a fiber reinforced plastic material, a ceramic material. Etc. can be used.

(Action of wear prevention member)
Next, the operation of the wear preventing member 30 which constitutes a characteristic part of the present invention will be described.

  In the disc-type shaft coupling 100 as shown in FIG. 1, each side of the flexure plate (plate spring) incorporated as the disc unit 20, that is, the disc 10 is deformed as a flexure plate when misalignment occurs. For the torque load from the shaft, one has the function of transmitting the torque from one input shaft 201 to the other output shaft 202 by functioning as a tension member and the other as a compression member. When the number is increased, the side on the compression side is eventually destroyed, and the disk unit 20 loses its torque transmission capability.

  According to the results of our research experiments, when a plurality of discs 10 (10A, 10B, 10C, 10D) are used in an overlapping manner as in the disc unit 20 of the invention, the polygonal disc 10 The corners 10s, 10t, 10u, and 10v are used as fixing parts, holes 13 and 14 are formed in the corner parts, and the disks 10 are fastened and fixed by rigid bolts 121, nuts 131, and fixing members 12. When bending deformation due to misalignment is applied to the disc unit 20 having such a configuration, the discs rub against each other immediately below the fixed portion area FA and the fixed portion peripheral region ΔFA, so-called fretting phenomenon, which is a metal material. It was found that a phenomenon similar to that of FIG.

  Further, according to the results of the research experiments by the present inventors, when the wear of the disks progresses due to repeated use of bending deformation, the thickness of both end portions of the side members 10a to 10d of the disk 10 decreases, and each side It has been confirmed that the bending rigidity is lowered in the fixed portion area FA and the peripheral area ΔFA of the member, and as a result, the breaking torque when the torsional torque is applied to the disk unit 20 is also reduced.

  It has been found that the above-described problems of the disk-type shaft coupling 100 can be solved by disposing the film-shaped anti-wear member 30 between the disks formed of laminated fiber-reinforced plastic plates. did.

  Experiments and experimental results conducted by the present inventors in order to verify the effects of the present invention will be described below.

(Experiment and experimental results)
In an experiment conducted by the present inventors, first, a change in residual capacity of the disk 10 subjected to repeated rotational bending was evaluated by a rotational bending fatigue test. Next, the state of damage and the cause of damage that occurred in the disk 10 subjected to repeated rotational bending were examined, and the influence of the damage generated in the disk 10 on the residual capacity was examined.

(1) Specimen and experimental method 1.1 Specimen (disc)
A disc (hereinafter, referred to as “disc test piece”) 10S, which is a test body used in this experiment, was manufactured in the following manner. The disk test piece 10S has the same configuration as the above-described disk 10 configured according to the present invention described with reference to FIGS. 2 (a), 2 (b), 6 and the like.

  The fiber sheet for producing the disk test piece 10S is a prepreg sheet (UD prepreg sheet) in which reinforcing fibers f are arranged in one direction and impregnated with a matrix resin Re as shown in FIGS. 1B was used.

  In this experiment, a PAN-based high-strength carbon fiber UD prepreg sheet was used as the UD prepreg sheet 1B. As the matrix resin Re, a thermosetting epoxy resin was used, and the fiber volume content (Vf) was 57%.

  The carbon fiber UD prepreg sheet 1B is laminated and bonded at an orientation angle of 0 ° / 90 ° / 90 ° / 0 ° / 90 ° / 90 ° / 0 °, and cured at 130 ° C. for 2 hours using an autoclave. The fiber-reinforced plastic flexible plate member 11 was obtained.

