JP6949221B2 - Hoisting machine support structure - Google Patents

Description

The present invention relates to a hoisting machine used for an elevator, and more particularly to a support structure of the hoisting machine for preventing damage to bearings.

One of the causes of the mechanical loss of the bearing of the hoisting machine is the temperature rise of the hoisting machine. During the operation of the hoist used for the elevator, frictional heat is generated in the bearing due to the rotation of the rotating shaft. When frictional heat is generated in the bearing, the temperature of the bearing rises, causing thermal expansion of the rotating shaft. As a result, the gap between the inner ring and outer ring of the bearing and the rolling element may change, causing an excessive load on the bearing and damaging the bearing.

As a method for solving the problem caused by the temperature rise of the bearing, for example, there is a configuration of Patent Document 1. In Patent Document 1, the rotating shaft and the rotor are cooled by using a refrigerant in order to prevent damage to the bearing due to the temperature rise of the hoisting machine. More specifically, in Patent Document 1, a rotor whose end of the rotating shaft is supported by a bearing and a refrigerant chamber are provided in the bearing box, and the axial direction of the rotor and the inner peripheral side of the iron core of the rotor are provided. There is a hole in and. In order to communicate these holes, shaft holes are provided in the radial direction of the rotating shaft.

As described above, Patent Document 1 uses a structure in which the bearing and the rotor are cooled by the refrigerant, so that the rotor is cooled by the refrigerant so that the gap between the inner ring and the outer ring of the bearing and the rolling element does not become zero. .. As a result, the reduction of the bearing gap due to thermal expansion is suppressed, and damage to the bearing is prevented.

Japanese Unexamined Patent Publication No. 2007-336646

However, when a refrigerant is used to prevent damage to the bearing, it is necessary to secure a flow path for the refrigerant for the bearing and the rotor. Therefore, in the technique of Patent Document 1, hole processing and the like are required. Furthermore, it is necessary to secure a space for parts for storing the refrigerant.

Further, such a special cooling mechanism is often used for a hoisting machine that is driven at a high speed because of its large load capacity and capacity. Therefore, there is a problem that a large processing cost and processing time are required by performing complicated processing on a large part.

Further, when a refrigerant is used for the hoisting machine, it is necessary to assume a certain degree of leakage of the refrigerant. Even if the hoisting machine was sealed, there was a lot of dust and the seal could be torn depending on the environment of the installation location. Therefore, the maintenance of the hoisting machine that requires a refrigerant becomes complicated, and it may be difficult to ensure the quality.

Further, when the amount of temperature rise is large, it is necessary to circulate the refrigerant in the hoisting machine even when the elevator, that is, the elevator is not in operation. Depending on the amount of heat generated by the hoist, a device that forcibly circulates the refrigerant is also required. As a result, the configuration of the hoisting machine becomes complicated, and it may be difficult to ensure reliability.

Further, when the cooling mechanism is maintained, it is necessary to rework the flange surface that contacts the seal component and the seal in order to ensure the sealability of the refrigerant. As a result, it may take a long time to start the operation.

The present invention has been made to solve the above problems, and suppresses an increase in the load of the bearing caused by thermal expansion of the rotating shaft of the hoist, prolonging the life of the bearing and preventing damage. The purpose is to obtain a support structure for a hoist with improved reliability.

In order to solve the above problems, the support structure of the hoist according to the present invention includes a bearing that supports the rotating shaft and a bearing support member that houses the bearing, and the inner peripheral portion of the bearing support member is a bearing. Due to the partial contact with the outer peripheral portion, a gap exists between the inner peripheral portion of the bearing support member and the outer peripheral portion of the bearing, and the inner peripheral portion of the bearing support member is in the axial direction of the rotation axis. It has a plurality of convex portions arranged in a row , the plurality of convex portions are in contact with the outer peripheral portion of the bearing, and a gap exists between the plurality of convex portions.

According to the present invention, the bearing has a structure in which the bearing slides more easily than before when the rotating shaft undergoes thermal expansion. As a result, it is possible to obtain a hoisting machine support structure with improved reliability by suppressing the increase in bearing load caused by thermal expansion of the rotating shaft of the hoisting machine, extending the life of the bearing and preventing damage. Can be done.

