Hoist

Abstract

To provide a hoist capable of stably fixing a shaft and a rotor and achieving downsizing and low cost of a fastened part of the shaft and the rotor.SOLUTION: A boss part 11 of a rotor 6 of a hoist 1 has: a cylindrical body into which one end of a shaft 3 is inserted; and a flange 11b that projects to an inner circumferential side of the cylindrical body and faces an end surface of the shaft 3 on one end side. The flange 11b and one end of the shaft 3 are bonded via a taper pin 22 axially fitted through the flange 11b to the shaft 3. The taper pin 22 is prevented from being coming out from a rear end side by a pressing member fixed to the flange 11b. The pressing member has: a fixed part fastened to the flange 11b by a bolt at a position misaligned from the pin in the axial direction; a plate-like extension part having a base end side connected to the fixed part and extending in the axial direction and an intersecting direction; and a pressing part connected to a tip side of the extension part and brought into contact with the rear end side of the pin.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a hoist. [Background technology]

[0002] Conventionally, elevator hoists have been known that use electric motors to rotate a drive sheave to move a car. In recent years, from the perspective of building a sustainable society, the ease of maintenance and replacement of hoists has come to be seen as one of the performance indicators of hoists.

[0003] For example, Patent Document 1 proposes a hoist structure in which a rotor is fastened to a shaft by multiple tapered pins, allowing easy disassembly and assembly in a machine room with limited space. Patent Document 1 also proposes a configuration in which a bolt is inserted into the through hole of the tapered pin to fasten the tapered pin to the shaft and prevent it from coming loose. In a fitting structure that uses this type of tapered pin, the tapered pin is pressed in by the axial force of the bolt, and a frictional force determined by the surface pressure of the tapered surface and the friction coefficient against the axial force acts as a seat, and the hoist is assembled in a stationary state in which the two are balanced. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] JP 2023-3611 A Summary of the Invention [Problem to be solved by the invention]

[0005] The tapered pin used in Patent Document 1 has a through hole formed therein that penetrates in the axial direction to allow insertion of a bolt for preventing the pin from falling out. If a large-diameter through hole is formed in the tapered pin so that a bolt for preventing the pin from falling out can be inserted, the shear strength of the tapered pin is structurally reduced. Therefore, in order to ensure the strength of the fastening portion, it is necessary to increase the diameter of the tapered pin or to increase the number of tapered pins, which would result in an increase in the size of the fastening portion and an increase in costs, leaving room for improvement.

[0006] In addition, in the case of a fitting structure using a tapered pin, when the surface pressure increases due to the load caused by operation, the unevenness of the tapered surface roughness is crushed, the interference decreases, and the frictional force of the tapered surface decreases, making it easier for the tapered pin to move in the direction it is pushed in. The taper value of the tapered pin is a few tenths, so even if there is a slight crushing in the radial direction, it can be magnified several tens of times and move in the pushing direction.

[0007] Furthermore, when a bolt is inserted through the tapered pin to prevent it from coming out as in Patent Document 1, if the tapered pin is pushed further from its initial position due to the vibration of the bolt during operation or external forces due to other impacts, the bolt may loosen, and the tapered pin's ability to prevent it from coming out may decrease. Therefore, there is a demand for a fastening configuration that can more stably fix the shaft and rotor.

[0008] The present invention has been made in consideration of the above-mentioned circumstances, and aims to provide a hoist that can fix the shaft and rotor more stably and achieve a smaller and less costly fastening portion between the shaft and rotor. [Means for solving the problem]

[0009] A hoist according to one aspect of the present invention includes a drive sheave for winding and unwinding a rope, a shaft arranged along the rotation axis of the drive sheave and rotating the drive sheave, and a rotor having a boss portion that fits with one end of the shaft and rotates by a magnetic force caused by the magnetic field of the stator. The boss portion of the rotor has a cylindrical main body into which one end of the shaft is inserted, and a flange portion that protrudes to the inner periphery of the cylindrical main body and faces the end face of the one end side of the shaft. The flange portion and one end of the shaft are fitted together via a pin that is inserted through the flange portion and fitted into the shaft in the axial direction. The pin has a tapered shape with a diameter decreasing at the tip side in the fitting direction, and is prevented from coming off from the rear end side by a pressing member fixed to the flange portion. The pressing member has a fixing portion that is fastened to the flange portion by a bolt at a position offset from the pin in the axial direction, a plate-shaped extension portion whose base end side is connected to the fixing portion and extends in a direction intersecting the axial direction, and a pressing portion that is connected to the tip side of the extension portion and abuts against the rear end side of the pin. The pressing member applies a tightening force in the axial direction at the fixed portion to the pin via the extension portion and the pressing portion, with one end of the fixed portion serving as a fulcrum.

[0010] In the above hoist, a notch may be formed in the boundary between the extending portion and the fixed portion of the pressing member by cutting the extending portion in the width direction or thickness direction. In the above hoist, the fixing portion of the pressing member may be fixed to the flange portion with a plurality of bolts, and the base end side of the extension portion of the pressing member may be connected to a region between the plurality of bolts of the fixing portion. Furthermore, in the hoist, the fixing portion of the pressing member may have groove-shaped notches on both sides of the extension portion, and the boundary portion between the extension portion of the pressing member and the fixing portion may be located inside the outer periphery of the fixing portion.