Various physical properties of the fiber reinforced plastic flexible plate member 11 are as follows.
Elastic modulus: 0 ° direction bending elastic modulus 88 GPa, 90 ° direction bending elastic modulus 59 GPa
Bending strength: 0 ° direction bending strength 1.9 GPa, 90 ° direction bending strength 1.7 GPa
・ Thickness (T0): 0.7mm

  In this experiment, the fiber reinforced plastic flexible plate member 11 was machined to produce an annular rectangular flexible plate, that is, a disk test piece 10S. As shown in FIG. 2 (and FIG. 7), the flexure plate member 11 has the reinforcing fibers f oriented in parallel along the inner edge portion 10in and the outer edge portion 10out of the side members 10a to 10d, which are linear. It was processed to be located. Further, the corners of the corner portions 10s to 10v were processed so that the protruding corner portion R1 and the entering corner portion R2 had a curved shape. The insertion holes 13 and 14 of the connecting bolt 121 were processed in the corner portions 10s to 10v forming the fixing portion region FA.

  Here, each of the linear side members 10a to 10d has a length (L) of 77 mm and a width (W) of 15 mm in FIG. The distance (L0) between the mounting holes 13 and 14 was 58 mm. Further, the protruding corner portion R1 and the entering corner portion R2 in the corner portions 10s to 10v have curved shapes having radii of 9.5 mm and 1.6 mm, respectively.

  In this experiment, as shown in FIG. 17, the four disc test pieces 10S (10SA, 10SB, 10SC, 10SD) are laminated in the same manner as the configuration of the disc 10 (10A, 10B, 10C, 10D) shown in FIG. As shown in FIGS. 4 (a) and 4 (b), the disc unit 20 was manufactured using the graphic member 12 (12a, 12b). The disk unit 20 was attached to the first hub 101 and the second hub 102 of the same disk type shaft coupling 100 as described with reference to FIG. Note that the four disk test pieces 10S (10SA, 10SB, 10SC, 10SD) were stacked so that the fiber directions on the adjacent disk surfaces were 90 ° different from each other.

(Fixing member)
In this experiment, as described above, the same fixing member 12 (12a, 12b) as shown in FIGS. 4 (a) and 4 (b) was used. The fixing member 12 is made of stainless steel, and has the following dimensional shape with reference to FIG.
・ Fixing member 12a
Disc outer diameter D12a1: 18mm
Disc thickness T12a1: 2.5mm
Cylindrical outer diameter D12a2: 8.1 mm
Cylindrical body thickness T12a2: 5 mm
Bolt through hole d12a: 10mm
・ Fixing member 12b
Disc outer diameter D12b: 18mm
Disc thickness T12b: 2.5mm
Cylindrical body mounting hole diameter d12b: 8.1 mm

(Abrasion prevention member)
In the experiment (Experimental Examples 1 and 2 of the present invention) for verifying the effects of the present invention described below and the comparative experiment (Comparative Examples 1, 2, and 3), the disk test piece 10S itself is The same configuration was used. However, the disk unit 20 used in Experimental Examples 1 and 2 of the present invention is between the disk test pieces 10S, that is, between the disk test pieces 10SA and 10SB, between 10SB and 10SC, and between 10SC and 10SD. The wear preventing member 30 is disposed between them.

As the wear preventing member 30, a cellophane sheet (Futamura Chemical Co., Ltd .: PS-1) was used. The cellophane sheet was an annular square body described with reference to FIG. 8A and had the same dimensions and shape as the disk test piece 10S. The characteristics of the used cellophane sheet were as follows.
・ Thickness: 21μm
・ Elastic modulus: 1500 MPa
-Coefficient of static friction: 0.27

1.2 Rotating Bending Fatigue Test under No-Torque Conditions FIG. 10 shows a schematic configuration of a rotating bending fatigue testing machine 300. The rotary bending fatigue testing machine 300 has a single type shaft coupling (coupling) 100 as shown in FIG. 1, and the disk unit 20 of the coupling 100 uses the fixing member 12 having the above-described configuration to disc. A test piece 10S was attached. The fixing member 12 can be mounted so as to cover substantially all the protruding corner portion R1 and the entering corner portion R2 of the corner portion of the disc test piece 10S, and the protruding corner portion R1 and the entering corner portion R2 of the disc corner portion are fixed. It was not exposed from the member 12.