It is a schematic diagram of the support structure of the hoist according to Embodiment 1 of this invention. It is a detailed schematic diagram of a bearing which shows the state at a constant time. It is a detailed schematic diagram of a bearing which shows the state which the inner ring moved by the thermal expansion of a rotating shaft. It is a schematic diagram of the bearing support structure according to Embodiment 1 of this invention. It is a schematic diagram of the bearing support structure according to Embodiment 2 of this invention. It is a schematic diagram of the bearing support structure according to Embodiment 3 of this invention. It is a schematic diagram of the bearing support structure according to Embodiment 4 of this invention. It is a schematic diagram of the bearing support structure according to Embodiment 5 of this invention. It is a schematic diagram of the bearing support structure according to Embodiment 6 of this invention. It is a schematic diagram of the bearing support structure according to Embodiment 7 of this invention. It is a schematic diagram of the bearing support structure according to Embodiment 8 of this invention. It is a schematic diagram of the bearing support structure by the modification of FIG. It is a schematic diagram of the bearing support structure according to Embodiment 9 of this invention.

Hereinafter, embodiments of the support structure for the hoisting machine of the present invention will be described with reference to the accompanying drawings.

Embodiment 1.
FIG. 1 is a schematic view of a support structure of the hoisting machine 100 according to the first embodiment of the present invention. The hoisting machine 100 includes a motor 1, a bearing 5, bearing support members 6 and 7, and a sheave 8. The hoisting machine 100 is fixed to the support pedestal 9.

The motor 1 includes a rotor 2, a stator 3, and a rotating shaft 4. The rotor 2 of the motor 1 is fixed to one end side 4a of the rotating shaft 4. A sheave 8 is fixed to the other end side 4b of the rotating shaft 4.

At both ends of the sheave 8, the rotating shaft 4 is rotatably supported by two bearings 5. The bearing 5 on the motor 1 side is held by the bearing support member 6, and the bearing 5 on the other end side 4b of the rotating shaft 4 is held by the bearing support member 7.

A main rope (not shown) is wound around the sheave 8. The main rope is lowered downward using a pulley (not shown). A car and a counterweight (not shown) are connected to both ends of the main rope. By driving the motor 1 to rotate the sheave 8, the car and the counterweight are moved up and down via the main rope wound around the sheave 8.

Next, the bearing 5 will be described with reference to FIGS. 1 and 2. FIG. 2 is a detailed schematic view of the bearing 5 showing a state in a steady state. As shown in FIG. 2, the bearing 5 is a rolling bearing including an inner ring 5a, a rolling element 5b, an outer ring 5c, and a cage (not shown).

A plurality of rolling elements 5b are arranged between the inner ring 5a and the outer ring 5c. The plurality of rolling elements 5b are held in the cage at regular intervals. The bearing 5 is usually provided with a predetermined gap 5d in the radial direction and the axial direction of the rotating shaft 4. The inner ring 5a is fitted to the rotating shaft 4. The outer ring 5c is fitted to the bearing support member 6 or the bearing support member 7 shown in FIG. The inner ring 5a and the outer ring 5c form a raceway ring of the bearing 5.

Next, the operation of the support structure of the hoisting machine will be described with reference to the schematic views of FIGS. 1 to 4. FIG. 3 is a detailed schematic view of the bearing 5 showing a state in which the inner ring 5a is moved due to thermal expansion of the rotating shaft 4.

When a current is supplied to the stator 3 shown in FIG. 1, a rotating magnetic field is generated around the stator 3. As a result, the rotor 2 rotates together with the rotating shaft 4. The rotation of the rotating shaft 4 due to the operation of the motor 1 is transmitted to the sheave 8. As the sheave 8 rotates, the car and the balance weight are moved up and down.

When the rotating shaft 4 rotates, frictional heat is generated and the bearing 5 generates heat. Therefore, the temperatures of the inner ring 5a, the rolling element 5b, and the outer ring 5c rise. Therefore, as the temperature of the bearing 5 rises, the temperature of the rotating shaft 4 also rises, and the rotating shaft 4 extends in the axial direction.

As shown in FIG. 3, when the rotating shaft 4 extends in the axial direction, the inner ring 5a is usually firmly fixed to the rotating shaft 4 by shrink fitting or the like, so that the inner ring 5a fixed to the rotating shaft 4 is the rotating shaft 4 Moves in the axial direction with. Therefore, when the amount of thermal expansion of the bearing 5 becomes larger than the axial gap 5d and the inner ring 5a moves in the axial direction, a force due to thermal expansion is generated in the axial direction.

