JP3179435B2 - Flexible shaft coupling - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flexible shaft coupling, and more particularly to a flexible shaft coupling used in a unidirectional high-speed transmission system. The flexible shaft coupling according to the present invention is used for a pump, a turbine, a paper machine, a printing machine, a machine tool, particularly a main shaft of a machining center, and the like.

[0002]

2. Description of the Related Art High-speed rotation is required in a drive system such as a pump or a turbine that requires high-speed rotation, or in a transmission system such as a main shaft of a machine tool. Further, it is desired that maintenance such as lubrication is unnecessary. For such applications,
2. Description of the Related Art Disk-type flexible joints in which a number of metal leaf springs are stacked are widely used. Although various types of disk-type flexible shaft couplings are commercially available, products of Thomas Company, Darnas Plug Company and the like are widely used. However, the disk-type flexible shaft coupling has the following disadvantages. 1) Since half of the bolts for fastening the laminated leaf springs are configured to transmit torque, the transmitted torque is smaller than the outer diameter. 2) Since the fastening bolt is supported in a cantilever manner, the support is unstable. 3) If there is a declination between the drive shaft and the driven shaft, no matter how many stacked leaf springs are stacked, only one leaf spring at each end acts on the tension, and the other leaf springs act to transmit torque. Not involved in Therefore, the greater the deflection angle, the more fatigue failure occurs. The bending stress of the leaf springs on both sides responsible for torque transmission is
It changes according to the angular position during one rotation. 4) Since the leaf spring is thin, the spring plate thickness of the shaft coupling with an outer diameter of up to about 250 mm is often about 0.2 to 0.4 mm. Even if the tightening torque is specified and the bolt is tightened, the leaf spring warps. The bolt loosens during use and needs to be tightened. 5) Since the spring constant in the radial direction is small, a shaft coupling having a long spacer is displaced in the vertical direction due to the weight of the spacer, and whirling vibration is likely to occur.

[0003]

SUMMARY OF THE INVENTION The present invention is an improvement over the above-mentioned drawbacks of the disk-type flexible shaft coupling, which has a small number of parts and a large transmission torque while being compact.
An object of the present invention is to provide a flexible shaft coupling that is easy to maintain.

[0004]

The flexible shaft coupling of the first invention mainly comprises a driving hub and a driven hub. The drive-side hub has a cylindrical first hub body to which a drive shaft is connected, and one end of the first hub body with the first hub body.
Along the outer circumference of the first hub body with a radial gap between
A plurality of arc-shaped first leaf springs are provided. The first leaf spring has a front end portion serving as a fastening portion projecting from the first hub main body in the axial direction, and a rear end portion serving as a connection portion integrated with the first hub main body. Front and rear ends of adjacent first leaf springs
A gap is provided in the circumferential direction between the first and second portions. The driven hub includes a cylindrical second hub body to which a driven shaft is connected, and a driven hub including the same number of arc-shaped second leaf springs as the first leaf spring. The first leaf spring and the second leaf spring extend in opposite directions about the fastening portion, and are fastened by bolts penetrating the fastening portion in a state where the fastening portions are in contact with each other.

[0005] The flexible shaft coupling according to the present invention, the direction of the leaf springs, that is, the rotation direction during use (ie, the rotation direction during use) so that a tensile force along the circumferential direction is applied to the first leaf spring and the second leaf spring during torque transmission. Forward rotation direction) is determined. During normal operation, the flexible coupling is used so that torque acts in the forward rotation direction. When torque is applied in the forward rotation direction, the torque is transmitted from the driving hub to the driven hub via the first leaf spring, the bolt, and the second leaf spring in that order.

As described above, since the fastening portion of the leaf spring projects from the hub body in the axial direction, a gap is generated between the fastened first leaf spring and the fastened second leaf spring. Due to this gap, the first leaf spring and the second leaf spring can be elastically deformed in the axial direction. The deflection angle and the axial displacement of the flexible shaft coupling are adjusted mainly by elastic deformation of the leaf spring in the axial direction. The eccentricity of both the driven and driven shafts is adjusted by the radial elastic deformation of both leaf springs, but the amount of adjustment is structurally smaller than the eccentric angle.
At the time of rotation in the reverse direction, a compressive force acts on both leaf springs, and the adjustment of the shaft center is the same as that at the time of rotation in the forward direction. However, if the compressive force exceeds the dangerous load, buckling occurs in the leaf spring. Therefore, it is necessary to use the flexible shaft coupling under the dangerous load.