In the rotary bending tester 300, the input shaft 201 and the output shaft 202 of the coupling 100 are supported by bearings 301, and the input shaft 201 of the coupling 100 is driven by the motor M via the gear mechanism 302. At this time, the deflection angle of the coupling 100 was set to 3 °. Further, the fastening torque by the bolt 121 and the nut 131 when the disc test piece 10S is fixed by the disc unit 20 was set to 30 N · m. In this experiment (Experimental Example 1 and Comparative Example 1), no torque was applied to the disk test piece 10S, the rotational speed of the shaft was 1800 rpm, the number of repeated load interruptions was 1.0 × 10 ⁷ times, and the test environment was A laboratory environment (temperature 23 degrees, humidity 50-60%) was used.

1.3 Rotating Bending Fatigue Test with Torque Maintained FIG. 11 shows a schematic configuration of a torque maintaining type rotating bending test machine 400 used in this experiment.

  The torque holding type rotary bending tester 400 includes two disc type shaft couplings (couplings) 100 (100A, 100B), in which a rotating shaft is supported by a bearing 401 and connected in series, and a friction type shaft fastening mechanism 402A. And a driving device 402 provided. The driving device 402 drives the output shaft 404 via the belt drive transmission mechanism 403 by the motor M, and the output shaft 404 drives the input shaft 201 of the coupling 100A via the belt drive transmission mechanism 405. The coupling 100A is connected to the coupling 100B by a rotating shaft 406, and the output shaft 202 of the coupling 100B is drivingly connected to the input shaft 408 of the driving device 400 via a belt drive transmission mechanism 407.

  In this experiment, an initial internal torque (hereinafter referred to as “load torque”) is provided between the pulley 407P on the drive device side of the belt drive transmission mechanism 407 and the pulley 405P on the drive device side of the belt drive transmission mechanism 405. Then, the frictional shaft fastening mechanism 402A was used to rotate while maintaining the declination (3 °) while maintaining the torque. The load torque was measured with a tension meter 409.

In this experiment, the load torque is 100 N · m (Comparative Example 2) and 250 N · m (Comparative Example 3), the rotation speed is 900 rpm, the number of times the repeated load is cut off is 1.0 × 10 ⁷ times, and the test environment is the laboratory. The environment (temperature 23 degrees, humidity 50-60%).

  As an experimental example (experimental example 2) of the present invention, the disk unit 20 has a structure in which the above-described cellophane sheet (Futamura Chemical Co., Ltd .: PS-1) is sandwiched between the disk test pieces 10S as the wear preventing member 30. The load torque was 250 N · m (Experimental example 2). Other experimental conditions were the same as those in Comparative Examples 2 and 3.

1.4 Measuring Method of Bending Rigidity FIG. 12A shows an outline of a testing machine 500 for grasping a change in a spring constant (hereinafter referred to as “bending rigidity”) with respect to bending deformation when the disk test piece 10S is used. The configuration is shown.

  In this experiment, the disk unit 20 in which the disk 10S (10SA, 10SB, 10SC, 10SD) is fixed integrally with the fixing member 12 is mounted between the upper jig 501 and the lower jig 502. At this time, the disk unit 20 was fixed so that one corner of the disk unit 20 protruded.

  A weight load W is applied to the tip of the corner of the disk unit 20 protruding in a triangular shape, measured by a laser displacement meter 505, and a displacement of 2.6 mm corresponding to the case where the coupling has a declination of 3 ° is obtained. The weight load W was applied until

1.5 Measuring Method of Residual Breaking Torque FIGS. 13A and 13B show a schematic configuration of a testing machine 600 used for a breaking test of the disk test piece 10S. The destructive testing machine 600 has the same configuration as the rotary bending fatigue testing machine 300 shown in FIG. That is, the destructive testing machine 600 has a disk type shaft coupling (coupling) 100 as shown in FIGS. 13A and 13B, and the input shaft 201 and the output shaft 202 of the coupling 100 are respectively connected. It was supported by a bearing 601. In the destructive testing machine 600, the declination angle of the coupling 100 was set to 0 °, and the disk test piece 10S was fixed in the coupling 100 in the same manner as the rotational bending fatigue test. One end (output shaft 202) of the coupling 100 was completely fixed to the test machine base 602, and a torque was applied to the shaft 201 using a pipe wrench 603 at the other end (input shaft 201). The maximum torque when the disk test piece 10S was broken was measured using a strain gauge.