As a result, the axial load of the bearing 5 increases due to the force due to thermal expansion. In the state shown in FIG. 3, the axial load of the bearing 5 increases because the axial gap 5d disappears. Therefore, the life of the bearing 5 is shortened, and there arises a problem that the bearing 5 is damaged.

A configuration for suppressing an overload due to thermal expansion due to a temperature rise of the rotating shaft 4 as shown in FIG. 3 will be described with reference to a schematic view of the bearing of FIG. FIG. 4 is a schematic view of the bearing support structure according to the first embodiment of the present invention. Although FIG. 4 shows the relationship between the bearing 5 and the bearing support member 6, the relationship between the bearing 5 and the bearing support member 7 is also the same. The support structure of the hoisting machine according to the first embodiment has a gap 6b formed by contacting the bearing 5, the bearing support member 6, the inner diameter surface 6a of the inner peripheral portion of the bearing support member 6, and the bearing 5. And.

That is, the inner diameter surface 6a of the bearing support member 6 partially contacts the outer ring 5c of the bearing 5, so that a gap 6b exists between the inner diameter surface 6a of the bearing support member 6 and the outer ring 5c of the bearing 5.
The inner diameter surface 6a of the bearing support member 6 to which the outer ring 5c of the outer peripheral portion of the bearing 5 is fitted is provided so that the bearing 5 and the bearing support member are in line contact at one place and inclined in the axial direction of the bearing 5. Has been done. As a result, the gap 6b formed between the bearing support member 6 and the bearing 5 is formed so as to gradually increase in the direction in which the rotating shaft 4 thermally expands. Further, the gap 6b is formed so as to gradually increase in the radial direction of the rotation axis.

Since the inner diameter surface 6a of the bearing support member 6 has a shape that is inclined so that the gap 6b gradually increases, the entire bearing 5 can easily slide in the axial direction. As a result, even when the rotating shaft 4 thermally expands due to the heat generated by the bearing 5, the entire bearing 5 can easily move in the axial direction. Therefore, when the inner ring 5a moves in the axial direction together with the rotating shaft 4, the outer ring 5c also tends to move in the same direction as the inner ring 5a. As a result, the change in the gap 5d between the inner ring 5a and the outer ring 5c and the rolling element 5b can be suppressed, and the increase in the axial load of the bearing 5 can be suppressed.

Further, the gap 6b between the bearing 5 and the bearing support member 6 gradually increases in the radial direction as well. Therefore, even when the bearing 5 thermally expands in the radial direction, the entire bearing 5 slides in the axial direction, so that only the inner ring 5a does not move in the axial direction together with the rotating shaft 4. As a result, it is possible to suppress a change in the gap 5d between each of the inner ring 5a and the outer ring 5c of the bearing 5 in the radial direction and the rolling element 5b, and it is possible to suppress an increase in the load in the radial direction of the bearing 5.

As described above, according to the first embodiment, the shape of the bearing support member and the machine groove are changed so that the position of the bearing can be easily slid with the thermal expansion of the rotating shaft. As a result, overload of the bearing can be prevented, damage to the bearing can be prevented, the life of the bearing can be extended, and the reliability of the device can be improved.

In addition, the conventional method of preventing heat generation by cooling has a problem that the configuration of the device becomes complicated. On the other hand, according to the first embodiment, it has a simple configuration in which only the shape of the bearing support member and the machine groove are changed to take measures against thermal expansion. As a result, a special cooling mechanism is not required, maintenance is facilitated, maintenance costs can be reduced, and highly reliable equipment can be obtained at low cost.

Embodiment 2.
In the second embodiment, the structure of the inner diameter surface of the bearing support member different from that of FIG. 4 in the first embodiment will be described in order to suppress the overload on the bearing 5. FIG. 5 is a schematic view of the bearing support structure according to the second embodiment of the present invention. In FIG. 5, the same reference numerals as those of the reference reference numerals of the first embodiment of FIG. 4 are the same or similar components, and detailed description thereof will be omitted.

In the second embodiment, a plurality of protrusions 12c for linear contact between the bearing 5 and the bearing support member 12 are provided on the inner diameter surface 12a of the bearing support member 12 into which the bearing 5 is fitted in the axial direction. That is, the inner diameter surface 12a of the bearing support member 12 is in line contact with the bearing 5 at a plurality of locations, so that a gap 12b is formed at a plurality of locations.