In the flexible shaft coupling according to the present invention, the hub body and the leaf spring are integrated, and each leaf spring is constituted by one leaf spring (not a laminated leaf spring). Therefore, the flexible shaft coupling is compact and has few parts.
Since the moment of inertia is small, high-speed rotation is possible.
Both leaf springs are fastened by bolts, and the drive side hub and the driven side hub are integrally formed, and the length of the leaf spring elastically deforming is between the bolts of the laminated disk type flexible shaft joint. The thickness of one sheet is thicker than that of the laminated leaf spring, but the length of the spring is longer, so that it has the same degree of flexibility as the laminated disk-type flexible shaft joint. Than you transfer each torque of each leaf spring in the present invention,
Large torque can be transmitted as compared with the disk-type flexible shaft coupling. For example, if there are three leaf springs and the bolt pitch diameter and the allowable transmission force of the leaf springs are the same, the flexural joint of the present invention is 1.5 times as large as a four bolt bolt-type flexural joint. It can transmit torque. Further, fatigue damage of the leaf spring and loosening of the bolt, which are liable to occur in the disk-type flexible shaft joint used in applications having a large deflection angle, do not occur.

[0008] A flexible shaft coupling according to a second aspect of the present invention mainly comprises the driving hub and the driven hub, and a spacer. In the spacer, a third leaf spring fastened to the first leaf spring of the drive side hub and a fourth leaf spring fastened to the second plate are provided at both ends of the cylindrical spacer body. The third leaf spring and the fourth leaf spring each have the same shape and dimensions as the first leaf spring.
The first leaf spring and the third leaf spring, and the second leaf spring and the fourth leaf spring respectively extend in opposite directions about the fastening portion, and penetrate the fastening portion in a state where the fastening portions are in contact with each other. Bolts.

In the flexible shaft coupling according to the first invention, a pair of elastic elements is constituted by the leaf springs of the driving hub and the driven hub. On the other hand, in the flexible shaft coupling of the second invention, two sets of elastic elements are constituted by the leaf springs at both ends of the spacer and the leaf springs of the driving hub and the driven hub. Therefore, the flexible shaft coupling of the second invention can adjust the axial displacement and the declination twice as large as those of the first invention. Further, the spacers can be obliquely oblique to each other to adjust the parallel displacement of the drive side hub and the driven side hub by the declination of each elastic element.

[0010]

1 to 4 show a flexible shaft coupling according to a first invention. The flexible shaft coupling 10 mainly includes a drive-side hub 11 and a driven-side hub 21. The drive side hub 11 includes a cylindrical first hub body 12 to which a drive shaft is connected. One end of the first hub body 12 extends rightward (see FIG. 2) along the outer periphery.
A plurality of arc-shaped first leaf springs 14 are provided with a gap a in the circumferential direction. The distal end of the first leaf spring 14 is a fastening portion 15 that projects from the first hub body 12 in the axial direction, and has a bolt hole 16 that has been reamer finished.
The rear end portion is a connecting portion 17 integrated with the first hub body 12. Between the first hub body 12 and the first leaf spring 14,
A radial gap b is provided. The driven hub 21 has the same structure as the driving hub 11 and includes a cylindrical second hub body 22 to which a driven shaft is connected.

The driven hub 21 has the same shape as the driving hub 11.
The dimensions are the same, and as can be seen in FIG.
Is provided with three arc-shaped second leaf springs 24 extending in the same direction as the first leaf springs 14 along the outer circumference with a gap a in the circumferential direction. The distal end of the second leaf spring 24 is a fastening portion 25 protruding in the axial direction, and has a bolt hole 26 that has been reamer finished. The rear end is the second
It is a connecting portion 27 integral with the hub body 22. A radial gap b is provided between the second hub body and the second leaf spring. The first leaf spring 14 and the second leaf spring 24 face each other as shown in the perspective view of FIG. 4, and the fastening portions 15 and 25 of these leaf springs 14 and 24 are in contact with each other. The drive hub 11 and the driven hub 21 are fastened by the reamer bolts 29 through the bolt holes of the fastening portions 15 and 25. In a state where the driving side hub 11 and the driven side hub 21 are fastened, for example, when the leaf springs 14 and 24 are viewed from the driving side, these leaf springs 14 and 24 are circumferentially opposite to each other around the reamer bolt 29. Extending.