[0011] In the above hoist, the pin may have a tapered pin body, a threaded portion formed on the rear end side of the pin body for connecting a pulling jig, and an annular stepped surface formed between the pin body and the threaded portion. The pressing member may have a pair of extending portions and pressing portions for one fixing portion, and the pair of extending portions and pressing portions may be disposed on both sides of the pin across the threaded portion and each pressing the stepped surface from the rear end side. Effect of the Invention

[0012] According to one aspect of the present invention, a hoist can be provided that can more stably fix a shaft and a rotor and achieve a smaller and less costly fastening portion between the shaft and the rotor. [Brief description of the drawings]

[0013] [Figure 1] FIG. 2 is a front view of the hoist of the first embodiment. [Diagram 2] FIG. 2 is a left side view of the hoist of the first embodiment. [Diagram 3] FIG. 2 is an exploded view of the shaft and rotor in FIG. 1. [Figure 4] FIG. 4 is a left side view of the retaining portion of the first embodiment. [Diagram 5] FIG. 2A is a front view showing a state before the retaining portion of the first embodiment is fixed, and FIG. 2B is a front view showing a state after the retaining portion of the first embodiment is fixed. [Figure 6] FIG. 11 is a left side view of the retaining portion of the second embodiment. [Figure 7] FIG. 13 is a left side view of the retaining portion of the third embodiment. [Figure 8] 13A is a front view showing a state before the retaining portion of the third embodiment is fixed, and FIG. 13B is a front view showing a state after the retaining portion of the third embodiment is fixed. [Figure 9] 13A is a left side view of the retaining portion of the fourth embodiment, and FIG. 13B is a front view showing the retaining portion of the fourth embodiment after it has been fixed. [Figure 10] 13A is a left side view of the retaining portion of the fifth embodiment, and FIG. 13B is a front view showing the retaining portion of the fifth embodiment after it has been fixed. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0014] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. In the embodiments, in order to make the description easier to understand, structures and elements other than the main parts of the present invention will be described in a simplified or omitted manner. In addition, in the drawings, the same elements are given the same reference numerals. Note that the shapes, dimensions, etc. of each element shown in the drawings are shown only for illustrative purposes, and do not represent the actual shapes, dimensions, etc.

[0015] In the drawings, the direction parallel to the extension direction of the rotation axis AX of the hoist is referred to as the axial direction. In the following description, the circumferential direction about the rotation axis AX is simply referred to as the circumferential direction, and the radial direction about the rotation axis AX is simply referred to as the radial direction.

[0016] First Embodiment Fig. 1 is a front view of a hoisting machine 1 of the first embodiment, and Fig. 2 is a left side view of the hoisting machine 1 of the first embodiment. The hoisting machine 1 of the first embodiment is applied to a hoisting machine for an elevator, for example.

[0017] The hoist 1 comprises a cylindrical driving sheave 2, a shaft 3, a first bearing stand 4, a second bearing stand 5, a rotor 6, and a stator 7. The driving sheave 2 has a rope winding surface 2a on its outer circumferential surface, and serves to wind up or unwind a rope (not shown) that connects the car and the weight. The shaft 3 passes through the driving sheave 2 in the axial direction, and is attached concentrically to the driving sheave 2.

[0018] The first bearing stand 4 and the second bearing stand 5 are each erected on a mounting stand 8. The mounting stand 8 is fixed to, for example, the floor of the elevator machine room. The first bearing stand 4 is disposed on one side (the left side in FIG. 1) of the driving sheave 2, and has a first bearing 4a that receives the shaft 3. The second bearing stand 5 is disposed on the other side (the right side in FIG. 1) of the driving sheave 2, and has a second bearing 5a that receives the shaft 3. For the first bearing 4a and the second bearing 5a, for example, a self-aligning roller bearing can be used. As a result, the shaft 3 and the driving sheave 2 are rotatably supported by the first bearing 4a of the first bearing stand 4 and the second bearing 5a of the second bearing stand 5.

[0019] Moreover, one end of the shaft 3 penetrates the first bearing stand 4 and protrudes to one side. Hereinafter, the portion of the shaft 3 that protrudes to one side beyond the first bearing stand 4 is also referred to as a cantilever shaft portion 10. The rotor 6 and the stator 7 are disposed on one side of the first bearing stand 4. In addition, the second bearing stand 5 is provided with a brake device (not shown) for stopping the rotation of the driving sheave 2.

[0020] The rotor 6 has a cylindrical boss portion 11 that is fitted onto the cantilever shaft portion 10 of the shaft 3, and a cylindrical magnetic pole portion 12 that is concentrically arranged on the outer periphery of the boss portion 11. A plurality of magnets 12a are attached to the outer periphery of the magnetic pole portion 12 so that different magnetic poles are periodically arranged in the circumferential direction. The boss portion 11 and the magnetic pole portion 12 are connected in the radial direction by a plurality of supports 13 that are arranged in the circumferential direction. In addition, a plurality of ventilation holes 14 are formed between each support 13 of the rotor 6 so as to form an annular shape in the circumferential direction.

