JP2014202271A - Shaft coupling - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a shaft coupling capable of performing its fitting to a shaft and a movable machine element rapidly, easily and positively and assuring a sufficient torque transmitting capability, high rigidity and durability.SOLUTION: A shaft coupling 1 comprises: an inner tapered ring 11 formed with a male thread part 11c and a tapered surface 11d at its outer circumference, having a slit 11e and outwardly fitted to a shaft; an outer tapered ring 12 formed with a front inner fitted part 12c at its outer circumference and a tapered surface 12d at its inner circumference and having a slit 12e and a rear inner fitting part 12f internally fitted to a gear; a rear cam 13 having the front inner fitted part 12c at a through-hole 13a and having a cam surface 13c and an acting surface 13f at its circumferential edge part; a front cam 14 having a female thread part 14a to which the male thread part 11c is engaged, a cam surface 14c and a flat surface 14f, forming a prescribed angle at the flat surface 14f, passing through a side surface 14g and punched with a through-hole 14h having a female thread part 14i formed there; and a fastening bolt 15 threadably engaged with the female thread part 14i, protruded from the flat surface 14f according to a thread displacement to press against the acting surface 13f.

Description

  The present invention relates to a shaft coupling that fixedly couples a shaft and movable mechanical elements such as gears, sprockets, pulleys, wheels, and levers.

  A conventional shaft coupling includes an inner ring (inner taper ring) that includes an axial slit and is externally fitted to the shaft and has a tapered surface on the outer periphery and a threaded portion that continues to the smaller diameter side, and a rotating body (movable machine element). And a ring-shaped groove formed in the inner surface on the side having a smaller inner diameter and a ring spring housed in the outer circumferential groove and divided into four in the circumferential direction. Some have an outer ring (outer tapered ring) and a tightening nut that is screwed into a threaded portion of the inner tapered ring and has an annular protrusion that engages with an annular groove of the outer tapered ring (for example, (See Patent Document 1). Hereinafter, this technique is referred to as a first conventional example.

  Further, in the conventional shaft coupling, an inner taper is achieved by wedge-engaging the fastening taper surfaces of the fastening ring interposed between the inner race (inner taper ring) and the outer race (outer taper ring). In some cases, the shaft and the rotating body (movable machine element) are fastened with a surface pressure generated by expanding the outer tapered ring while reducing the diameter of the ring. In this shaft coupling, one axial end surface of the inner taper ring or the outer taper ring is formed as an axial pressing taper surface inclined with respect to a plane perpendicular to the shaft.

  The shaft coupling is provided on the other of the clamping ring formed with the axial pressing taper surface complementary to the axial pressing taper surface and the inner taper ring or the outer taper ring, and the axial pressing taper of the clamping ring is provided. A cylindrical portion that is screwed into a sleeve having a flange portion in contact with an end surface opposite to the surface and a cylindrical portion located on the outer peripheral side of the tightening ring, and a radial screw hole formed in one of the cylindrical portion or the tightening ring The fastening ring has a single fastening bolt (a fastening bolt) for moving the fastening ring in the radial direction (see, for example, Patent Document 2). Hereinafter, this technique is referred to as a second conventional example.

  Further, in the conventional shaft coupling, a mounted member (movable machine element) is attached to the outer peripheral portion and inserted into the outer peripheral portion of the support shaft (shaft), and the outer peripheral portion of the shaft An inner sleeve (inner taper ring) that is inserted and fitted into the outer taper ring by a wedge action, a male screw part formed at one end part of the inner taper ring protruding from one end part of the outer taper ring, and a large number of outer peripheral parts An annular nut member that is formed at equal intervals and is screwed into the male threaded portion of the inner taper ring, and an outer taper ring that is rotatably provided near the outer periphery of the nut member so as to be orthogonal to the axis Some of them are provided with screw members (clamping bolts) which are oriented in the direction and mesh with the tooth portions.

  In this shaft coupling, the nut member rotates in a predetermined direction through the tooth portion in accordance with the rotation operation of the tightening bolt, and is screwed and displaced along the male screw portion, thereby pulling the inner tapered ring into the outer tapered ring. The wedge action is generated, and the outer taper ring is fastened to the shaft together with the inner taper ring (see, for example, Patent Document 3). Hereinafter, this technique is referred to as a third conventional example.

Japanese Utility Model Publication No. 3-15858 (Claim 1) Japanese Patent No. 3319811 (Claim 1) JP 2007-85365 A (Claim 1)

  The first conventional example described above has a problem that a large tool (for example, a torque wrench) matched to a large-diameter tightening nut is required. Further, in the first conventional example described above, since the tightening nut is tightened with a large torque, there is a possibility that the shaft or the movable machine element may rotate together, and it is difficult to fix at an appropriate position. Along with the tightening operation, a large torsional torque is applied to the shaft and the shaft may be damaged. Therefore, it is necessary to provide a detent means for preventing unnecessary rotation of the tightening nut.

  Further, in the above-described second conventional example, since it is necessary to interpose a plurality of fastening rings composed of an inner ring and an outer ring between the inner tapered ring and the outer tapered ring, the number of parts is large and the shaft coupling is expensive. Become. In the second conventional example described above, it takes time to interpose the fastening ring between the inner taper ring and the outer taper ring. If installation is completed while riding on another set of outer rings, the device may break down due to the eccentric motion of the movable machine elements, or the tightening bolts may loosen due to vibrations caused by long-term use, etc. There is a risk of falling.

  Furthermore, in the above-described second conventional example, when the tightening bolt is screwed more than necessary, the tightening ring may be excessively attracted to the tightening bolt and deformed into an elliptical shape. In this case, the force that presses the inner taper ring or the outer taper ring in the axial direction becomes uneven, and there is a possibility that the shaft and the movable mechanical element are not properly coupled. In order to prevent this situation, it is necessary to secure the strength of the tightening ring. For this purpose, the entire length of the tightening ring must be extended or the diameter of the tightening ring must be increased. When the diameter of the tightening ring is increased, the entire shaft coupling is increased in size because the tightening bolt is attached to the cylindrical portion at a right angle to the shaft center. In this case, rotating parts such as fastening wheels attached to the shaft require large diameters, and movable mechanical elements such as gears to be coupled to the shaft are limited to large ones.

  Furthermore, in the above-described third conventional example, the nut member rotates in a predetermined direction through the tooth portion in accordance with the rotation operation of the tightening bolt, and is screwed and displaced along the male screw portion, so that the inner taper ring is moved outward. It is drawn into the tapering. This work is performed by the operator inserting the tip of a torque wrench into a square hole drilled in the head of the tightening bolt and rotating the tightening bolt. In this case, it is necessary to rotate the torque wrench with a larger torque as the degree of fitting between the outer circumference of the outer tapered ring and the inner circumference of the movable machine element and the degree of fitting between the inner circumference of the inner tapered ring and the outer circumference of the shaft increase. is there.