The fastening portions 15, 25 of the first leaf spring 14 and the second leaf spring 24 protrude in the axial direction about twice the thickness of the spring plate. A gap c occurs. The gap c allows the leaf springs 14 and 24 to freely elastically deform when adjusting the axial displacement and the declination. Further, since the fastening portions 15 and 25 protrude in the axial direction and have a large thickness, the bolt holes 16 and 2
6, the strength of the fastening portions 15, 25 of the leaf springs 14, 24 is reduced. As is clear from FIG.
The amount of axial center adjustment by the elastic deformation of the spring 24 is determined by the total length of the leaf springs from the connection portion 17 of the first leaf spring 14 to the connection portion 27 of the second leaf spring 24 via the fastening portion 15.
The sum L of the effective lengths of the pair of leaf springs 14 and 24 fastened by the reamer bolt 29 is substantially half the pitch circumference of the reamer bolt 29 as shown in FIG. In a disk-type flexible shaft coupling, the effective length of a disk (leaf spring) is the maximum in a four-bolt system. In the four-bolt method, since the tightening bolt is provided at a position of 90 °, the effective length of the disk is equal to or less than １ ／ the pitch circumference of the tightening bolt. Accordingly, the effective length of the leaf spring of the present invention is twice or more that of a commercially available disk-type flexible shaft coupling, and a large flexure can be obtained. Even if the thickness of the spring plate of the present invention is greater than the thickness of one laminated leaf spring of the conventional disk-type flexible shaft coupling, the same amount of deflection can be obtained. As shown in FIG. 4, if the connection fillet portions of the connection portions 17 and 27 of the respective leaf springs to the hub main bodies 12 and 22 are formed as large radius portions r, stress concentration is reduced and strength is increased.

The driving hub 11 and the driven hub 21 are
In any case, it is necessary to select a material that can sufficiently perform the action of the spring and heat-treat it. Since a part of the hub material acts as a leaf spring, SUP-9, S
It is desirable to use a spring material such as UP-10. In order to produce performance close to these spring materials at low cost, S
When using a carburized material such as CM-415 and carburizing and quenching the plate spring part and heat-treating it to Hs of about 55 to 65, the same performance as that of the SUS material disk of the disk-type flexible shaft coupling is sufficiently possible. is there. For large size flexible shaft couplings,
The drive side hub and the driven side hub are made of structural steel, and the leaf spring portions are separately manufactured using SUP-9, SUP-10, etc., and the flange-shaped leaf spring portions are shrink-fitted or welded to the hub body. It is effective to form a single piece by machining an object or the like.

The flexible shaft coupling according to the first aspect of the invention configured as described above operates as follows. As shown in FIG. 2, the drive shaft and the driven shaft are applied to the flexible shaft coupling 10 so that a torque is applied in a counterclockwise direction, that is, a tensile force is applied to the first and second leaf springs 14 and 24 in a circumferential direction. (Both not shown) are connected. The torque is transmitted from the driving hub 11 to the driven hub 21 through the first leaf spring 14, the reamer bolt 29, and the second leaf spring 24 in this order. In this flexible shaft coupling 10, the number of elastic elements that transmit torque is three leaf springs fastened by reamer bolts 29.
A set of leaf springs transmits torque. So, for example,
Assuming that the bolt pitch diameter and the leaf spring fatigue strength are the same as those of the disk-type flexible shaft coupling, a torque 1.5 times larger than that of the 4-bolt disk-type flexible shaft coupling can be transmitted.

The displacement of the axis between the drive shaft and the driven shaft is adjusted as follows. The axial displacement is determined by the displacement of the drive side hub 11 and the driven side hub 2 in both the extension and compression directions of the shaft.
The three sets of leaf springs 14 and 24 fastened by the one reamer bolt 29 flex and adjust uniformly in the axial direction. The deflection angle varies in the amount of deformation depending on the rotational position of the flexible shaft coupling, but is adjusted mainly by the axial deformation of the leaf spring and the elastic deformation accompanied by a slight torsional deformation. The amount of eccentricity is extremely small compared to the axial displacement and the eccentric angle, but is adjusted by the radial deflection of each of the three sets of leaf springs 14, 24.

