JP2006275079A - Flexible shaft joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To achieve miniaturization and low price without deteriorating shaft center adjusting action, buffer action and vibration damping action in a flexible shaft joint utilizing a barrel-shaped coil spring. <P>SOLUTION: In a flexible shaft joint equipped with a barrel-shaped coil spring, a tip of a spring supporting pin 38 is fitted in a spring supporting pin hole 25 provided to a second hub flange 23 so as to be cantilevered by the second hub flange 23. The maximum diameter part 42 of a barrel-shaped coil spring 41 is fitted in a spring hole 14 by clearance fit or transition fit. The minimum diameter part 43 of the barrel-shaped coil spring 41 is fitted in the spring supporting pin 38 by transition fit to be supported thereby. The rear end surface of the spring supporting pin 38 comes into contact with a cover annular part 34. The barrel-shaped coil spring 41 is deformed at the time of torque transmission, and compressed in a axial direction of the coil to be held between the second hub flange 23 and the cover annular part 34 so that adjacent spring coils are brought into contact with each other. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a flexible shaft joint that uses a coil spring as a flexible member of a torque transmission portion.

  Among flexible shaft couplings that use a coil spring as a flexible member of a torque transmission unit, there is a flexible shaft coupling having a structure in which the coil spring is deformed in a direction perpendicular to the coil shaft. The flexible shaft coupling has a flange at one end of the hub body, and the first hub and the second hub to which the transmission shaft is coupled, the hub body of the first hub penetrates, and the flange of the first hub is accommodated. And a cover fixed to the flange of the second hub, and a coil spring penetrating through a plurality of spring holes provided in the circumferential direction in the flange of the first hub. The first hub and the second hub are disposed so that the flanges of the first hub and the second hub face each other with a gap therebetween, and the coil spring is compressed between the flange of the second hub and the cover. Torque is transmitted between the first hub and the second hub via a coil spring (see, for example, Patent Document 1).

  Since the flexible shaft coupling having the above structure does not require a spring seat, there is an advantage that the structure is simple and small, and the moment of inertia is reduced. However, since the coil spring is deformed in the lateral direction, a large stress is generated in the coil spring, and the amount of deformation of the coil spring cannot be increased. As a result, there has been a problem that the axial center adjusting action, the buffering action and the torsional vibration damping action are small.

  The inventor of this application has invented the following flexible shaft coupling in order to solve the above problem. The coil spring is a drooping coil spring, and the drooping coil spring is fitted into the spring hole of the first hub at the maximum outer diameter portion and is supported between the flange of the second hub and the cover at the minimum inner diameter portion. It is an interference fit on the support pin. When the torque is transmitted, the coil spring is deformed and compressed so that adjacent coils are in contact with each other, and is attached between the flange of the second hub and the cover (see, for example, Patent Document 2).

Since the flexible shaft joint has a coil spring shape, it can be greatly deformed in the lateral direction without causing excessive stress on the spring. Accordingly, it is possible to increase the effects of adjusting the shaft center, buffering and damping the vibration.
JP 59-212528 (first page, FIG. 1) JP-A-6-213247 (second page, right column and FIG. 1)

  The flexible shaft coupling using the above-described helical coil spring can be used for equipment having a large transmission torque, such as an iron making machine and a large marine engine. On the other hand, for machine tools, blowers, pumps, and other devices with relatively small transmission torque, the shaft center adjustment, buffering, and vibration damping functions are the same as those of the conventional flexible shaft joints. A joint was sought.

  An object of the present invention is to provide a flexible shaft coupling that is small and low-priced in a flexible shaft joint that uses a helical coil spring without reducing the functions of adjusting the shaft center, buffering, and damping vibration.

  The flexible shaft coupling of the present invention has a first hub flange at the tip of a cylindrical hub body, a first hub to which the transmission shaft is connected, and a second hub flange at the tip of the cylindrical hub body. The second hub to which the transmission shaft is connected, and the cover annular portion at the rear end of the cylindrical cover body, the first hub body passes through the through hole of the cover annular portion and accommodates the first hub flange. A cover fixed to the second hub flange, a plurality of spring support pins supported by the second hub flange, and a plurality of spring holes provided in the circumferential direction in the first hub flange. A plurality of helical coil springs penetrating and supported by the spring support pins, and connecting bolts for fixing the cover to the second hub flange are provided. Between the first hub flange and the second hub flange, between the first hub flange and the cover annular portion, between the first hub flange and the cover main body, and between the first hub main body and the through hole of the cover annular portion. Clearances of the size necessary for adjusting the shaft center are provided between them. Torque is transmitted between the first hub and the second hub via the helical coil spring. In the flexible shaft joint thus configured, the tip of the spring support pin fits into a spring support pin hole provided in the second hub flange and is cantilevered by the second hub flange. A diameter portion is fitted into the spring hole by a clearance fit or an intermediate fit, and a minimum inner diameter portion of the helical coil spring is supported by being fitted to the spring support pin by an intermediate fit, and a rear end surface of the spring support pin Is in contact with the annular portion of the cover and is compressed in the coil axial direction between the second hub flange and the annular portion of the cover so that the helical coil spring is deformed during torque transmission and the adjacent spring coil contacts. It is characterized by being held.