  Therefore, if an excessive load is applied to the meshing portion of the nut member's tooth portion and the male screw portion of the tightening bolt, and the meshing portion of the inner taper ring's male screw portion and the female screw portion of the nut member, tooth spillage may occur. Or a square hole drilled in the head of the tightening bolt may be deformed before the shaft and the movable machine element are fully connected, or due to vibrations caused by long-term use, etc. May occur. Moreover, when the operator's attachment technique using tools, such as a torque wrench, is immature, there exists a possibility that a shaft and a movable machine element cannot fully be combined.

  This invention is made | formed in view of the situation mentioned above, and makes it an example of a subject to solve the above problems, and provides the shaft coupling which can solve these subjects. With the goal.

  In order to solve the above-described problem, the shaft coupling according to the first aspect of the present invention has a male screw portion formed at the front portion of the outer periphery and a first tapered surface formed at the rear portion of the outer periphery, An inner tapered ring that has a slit in the direction and is fitted to the shaft, and a coupling portion is formed at the front part of the outer periphery, and a second tapered surface that is inscribed by the first tapered surface is formed on the inner periphery An outer tapered ring having a slit in the axial direction and having an inner fitting portion fitted into the center hole of the movable machine element, and a through hole for coupling the coupling portion of the outer tapered ring are formed in the axial direction. The first cam surface is formed so that the axial thickness of the peripheral portion decreases from the start point by a predetermined inclination angle while making a round and reaches the end point, and between the start point and the end point A rear cam having a first step portion formed, and A first female thread part into which the male thread part of the paring is screwed is formed in the axial direction, is opposed to the first cam surface, and the axial thickness of the peripheral part is the predetermined inclination angle from the starting point. The second cam surface is formed so as to decrease substantially in the opposite direction to the cam surface of the first cam surface and reach the end point. The second cam surface is opposed to the first step portion, and the start point and the end point A through hole having a second step portion formed therebetween, penetrating the side surface of the second step portion at a predetermined angle and having a second female screw portion formed in part. And a fastening bolt that is screwed into the second female threaded portion of the front cam and protrudes from the second stepped portion according to the screw displacement and presses the first stepped portion. It is characterized by.

  The invention according to claim 2 relates to the shaft coupling according to claim 1, wherein the coupling portion of the outer taper ring is a front inner fitting portion fitted into the through hole of the rear cam, The outer diameter of the front inner fitting portion is smaller than the outer diameter of the inner fitting portion, and a step portion is formed between the front inner fitting portion and the inner fitting portion.

  The invention according to claim 3 relates to the shaft coupling according to claim 1, wherein the coupling portion of the outer taper ring is a male screw portion formed at a front portion of the outer periphery of the outer taper ring, An internal thread portion into which the external thread portion of the outer taper ring is screwed is formed in the through hole of the rear cam.

  According to a fourth aspect of the present invention, there is provided the shaft coupling according to the first aspect, wherein the coupling portion of the outer taper ring is formed to project radially outward at an outer peripheral front end of the outer taper ring. An annular groove having a diameter larger than the diameter of the through hole and fitted with the annular protrusion is formed in the vicinity of the rear surface of the through hole of the rear cam. .

  The invention according to claim 5 relates to the shaft coupling according to any one of claims 1 to 4, wherein the first cam surface and the second cam surface are in an axial direction of the peripheral portion. Is formed from the start point to the intermediate point while decreasing at the predetermined inclination angle, and once increasing at the intermediate point, the thickness decreases from the intermediate point to the end point while decreasing at the predetermined inclination angle. It is characterized by being formed.

  The invention according to claim 6 relates to the shaft coupling according to any one of claims 1 to 5, wherein the first step portion has a curved shape protruding in the circumferential direction. It is characterized by.

  According to the present invention, since the rear cam and the front cam can be temporarily fixed before the shaft and the movable machine element are firmly coupled, the mounting to the shaft and the movable machine element can be performed quickly, easily and reliably. it can. Further, when the rear cam and the front cam move relatively in the axial direction, due to the wedge action due to the inclination angles of the first cam surface of the rear cam and the second cam surface of the front cam, The pressing force can be amplified in the axial direction. As a result, the inner peripheral surface of the inner taper ring is further pressed against the outer peripheral surface of the shaft, and the outer peripheral surface of the outer taper ring is further pressed against the inner peripheral surface of the movable machine element, so that the shaft and the movable machine element are firmly coupled. To do. Therefore, sufficient torque transmission capability, high rigidity, and durability can be ensured.

It is a disassembled perspective view which shows the structure of the shaft coupling which concerns on Embodiment 1 of this invention. It is sectional drawing of the axial direction which shows the state in the middle of connecting a gearwheel to a shaft using the shaft coupling of FIG. It is a top view which shows the state in the middle of connecting a gearwheel to a shaft using the shaft coupling of FIG. It is a top view which shows the state which couple | bonded the gearwheel with the axis | shaft using the shaft coupling of FIG. It is AA sectional drawing of FIG. It is a disassembled perspective view which shows the structure of the shaft coupling which concerns on Embodiment 2 of this invention. It is sectional drawing of the axial direction which shows the state in the middle of combining a gearwheel with a shaft using the shaft coupling of FIG. It is sectional drawing of the axial direction which shows the state in the middle of combining a gearwheel with a shaft using the shaft coupling which concerns on Embodiment 3 of this invention.

Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is an exploded perspective view showing a configuration of a shaft coupling 1 according to Embodiment 1 of the present invention. The shaft coupling 1 according to the first embodiment includes an inner taper ring 11, an outer taper ring 12, a rear cam 13, a front cam 14, and a tightening bolt 15.

  The inner taper ring 11 has a substantially prefix cone shape in which the outer peripheral diameter gradually increases from the front end 11a toward the rear end 11b, and is hollow. On the outer periphery of the inner taper ring 11, a male screw portion 11c is formed from the front end 11a to the rear end 11b to a predetermined position. The male screw portion 11c is screwed into a female screw portion 14a of the front cam 14 described later. The formation direction of the male screw portion 11c and the female screw portion 14a is a so-called “right screw” that is screwed and displaced when the front cam 14 is rotated clockwise with respect to the inner taper ring 11.

  A tapered surface 11d is formed on the outer periphery of the inner taper ring 11 at least from the rear end of the male screw portion 11c to a rear end 11b starting from a position separated by a predetermined distance in the axial direction. The axial length of the tapered surface 11 d is substantially equal to the axial length of the outer tapered ring 12. The inner taper ring 11 is formed with a slit 11e having a predetermined width over the entire axial length. The inner diameter of the inner tapered ring 11 is substantially equal from the front end 11a to the rear end 11b, and is slightly larger than the outer diameter of the shaft 2 (see FIG. 2).