When speed control is performed, torque may act on the flexible shaft coupling 10 in the opposite direction due to sudden braking or the like. In such a case, the leaf springs 14, 24 receive a compressive force along the circumferential direction, and if the compressive force exceeds a dangerous load, the leaf springs 14, 24 may buckle. As shown in FIGS. 2, 4 and 5, a claw 18 is provided on the drive side hub 11 and a claw groove 28 is provided on the driven side hub 24, respectively. An appropriate gap is provided between the claw 18 and the claw groove 28 within a range that does not affect the axial center adjustment. When the leaf springs 14, 24 are deformed by buckling due to excessive compressive force, the pawl 18
To support the load and prevent breakage of the leaf springs 14 and 24 due to buckling. Gap d between claw 18 and side wall of claw groove 28
Is set to a minimum within a range that does not interfere with the deflection angle adjustment, and is set so as not to be affected by breakage due to buckling. By providing the crown 19 in contact with the side wall of the claw groove 28 on the side surface of the claw 18, it is possible to adjust the deflection angle and reduce the backlash in the compression direction.

FIGS. 6 and 7 show the flexible shaft coupling of the second invention, respectively. Members similar to those of the flexible shaft coupling shown in FIGS. 1 to 4 are denoted by the same reference numerals, and description thereof will be omitted. The flexible shaft coupling 30 mainly includes a drive-side hub 11, a driven-side hub 21, and a spacer 31. The drive side hub 11 and the driven side hub 21
This is the same as that of the flexible shaft coupling 10 of the invention of the present invention. The spacer 31 includes a cylindrical spacer body 32, three arc-shaped third leaf springs 34, and three arc-shaped fourth leaf springs 41. The third leaf spring 34 is the spacer body 3
2 extends in the same direction as the first leaf spring 14 along the outer periphery of the spacer body 32 at one end. Spacer body 32
A radial gap “b” is provided between the first and second leaf springs 34. The distal end portion of the third leaf spring 34 is a fastening portion 35 projecting from the spacer body 32 in the axial direction, and has a bolt hole 36 that has been reamer finished. The rear end of the third leaf spring 34 is connected to the connecting portion 3 integrated with the spacer body 32.
It is 8. The fourth leaf spring 41 extends in the same direction as the second leaf spring 24. The distal end of the fourth leaf spring 41 is a fastening portion 42 protruding from the spacer body 32 in the axial direction, similarly to the third leaf spring 34, and has a bolt hole 43 that has been reamer finished. A radial gap b is provided between the spacer body 32 and the fourth leaf spring 41.
The rear end of the fourth leaf spring forms a connecting portion 45 integrated with the spacer body 32. And the first facing each other
The fastening portion of the leaf spring 14 and the fastening portion of the third leaf spring 34 and the fastening portion of the second leaf spring 24 and the fastening portion of the fourth leaf spring 41 are fastened by reamer bolts 47, respectively. Are fastened to both ends of the spacer body 32.

The flexible shaft coupling 30 constructed as described above
Operates similarly to the flexible shaft coupling 10 of the first invention. However, since the flexible shaft coupling 30 includes the first to fourth four sets of leaf springs 14, 24, 34, and 41, the axial displacement and the deflection angle are about twice as large as those of the flexible shaft coupling 10. Can be adjusted. Further, it is also possible to adjust the parallel displacement due to the oblique crossing of the spacer body 32. At this time,
The leaf springs are deviated from 14, 34, and the leaf springs 24,
An angle of 41 is generated to cause obliqueness in the spacer body 32. At this time, the leaf springs 14, 24, 34,
The elastic deformation of 41 mainly deforms in the axial direction and is slightly twisted.

The drive side hub 11 and the driven side hub 2
If the strength of the leaf springs 14 and 24 is set to be higher than the strength of the leaf springs 34 and 41 of the spacer 30, and if the fatigue failure occurs, the spacer 30 is designed to be always on the spacer side.
You only need to replace it.