[0021] A cylindrical stator 7 is disposed on the outer periphery of the rotor 6 so as to face the magnetic pole portion 12 of the rotor 6 across an air gap. As shown in FIG. 2, the underside of the stator 7 is fixed to a mounting base 8. A coil (not shown) is wound around the stator 7. By sequentially switching the magnetic field of the stator 7 by controlling the current in the coil, an attractive force or a repulsive force with respect to the magnetic field of the rotor 6 is generated in the stator 7. As a result, the driving sheave 2 is rotationally driven via the shaft 3 to which the rotor 6 is attached.

[0022] Next, the fitting structure of the shaft 3 and the rotor 6 in the first embodiment will be described in detail. Here, the partial cross section of the shaft 3 and the rotor 6 in Fig. 1 is a cross section taken along the line BOCDE in Fig. 2. Also, Fig. 3 is an exploded view of the shaft 3 and the rotor 6 in Fig. 1.

[0023] The cantilever shaft portion 10 of the shaft 3 is cylindrical, and the outer circumferential surface of the cantilever shaft portion 10 forms an outer circumferential fitting surface 10a that fits into the boss portion 11 of the rotor 6. The outer circumferential fitting surface 10a is concentric with the rotation axis AX of the shaft 3. One end face of the cantilever shaft portion 10 forms a first joint surface 10b. The first joint surface 10b of the cantilever shaft portion 10 is a plane perpendicular to the outer circumferential fitting surface 10a, and has a plurality of pin holes 15 and bolt holes 16 that extend in the axial direction.

[0024] The pin hole 15 is a cylindrical shape with one side open and the other side is a tapered recess with a smaller diameter than the one side. The bolt hole 16 has a female thread engraved on the inner periphery so that a fixing bolt 19 can be screwed into the bolt hole 16.

[0025] The pin holes 15 and the bolt holes 16 are arranged at regular intervals in the circumferential direction on a circle concentric with the rotation axis AX. In the first embodiment, four pin holes 15 and four bolt holes 16 are opened in the first joint surface 10b at 90 degree intervals, and the positions of the pin holes 15 and the bolt holes 16 are shifted from each other by 45 degrees.

[0026] The boss portion 11 of the rotor 6 has a cylindrical boss body 11a and an annular flange portion 11b formed on one side of the boss body 11a. The inner diameter of the boss body 11a is a size that provides an interference fit with the outer diameter of the cantilever shaft portion 10, and the inner peripheral surface of the boss body 11a forms an inner peripheral fitting surface 11a1 that fits with the outer peripheral fitting surface 10a of the cantilever shaft portion 10.

[0027] The flange portion 11b of the boss portion 11 is a flat plate that protrudes toward the inner periphery of the boss body 11a and has a circular opening in the center. The other surface of the flange portion 11b constitutes a second joint surface 11b1 that faces the first joint surface 10b of the cantilever shaft portion 10. The second joint surface 11b1 of the flange portion 11b is a plane that is perpendicular to the inner periphery fitting surface 11a1 of the boss body 11a.

[0028] Furthermore, in flange portion 11b, a pin hole 17 and a bolt hole 18 are formed at positions corresponding to pin hole 15 and bolt hole 16 of cantilever shaft portion 10, respectively. Pin hole 17 in flange portion 11b is a tapered hole corresponding to pin hole 15 of cantilever shaft portion 10, and passes through flange portion 11b. When shaft 3 and rotor 6 are in an assembled state, pin hole 17 in flange portion 11b is integrated with tapered pin hole 15 of cantilever shaft portion 10 and becomes flush with it. Furthermore, bolt hole 18 in flange portion 11b is, for example, a circular hole through which a fixing bolt 19 can be inserted.

[0029] Furthermore, in flange portion 11b, bolt holes 23 for screwing in bolts 27 of retaining portion 25 described below are formed on the inner peripheral side of pin holes 17 and bolt holes 18.

[0030] The cantilever shaft portion 10 of the shaft 3 is inserted into the boss portion 11 of the rotor 6 from the other side. When the shaft 3 and the rotor 6 are assembled, the outer peripheral fitting surface 10a of the cantilever shaft portion 10 and the inner peripheral fitting surface 11a1 of the boss body 11a are fitted together and come into surface contact with each other, forming a radial fitting portion 20.

[0031] The radial fitting portion 20 fixes the rotor 6 to the cantilever shaft portion 10 and also functions to suppress the eccentricity of the rotor 6. The specifications of the radial fitting portion 20, such as the diameter, length, and tightening margin, can be appropriately set under conditions that support the radial forces acting on the rotor 6 (for example, the load due to the mass of the rotor 6, the centrifugal force during rotation due to eccentricity, magnetic attraction force, etc.) and allow the rotor 6 to be fixed concentrically to the cantilever shaft portion 10 with high precision.

[0032] In addition, when the shaft 3 and the rotor 6 are assembled, the second joint surface 11b1 of the flange portion 11b faces the first joint surface 10b of the cantilever shaft portion 10. The fixing bolt 19 is inserted through the bolt hole 18 of the flange portion 11b and screwed into the bolt hole 16 of the cantilever shaft portion 10. As a result, the first joint surface 10b and the second joint surface 11b1 are tightly attached by the mechanical joining of the fixing bolt 19, and a joint 21 is formed on a plane intersecting the axial direction.