(2) Experimental Results and Considerations 2.1 Disc Destruction Mode FIG. 14A shows the state of disc deformation that occurs when a torque of 250 N · m is applied to the disc specimen 10S before fatigue loading. FIG. 14 (b) shows the destruction state of the disk test piece 10S.

  When the disks were loaded with torque, each disk deformed in the out-of-plane direction, eventually leading to destruction. The breaking mode of the disk is a buckling fracture of a belt-shaped part (side member) that receives compressive force in a well-shaped disk, and isher part (fixing member) that is locally used for bolt fastening It was found that bending fracture in the vicinity of the fixed part preceded.

2.2 Residual Fracture Torque of Disc FIG. 15 shows the change (decrease rate) in the residual fracture torque of the disc test piece 10S with respect to the number of repetitions under each test condition. Further, in FIG. 15, the change in the residual torque is also shown in the experimental example of the present invention when the friction preventing condition (cellophane in this experiment) 30 is sandwiched between the disks and the low friction condition is achieved. This is shown (Experimental Examples 1 and 2).

  The residual fracture torque of the disk test piece 10S subjected only to repeated rotational bending was reduced by about 2.4% compared to the residual fracture torque of the disk test piece 10S before fatigue loading (Comparative Example 1). Similarly, the residual torque of the test piece subjected to repeated rotational bending while receiving a constant torque was also reduced by about 1.5 to 2.0% (Comparative Examples 2 and 3).

  It was found that the reduction rates of both were similar, and that the influence of the load torque was relatively small on the change in the residual breaking torque.

2.3 Bending rigidity in the out-of-plane direction of the disk FIG. 16 shows changes in bending rigidity with respect to the number of repetitions under each test condition. FIG. 16 also shows an example of the experiment of the present invention, in which the change in the bending stiffness when the wear preventing member (cellophane in this experiment) 30 is sandwiched between the disks and the frictional condition is low is also shown. This is shown (Experimental Examples 1 and 2). In either case, the rigidity in the out-of-plane direction decreased from around 1.0 × 10 ⁵ cycles. The rate of decrease was 1-2%.

  Here, if it is considered that the load form of the disk test piece 10S is close to the condition of a long column with both ends fixed between two bolts, it can be said that the critical buckling load has a linear relationship with the bending rigidity. In the disk unit configurations according to the present invention shown in Experimental Examples 1 and 2, the same tendency was observed in the decrease in bending rigidity and the decrease in residual breaking torque, so the decrease in residual breaking torque was explained by the decrease in bending rigidity. I understood that I could do it.

2.4 Disk Surface Damage Location / Internal State of Disc FIG. 17 schematically shows the damage location of four disk test pieces 10S (10SA, 10SB, 10SC, 10SD) after 1.0 × 10 ⁷ cycles. . In general, a disk configured by laminating a plurality of fiber reinforced plastic plates 11 has a reduced buckling load when peeling occurs between the layers. Therefore, the internal state of the damaged portion of the disk test piece 10S shown in FIG. 17 was observed.

The disc test piece 10S after fatigue was cut out to 25 × 25 mm, placed in a silicone rubber mold and fixed, and then a liquid resin was placed in the mold and cured at room temperature for 24 hours. As shown in FIG. 18A, the internal state at a position of about 7.0 mm from the side surface of the disk test piece 10S was observed from the arrow direction. FIG. 18B shows the internal state of the disk after 1.0 × 10 ⁷ cycles. In FIG. 18B, (a) is the load torque of 0 N · m (Comparative Example 1), (b) is 100 N · m (Comparative Example 2), and (c) is 250 N · m (Comparative). Example 3) A case is shown. An optical microscope was used for observation. None of the test pieces showed any cracks or peeling inside. For this reason, it is considered that the damage of the disc occurs not near the inside of the disc but near its surface.