FIG. 8 shows another embodiment of the present invention. The same members as those of the flexible shaft coupling 30 shown in FIGS. 6 and 7 are denoted by the same reference numerals, and description thereof will be omitted. In this flexible shaft coupling 50, the drive side hub 51 and the driven side hub 52 are flanges 53 instead of leaf springs. The flange 53 has higher rigidity than the leaf springs 34 and 41. Further, a flange having no spring action can be used. The flexible joint 50 is used when the centering accuracy of the drive shaft and the driven shaft is high, or when the deflection and parallel displacement are small and the axial displacement is small. When the leaf spring is broken, only the spacer 31 needs to be replaced. When a shear bolt is required, it may be installed only on one of the flanges, for example, only on the drive side hub 51, and the flexible shaft coupling 50 can stably fix the shear bolt to the flange. For disk type shaft couplings,
When installing shear pins or shear bolts, they are often installed on spacers, and there are restrictions on space,
In addition, the cost increases. In the flexible shaft coupling 10 shown in FIGS. 1 to 4, one of the drive side hub 11 and the driven side hub 21 may be a flange.

FIG. 9 shows that the distance between the driving side hub and the driven side hub is large in the flexible shaft coupling shown in FIG.
Fig. 4 shows a flexible shaft coupling when a long spacer is required. The spacer 54 includes a spacer driving side hub 55, a spacer driven side hub 56, and an intermediate shaft 58. The spacer driving hub 55 and the spacer driven hub 56 are fastened to the driving hub 55 and the driven hub 56 by reamer bolts 47, respectively. The leaf springs 57 of the spacer driving side hub 55 and the spacer driven side hub 56 are the same as the leaf springs 34 and 41 of FIG. The intermediate shaft 58 is connected to the spacer driving side hub 5 via a key 59.
5 and the spacer driven hub 56. By using the intermediate shaft 58, the cost and the moment of inertia of the flexible shaft coupling can be reduced. Generally, when the length of the spacer is long (1m or more)
In many cases, an intermediate shaft spacer is used.

FIGS. 10 and 11 show another embodiment of the present invention, particularly another example of a leaf spring. In this example, the drive-side hub and the driven-side hub are simply referred to as a hub. The hub 60 has a flange 62 at the tip of a hub body 61. An annular leaf spring main body 63 is shrink-fitted to an end of the flange 62 and fixed with a bolt 69. The leaf spring body 63 includes an annular base portion 64 and three arc-shaped leaf springs 65. The distal end of the leaf spring 65 is a fastening portion 66 protruding from the annular base 64 in the axial direction, and has a bolt hole 67 that has been reamer finished. Leaf spring 65
The rear end is a connecting portion 68 integral with the base 64. The leaf spring 65 is provided with a gap a in the circumferential direction and a radial gap b with the base 64. Leaf spring 65
Is determined so that a tensile force acts when torque is applied to the flexible shaft coupling.

In this flexible shaft coupling, since the hub body 61 can be made of structural steel and the leaf spring body 63 can be made of a spring steel plate, the cost can be reduced in the case of a large flexible shaft coupling. When the leaf spring 65 is damaged, the leaf spring body 63 may be replaced. This structure can also be applied to the spacer type and intermediate shaft type flexible shaft couplings.

FIGS. 12 and 13 show still another embodiment of the present invention. The flexible shaft coupling 70 includes a drive-side hub 71, a driven-side hub 81, two thrust flanges 90,
And two sets of ring spring-type fastening elements (locking elements) 95. The drive side hub 71 includes a cylindrical first hub body 72 to which a drive shaft is connected. First
A stopper 7 protruding in the inner diameter direction at one end of the hub body 72
3 are provided. Stopper 7 of first hub body 72
3 extending along the outer periphery on the outer diameter side of the end provided with
Four arc-shaped first leaf springs 75 are provided with a gap a in the circumferential direction and a gap b in the radial direction. First leaf spring 75
Is a fastening portion 76 protruding in the axial direction,
Bolt holes 77 with reamer finish are open. First
The rear end of the leaf spring 75 forms a connecting portion 79 integrated with the first hub body 72. The driven hub 81 is a driving hub 71.
The second hub body 82 is provided with a stopper 83 and four second leaf springs 85. Second
The leaf spring 85 extends in the same direction as the first leaf spring 75 along the outer circumference. The thrust flange 90 has a thrust portion 92 that fits on the inner diameter sides of the first hub body 72 and the second hub body 82. The ring spring type fastening element 95 is formed by fitting two ring springs 96 and 97 each having a trapezoidal cross section.