[0033] Both the first joint surface 10b and the second joint surface 11b1 are perpendicular to the fitting surface of the radial fitting portion 20, and the axial position of the rotor 6 is determined by the joining of the first joint surface 10b and the second joint surface 11b1. Furthermore, when the first joint surface 10b and the second joint surface 11b1 are brought into close contact with each other and fastened with the fixing bolt 19, no inclination of the members occurs due to fastening. As described above, the joint portion 21 functions to determine the axial position of the rotor 6 relative to the shaft 3, and to maintain a state in which the rotor 6 is fixed concentrically to the cantilever shaft portion 10 with high precision.

[0034] In addition, when the shaft 3 and rotor 6 are assembled, a solid tapered pin 22 is fitted into each of the pin holes 15, 17 of the cantilever shaft portion 10 and the flange portion 11b. The tapered pin 22 has a tapered shape in which the diameter is smaller at the front end than at the rear end, and the outer diameter is tightly fitted into the tapered pin holes 15, 17. The rear end of the tapered pin 22 is perpendicular to the axial direction and forms a circular flat surface when viewed from the axial direction.

[0035] In addition, an air vent hole (not shown) penetrating in the axial direction may be formed in the tapered pin 22 in order to allow air remaining at the bottom of the pin hole 15 during assembly to escape to the outside and suppress an increase in the insertion resistance of the tapered pin 22 due to air pressure. When an air vent hole is formed in the tapered pin 22, the opening dimension of the air vent hole is set to a very small size that hardly reduces the shear strength of the tapered pin 22.

[0036] As described above, the tapered pin 22 is fitted into the pin hole 15 of the cantilever shaft portion 10 and the pin hole 17 of the flange portion 11b, thereby forming a plurality of axial fitting portions 24 on a plane intersecting the axial direction. The plurality of axial fitting portions 24 function to transmit torque from the rotor 6 to the shaft 3. The axial fitting portions 24 also function to firmly fix the rotor 6 to the cantilever shaft portion 10 against the movement of the rotor 6 in the rotational and radial directions.

[0037] By using the tapered pin 22 in the axial fitting portion 24, the insertion allowance from the start of fitting the tapered pin 22 to the end of fitting is significantly shortened during disassembly and assembly. This makes it easier to disassemble and assemble the axial fitting portion 24, and also shortens the work time. Also, in the axial fitting portion 24, the interference can be precisely controlled by the insertion amount of the tapered pin 22. This makes it easier to suppress the variation in interference among the multiple axial fitting portions 24, and allows the maximum fitting friction force of the axial fitting portions 24 to be designed to be small.

[0038] 1 and 2, each axial fitting portion 24 is provided with a retaining portion 25 that prevents the taper pin 22 from coming off in the axial direction. The retaining portion 25 is composed of a retaining member 26 and a bolt 27, and is fixed to the flange portion 11b of the rotor 6.

[0039] Fig. 4 is a left side view of the retaining portion 25 of the first embodiment. Fig. 5(a) is a front view showing the retaining portion 25 of the first embodiment in a state before being fixed, and Fig. 5(b) is a front view showing the retaining portion 25 of the first embodiment in a state after being fixed.

[0040] The pressing member 26 has a fixing portion 30 having a hole through which the bolt 27 is inserted, and an extending portion 31 connected to the fixing portion 30, and is a member having a substantially rectangular flat plate shape when viewed from the axial direction. The pressing member 26 is fixed to the flange portion 11b by screwing the bolt 27 inserted through the fixing portion 30 into the flange portion 11b. For example, the fixing portion 30 is fixed to the flange portion 11b at a position on the radially inner periphery side with respect to the tapered pin 22.

[0041] The extending portion 31 of the pressing member 26 has a base end connected to the fixed portion 30, extends radially outward, and has a pressing portion 32 at its tip end. The pressing portion 32 is formed by bending the tip end of the extending portion 31 inward toward the flange portion 11b.

[0042] In the pressing member 26 of the first embodiment, the pressing portion 32 is formed so as to be bent at an angle of approximately 90° with respect to the extending portion 31. However, the bending angle of the pressing portion 32 with respect to the extending portion 31 is not limited to the example shown in the figure. For example, the bending angle of the pressing portion 32 with respect to the extending portion 31 may be set so that the pressing portion 32 is horizontal with the axial direction of the tapered pin 22 in a state where the fixing portion 30 is fixed to the flange portion 11b.

[0043] Moreover, the pressing member 26 is formed in a shape that generates a large bending stress at the boundary between the fixed portion 30 and the extending portion 31. In the first embodiment, for example, the plate thickness of the pressing member 26 is constant, the width W of the extending portion 31 and the pressing portion 32 are the same dimension, and the width of the fixing portion 30 is formed to be wider than the width of the extending portion 31. Furthermore, the material of the pressing member 26 is appropriately selected from, for example, metal materials having an elongation rate that can withstand bending of the plastic deformation described below. Note that the pressing member 26 may be formed of other materials such as resin materials as long as the material has an elongation rate that can withstand bending of the above-mentioned plastic deformation and has a strength that does not break when a force is applied to press the taper pin 22.