  In the flexible shaft coupling, the first hub flange has a plurality of stopper bolt holes arranged along a circumferential direction, and each of the plurality of stopper bolts having a cylindrical portion serving as a stopper pin passes through the stopper bolt hole. And may be supported by the second hub flange and the cover annular portion.

  In the flexible shaft joint, each of the plurality of spring sets is constituted by a plurality of coil springs, and the spring sets are inserted into the spring holes such that end surfaces of adjacent coil springs are in contact with each other and arranged in series, You may make it support with the said spring support pin.

  In the flexible shaft coupling, an annular disk stopper may be inserted between the adjacent coil springs and held by the spring support pin.

  In the above-described flexible shaft coupling, the clearance between the maximum diameter portion of the coil spring and the spring hole can be set to -0.2 to + 15% of the maximum coil spring maximum diameter portion.

  In the flexible shaft coupling of the present invention, the tip of the spring support pin fits into the pin hole provided in the second hub flange and is cantilevered by the second hub flange, so that the structure for supporting the helical coil spring is simple. It has become. In addition, since the maximum diameter portion of the helical coil spring fits into the spring hole with a clearance fit or an intermediate fit, and the minimum inside diameter portion fits with the spring support pin with an intermediate fit, it is supported by the conventional tight fit. Therefore, the shaft and the hole can be machined with lower accuracy. As a result, the cost of the flexible shaft joint can be reduced.

  In the flexible shaft joint provided with the stopper bolt, it is possible to prevent an excessive load from being applied to the helical coil spring and to prevent the flexible shaft joint from being damaged. In particular, it is very effective for applications where heavy impacts are applied, such as steelmaking facilities.

  In a flexible shaft joint in which a plurality of barrel coil springs are mounted in one spring hole, the load at the time of torque transmission is applied to the plurality of barrel coil springs, so one barrel coil spring of the same size. Compared to the above, it is possible to transmit torque that is twice the number of springs. The flexible shaft joint becomes longer in the axial direction by the length corresponding to the increased number of springs. If the spring diameter is the same, the moment of inertia of the joint is, for example, about 30 to 60% larger. Therefore, the flexure shaft coupling can be prevented from increasing in size and the transmission torque can be increased without reducing the effects of the shaft center adjustment, buffering and vibration damping.

  In the case of a flexible shaft joint in which an annular disk stopper is inserted between adjacent coil springs, it is not necessary to provide a separate stopper mounting portion. Therefore, the flexible shaft joint has a simple structure and is lightweight.

  1 and 2 show a first best mode of the present invention. FIG. 1 is a sectional view of a flexible shaft coupling according to a first embodiment, and FIG. 2 is a front view thereof. The flexible shaft joint is mainly configured by the first hub 11, the second hub 21, the cover 31, the spring support pin 38, the helical coil spring 41, and the connecting bolt 51.

  The first hub 11 includes a flange 13 at the tip of a cylindrical hub body 12. The flange 13 is provided with eight spring holes 14 along the circumferential direction, and four connecting bolt holes 15 are provided on a pitch circle larger than the pitch circle of the spring holes 14. The spring hole 14 and the connecting bolt hole 15 are arranged point-symmetrically with respect to the axis of the first hub 11. The hub body 12 has a keyway cut inward, and a transmission shaft (both not shown) is connected to the shaft hole via a key. The spring holes 14 and the connecting bolt holes 15 are disposed on different pitch circumferences, but may be on the same pitch circumference. In order to minimize the unbalance of the rotation of the shaft joint, the spring hole 14 and the connecting bolt hole 15 (that is, the barrel coil spring 41 and the connecting bolt 51) are preferably arranged point-symmetrically with respect to the joint axis center line. .