  The outer taper ring 12 has a substantially cylindrical shape. A front inner fitting portion 12c is formed on the outer periphery of the outer tapered ring 12 so as to be fitted into a through hole 13a formed in the center in the axial direction of the rear cam 13 from the front end 12a toward the rear end 12b to a predetermined position. Has been. The outer diameter of the front inner fitting portion 12c is slightly smaller than the inner diameter of the through hole 13a. At the inner periphery of the outer taper ring 12, at least a tapered surface 12d whose inner peripheral diameter gradually increases toward the rear end 12b from the position separated from the front end 12a by a predetermined distance in the axial direction and reaches the rear end 12b. Is formed. The inclination angle of the tapered surface 12d is substantially equal to the inclination angle of the tapered surface 11d.

  The outer taper ring 12 is formed with a slit 12e having a predetermined width over the entire axial length. Of the outer diameter of the outer taper ring 12, a rear inner fit that fits in a portion from the rear end to the rear end 12b of the front inner fitting portion 12c, that is, a center hole of the gear 3 (see FIG. 2) that is a movable mechanical element. The outer diameter of the portion 12f is substantially equal and is slightly smaller than the inner diameter of the center hole drilled at the axial center of the gear 3. A step portion 12g is formed between the front inner fitting portion 12c and the rear inner fitting portion 12f.

  The rear cam 13 has a through hole 13a into which the front inner fitting portion 12c of the outer tapered ring 12 is fitted, and the rear surface 13b of the peripheral portion has a substantially flat shape, and the front surface of the peripheral portion. Constitutes a cam surface 13c having a substantially spiral shape. The cam surface 13c is formed so that the axial thickness of the rear cam 13 is continuously thin from the thickest portion 13d at a predetermined inclination angle counterclockwise in FIG. 1 to the thinnest portion 13e. By doing so, it is formed in a spiral shape. The connecting portion between the thickest portion 13d and the thinnest portion 13e, that is, the stepped portion constitutes a working surface 13f that is pressed by the tip portion 15b of the tightening bolt 15. The action surface 13f has a curved shape protruding in the circumferential direction.

  The front cam 14 has a through hole formed in the center in the axial direction, and an internal thread portion 14 a into which the external thread portion 11 c of the inner taper ring 11 is screwed is formed in the through hole. The front cam 14 forms a cam surface 14c in which the front surface 14b of the peripheral edge portion has a substantially flat shape and the rear surface of the peripheral edge portion has a substantially spiral shape. The cam surface 14c is clockwise in FIG. 1, that is, the cam surface is the same as the inclination angle of the cam surface 13c of the rear cam 13 with respect to the axial thickness of the front cam 14 from the thickest portion 14d. It is formed in a spiral shape by being formed thin continuously in the direction opposite to the direction in which 13c is formed and by making one round to the thinnest part 14e. Accordingly, the cam surface 13c of the rear cam 13 and the cam surface 14c of the front cam 14 are brought into contact with each other, and the action surface 13f of the rear cam 13 is brought into contact with a flat surface 14f to be described later, thereby forming the overall shape. As a result, it has a substantially cylindrical shape.

  A plane portion 14f along the axial direction is formed at a connection portion between the thickest portion 14d and the thinnest portion 14e, that is, a stepped portion. A through hole 14h that penetrates the side surface 14g at a predetermined angle with respect to the flat surface 14f is formed in the flat surface 14f. The through-hole 14h is formed with a female screw portion 14i into which the male screw portion 15a of the tightening bolt 15 is screwed from the flat surface 14f to a predetermined distance.

  The tightening bolt 15 has a male screw portion 15a formed on the peripheral surface thereof, and is screwed into the female screw portion 14i of the through hole 14h. The direction in which the male screw portion 15a and the female screw portion 14i are formed is a so-called “right-hand screw” in which when the tightening bolt 15 is rotated clockwise, the distal end portion 15b of the tightening bolt 15a protrudes from the flat surface 14f of the front cam 14. Or a so-called “left-handed screw” in which the tip 15b of the tightening bolt 15 protrudes from the flat surface 14f of the front cam 14 when the tightening bolt 15 is rotated counterclockwise. In addition, a bottomed square hole is formed in the head 15c of the tightening bolt 15 so as to be operable using a tool such as a torque wrench.

  Next, the operation | movement which couple | bonds the gearwheel 3 which is a movable machine element with the axis | shaft 2 using the shaft coupling 1 of the said structure is demonstrated with reference to FIGS. FIG. 2 is an axial cross-sectional view showing a state in the middle of coupling the gear 3 to the shaft 2 using the shaft coupling 1. FIG. 3 is a top view showing a state in the middle of coupling the gear 3 to the shaft 2 using the shaft coupling 1. FIG. 4 is a top view showing a state in which the gear 3 is coupled to the shaft 2 using the shaft coupling 1. 5 is a cross-sectional view taken along the line AA in FIG.

  First, the shaft 2 is inserted into the inner periphery of the inner taper ring 11 and held at the fixed position of the gear 3. On the other hand, the outer tapered ring 12 is inserted into the inner periphery of the gear 3 to fix the gear 3 to the rear inner fitting portion 12 f of the outer tapered ring 12. Next, after the shaft 2 is inserted into the inner periphery of the outer tapered ring 12 to which the gear 3 is fixed, the outer tapered ring 12 to which the gear 3 is fixed is moved to the holding position of the inner tapered ring 11, that is, the fixed position of the gear 3. And the outer periphery of the inner tapered ring 11 is fitted to the inner periphery of the outer tapered ring 12. Thereby, the taper surface 11 d of the inner taper ring 11 and the taper surface 12 d of the outer taper ring 12 abut at the fixed position of the gear 3.

  Next, the tightening bolt 15 is screwed into the female screw portion 14i of the front cam 14 so that the tip portion 15b does not protrude from the flat surface 14f. In a state where the cam surface 13c of the rear cam 13 and the cam surface 14c of the front cam 14 are brought into contact with each other, and the action surface 13f of the rear cam 13 and the flat surface 14f of the front cam 14 are brought into contact with each other, the rear cam After inserting the shaft 2 into the thirteen through holes 13a and the through holes of the front cam 14, the rear cam 13 and the front cam 14 are rotated together with respect to the shaft 2 in a clockwise direction. As a result, the front inner fitting portion 12c of the outer taper ring 12 is fitted into the through hole 13a of the rear cam 13, and the male screw portion 11c of the inner taper ring 11 is screw-displaced into the female screw portion 14a of the front cam 14. The state shown in FIG. 2 is obtained.

  Also in the state shown in FIG. 2, the inner taper ring 11 and the outer taper ring 12 move relative to each other in the axial direction, so that the inner taper ring 11 reduces the width of the slit 11e by the wedge action of the taper surface 11d and the taper surface 12d. While narrowing and reducing the diameter, the outer taper ring 12 widens the diameter of the slit 12e. As a result, the inner peripheral surface of the inner tapered ring 11 is pressed against the outer peripheral surface of the shaft 2, and the outer peripheral surface of the outer tapered ring 12 is pressed against the inner peripheral surface of the gear 3 so that the shaft 2 and the gear 3 are coupled. Yes.