[0044] Although the extension portion 31 of the pressing member 26 does not contact the tapered pin 22, the tip of the pressing portion 32 is arranged to abut against the axis or the vicinity of the axis of the tapered pin 22 at the rear end of the tapered pin 22. As a result, the tapered pin 22 is pressed in the axial direction by the pressing member 26 toward the flange portion 11b and the cantilever shaft portion 10. Note that the tip of the pressing portion 32 is not limited to being in point contact with the tapered pin 22 in a side view, and may be configured to be in surface contact with the rear end of the tapered pin 22.

[0045] In addition, the force with which the pressing member 26 presses the rear end of the tapered pin 22 is set to exceed the force caused by vibration acceleration when the hoisting machine 1 is operated in a state in which the frictional force caused by the clamping margin of the tapered surface of the tapered pin 22 is significantly reduced.

[0046] When attaching the pressing member 26, as shown in Fig. 5(a), the tapered pin 22 is inserted into the pin holes 15, 17, and then the pressing member 26 is placed on the flange portion 11b with the tip of the pressing portion 32 abutting against the rear end of the tapered pin 22, and the bolt 27 is inserted into the hole of the fixing portion 30. The pressing member 26 in Fig. 5(a) is supported at two points, the tip of the pressing portion 32 and the end of the fixing portion 30 (the end opposite the extension portion 31 and the pressing portion 32).

[0047] Next, the bolt 27 inserted through the hole in the fixing portion 30 is screwed into the flange portion 11b, and the pressing member 26 is fixed to the flange portion 11b as shown in Fig. 5(b). When the pressing member 26 is fixed, a third type of lever relationship is established, with the end of the fixing portion 30 as the fulcrum, the position of the bolt 27 of the fixing portion 30 as the force point, and the tip of the pressing portion 32 as the point of action.

[0048] When the pressing member 26 is fixed, at the position of the bolt 27 of the fixing portion 30, which is the point of force, the fixing portion 30 is displaced so as to be pressed against the flange portion 11b by the axial force N of the bolt. At this time, the pressing member 26 begins to elastically deform, and the largest bending stress acts on the boundary between the fixing portion 30 and the extending portion 31, where the width of the pressing member 26 changes. When the tightening of the bolt 27 is completed and the fixing portion 30 is in contact with the flange portion 11b, plastic deformation occurs at the boundary between the fixing portion 30 and the extending portion 31, and the extending portion 31 deforms so as to tilt outward relative to the fixing portion 30. Note that since the material of the pressing member 26 has an elongation rate that can withstand the above-mentioned plastic deformation, the function of the retaining portion 25 is not reduced due to breakage or cracking of the pressing member 26.

[0049] On the other hand, at the tip of the pressing portion 32, which is the point of application, the movement at the point of application is greater than that at the point of force due to the principle of leverage, and force is applied to the rear end of the tapered pin 22 via the extension portion 31 and the pressing portion 32. Therefore, the pressing member 26 can press the tapered pin 22 in the axial direction. Note that the bending stress at the boundary between the fixed portion 30 and the extension portion 31 caused by the tightening of the bolt 27 is constant regardless of the amount of plastic deformation, and the force applied to the rear end of the tapered pin 22 is also constant regardless of variations in the amount of axial protrusion of the tapered pin 22.

[0050] In addition, the force applied to the rear end of the tapered pin 22 by the retaining portion 25 can be appropriately adjusted by selecting the longitudinal dimension L of the extending portion 31, the width dimension W and plate thickness of the boundary between the fixed portion 30 and the extending portion 31, the material of the pressing member 26, etc. In addition, by adjusting the longitudinal dimension L of the extending portion 31, the protrusion amount of the pressing portion 32 from the extending portion 31, and the bending angle of the extending portion 31 and the pressing portion 32, the allowable tolerance of the axial protrusion amount of the tapered pin 22 at the retaining portion 25 can be changed.

[0051] The effects of the first embodiment will be described below. The shaft 3 and rotor 6 in the first embodiment have two types of fitting portions: a radial fitting portion 20 formed by the fitting of the cantilever shaft portion 10 with the boss body 11a, and multiple axial fitting portions 24 formed by tapered pins 22 fitted into the cantilever shaft portion 10 and the flange portion 11b.

[0052] The radial fitting portion 20 is a cylindrical interference fit that can be machined and assembled with high precision, and serves to reduce the eccentricity of the rotor 6 relative to the shaft 3 and to fix the rotor 6 to the cantilever shaft portion 10 with high precision. The radial fitting portion 20 mainly functions to support the radial force acting on the rotor 6. As described above, the torque transmission between the shaft 3 and the rotor 6 is mainly performed by the axial fitting portion 24, and the radial fitting portion 20 is not expected to have a torque transmission function, so the fitting force required for the radial fitting portion 20 is significantly reduced. Therefore, in the first embodiment, the dimensions of the radial fitting portion 20 can be reduced, and therefore the boss portion 11 of the rotor 6 can be made smaller and lighter.

[0053] In the hoist 1 of the first embodiment, torque transmission between the shaft 3 and the rotor 6 is performed by a plurality of axial fitting parts 24. Therefore, each of the axial fitting parts 24 can be configured to be disassembled and assembled manually. In other words, the hoist 1 of the first embodiment does not require large hydraulic equipment, etc. to be carried into the machine room when disassembling and assembling, so maintenance and replacement work can be easily performed.