  The second hub 21 is provided with a flange 23 at the tip of a cylindrical hub body 22. The hub main body 22 has a keyway cut inward, and a transmission shaft (both not shown) is connected to the shaft hole via a key. The outer peripheral portion of the front end surface of the flange 23 is an annular and tapered taper protrusion 24 protruding forward. The taper angle of the taper protrusion 24 is, for example, 10 degrees. A spring support pin hole 25 is provided on the front end surface of the flange 23 so as to correspond to the spring hole 14 of the flange 13 of the first hub 11, and corresponds to the connecting bolt hole 15 of the first hub flange 13. Thus, the connecting bolt screw hole 26 is provided.

  The cover 31 includes a cylindrical cover body 32. The front end portion of the cover body 32 is a tapered hole 33 in which the taper protrusion 24 of the second hub flange 23 fits, forms a taper inlay and tightens the second hub flange 23 and the cover body 32. Are fixed together. A cover annular portion 34 is provided at the rear end of the cover body 32. The first hub body 12 passes through the through hole 35 of the cover annular portion 34. The cover 31 is provided with a connecting bolt hole 36 so as to face the connecting bolt hole 15 of the first hub flange 13.

  The front end portion of the spring support pin 38 is inserted into the spring support pin hole 25 of the second hub flange 23. The connecting bolt 51 is screwed into the connecting bolt screw hole 26 of the second hub flange at the tip screw portion 52.

  The second hub 21 and the cover 31 are connected by a connecting bolt 51 at a portion between the second hub flange 23 and the cover annular portion 34. In a state where the second hub 21 and the cover 31 are connected, the tip of the spring support pin 38 is fitted in the spring support pin hole 25 of the second hub flange 23, and the rear end surface of the spring support pin 38 is the cover. It is in contact with the annular portion 34. Therefore, the spring support pin 38 is cantilevered by the second hub 21. The first hub body 12 passes through the through hole 35 of the cover annular portion 34, and the first hub flange 13 is housed inside the cover 31 so as to face the flange 23 of the second hub 21. Between the first hub flange 13 and the second hub flange 23, between the first hub flange 13 and the cover annular portion 34 of the cover 31, and between the outer peripheral surface of the first hub flange 13 and the inner peripheral surface of the cover body 32. Between the outer peripheral surface of the first hub body 12 and the inner peripheral surface of the through hole 35 of the cover 31, gaps a, b, c, d having sizes necessary for adjusting the axial center are provided. Yes.

  Eight of the helical coil springs 41 pass through the spring holes 14 of the first hub flange 13. The maximum outer diameter portion 42 of each helical coil spring 41 is fitted into the spring hole 14 of the first hub 11 by a clearance fit or an intermediate fit, and the minimum inner diameter portion 43 is fitted to the spring support pin 38 by an intermediate fit. Yes. The clearance between the spring hole 14 and the maximum outer diameter portion 42 of the coil spring 41 is −0.2 to + 15% of the maximum spring outer diameter. The size of the fit is determined by the rotational speed of the shaft coupling and the magnitude of the eccentricity between the drive shaft and the driven shaft connected to the shaft coupling.

  The cover 31 is attached to the second hub flange 23 by tightening the connecting bolt 51 until the rear end surface of the spring support pin 38 contacts the cover annular portion 34. The helical coil spring 41 is compressed and held in the coil axial direction between the second hub flange 23 and the cover annular portion 34. Therefore, the difference between the free length of the coil spring 41 and the protruding length of the spring support pin 38 from the second hub flange 23 is the spring compression amount. The amount of spring compression (or the length of the spring support pin 38) is set so that the coil spring 41 is deformed during torque transmission and adjacent coils come into contact with each other.

  The flexible shaft coupling 1 configured as described above has a torque in the order of the drive shaft, the first hub 11 to which the drive shaft is connected, the coil spring 41, the spring support pin 38, the second hub 21, and the second hub. Is transmitted to the driven shaft connected to 21 or vice versa. At this time, in the helical coil spring 41, a part of the middle portion between the large-diameter portion 42 and the small-diameter portion 43 of the spring is displaced in the inner diameter direction according to the magnitude of the transmission torque. Therefore, the opposite side is elastically deformed so as to extend in the outer diameter direction.

  The eccentricity of the transmission shaft (the radial error of the shaft center) is caused by the fact that the helical coil spring 41 is displaced in the spring radial direction by the clearance between the maximum outer diameter portion 42 and the spring hole 14 at first. After 42 contacts the inner peripheral surface of the spring hole 14, the barrel coil spring 41 is deformed in the radial direction and absorbed. The axial error is absorbed by the deformable coil spring 41 being deformed in the axial direction. Further, the declination is absorbed by the helical coil spring 41 being deformed in an oblique direction with respect to the spring axis.