  Next, when the formation direction of the male screw portion 15a and the female screw portion 14i is “right-handed screw”, the tightening bolt 15 is rotated clockwise using a tool. As a result, as shown in FIG. 5, the fastening bolt 15 is screw-displaced, and the distal end portion 15 b of the fastening bolt 15 presses the action surface 13 f of the rear cam 13, while the distal end portion 15 b is the flat surface 14 f of the front cam 14. Protruding from. For this reason, as shown in FIG. 3, the rear cam 13 and the front cam 14 are opposite to each other perpendicular to the shaft 2, that is, the rear cam 13 is in the Y1 direction in FIG. Moves relative to each other in the Y2 direction in FIG. 3 while the working surface 13f and the flat surface 14f move away from each other.

  Since the cam surface 13c of the rear cam 13 and the cam surface 14c of the front cam 14 are substantially spiral, the rear cam 13 and the front cam 14 are parallel to the shaft 2 simultaneously with the above-described operation. The rear cam 13 moves relatively in the X1 direction in FIG. 3, and the front cam 14 moves in the X2 direction in FIG. For this reason, the thickness of the overall shape of the rear cam 13 and the front cam 14 after tightening in the axial direction increases from the thickness d1 before tightening to the thickness d2, as can be seen from FIGS. To do.

  As described above, the rear cam 13 and the front cam 14 move relatively in the axial direction, whereby the inner taper ring 11 is drawn into the outer taper ring 12 to cause a wedge action, and the inner taper ring 11 is slit. The width of 11e is reduced to reduce the diameter, and the outer taper ring 12 increases the width of the slit 12e to increase the diameter. As a result, the inner peripheral surface of the inner tapered ring 11 is further pressed into contact with the outer peripheral surface of the shaft 2, and the outer peripheral surface of the outer tapered ring 12 is further pressed into contact with the inner peripheral surface of the gear 3, so that the shaft 2 and the gear 3 are strong. To join.

  According to the first embodiment of the present invention described above, when the rear cam 13 and the front cam 14 are relatively moved in the axial direction and the shaft 2 and the gear 3 are firmly coupled, a small tool may be used. Therefore, a large tool matched with a large-diameter tightening nut as in the first conventional example is unnecessary.

  Further, according to the first embodiment of the present invention, when the rear cam 13 and the front cam 14 are relatively moved in the axial direction, the front inner fitting portion 12c of the outer tapered ring 12 is fitted into the rear cam 13. In addition, the front cam 14 and the inner tapered ring 11 are screwed together in a rotatable state. Therefore, it is possible to suppress a state where the shaft or the movable mechanical element rotates together as in the first conventional example. Thereby, the gear 3 can be fixed to the shaft 2 at an appropriate position. At this time, the rear surface 13b of the rear cam 13 presses the step portion 12g of the outer taper ring 12 in the X1 direction in FIG. 3, so that the outer taper ring 12 is prevented from rotating together with the inner taper ring 11.

  Furthermore, according to the first embodiment of the present invention, when the rear cam 13 and the front cam 14 are relatively moved in the axial direction, a large torsion torque is not applied to the shaft 2, so that the shaft 2 may be damaged. There are few, and it is not necessary to provide the anti-rotation means (refer paragraph 0008) which prevents unnecessary rotation of the rear cam 13 and the front cam 14. Further, according to the first embodiment of the present invention, the cam surface 13c of the rear cam 13 and the cam surface 14c of the front cam 14 are interposed through portions having a larger contact area compared to the first conventional example. Since the shaft 2 and the gear 3 are firmly coupled, the frictional resistance generated between the cam surface 13c and the cam surface 14c is larger than that in the first conventional example. Therefore, according to the first embodiment of the present invention, the coupling between the shaft 2 and the gear 3 is less likely to loosen than the first conventional example.

  Further, according to the first embodiment of the present invention, the shaft coupling 1 includes only five of the inner tapered ring 11, the outer tapered ring 12, the rear cam 13, the front cam 14, and the tightening bolt 15. It consists of parts with a simple structure. Therefore, as compared with the second conventional example, the shaft coupling 1 can be configured at a low cost, and before the shaft 2 and the gear 3 are firmly coupled, the internal threaded portion 14a of the front cam 14 has an inner taper. By screwing the male thread portion 11c of the ring 11, the rear cam 13 and the front cam 14 can be temporarily fixed in advance, so that the shaft 2 and the gear 3 can be mounted quickly, easily and reliably. .

  Furthermore, according to Embodiment 1 of the present invention, as in the second conventional example, it takes time to interpose the fastening ring between the inner taper ring and the outer taper ring, or the interposition is correct. Installation will not end without being done. For this reason, as compared with the second conventional example, the device breaks down due to the eccentric motion of the movable machine element, or the tightening bolt is loosened due to vibrations associated with long-term use, and the rear cam 13 and the front cam 14. There is little risk of falling loose.

  Furthermore, according to the first embodiment of the present invention, when the rear cam 13 and the front cam 14 move relatively in the axial direction, the cam surface 13c of the rear cam 13 and the cam surface 14c of the front cam 14 respectively. By the wedge action due to the inclination angle, the pressing force by the tightening bolt 15 can be amplified in the axial direction. Due to the pressing force amplified in the axial direction, the inner taper ring 11 is attracted into the outer taper ring 12 to cause a wedge action. The inner taper ring 11 is reduced in diameter by reducing the width of the slit 11e, and the outer taper ring. 12 increases the width of the slit 12e to increase the diameter.

  As a result, the inner peripheral surface of the inner tapered ring 11 is further pressed into contact with the outer peripheral surface of the shaft 2, and the outer peripheral surface of the outer tapered ring 12 is further pressed into contact with the inner peripheral surface of the gear 3, so that the shaft 2 and the gear 3 are strong. To join. Therefore, sufficient torque transmission capability, high rigidity, and durability can be ensured. At this time, the inner tapered ring 11 and the outer tapered ring 12 are uniformly coupled over the entire region where the tapered surface 11d and the tapered surface 12d are in contact with each other. Compared with -207686), the coaxiality can be ensured quickly and easily.

  Further, according to the first embodiment of the present invention, the tightening bolt 15 is attached in a direction orthogonal to the shaft 2, and therefore, compared to the conventional flange-type shaft coupling, the influence on the surrounding structure, In particular, the gear 3 can be firmly coupled to the shaft 2 quickly and easily without being restricted by the space for inserting the tool in the axial direction.