The driving-side hub 71 and the driven-side hub 81 configured as described above are connected to a first leaf spring 75 and a second leaf spring 85.
Are faced to each other and fastened by reamer bolts 98 at the fastening portions 76 and 87 of the leaf springs 75 and 85. Further, a wheel spring type fastening element 95 is inserted between the drive shaft and the drive side hub 71, and the thrust flange 90 is tightened to the drive side hub 71 side by the fastening bolt 99, and the wheel spring fastening element 95 is driven by the thrust portion 92. Press against stoppers 73 and 83 of side hub 71. The drive side hub 71 is held on the drive shaft by the wedge action of the pressed ring spring type fastening element 95. Similarly, the driven hub 81 is held on the driven shaft.

FIG. 14 shows another embodiment in which the leaf springs 101 and 102 are fastened to each other. Leaf springs 101, 102
Is a shear bolt 103, and a groove 104 is formed at a position where the bolt is joined to the leaf spring.
When the transmission torque reaches the set torque for breaking the shear bolt, the shear bolt 103 breaks to disconnect the drive-side hub and the driven-side hub, thereby preventing the drive device or the driven device from being damaged.

When the shear bolt 103 is fastened, the leaf springs 101 and 102 are bent so that when the shear bolt 103 is broken, the joining surfaces of the leaf springs 101 and 102 are separated from each other in the axial direction to form a gap (for example, 2 mm). Not conclude. By doing so, when the shear bolt 103 is broken, it is possible to avoid damaging the joint surfaces of the leaf springs 101 and 102 with the broken surface, which is extremely effective for reuse.

[0028] In general, a disk-type flexible shaft coupling, when shear pins or Shiyaboruto is required, usually of being provided to the spacer portion, the structure becomes complicated and the cost becomes high. However, in the flexible shaft coupling according to the present invention, a shear bolt may be used instead of the reamer bolt, so that it is not necessary to take special measures in terms of design, which is advantageous in terms of cost.

Recently, a flexible shaft coupling used for a machine tool, particularly a spindle of a machining center, has a 10,000 rp.
m or more high-speed rotation is required in many cases,
Also, noise due to high-speed rotation is a problem. For example,
In the disk-type flexible shaft coupling, the laminated plate of the disks is fastened in a cantilever state with bolts, so that the heads and nuts of the bolts protrude in the axial direction, causing wind noise. FIG. 1
2 has a similar problem.

FIG. 15 shows a structure of a fastening portion for reducing wind noise, and the basic structure is the same as the flexible shaft coupling shown in FIG. Hub body 112 of drive side hub 111
Has a first leaf spring 114 at the distal end. The fastening portion 115 of the first leaf spring 114 is thicker in the axial direction than that shown in FIG. Fastening portion 1 of second leaf spring 124 provided on hub body 122 of driven hub 121
25 is similarly thicker. The fastening portions of the first leaf spring 114 and the second leaf spring 124 are fastened with hexagonal reamer bolts 129 so that the bolts and the heads of the bolts do not project from the fastening portions. Therefore, the generation of wind noise is very small, and is suitable for high-speed rotation. When the first leaf spring 114 and the second leaf spring 124 are fastened by fastening with the reamer bolt 129, it is possible to prevent the bolt from being loosened most at high speed rotation.
The structure of the fastening portion can be used for, for example, the flexible shaft couplings shown in FIGS. 1 and 6 other than the flexible shaft coupling shown in FIG.

[Brief description of the drawings]

FIG. 1, showing an embodiment of the first invention, is a cross-sectional view of a flexible shaft coupling.

FIG. 2 is a right side view of the joint shown in FIG.

FIG. 3 is a plan view of a fastening portion of the joint.

FIG. 4 is a perspective view of a drive side hub and a driven side hub of the joint.

FIG. 5 is an enlarged plan view showing claw portions of a driving side hub and a driven side hub.

FIG. 6 shows a form of the second invention, and is a cross-sectional view of a flexible shaft coupling.

FIG. 7 is a view taken in the direction of arrows AA in FIG. 6;

FIG. 8 shows another embodiment of the present invention, and is a cross-sectional view of a flexible shaft coupling.

FIG. 9 shows still another embodiment of the present invention, and is a cross-sectional view of a flexible shaft coupling.

FIG. 10 is a sectional view showing another embodiment of the hub.