  The shock and torsional vibration of the torque transmission system are absorbed and damped by the elastic deformation of the barrel coil spring 41 and the friction between adjacent coils. Torque transmission, adjustment of the shaft center error, shock absorption, and vibration absorption are simultaneously performed while the helical coil spring 41 is elastically deformed.

  In a state where the second hub 21 and the cover 31 are connected by the connecting bolt 51, the taper protrusion 24 of the second hub 21 forming the inlay portion can withstand the transmission torque in the taper hole 33 at the tip portion of the cover 31. I'm stuck in a fit. When the connecting bolt 51 is removed, the first hub 11 and the cover 31 can be detached from the second hub 21 as a unit. Accordingly, since it is not necessary to pull out the spring support pin 38, maintenance work such as inspection, repair, replacement, and grease replenishment of the coil spring 41 and the spring support pin 38 is facilitated.

  3 and 4 show the second best mode of the present invention. FIG. 3 is a sectional view of a flexible shaft coupling according to the second embodiment, and FIG. 4 is a front view thereof. In the best mode described below, members having the same members as those shown in FIGS. 1 and 2 are given the same reference numerals, and detailed descriptions thereof are omitted.

  The flexible shaft coupling 2 is mainly composed of a first hub 61, a second hub 71, a cover 81, a spring support pin 38, a helical coil spring 41, and a stopper bolt 91. In the flexible shaft coupling 2 of the best mode, the three stopper bolts 91 have both a function of connecting the second hub 71 and the cover 81 and a stopper function.

  The stopper bolt 91 is a through bolt, and the cylindrical portion is a stopper pin 93. Both end portions of the stopper pin 93 are fitted with the second hub flange 73 and the stopper bolt holes 76 and 86 of the cover annular portion 84 by an intermediate fit, and the clearance between the stopper pin 93 and the stopper bolt holes 76 and 86 is assembled. Is preferably close to 0 within the possible range. The number of stopper bolts 91 is suitably 1/6 to 1/2 of the helical coil spring 41.

  The clearance between the stopper pin 93 and the stopper bolt hole 65 of the first hub flange 63 is such that when the load exceeding the allowable load is applied to the barrel coil spring 41, the stopper pin 93 is fixed to the stopper bolt hole 65. It is set so as to contact the inner peripheral surface. The allowable load is determined based on the fatigue limit of the barrel coil spring 41, for example. When the load of the helical coil spring 41 reaches the allowable load, the stopper pin 93 comes into contact with the inner peripheral surface of the stopper bolt hole 65 of the first hub flange 61. The transmission torque is transmitted through the helical coil spring 41 and the spring support pin 38. When the load of the helical coil spring 41 exceeds the allowable load, the load is borne by the helical coil spring 41 and the stopper pin 93. Therefore, since the load applied to the drooping coil spring 41 does not exceed the allowable load, the drooping coil spring 41 is prevented from being damaged by fatigue.

  An O-ring groove 88 is provided on the inner peripheral surface of the cover through hole 85. The O-ring 89 inserted into the O-ring groove 88 prevents water and dust from entering the cover 81 from the outside. Further, grease is supplied into the cover 81 to lubricate the contact surfaces between the spring coils, between the coil spring 41 and the spring hole 64, and between the stopper pin 93 and the stopper bolt hole 65, and the first hub. 61 Prevents other members from rusting.

  5 and 6 show a third best mode of the present invention. FIG. 5 is a cross-sectional view of a third embodiment of a flexible shaft coupling, and FIG. 6 is a front view thereof. The flexible shaft joint 3 is mainly composed of a first hub 101, a second hub 111, a cover 121, a spring support bolt 130, a coil spring set 46, a disc stopper 138, and a stopper bolt 91.

  The spring support bolt 130 has a cylindrical support portion 132 as a cylindrical portion. Both end portions of the spring support portion 132 are fitted in the second hub flange 113 and the spring support bolt holes 115 and 126 of the cover annular portion 124 by an intermediate fit, respectively. The spring support bolt 130 is fitted by the second hub 111 and the cover 121. It is supported. The size of the clearance between the spring support portion 132 and the spring support bolt holes 115 and 126 is almost zero.