  Furthermore, according to the first embodiment of the present invention, when the tightening bolt 15 is rotated, the tightening bolt 15 is screw-displaced and the front end portion 15b presses the action surface 13f of the rear cam 13, whereby the rear side The cam 13 and the front cam 14 are relatively moved in the axial direction. For this reason, according to the first embodiment of the present invention, as in the third conventional example, the meshing between the teeth of the nut member and the male thread of the tightening bolt, and the male thread of the inner tapered ring and the nut member Since there is no meshing with the female thread portion, there is no occurrence of tooth spilling or deformation of a square hole drilled in the head of the tightening bolt. Therefore, before the shaft and the movable machine element are sufficiently combined, or due to vibrations associated with long-term use, a failure occurs, or due to the inexperienced installation technique of the operator using a tool such as a torque wrench. Insufficient coupling between the rotating shaft and the movable mechanical element is less likely to occur. Further, since the working surface 13f pressed by the tip 15b of the tightening bolt 15 has a curved shape protruding in the circumferential direction, the pressing force of the tightening bolt 15 is not dispersed and is accurately transmitted to the working surface 13f. The

  As described above, according to the first embodiment of the present invention, a diagram that cannot be easily conceived from a configuration in which known techniques such as the first to third conventional examples and the conventional flange-type shaft coupling are gathered together. Since the configuration shown in FIG. 1, particularly the configuration of the rear cam 13 and the front cam 14 is provided, the above-described unique effect that cannot be obtained from the gathering configuration is obtained.

Embodiment 2. FIG.
FIG. 6 is a schematic diagram showing the configuration of the shaft coupling according to Embodiment 2 of the present invention. The shaft coupling 21 according to the second embodiment includes an inner tapered ring 11, an outer tapered ring 22, a rear cam 23, a front cam 24, and a tightening bolt 15. In the second embodiment, an outer tapered ring 22, a rear cam 23, and a front cam 24 are newly provided in place of the outer tapered ring 12, the rear cam 13, and the front cam 14 shown in FIG. In FIG. 6, parts corresponding to those in FIG. 1 are given the same reference numerals, and detailed descriptions thereof are omitted.

  The outer taper ring 22 has a substantially cylindrical shape. On the outer periphery of the outer taper ring 22, a male screw portion 22c is formed from the front end 22a toward the rear end 22b to a predetermined position. The male screw portion 22c is screwed into a female screw portion 23a of the rear cam 23 described later. The formation direction of the male screw portion 22c and the female screw portion 23a is the same as the formation direction of the male screw portion 11c and the female screw portion 24a. In the second embodiment, the formation direction of the male screw portion 11c and the female screw portion 24a is a so-called “right screw”. Therefore, when the rear cam 23 is rotated clockwise with respect to the outer taper ring 22, the screw is displaced. It is referred to as a “right-handed screw” to be fastened. In addition, the pitch (distance between adjacent screw threads) between the male screw portion 22c and the female screw portion 23a is shorter than the pitch between the male screw portion 11c and the female screw portion 24a.

  On the inner periphery of the outer taper ring 22, there is at least a tapered surface 22d whose inner peripheral diameter gradually increases toward the rear end 22b from the position separated from the front end 22a by a predetermined distance in the axial direction and reaches the rear end 22b. Is formed. The inclination angle of the tapered surface 22d is substantially equal to the inclination angle of the tapered surface 11d.

  The outer taper ring 22 is formed with a slit 22e having a predetermined width over the entire axial length. Of the outer diameter of the outer taper ring 22, a portion from the rear end to the rear end 22 b of the male screw portion 22 c, that is, the inner fitting portion 22 f that fits in the movable machine element or the center hole of the gear 3 (see FIG. 7). The outer diameter is substantially equal and slightly smaller than the inner diameter of the gear 3.

  The rear cam 23 has a through hole formed in the center in the axial direction, and a female screw portion 23 a into which the male screw portion 22 c of the outer taper ring 22 is screwed is formed in the through hole. The rear cam 23 forms a cam surface 23c in which the rear surface 23b of the peripheral edge portion has a substantially flat shape and the front surface of the peripheral edge portion has a substantially spiral shape. The cam surface 23c is formed such that the axial thickness of the rear cam 23 is continuously thin from the thickest portion 23d to the thinnest portion 23e in a predetermined inclination angle in the counterclockwise direction in FIG. By doing so, it is formed in a spiral shape. A connecting portion between the thickest portion 23d and the thinnest portion 23e, that is, a stepped portion constitutes a working surface 23f that is pressed by the tip portion 15b of the fastening bolt 15. The action surface 23f has a curved surface shape protruding in the circumferential direction.

  Through-holes for releasing the coupling between the shaft 2 and the gear 3 are formed by releasing the coupling between the inner taper ring 11 and the outer taper ring 22 at positions symmetrical to the axis of the cam surface 23c. Female thread portions 23g and 23h are respectively formed.

  The front cam 24 has a through hole formed in the center in the axial direction, and a female screw portion 24a into which the male screw portion 11c of the inner taper ring 11 is screwed is formed in this through hole. The front cam 24 forms a cam surface 24c in which the front surface 24b of the peripheral edge portion has a substantially flat shape and the rear surface of the peripheral edge portion has a substantially spiral shape. The cam surface 24c is clockwise in FIG. 6 in the axial direction of the front cam 24 at the same inclination angle as the cam surface 23c of the rear cam 23 from the thickest portion 24d, that is, the cam surface. 23c is formed in a spiral shape by being continuously thinly formed in the direction opposite to the formation direction of 23c and substantially making a round to the thinnest portion 24e. Accordingly, the cam surface 23c of the rear cam 23 and the cam surface 24c of the front cam 24 are brought into contact with each other, and the action surface 23f of the rear cam 23 is brought into contact with a flat surface 24f to be described later. As a result, it has a substantially cylindrical shape.

  A plane portion 24f along the axial direction is formed at a connection portion between the thickest portion 24d and the thinnest portion 24e, that is, a stepped portion. A through hole 24h that penetrates the side surface 24g at a predetermined angle with respect to the flat surface 24f is formed in the flat surface 24f. The through hole 24h is formed with a female screw portion 24i into which the male screw portion 15a of the fastening bolt 15 is screwed from the flat surface 24f to a depth of a predetermined distance. The direction in which the male screw portion 15a and the female screw portion 24i are formed is so-called “right-handed screw” in which when the tightening bolt 15 is rotated clockwise, the tip portion 15b of the tightening bolt 15 protrudes from the flat surface 24f of the front cam 24. Or a so-called “left screw” in which the tip 15b of the tightening bolt 15 protrudes from the flat surface 24f of the front cam 24 when the tightening bolt 15 is rotated counterclockwise.

  At positions symmetrical to the axis of the front surface 24b, through holes 24j and 24k for releasing the coupling between the shaft 2 and the gear 3 by releasing the coupling between the inner taper ring 11 and the outer taper ring 22 are formed. Has been. The through holes 24j and 24k are aligned with the internal threaded portions 23g and 23h of the rear cam 23 even when the working surface 23f and the flat surface 24f are brought into contact with or separated from each other by the use of the tightening bolt 15. 11 is a long hole so that a release bolt (not shown) for releasing the coupling between the outer taper ring 22 and the outer taper ring 22 can be screwed into the female screw portions 23g and 23h of the rear cam 23.