[0054] Moreover, the tapered pin 22 applied to the axial fitting portion 24 in the first embodiment is a solid material. Therefore, compared to the case where a hollow tapered pin having a large-diameter through-hole through which a retaining bolt can be inserted is applied, the cross-sectional area of ​​the tapered pin 22 in this embodiment is increased, and locally generated peak stress is reduced, so that the shear strength of the tapered pin 22 is significantly increased. Therefore, according to the first embodiment, it is possible to realize a reduction in size, weight, and cost of the axial fitting portion 24.

[0055] Moreover, the axial fitting portion 24 in the first embodiment is provided with a retaining portion 25 that prevents the taper pin 22 from coming off in the axial direction. The retaining portion 25 presses the rear end of the solid taper pin 22 from the outside with a pressing member 26 using the principle of leverage, making it difficult for the taper pin 22 to fall off, and therefore the shaft 3 and the rotor 6 can be stably fixed.

[0056] Furthermore, the retaining portion 25 can press the rear end of the taper pin 22 without adjusting the amount of axial protrusion of the taper pin 22 by inserting the bolt 27 into the fixing portion 30 of the pressing member 26 and tightening the fixing portion 30 with the bolt 27. This reduces the assembly time of each axial fitting portion 24, greatly improving the workability during assembly.

[0057] Moreover, the force with which the above-mentioned retaining portion 25 presses the rear end of the tapered pin 22 is significantly smaller than the frictional force of the normal tapered surface, since it is only necessary for it to exceed the force caused by the vibration acceleration when the hoist 1 is operated in a state in which the frictional force caused by the clamping margin of the tapered surface of the tapered pin 22 is significantly reduced. Therefore, even if the clamping margin of the tapered pin 22 decreases due to the operating load and the frictional force of the tapered surface decreases, the tapered pin 22 will not be pressed in by the pressing member 26. In other words, even in the above case, the force with which the pressing member 26 presses the rear end of the tapered pin 22 is unlikely to decrease and rattling of the tapered pin 22 is unlikely to occur, so the retaining portion 25 can maintain a stable retaining effect.

[0058] Furthermore, compared to a configuration in which a bolt is inserted into the through hole of the tapered pin to prevent it from falling out, the above-mentioned anti-pullout portion 25 does not require machining of the through hole of the tapered pin or the female thread in the tapered hole of the shaft, which allows for a significant reduction in manufacturing costs.

[0059] <Second embodiment> 6(a) to 6(c) are left side views of the retaining portion 25 of the second embodiment. In the following description of each embodiment, elements common to the first embodiment are given the same reference numerals, and duplicated description will be omitted as appropriate.

[0060] The second embodiment is an example in which the widths of the fixed portion 30 and the extending portion 31 of the pressing member 26 are the same, while notches 33, 33a are formed to reduce the width dimension W of the boundary portion between the fixed portion 30 and the extending portion 31. FIGS. 6(a) and 6(b) show examples in which notches 33 are formed on both sides of the pressing member 26 in the width direction. As an example of the notches 33, a pair of acute-angled notches 33 may be arranged facing inward as shown in FIG. 6(a), or a pair of rectangular groove-shaped notches 33 may be arranged facing inward as shown in FIG. 6(b). FIG. 6(c) shows an example in which a hole-shaped notch 33a extending in the width direction is formed at the boundary portion between the fixed portion 30 and the extending portion 31 of the pressing member 26. 6(c), the width of the portion connecting fixed portion 30 and extending portion 31 in the longitudinal direction of the member is the sum of the portions on both sides of notch 33a (w1+w2), which is narrower than the width of fixed portion 30 and extending portion 31.

[0061] 6(a) to 6(c), in the boundary portion between the fixed portion 30 and the extending portion 31 of the pressing member 26, the width of the portion connecting the fixed portion 30 and the extending portion 31 in the member longitudinal direction is partially narrowed by the notches 33, 33a. As a result, in addition to the same effect as in the first embodiment, the configuration of the second embodiment also produces a large bending stress that protrudes into the boundary portion between the fixed portion 30 and the extending portion 31 when the pressing member 26 is fixed with the bolt 27, and it is possible to produce a large bend in the pressing member 26 at the boundary portion.

[0062] <Third embodiment> Fig. 7 is a left side view of the retaining portion 25 of the third embodiment. Fig. 8(a) is a front view showing the retaining portion 25 of the third embodiment in a state before being fixed, and Fig. 8(b) is a front view showing the retaining portion 25 of the third embodiment in a state after being fixed.

[0063] In the third embodiment, the width W of the fixed portion 30 and the extending portion 31 of the pressing member 26 are set to the same dimension, while a groove-shaped notch 34 extending in the width direction is formed at the boundary between the fixed portion 30 and the extending portion 31. In the pressing member 26 of the third embodiment, the thickness of the pressing member 26 is partially thin at the boundary between the fixed portion 30 and the extending portion 31 due to the formation of the notch 34.