  The coil spring set 46 comprises a first barrel coil spring 47 and a second barrel coil spring 48, and nine groups are arranged along the circumferential direction. Each coil spring set 46 passes through the spring hole 104 of the first hub flange 103 and is supported by spring support bolts 130 so that two barrel-shaped coil springs 47 and 48 are arranged in series. The maximum outer diameter portion of each of the helical coil springs 47 and 48 fits into the spring hole 104 of the first hub flange 103 by a clearance fit, and the minimum inner diameter portion is an intermediate fit to the spring support portion 132 of the spring support bolt 130. It fits. Further, compression is performed between the second hub flange 113 and the cover annular portion 124 so that the coil springs 47 and 48, which are formed in the torque transmission, are deformed and adjacent coils come into contact with each other. A disc stopper 138 described below is inserted between the first barrel coil spring 47 and the second barrel coil spring 48, and one end surface of the barrel coil springs 47 and 48 is in contact with the disc stopper 138 surface. ing. The number of disk stoppers 138 is suitably 1/1 to 1/4 of the number of coil spring sets.

  The disk stopper 138 is composed of an annular disk, and is attached to each set of nine coil spring sets 46. The inner diameter side of the disk stopper 138 is intermediately fitted to the spring support portion 132 of the spring support bolt 130. The gap h between the outer peripheral surface of the disk stopper 138 and the inner peripheral surface of the spring hole 104 of the first hub flange 101 is such that when a load exceeding the allowable load is applied to the coil springs 47 and 48, the disk stopper The outer peripheral surface of 138 is set so as to contact the inner peripheral surface of the spring hole 104.

  The stopper bolt 91 is the same as that shown in FIGS. 3 and 4, and the cylindrical portion is a stopper pin 93. Both ends of the stopper pin 93 are fitted in the second hub flange 113 and the stopper bolt holes 116 and 127 of the cover annular portion 124 by an intermediate fit, and the stopper bolt 91 is supported by the second hub 111 and the cover 121. . The size of the clearance between the stopper pin 93 and the stopper bolt holes 116 and 127 is almost zero.

  The spring support bolt 130 passes through the spring support bolt hole 115 of the second hub flange 113, the coil springs 47 and 48, the disc stopper 138 and the spring support bolt hole 126 of the cover annular portion 124, and the stopper bolt 91 is connected to the second hub flange. The stopper bolt hole 116 of 113, the stopper bolt hole 105 of the first hub 101 and the stopper bolt hole 127 of the cover annular portion 124 are penetrated, and the second hub 111 and the cover 121 are connected by both bolts 130 and 91. The lengths of the spring support portion 132 of the spring support bolt 130 and the stopper pin 93 of the stopper bolt 91 are set so that the coil springs 47 and 48 that are the barrels are deformed when the torque is transmitted and the adjacent coils come into contact with each other. .

  In the flexible shaft joint 3 configured as described above, since the load at the time of torque transmission is applied to the two barrel coil springs 47 and 48, compared to that of one barrel coil spring of the same size. A torque twice as large can be transmitted. The flexible shaft joint 3 becomes longer in the axial direction by one spring, but the joint outer diameter is the same. Therefore, the moment of inertia of the joint is, for example, about 30 to 60% larger.

    7 and 8 show the fourth best mode of the present invention. FIG. 7 is a sectional view of the flexible shaft coupling 4 of the fourth embodiment, and FIG. 8 is a front view thereof. The flexible shaft coupling 4 is mainly configured by a first hub 141, a second hub 151, a cover 161, a spring support bolt 130, a coil spring set 46, and a disk stopper 138. Of these components, the spring support bolt 130, the coil spring set 46, and the disk stopper 138 are the same as those shown in FIGS. In this flexible shaft joint, all twelve bolts are made of spring support bolts 130, and a disk stopper 138 is provided on each bolt.

  The spring support bolt 130 passes through the spring support bolt hole 155 of the second hub flange 153, the coil springs 47 and 48, the disk stopper 138 and the spring support bolt hole 166 of the cover annular portion 164, and connects the second hub 151 and the cover 161. It is connected. The length of the spring support portion 132 of the spring support bolt 130 is set so that the coil springs 47 and 48 that are the barrels deform when the torque is transmitted and the adjacent coils come into contact with each other.

  In the flexible shaft coupling configured as described above, the helical coil spring set 46 and the disk stopper 138 are supported by the spring support bolt 130, and there is no stopper other than the disk stopper 138. Therefore, the flexible shaft coupling of this form has a good rotation balance and is suitable for a power transmission system that rotates at high speed.