  The direction in which the internal thread portions 23g and 23h and the external thread portion of the release bolt are formed is the so-called "" where the release bolt rotates when the release bolt is rotated clockwise and the distal end portion of the release bolt protrudes from the rear surface 23b of the rear cam 23. It may be a “right-handed screw”, or a so-called “left-handed screw” in which the tip of the release bolt protrudes from the rear surface 23b of the rear cam 23 when the release bolt is rotated counterclockwise. In addition, a bottomed square hole is formed in the head of the release bolt (not shown) so as to be operable using a tool such as a hexagon wrench.

  Next, the operation | movement which couple | bonds the gearwheel 3 with the axis | shaft 2 using the shaft coupling 21 of the said structure is demonstrated with reference to FIG. FIG. 7 is an axial cross-sectional view showing a state in the middle of coupling the gear 3 to the shaft 2 using the shaft coupling 21.

  First, the shaft 2 is inserted into the inner periphery of the inner taper ring 11 and held at the fixed position of the gear 3. On the other hand, the outer tapered ring 22 is inserted into the inner periphery of the gear 3 to fix the gear 3 to the inner fitting portion 22 f of the outer tapered ring 22. Next, after the shaft 2 is inserted into the inner periphery of the outer tapered ring 22 to which the gear 3 is fixed, the outer tapered ring 22 to which the gear 3 is fixed is moved to the holding position of the inner tapered ring 11, that is, the fixed position of the gear 3. And the outer periphery of the inner tapered ring 11 is fitted to the inner periphery of the outer tapered ring 22. Thereby, the taper surface 11 d of the inner taper ring 11 and the taper surface 22 d of the outer taper ring 22 abut at the fixed position of the gear 3.

  Next, the fastening bolt 15 is screwed into the female thread portion 24i of the front cam 24 so that the tip portion 15b does not protrude from the flat surface 24f. In a state where the cam surface 23c of the rear cam 23 and the cam surface 24c of the front cam 24 are brought into contact with each other, and the action surface 23f of the rear cam 23 and the flat surface 24f of the front cam 24 are brought into contact with each other, the rear cam After the shaft 2 is inserted into the through hole 23 and the through hole of the front cam 24, the rear cam 23 and the front cam 24 are rotated together with respect to the shaft 2. As a result, the male screw portion 22c of the outer tapered ring 22 is screw-displaced into the female screw portion 23a of the rear cam 23, and the male screw portion 11c of the inner taper ring 11 is screw-displaced into the female screw portion 24a of the front cam 24.

  At this time, the pitch between the male screw portion 22c and the female screw portion 23a is shorter than the pitch between the male screw portion 11c and the female screw portion 24a. The distance is shorter than the male screw portion 11c of the inner taper ring 11 with respect to the female screw portion 24a of the front cam 24 is screw-displaced. Therefore, when the inner taper ring 11 and the outer taper ring 22 are relatively moved in the axial direction, the state shown in FIG. 7 is obtained.

  In the state shown in FIG. 7 as well, the inner tapered ring 11 reduces the diameter of the slit 11e by reducing the width of the slit 11e by the wedge action of the tapered surface 11d and the tapered surface 22d, and the outer tapered ring 22 increases the width of the slit 22e. It has a diameter. As a result, the inner peripheral surface of the inner tapered ring 11 is pressed against the outer peripheral surface of the shaft 2, and the outer peripheral surface of the outer tapered ring 22 is pressed against the inner peripheral surface of the gear 3 so that the shaft 2 and the gear 3 are coupled. Yes.

  Next, when the formation direction of the male screw portion 15a and the female screw portion 24i is “right-handed”, the tightening bolt 15 is rotated clockwise using a tool. As a result, the tightening bolt 15 is screw-displaced, and the front end portion 15 b protrudes from the flat surface 24 f of the front cam 24 while the front end portion 15 b of the tightening bolt 15 presses the action surface 23 f of the rear cam 23. For this reason, the rear cam 23 and the front cam 24 move so that the action surface 23f and the flat surface 24f are separated from each other while relatively rotating in opposite directions orthogonal to the shaft 2 respectively.

  Since the cam surface 23c of the rear cam 23 and the cam surface 24c of the front cam 24 are substantially spiral, the rear cam 23 and the front cam 24 are parallel to the shaft 2 simultaneously with the above-described operation. They move relative to each other in opposite directions. For this reason, the thickness of the overall shape of the rear cam 23 and the front cam 24 after tightening in the axial direction increases from the thickness before tightening.

  As described above, the rear cam 23 and the front cam 24 move in the axial direction relatively, whereby the inner tapered ring 11 is drawn into the outer tapered ring 22 to cause a wedge action, and the inner tapered ring 11 is slit. The width of 11e is reduced to reduce the diameter, and the outer tapered ring 22 increases the width of the slit 22e to increase the diameter. As a result, the inner peripheral surface of the inner tapered ring 11 is further pressed into contact with the outer peripheral surface of the shaft 2, and the outer peripheral surface of the outer tapered ring 22 is further pressed into contact with the inner peripheral surface of the gear 3, thereby strengthening the shaft 2 and the gear 3. To join.

  When the coupling between the shaft 2 and the gear 3 is released, when the fastening bolt 15 is a “right-handed screw”, the tip 15b of the fastening bolt 15 is rotated by rotating the fastening bolt 15 counterclockwise using a tool. Is not projected from the flat surface 24 f of the front cam 24. Next, when the formation direction of the female screw portions 23g and 23h and the male screw portion of the release bolt is “right-handed”, the tip ends of the release bolts are screwed into the female screw portions 23g and 23h through the through holes 24j and 24k, respectively. After that, use a tool to rotate each release bolt clockwise.

  As a result, the release bolt is screwed and displaced, and the leading end portion of the male screw portion approaches the rear surface 23 b side of the rear cam 23. At this time, since the male threaded portion 22c of the outer tapered ring 22 is screwed into the female threaded portion 23a of the rear cam 23, the rear cam 23 and the outer tapered ring 22 are integrally moved to move rearward in the axial direction. On the other hand, since the male threaded portion 11c of the inner tapered ring 11 is screwed into the female threaded portion 24a of the front cam 24, the front cam 24 and the inner tapered ring 11 are united to move forward in the axial direction. .