[0064] As a result, in addition to the same effects as in the first embodiment, the configuration of the third embodiment also has the advantage that, when the pressing member 26 is fixed with the bolt 27, a large bending stress is generated at the boundary portion between the fixing portion 30 and the extension portion 31, causing a large bend in the pressing member 26 at the boundary portion.

[0065] <Fourth embodiment> FIG. 9(a) is a left side view of the retaining portion 25 of the fourth embodiment, and FIG. 9(b) is a front view showing the retaining portion 25 of the fourth embodiment in a fixed state.

[0066] The fourth embodiment is a configuration example in which a fixing portion 30 of a pressing member 26 is fixed to a flange portion 11b with a plurality of bolts 27. The pressing member 26 of the fourth embodiment is a member having a substantially T-shaped flat plate shape when viewed from the axial direction, and has a fixing portion 30, an extension portion 31, and a pressing portion 32.

[0067] The fixing portion 30 of the fourth embodiment has two holes, through which the bolts 27 are inserted, formed at an interval in the longitudinal direction (the left-right direction in FIG. 9(a)) of the fixing portion 30. The pressing member 26 of the fourth embodiment is fixed to the flange portion 11b by screwing the two bolts 27 inserted through the fixing portion 30 into the flange portion 11b.

[0068] Moreover, in the pressing member 26 of the fourth embodiment, one extension portion 31 is disposed in a region between two bolts 27 in the longitudinal direction of the fixing portion 30. The extension portion 31 extends in a direction perpendicular to the longitudinal direction of the fixing portion 30 (the vertical direction in FIG. 9(a)), and a pressing portion 32 is formed on the tip side of the extension portion 31 protruding from the fixing portion 30. The pressing portion 32 is formed by bending the tip side of the extension portion 31 inward toward the flange portion 11b.

[0069] Two notches 35 are formed in the fixed portion 30 on the base end side of the extending portion 31 of the pressing member 26. The notches 35 of the fixed portion 30 are formed in a groove shape on both sides of the extending portion 31 along the extension direction of the extending portion 31. As a result, the boundary portion between the extending portion 31 and the fixed portion 30 is located inside the outer periphery of the fixed portion 30, and the boundary portion between the extending portion 31 and the fixed portion 30 is located in the vicinity of the fastening position of the bolt 27.

[0070] According to the configuration of the fourth embodiment, in addition to the same effects as those of the first embodiment, since the fixing portion 30 is fastened by a plurality of bolts 27, the pressing member 26 can be fixed to the flange portion 11b. Furthermore, in the configuration of the fourth embodiment, the boundary portion between the extending portion 31, where bending due to plastic deformation occurs, and the fixing portion 30 is separated from the position where the axial force is applied to the fixing portion 30 by screwing the bolt 27, so the bolt 27 of the fixing portion 30 is less likely to float. Therefore, the retaining portion 25 of the fourth embodiment can easily suppress loosening of the bolt 27 even when used in equipment with large vibrations.

[0071] In addition, in the configuration of the fourth embodiment, the boundary between the extending portion 31 and the fixing portion 30 is positioned inside the outer periphery of the fixing portion 30, so that the protruding length from the outer periphery of the fixing portion 30 to the tip of the extending portion 31 can be reduced while ensuring the longitudinal dimension L of the extending portion 31. In other words, the dimension of the pressing member 26 is reduced, and the design freedom for the attachment of the retaining portion 25 is improved.

[0072] <Fifth embodiment> Fig. 10(a) is a left side view of the retaining portion 25 of the fifth embodiment, and Fig. 10(b) is a front view showing the state after the retaining portion 25 of the fifth embodiment has been fixed. The fifth embodiment is a configuration example in which a taper pin 22 having a threaded portion 22b for extraction is applied to the retaining portion 25.

[0073] As shown in Fig. 10(b), the taper pin 22 of the fifth embodiment has a taper-shaped pin body 22a whose front end is smaller in diameter than its rear end, and a threaded portion 22b formed on the rear end side of the pin body 22a. The taper pin 22 is solid, and the pin body 22a and the threaded portion 22b are integrally formed. The taper pin 22 of the fifth embodiment may also have an air vent hole (not shown).

[0074] The pin body 22a of the tapered pin 22 is fitted into the pin holes 15, 17 of the cantilever shaft portion 10 and the flange portion 11b. The threaded portion 22b of the tapered pin 22 is a male thread that is connected to a jig (not shown) when the tapered pin 22 is pulled out from the cantilever shaft portion 10 and the flange portion 11b. As shown in Fig. 10(a), the diameter of the rear end of the pin body 22a is larger than the diameter of the threaded portion 22b, and an annular stepped surface 22c is formed at the connection portion between the pin body 22a and the threaded portion 22b.

[0075] The fixing portion 30 of the fifth embodiment has two holes, through which the bolts 27 are inserted, spaced apart in the longitudinal direction (the left-right direction in FIG. 10(a)) of the fixing portion 30. The pressing member 26 of the fifth embodiment is fixed to the flange portion 11b by screwing the two bolts 27 inserted through the fixing portion 30 into the flange portion 11b.