2.5 Residual Fracture Torque and Flexural Rigidity of Discs with Low Friction Between Discs FIGS. 19A and 19B are examples of experiments according to the present invention, and wear prevention members between discs. (In this experiment, cellophane) 30 shows the internal state of the disk after 1.0 × 10 ⁷ cycles when a low friction condition is obtained. Also in this experimental example, as in the case of Comparative Examples 1, 2, and 3 described with reference to FIG. 18, the fatigued disc test piece 10S was cut into 25 × 25 mm and placed in a silicon rubber mold. After fixing, a liquid resin was placed in a mold and cured at room temperature for 24 hours. As shown in FIG. 19A, the internal state at a position of about 7.0 mm from the side surface of the disk test piece 10S was observed from the arrow direction. FIG. 19B shows the internal state of the disk after 1.0 × 10 ⁷ cycles.

  In the case of the experimental example of the present invention, neither crack nor peeling was observed even inside the disk. Further, as shown as Experimental Examples 1 and 2 in FIGS. 15 and 16, a low friction condition is achieved by sandwiching an anti-wear member (cellophane in this experiment) 30 between the disk 10S and the disk 10S according to the present invention. In the case configuration, almost no decrease in bending rigidity and residual breaking torque was observed. From this, it was confirmed that when the occurrence of damage on the surface of each disk in the vicinity of the bolt fastening portion is suppressed, the decrease in the residual fracture torque is suppressed.

2.6 Disk surface damage mechanism FIGS. 20 (a1) and 20 (a2) show the surface condition of the disk specimen 10S before fatigue loading, and FIGS. 20 (b1) and 20 (b2) show different load torque conditions. The surface state of the second disk (second disk 10SB in FIG. 17) after 1.0 × 10 ⁷ cycles is shown. FIGS. 21 (a1) and 21 (a2) show a surface state after fatigue loading when a wear preventing member, in this experimental example, a low friction cellophane 30 is sandwiched between the disks according to the configuration of the present invention. A laser microscope was used for observation.

The surface condition of the test piece after 1.0 × 10 ⁷ cycles shown in FIGS. 20 (b1) and (b2) is compared with that before the fatigue load shown in FIGS. 20 (a1) and 20 (a2). Was worn out. The cause of such fiber breakage and fiber abrasion is thought to be due to fretting wear. On the other hand, in the experimental example of the present invention, as shown in FIGS. 21 (a1) and (a2), such fiber breakage and fiber wear were not observed even after fatigue loading.

  FIG. 22 is a schematic view showing a state of deformation of the disk test piece 10S when a declination is given after the disk test piece 10S is fastened during coupling. Generally, when the coupling has a declination, the deformation shown in FIG. 22 occurs in the disk fastened during the coupling, and relative slip (S) occurs. That is, with reference to FIG. 22, for example, focusing on the first disk test piece 10SA and the second disk test piece 10SB, the fixing member 12 is placed between the two adjacent stacked disks 10SA and 10SB. Each disk 10S is bent and deformed as shown in this example in the area directly below the fixed portion area FA where the disk 10S is pressed and fixed, and in the area away from the fixed area FA by ΔFA. In this case, compression occurs on the lower surface of the first disk 10SA, and tension occurs on the upper surface of the second disk SB. The relative slip (S) between the disks is considered to cause fiber breakage and fiber abrasion.

  From the above, when fiber reinforced plastic is used for the disk, abrasion between the disks causes local fiber breakage near the disk surface during fatigue loading, which reduces the rigidity of the disk and the residual breaking torque. It turned out to be a cause.

From the results of the above experiments conducted by the present inventors, the following has been found. That means
(1) The form of fracture of the disk is a buckling fracture of a belt-shaped part (side member) that receives a compressive force in a well-shaped disk, and a washer part used locally for bolt fastening ( Bending fracture in the vicinity of the fixing part of the fixing member) precedes.
(2) The decrease in residual fracture torque can be explained by the decrease in bending rigidity.
(3) When fiber-reinforced plastic is used for the disk, abrasion between the fiber-reinforced plastic plates causes local fiber breakage near the surface of the fiber-reinforced plastic plate during fatigue loading, which reduces the rigidity and residual failure of the disk. This will cause a decrease in torque.
I understood that.