  Further, when the respective release bolts are rotated clockwise using a tool, the release bolts are screw-displaced, and the front end portion protrudes from the rear surface 23b of the rear cam 23 to press the front surface of the gear 3. As a result, a gap is generated between the front surface of the gear 3 and the rear surface 23 b of the rear cam 23, the pressure contact between the cam surface 23 b of the rear cam 23 and the cam surface 24 c of the front cam 24, and the taper of the inner taper ring 11. Since the pressure contact between the surface 11d and the tapered surface 22d of the outer tapered ring 22 is released, the coupling between the shaft 2 and the gear 3 can be released.

  According to the second embodiment of the present invention described above, the effects obtained by the first embodiment of the present invention can be similarly obtained. Further, according to the second embodiment of the present invention, the internal thread portions 23g and 23h are formed on the cam surface 23c of the rear cam 23, and the through holes 24j and 24k are formed in the front surface 24b of the front cam 24. Therefore, the coupling between the shaft 2 and the gear 3 can be easily released by screwing the release bolts into the female screw portions 23g and 23h through the through holes 24j and 24k, respectively.

Embodiment 3 FIG.
In the first embodiment described above, the example in which the front inner fitting portion 12c of the outer taper ring 12 is fitted into the through hole 13a formed in the rear cam 13 is shown, but the present invention is not limited to this. For example, as shown in FIG. 8, an annular protrusion 12 h protruding radially outward is formed integrally with the front end 12 a at the front end 12 a of the outer tapered ring 12, and a through hole 13 a formed in the rear cam 13 is formed. An annular groove 13g having a diameter larger than the diameter of the through hole 13a may be formed in the vicinity of the rear surface 13b.

  If comprised in this way, the annular protrusion 12h formed in the front end 12a of the outer taper ring 12 is fitted to the annular groove 13g drilled in the through-hole 13a of the rear cam 13, thereby implementing the present invention. The effect obtained by the first embodiment can be obtained in the same manner, and the connecting operation of the shaft 2 and the gear 3 can be performed more quickly and easily. Further, after the shaft 2 and the gear 3 are coupled, the coupling between the rear cam 13 and the outer taper ring 12 is not released even when an external force such as vibration is applied, so the coupling between the shaft 2 and the gear 3 is released. It is possible to suppress the risk of being damaged.

Embodiment 4 FIG.
In the first embodiment described above, the formation direction of the male screw portion 11c and the female screw portion 14a is “right screw”, and the cam surface 13c of the rear cam 13 is formed in a counterclockwise spiral shape in FIG. Although an example in which the cam surface 14c of the cam 14 is formed in a clockwise spiral shape in FIG. 1 is shown, the present invention is not limited to this. For example, when the front cam 14 is rotated counterclockwise with respect to the inner taper ring 11 in the direction in which the male screw portion 11c and the female screw portion 14a are formed, a so-called “left screw” is used. The cam surface 13c of the side cam 13 may be formed in a clockwise spiral shape in FIG. 1, and the cam surface 14c of the front cam 14 may be formed in a counterclockwise spiral shape in FIG. If comprised in this way, according to the rotation direction of the axis | shaft 2, ie, clockwise or counterclockwise, the structure which the coupling | bonding of the axis | shaft 2 and the gearwheel 3 becomes stronger during use can be selected.

Embodiment 5. FIG.
In the second embodiment described above, the formation direction of the male screw portion 11c and the female screw portion 24a and the formation direction of the male screw portion 22c and the female screw portion 23a are both “right-handed”, and the cam surface 23c of the rear cam 23 is illustrated in FIG. 6 shows an example in which it is formed in a counterclockwise spiral shape and the cam surface 24c of the front cam 24 is formed in a clockwise spiral shape in FIG. 6, but is not limited thereto. For example, when the front cam 24 is rotated counterclockwise with respect to the inner taper ring 11 in the direction in which the male thread portion 11c and the female thread portion 24a are formed, a so-called “left-hand thread” is used. When the rear cam 23 is rotated counterclockwise with respect to the outer taper ring 22 in the direction in which the portion 22c and the female screw portion 23a are formed, it is a so-called “left-handed screw” that is fastened and displaced. The cam surface 23c of 23 may be formed in a clockwise spiral shape in FIG. 6, and the cam surface 24c of the front cam 24 may be formed in a counterclockwise spiral shape in FIG. If comprised in this way, according to the rotation direction of the axis | shaft 2, ie, clockwise or counterclockwise, the structure which the coupling | bonding of the axis | shaft 2 and the gearwheel 3 becomes stronger during use can be selected.

Embodiment 6 FIG.
In the second embodiment and the fifth embodiment described above, the example in which the formation direction of the male screw portion 22c and the female screw portion 23a is the same as the formation direction of the male screw portion 11c and the female screw portion 24a is shown, but the present invention is not limited to this. In the case of the above-described second embodiment, for example, when the formation direction of the male screw portion 11c and the female screw portion 24a is “right screw”, the formation direction of the male screw portion 22c and the female screw portion 23a may be “left screw”. If comprised in this way, when the rear cam 23 and the front cam 24 which contacted the cam surface 23c and the cam surface 24c are temporarily fixed collectively, the inner taper ring 11 and the outer taper ring 22 will mutually fit. Since it is screwed in the moving direction, temporary fixing can be performed quickly. On the other hand, when the coupling between the shaft 2 and the gear 3 is released, the rear cam 23 and the front cam 24 are put together and rotated counterclockwise as compared with the coupling, whereby the inner taper ring 11 and the outer taper ring. Since the screws 22 are screwed in the direction of releasing the mutual connection, the connection between the shaft 2 and the gear 3 can be quickly and easily released.

Embodiment 7 FIG.
In each above-mentioned embodiment, although the example which forms the slit 11e over the axial direction full length of the inner side taper ring 11 was shown, it is not limited to this. For example, the slit 11e should just be formed in the range which the outer side tapering 12 or 22 fits at least. In this case, a plurality of slits 11e may be formed at equal intervals on the circumference of the inner tapered ring 11. If a plurality of slits 11e are formed, the amount by which the inner taper ring 11 is reduced in diameter increases, so even if the diameter of the shaft 2 varies somewhat, it can be dealt with.

Embodiment 8 FIG.
In each of the above-described embodiments, the cam surface 13c of the rear cam 13, the cam surface 14c of the front cam 14, the cam surface 23c of the rear cam 23, and the cam surface 24c of the front cam 24 all have a single slope. Although an example of forming is shown, it is not limited to this. For example, a plurality of slopes may be formed on a pair of cam surfaces including the cam surface 13c and the cam surface 14c. That is, for example, the cam surface 13c and the cam surface 14c are formed from the starting point to the intermediate point while decreasing at a predetermined inclination angle from the starting point, and once increased at the intermediate point, from the intermediate point It is formed so as to reach the end point while decreasing at a predetermined inclination angle. Similarly, the cam surface 23c and the cam surface 24c are formed from the starting point to the intermediate point while decreasing in the axial direction at a predetermined inclination angle, and once increased at the intermediate point, the cam surface 23c and the cam surface 24c are predetermined from the intermediate point. It is formed so as to reach the end point while decreasing at an inclination angle of. If comprised in this way, since the movement amount (stroke) of the axial direction of the rear side cam 13 and the front side cam 14 increases, the shaft 2 and the gearwheel 3 can be combined more firmly.