[0076] In the pressing member 26 of the fifth embodiment, two extending portions 31 are provided in the longitudinal direction of the fixing portion 30 at an interval corresponding to the diameter of the threaded portion 22b. Each extending portion 31 extends in a direction perpendicular to the longitudinal direction of the fixing portion 30 (the vertical direction in FIG. 10(a)), and a pressing portion 32 is formed on the tip side of the extending portion 31 protruding from the fixing portion 30. The pressing portion 32 is formed by bending the tip side of the extending portion 31 inward toward the flange portion 11b.

[0077] Each pressing portion 32 of the fifth embodiment is disposed so as to press the step surface 22c of the tapered pin 22 from the rear end side by fastening the bolt 27 of the fixing portion 30. Each pressing portion 32 is disposed so as to straddle the threaded portion 22b and press both sides of the tapered pin 22.

[0078] According to the configuration of the fifth embodiment, in addition to the same effects as those of the first embodiment, the tapered pin 22 having the threaded portion 22b on the rear end side can be prevented from coming off, and the shaft 3 and the rotor 6 can be stably fixed. Furthermore, in the configuration of the fifth embodiment, the fixing portion 30 is fastened by a plurality of bolts 27 as in the fourth embodiment, so that the pressing member 26 can be firmly fixed to the flange portion 11b.

[0079] Furthermore, according to the configuration of the fifth embodiment, a jig can be connected to the threaded portion 22b of the taper pin 22 and the jig can be used to pull out the taper pin 22 from the cantilever shaft portion 10 and the flange portion 11b, thereby improving workability when disassembling the hoist 1.

[0080] <Supplementary information for the embodiment> The present invention is not limited to the above-described embodiment, and various improvements and design changes may be made without departing from the spirit of the present invention.

[0081] In the above embodiment, a configuration example in which the present invention is applied to an elevator hoist has been described. However, the present invention can be applied to any hoist that hoists a rope.

[0082] The pressing member applied to the retaining portion of the present invention may be a combination of the configurations of the above embodiments as appropriate. For example, in each of the pressing members of the first, fourth, and fifth embodiments, the notch of the second embodiment or the notch of the third embodiment may be formed at the boundary between the fixed portion and the extending portion.

[0083] In addition, the embodiments disclosed herein should be considered to be illustrative and not restrictive in all respects. The scope of the present invention is defined by the claims, not the above description, and is intended to include all modifications within the meaning and scope of the claims. [Explanation of symbols]

[0084] 1...hoist, 2...driving sheave, 3...shaft, 6...rotor, 7...stator, 10...cantilever shaft portion, 10a...outer peripheral fitting surface, 10b...first joint surface, 11...boss portion, 11a...boss body, 11a1...inner peripheral fitting surface, 11b...flange portion, 11b1...second joint surface, 15, 17...pin hole, 16, 18...bolt hole, 19...fixing bolt, 20...radial fitting portion, 21...joint portion, 22...tapered pin, 22a...pin body, 22b...threaded portion, 22c...step surface, 24...axial fitting portion, 25...preventive portion, 26...holding member, 27...bolt, 30...fixing portion, 31...extension portion, 32...holding portion, 33, 33a, 34, 35...notch

Claims

1. a drive sheave for winding and unwinding the rope; a shaft disposed along a rotation axis of the traction sheave and configured to rotate the traction sheave; a rotor having a boss portion that fits onto one end of the shaft and that rotates due to a magnetic force generated by a magnetic field of the stator; the boss portion of the rotor has a cylindrical main body into which one end of the shaft is inserted, and a flange portion that protrudes toward the inner periphery of the cylindrical main body and faces an end face of the one end of the shaft, The flange portion and one end of the shaft are fitted together via a pin that is inserted through the flange portion and axially fitted into the shaft, The pin has a tapered shape with a diameter decreasing toward a tip side in a fitting direction, and is prevented from coming out from a rear end side by a pressing member fixed to the flange portion. The pressing member is a fixing portion fastened to the flange portion by a bolt at a position shifted from the pin in the axial direction; a plate-shaped extending portion having a base end connected to the fixed portion and extending in a direction intersecting the axial direction; a pressing portion connected to a tip end side of the extension portion and abutting against a rear end side of the pin, The pressing member applies a fastening force in the axial direction at the fixing portion to the pin via the extending portion and the pressing portion, with one end of the fixing portion as a fulcrum. Hoisting machine.

2. A notch is formed in the boundary between the extending portion and the fixing portion of the pressing member by cutting the extending portion in the width direction or thickness direction. A hoist as claimed in claim 1.

3. The fixing portion of the pressing member is fixed to the flange portion by a plurality of the bolts, The base end side of the extension portion of the pressing member is connected to a region between the plurality of bolts of the fixing portion. A hoist as claimed in claim 1.

4. The fixing portion of the pressing member has groove-shaped notches on both sides of the extension portion, A boundary portion between the extension portion and the fixed portion of the pressing member is located inside an outer periphery of the fixed portion. A hoist according to claim 3.

5. The pin has a tapered pin body, a threaded portion formed on a rear end side of the pin body for connecting a removal jig, and an annular stepped surface formed between the pin body and the threaded portion, The pressing member has a pair of the extending portion and the pressing portion for one of the fixing portions, The pair of extension portions and the pressing portion are disposed on both sides of the pin across the threaded portion, and press the step surface from the rear end side. A hoist as claimed in claim 1.

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