Example 2
In the first embodiment, the disk 10 used in the present invention is an annular square body having an outer shape of a rectangular shape (quadrangle) and a rectangular shape (quadrangle) formed in the inside. explained. However, the disk 10 of the present invention is not limited to the one described above. A typical modified embodiment will now be described.

Modified example 1
In the first embodiment, the disk 10 used in the present invention has been described on the assumption that the shape of the side members 10a, 10b, 10c, and 10d forming the disk 10 is linear, but FIG. As shown in FIG. 5A, the outer shape and the inner hole shape of each of the side members 10a, 10b, 10c, and 10d may be a rectangular body that can be a curved shape.

Modified embodiment 2
The shape and size of the disk 10 used in the present invention is not limited to a quadrangle, and may be a polygon more than a triangle. For example, as shown in FIG. An annular hexagonal disk 10 composed of the members 10a to 10f may be used. In this modified embodiment, the side members 10a to 10f are linear, but may be curved.

Modified embodiment 3
In the first embodiment and the first and second modified embodiments, the disk 10 used in the present invention is an annular polygon having a polygonal outer shape and a hole having a similar shape formed inside. explained. However, as shown in FIG. 23 (c), it can be a single polygonal flat plate in which no hole is formed inside the disk.

  Also in the case of the disk unit 20 using the disk 10 shown in the modified examples 1, 2, and 3, according to the present invention, between the stacked disks and at least pressed by the fixing member 12. The wear preventing member 30 is disposed directly below the fixed portion region and in a peripheral portion of the fixed portion that is larger than the fixed portion region. With such a configuration, the same effects as in the first embodiment can be achieved in the first to third modified embodiments.

Modified embodiment 4
In the above-described embodiments and modified embodiments, the disk 10 has been described as an annular polygon formed integrally with a plurality of linear side members 10a to 10f. However, the form of the disk 10 that can be used in the present invention is not limited to this, and a strip-shaped link member can be integrally combined to form an annular polygonal body.

  FIG. 24 (a) shows a configuration in which the side members 10a to 10d, which are formed into four strip-shaped link members, are combined into a rectangular disk shape having four sides as in the first embodiment. Indicates. The strip-shaped side members 10a to 10d can be integrated by adhering both ends of the side members 10a to 10d with an adhesive, but are fixed via the fixing member 12 when fastening the bolts and nuts. By doing so, the structure is substantially the same as the annular square body of the first embodiment. In the modified embodiment shown in FIG. 24A, the fixing member 12 is rectangular. Of course, it may be circular as in the other embodiments.

  According to the present invention, as described above, when both ends of each of the strip-shaped side members 10a to 10d are bonded to each other with an adhesive, the disk 10 is integrally formed, as shown in FIG. Thus, when the discs 10A, 10B, and 10C are used as a plurality of discs 10 in an overlapping manner, the shape is substantially the same as that of the disc between adjacent discs, as shown in FIG. A square wear prevention member 30 can be interposed. Of course, instead of the square-shaped wear prevention member shown in FIG. 8A, the wear prevention member 30 having a circular or elongated band shape shown in FIGS. 8B and 8C may be used.

  Furthermore, when it is set as the structure fixed to the both ends of each strip-shaped side member 10a-10d by the fixing member 12 without mutually adhering with an adhesive agent, as shown in FIG.24 (c), it adjoins mutually. The strip-shaped side members 10 a to 10 d can be fixed by the fixing member 12 by interposing the wear preventing member 30 at the end portion of each strip-shaped side member. Of course, in this case as well, the wear preventing member 30 is not an annular rectangular body as shown in the figure, and the wear preventing member 30 having a circular shape or an elongated band shape shown in FIGS. 8B and 8C can also be used. .