FIG. 11 is a left side view of the hub.

FIG. 12 shows another embodiment of the first invention, and is a cross-sectional view of a flexible shaft coupling.

13 is a left side view of the joint shown in FIG 2.

FIG. 14 is a sectional view showing an example in which hubs are connected by a shear bolt.

FIG. 15 is a sectional view showing another example of the structure of the fastening portion.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 Flexible shaft coupling 58 Intermediate shaft 11 Drive side hub 60 Hub 12 1st hub main body 61 Hub main body 14 1st leaf spring 62 Flange 15 Fastening part 63 Leaf spring main body 17 Connection part 65 Leaf spring 21 Driven side hub 70 Flexural joint 22 2nd hub body 71 drive side hub 24 2nd leaf spring 72 1st hub body 25 fastening part 75 1st leaf spring 27 connection section 81 driven hub 29 reamer bolt 82 2nd hub body 30 flexible shaft coupling 85 2nd leaf spring REFERENCE SIGNS LIST 31 spacer 95 wheel spring-type fastening element 32 spacer body 103 shear bolt 34 third leaf spring 104 groove 41 fourth leaf spring 111 drive-side hub 50 flexible shaft coupling 114 first leaf spring 51 drive-side hub 115 fastening portion 52 driven-side hub 121 Driven hub 53 Flange 124 Second leaf spring 54 Spacer 125 Tightening Part 55 spacer drive side hub 129 hexagon socket Rimaborito 56 spacer driven side hub

Continuation of the front page (56) References JP-A-52-110357 (JP, A) JP-A-8-232976 (JP, A) JP-A-7-63227 (JP, A) JP-A-2-113125 (JP) , A) Japanese Utility Model Hei 6-51564 (JP, U) Japanese Utility Model Showa 50-80655 (JP, U) Japanese Utility Model Utility Model 53-120659 (JP, U) Japanese Utility Model Utility Model 4-74741 (JP, U) 4-502663 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16D 3/50 F16D 3/56 F16D 3/74 F16D 3/76-3/77

Claims (3)

(57) [Claims] A cylindrical first hub body to which a drive shaft is connected, and one end of the first hub body between one end of the first hub body and the first hub body.
Extending along the outer periphery of the first hub body with a radial gap
A plurality of arc-shaped first leaf springs, the first leaf springs each having a distal end serving as a fastening portion projecting from the first hub main body in the axial direction, and a rear end extending integrally with the first hub main body. It is a connecting part , between the front end and the rear end of the adjacent first leaf spring.
A driven hub including a drive-side hub provided with a circumferential gap, a cylindrical second hub body to which a driven shaft is connected, and the same number of arc-shaped second leaf springs as the first leaf spring. A first hub, wherein the first leaf spring and the second leaf spring extend in opposite directions about the fastening portion, and are fastened by bolts penetrating the fastening portion in a state where the fastening portions are in contact with each other. And flex shaft coupling. 2. A driving hub and a driven hub according to claim 1, and a spacer, wherein a first of said driving hubs is provided.
A third leaf spring and a fourth leaf spring similar to the leaf spring are provided at both ends of the cylindrical spacer body, respectively.
The leaf spring and the third leaf spring, and the second leaf spring and the fourth leaf spring, respectively, extend in opposite directions about the fastening portion, and are fastened by bolts penetrating the fastening portion in a state where the fastening portions are in contact with each other. A flexible shaft coupling characterized in that: 3. A cylindrical first hub main body to which one of a drive shaft and a driven shaft is connected, and a first hub having a radial gap between one end of the first hub main body and the first hub main body. A plurality of arc-shaped first leaf springs extending along the outer periphery of the main body are provided, the first leaf springs each having a distal end portion serving as a fastening portion projecting from the first hub main body in the axial direction, and a rear end portion having a second end portion. A first connecting portion integrally formed with the hub body, wherein a circumferential gap is provided between the connecting portion and the fastening portion of the adjacent first leaf spring;
A second hub body having a cylindrical shape, to which the other of the drive shaft and the driven shaft is connected, and a second hub having a flange provided at one end of the second hub body, for fastening the first leaf spring; part of the distal end surface and the flexible joint of the first hub and second hub in a state where the flange surface is in contact with the second hub, characterized in that it is fastened by bolts passing through the fastening portion and the flange.