As described above, the embodiments of the present invention have been described in detail with reference to the drawings. However, the specific configuration is not limited to these embodiments, and the design can be changed without departing from the scope of the present invention. Is included in the present invention.
For example, in each of the above-described embodiments, the outer periphery of each of the rear cam 13 and the front cam 14 and the rear cam 23 and the front cam 24 is circular, but the present invention is not limited thereto. In addition, it may have a square shape. If comprised in this way, since the rear cam 13 and the front cam 14, or the rear cam 23 and the front cam 24 are easy to hold together, the coupling operation of the shaft 2 and the gear 3 becomes easy.

  Further, in each of the above-described embodiments, the surface states of the outer periphery of each of the rear cam 13 and the front cam 14 and the rear cam 23 and the front cam 24 are not particularly defined. Each surface may be subjected to anti-slip processing such as knurling. If comprised in this way, since the rear cam 13 and the front cam 14, or the rear cam 23 and the front cam 24 are easy to hold reliably, the coupling | bonding operation | work of the axis | shaft 2 and the gearwheel 3 becomes easy.

  In the above-described embodiments, the surface states of the cam surface 13c, the cam surface 14c, the cam surface 23c, and the cam surface 24c are not particularly defined, but the present invention is not limited to this. For example, each surface is mirror-finished. May be applied. If comprised in this way, since each frictional resistance between the cam surface 13c and the cam surface 14c and between the cam surface 23c and the cam surface 24c increases to that extent, the shaft 2 and the gear 3 are made stronger. Can be combined.

  Furthermore, the above-described embodiments can utilize each other's technology as long as there is no particular contradiction or problem in the purpose and configuration. For example, the coupling release mechanism in the second embodiment described above, that is, the female screw portions 23g and 23h and the through holes 24j and 24k may be formed in the rear cam 13 and the front cam 14 in the first embodiment.

  DESCRIPTION OF SYMBOLS 1 ... Shaft coupling, 2 ... Shaft, 3 ... Gear, 11 ... Inner tapering, 11a ... Front end, 11b ... Rear end, 11c ... Male thread part, 11d ... Tapered surface (1st taper surface), 11e ... Slit, 12 ... outer taper ring, 12a ... front end, 12b ... rear end, 12c ... front inner fitting part (joining part), 12d ... taper surface (second taper surface), 12e ... slit, 12f ... rear inner fitting part (inner fitting) Part), 12g ... step part, 12h ... annular protrusion, 13 ... rear cam, 13a ... through hole, 13b ... rear face, 13c ... cam face (first cam face), 13d ... thickest part (start point), 13e ... thinnest part (end point), 13f ... working surface (first step part), 13g ... annular groove, 14 ... front cam, 14a ... female screw part (first female screw part), 14b ... front surface, 14c ... cam surface (Second cam surface), 14d ... thickest part (start point), 14e ... thinnest part (end point) , 14f ... plane (second stepped portion), 14g ... side surface, 14h ... through hole, 14i ... female screw portion (second female screw portion), 15 ... tightening bolt, 15a ... male screw portion, 15b ... tip portion, 15c ... Head, 22 ... outer tapering, 22a ... front end, 22b ... rear end, 22c ... male threaded portion, 22d ... tapered surface (second tapered surface), 22e ... slit, 22f ... inner fitting portion, 23 ... rear cam , 23a ... female thread portion, 23b ... rear surface, 23c ... cam surface (first cam surface), 23d ... thickest portion (start point), 23e ... thinnest portion (end point), 23f ... working surface (first step portion) ), 23g, 23h ... female threaded portion, 24 ... front cam, 24a ... female threaded portion (first female threaded portion), 24b ... front surface, 24c ... cam surface (second cam surface), 24d ... thickest portion (starting point) 24e ... thinnest part (end point), 24f ... plane (second step) ), 24 g ... aspect, 24h ... through hole, 24i ... female screw portion (the second female screw portion), 24j, 24k ... through hole

Claims (6)

A male threaded portion is formed at the front part of the outer periphery, a first tapered surface is formed at the rear part of the outer periphery, an inner tapered ring that has a slit in the axial direction and is fitted around the shaft,
A coupling portion is formed at the front portion of the outer periphery, and a second tapered surface that is inscribed by the first tapered surface is formed on the inner periphery, has a slit in the axial direction, and serves as a central hole of the movable machine element. An outer tapered ring having an inner fitting portion to be fitted;
A through hole to which the coupling portion of the outer tapered ring is coupled is formed in the axial direction, and the axial thickness of the peripheral edge portion is decreased from the start point by a predetermined inclination angle, and is formed so as to substantially complete a circle and reach the end point. A rear cam having a first stepped surface and a first step formed between the start point and the end point;
A first female thread part into which the male thread part of the inner tapered ring is screwed is formed in the axial direction, is opposed to the first cam surface, and the axial thickness of the peripheral part is the predetermined inclination angle from the starting point. And having a second cam surface formed so as to decrease substantially in the opposite direction to the first cam surface and to reach the end point, facing the first stepped portion, and the start point and the A through-hole having a second step portion formed between the end point, penetrating the side surface of the second step portion at a predetermined angle and having a second female screw portion formed in part; A perforated front cam;
And a fastening bolt that is screwed into the second female threaded portion of the front cam and protrudes from the second stepped portion according to a screw displacement and presses the first stepped portion. Fittings.   The coupling portion of the outer taper ring is a front inner fitting portion that fits into the through hole of the rear cam, and an outer diameter of the front inner fitting portion is smaller than an outer diameter of the inner fitting portion, The shaft coupling according to claim 1, wherein a step portion is formed between the inner fitting portion and the inner fitting portion. The coupling part of the outer taper ring is a male screw part formed at the front part of the outer periphery of the outer taper ring,
2. The shaft coupling according to claim 1, wherein an internal thread portion into which the external thread portion of the outer taper ring is screwed is formed in the through hole of the rear cam. The coupling portion of the outer taper ring is an annular protrusion formed to protrude radially outward at an outer peripheral front end of the outer taper ring,
2. An annular groove having a diameter larger than a diameter of the through hole and fitted with the annular protrusion is formed in the vicinity of the rear surface of the through hole of the rear cam. The shaft coupling described.   The first cam surface and the second cam surface are formed from the starting point to an intermediate point while decreasing in axial direction from the starting point, and once increase at the intermediate point. The shaft coupling according to any one of claims 1 to 4, wherein the shaft coupling is formed so as to reach the end point while decreasing at the predetermined inclination angle from the intermediate point.   The shaft coupling according to any one of claims 1 to 5, wherein the first step portion has a curved shape protruding in a circumferential direction.

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