  In the case of the configuration shown in FIG. 24C, the disk 10 can be made one by appropriately designing the side members 10a to 10d. Of course, even in such a configuration, a plurality of discs 10 can be used in an overlapping manner. In this case, as shown in FIG. 24B, the wear preventing member 30 is also interposed between adjacent discs. Set up.

  As described above, by using the wear preventing member 30, the same effect as the first embodiment can be achieved in the fourth modified embodiment.

1 Fiber sheet 10 (10A to 10D) Deflection plate (disc)
10a to 10f Side member 10s to 10x Corner portion (fixed portion)
11 Fiber reinforced plastic plate (flexible plate member)
12 Fixing member 13, 14 Mounting hole 20 Disc unit 30 Wear prevention member 30a-30d Side member 33, 34 Mounting hole 100 Disc type shaft coupling 101, 102 First and second hubs FA Fixing area △ FA fixing area

Claims (10)

A disk unit that transmits rotational torque between a drive shaft and a driven shaft in a disk-type shaft coupling,
A plurality of discs made of fiber-reinforced plastic plates;
A fixing member disposed in a fixing portion of the disk to overlap and sandwich the plurality of disks integrally;
In a disk unit with
A film having a thickness of 10 to 200 μm located between the stacked discs and at least in a fixed portion region pressed by the fixing member and a fixed portion peripheral region outside the fixed portion region A disk unit characterized in that a wear-resistant member in a shape is arranged.   2. The disk according to claim 1, wherein the disk is a polygon without holes or an annular polygon integrally formed by a plurality of side members, and the fixing portion is formed at a corner of the polygon. The disk unit according to 1.   The disk is formed into an annular polygonal body integrally formed by a plurality of side members by integrally combining strip-shaped link members, and the fixing portion is formed at a connection portion of each side member. The disk unit according to claim 1. A disk unit that transmits rotational torque between a drive shaft and a driven shaft in a disk-type shaft coupling,
A plurality of side members made of fiber-reinforced plastic plates connected to each other at both ends thereof to form an annular polygonal body; and
In a disk unit comprising: a fixing member disposed so as to sandwich the fixing part of the disk, which is a connection part of each side member of the disk,
A thickness of 10 to 200 μm located between adjacent side members of the disk and at least in a fixing portion region pressed by the fixing member and a fixing portion peripheral region outside the fixing portion region. A disk unit comprising a film-shaped anti-wear member.   The disk unit according to claim 1, wherein the wear preventing member is a resin film or a metal film.   The wear prevention member may have the same shape as the disk, or an elongated band shape having a predetermined width extending between the fixed part and the fixed part of the disk, or may be pressed by the fixed member. The disk unit according to claim 1, wherein the disk unit has a circular shape or a polygonal shape larger than the fixed portion region.   The disk unit according to claim 1, wherein the fixing member has a circular shape or a polygonal shape.   The disk unit according to claim 1, wherein the fixing member is a metal material such as a steel material or an aluminum material, a resin plate, a fiber-reinforced plastic material, or a ceramic material. Reinforcing fibers of the fiber reinforced plastic include: carbon fibers, glass fibers, basalt fibers, and other inorganic fibers; boron fibers, titanium fibers, steel fibers, and other metal fibers; aramid, PBO (polyparaphenylene benzbisoxazole), polyamide, poly Organic fibers such as arylate and polyester are used singly or mixed in plural types and used in a hybrid.
Examples of the resin of the fiber reinforced plastic include a thermosetting resin such as a room temperature curing type or thermosetting type epoxy resin, vinyl ester resin, MMA resin, acrylic resin, unsaturated polyester resin, or phenol resin; The disk unit according to any one of claims 1 to 8, wherein a thermoplastic resin such as a resin, a polyamide resin, a polycarbonate resin, a polyether ether ketone resin, or a polyphenylene sulfide resin is used. A disk type having a disk unit disposed between a first hub attached to the drive shaft and a second hub attached to the driven shaft and transmitting rotational torque between the drive shaft and the driven shaft In the shaft coupling of
The disc type shaft coupling according to claim 1, wherein the disc unit is the disc unit according to claim 1.