  The present invention is not limited to the best mode described above. For example, the appropriate number of barrel coil springs, coil spring sets, disk stoppers and connecting bolts, spring support bolts and stopper bolts should be selected according to the magnitude of the transmission torque, the rotational speed of the shaft coupling, etc. Can do. Although the number of the helical coil springs constituting each coil spring set is two, it may be three or more. Further, a plurality of coil springs and disk stoppers may be supported by spring support pins.

It is a longitudinal cross-sectional view of the flexible shaft coupling which shows the 1st best form of this invention. It is a front view of the flexible shaft coupling shown in FIG. It is a longitudinal cross-sectional view of the flexible shaft coupling which shows the 2nd best form of this invention. It is a front view of the flexible shaft coupling shown in FIG. It is a longitudinal cross-sectional view of the flexible shaft coupling which shows the 3rd best form of this invention. It is a front view of the flexible shaft coupling shown in FIG. It is a longitudinal cross-sectional view of the flexible shaft coupling which shows the 4th best form of this invention. It is a front view of the flexible shaft coupling shown in FIG.

Explanation of symbols

1, 2, 3, 4 Flexible shaft coupling 11, 61, 101, 141 First hub 12, 72, 102, 142 First hub body 13, 63, 103, 143 First hub flange 14, 64, 104, 144 Spring Hole 15 Connection bolt hole 21, 71, 111, 151 Second hub 22, 72, 112, 152 Second hub body 25, 75 Spring support pin hole 26 Connection bolt screw hole 31, 81, 121, 151 Cover 32, 82, 122, 152 Cover body 34, 84, 124, 164 Cover annular portion 35, 85, 125, 165 Cover through hole 36 Connecting bolt hole 41, 47, 48 Coil spring 42 Spring maximum diameter portion 43 Spring minimum diameter portion 46 Coil Spring set 51 Connecting bolt 65, 76, 86, 105, 116 Stopper bolt hole 89 O-ring 115, 126 145, 155, 166 Spring support bolt hole

Claims (5)

A first hub flange having a first hub flange at the distal end of a cylindrical hub body and a transmission shaft coupled thereto, and a second hub flange having a first hub flange coupled at a distal end of the cylindrical hub body and coupled to the transmission shaft. A second hub flange having a cover annular portion at the rear end of the two hubs and the cylindrical cover body, the first hub body passing through the through hole of the cover annular portion and accommodating the first hub flange. A plurality of spring support pins supported by the second hub flange, and a plurality of spring holes provided in a circumferential direction in the first hub flange, respectively. A plurality of helical coil springs supported; and a connecting bolt for fixing the cover to the second hub flange; and between the first hub flange and the second hub flange, the first hub flange and the cover annular portion. Between the first hub flange Clearances of a size necessary for adjusting the axial center are provided between the cover main body and between the first hub main body and the through hole of the cover annular portion, and the first hub is interposed via the barrel coil spring. In a flexible shaft coupling in which torque is transmitted between the second hub and the second hub,
The tip of the spring support pin fits into a spring support pin hole provided in the second hub flange and is cantilevered by the second hub flange, and the helical coil spring has a maximum diameter portion fitted into the spring hole. It is fitted with an intermediate fit, the minimum inner diameter portion of the helical coil spring is supported by the spring support pin and fitted with an intermediate fit, and the rear end surface of the spring support pin is in contact with the cover annular portion, The shaped coil spring is compressed and held in the coil axial direction between the second hub flange and the cover annular portion so that the adjacent spring coil contacts when deformed during torque transmission. Flexible shaft coupling. The first hub flange has a plurality of stopper bolt holes arranged along the circumferential direction, and a plurality of stopper bolts having cylindrical portions as stopper pins penetrate the stopper bolt holes, respectively, The flexible shaft coupling according to claim 1, which is supported by a cover annular portion. A plurality of spring sets are constituted by a plurality of coil springs, and the spring sets are inserted into the spring holes so that end faces of adjacent coil springs are in contact with each other and arranged in series, and are supported by the spring support pins. The flexible shaft coupling according to claim 1 or 2, wherein 4. The flexible shaft coupling according to claim 3, wherein an annular disc stopper is inserted between the adjacent coil springs and held by the spring support pin. The deflection shaft according to any one of claims 1 to 4, wherein a clearance between the maximum diameter portion of the helical coil spring and the spring hole is -0.2 to + 15% of the maximum diameter portion of the helical coil spring. Fittings.

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