As shown in the first embodiment of FIG. 4, when the bearing 5 and the bearing support member 6 are in line contact at one place, when the rotating shaft 4 thermally expands, the bearing 5 moves in the axial direction as compared with the conventional structure. It becomes easier to slide. However, when the radial load applied to the bearing 5 is large, the bearing support member 6 cannot support the bearing 5 only by line contact at one place, and the bearing 5 may be damaged.

Therefore, in the second embodiment, as shown in FIG. 5, a plurality of protrusions 12c are formed side by side on the inner diameter surface 12a of the bearing support member 12 in the axial direction of the rotating shaft 4. Since the plurality of protrusions 12c come into contact with the outer diameter surface of the bearing 5, there are gaps between the plurality of protrusions 12c.
With such a structure, the number of places where the bearing 5 is supported increases, and the supporting strength of the bearing 5 can be ensured. As a result, damage to the bearing 5 can be suppressed even when the radial load applied to the bearing 5 is large.

Embodiment 3.
In the third embodiment, the structure of the inner diameter surface of the bearing support member when the load of the radial load applied to the bearing 5 is larger than that of the structures of the first and second embodiments will be described with reference to FIG. .. FIG. 6 is a schematic view of the bearing support structure according to the third embodiment of the present invention. In FIG. 6, the same reference numerals as those of the reference reference numerals of the first embodiment of FIG. 4 are the same or similar components, and detailed description thereof will be omitted.

In the third embodiment, the inner diameter surface 13a of the bearing support member 13 into which the bearing 5 is fitted is provided with a curved surface shape. That is, a plurality of gaps 13b are provided by the contact between the inner diameter surface 13a of the bearing support member 13 and the bearing 5.

In the third embodiment, the bearing 5 and the bearing support member 13 can be brought into surface contact with each other by forming the inner diameter surface 13a of the bearing support member 13 into a curved surface shape. As a result, even if a larger radial load is applied to the bearing 5, the bearing 5 can be supported by the bearing support member 13, and damage to the bearing 5 can be suppressed.

Embodiment 4.
In the fourth embodiment, the structure of the contact surface of the bearing support member when the radial load applied to the bearing 5 is larger than that of the structure of the third embodiment will be described with reference to FIG. 7. FIG. 7 is a schematic view of the bearing support structure according to the fourth embodiment of the present invention. In FIG. 7, the same reference numerals as those of the reference reference numerals of the first embodiment of FIG. 4 are the same or similar components, and detailed description thereof will be omitted.

In the fourth embodiment, a plurality of curved protrusions 14c are provided on the inner diameter surface 14a of the bearing support member 14 to which the bearing 5 is fitted. That is, gaps 14b are provided at a plurality of locations due to surface contact between the plurality of protrusions 14c of the bearing support member 14 and the bearing 5. A plurality of protrusions 14c are formed side by side on the inner diameter surface 14a of the bearing support member 14 in the axial direction of the rotating shaft 4. Since the plurality of protrusions 14c come into contact with the outer diameter surface of the bearing 5, there are gaps between the plurality of protrusions 14c.

In the fourth embodiment, by providing the plurality of protrusions 14c on the inner diameter surface 14a of the bearing support member 14, the bearing 5 and the bearing support member 14 can be brought into surface contact at a plurality of places. As a result, even if a larger radial load is applied to the bearing 5, the bearing 5 can be supported at a plurality of locations by the bearing support member 14, and damage to the bearing can be suppressed.

Further, as the load applied to the bearing 5 increases, the heat generation also increases, so that a special cooling mechanism may be required for the hoisting machine. On the other hand, in the fourth embodiment, the simple structure eliminates the need for a cooling mechanism and suppresses heat generation of the bearing 5. As a result, an inexpensive and highly reliable device can be obtained.

Embodiment 5.
In the first to fourth embodiments, only the shape of the bearing support member is changed so that the entire bearing can easily slide in the axial direction. On the other hand, in the fifth embodiment, a structure for changing the shape of the bearing will be described with reference to FIG. FIG. 8 is a schematic view of the bearing support structure according to the fifth embodiment of the present invention. In FIG. 8, the same reference numerals as those of the reference reference numerals of the first embodiment of FIG. 4 are the same or similar components, and detailed description thereof will be omitted.

The outer diameter surface 15a of the outer ring of the bearing 15 is provided with a bearing inclined surface so as to be inclined in the axial direction. The inner diameter surface 6a of the bearing support member 6 is provided with a support member inclined surface that comes into contact with the bearing inclined surface. Here, the bearing inclined surface corresponds to the outer diameter surface 15a of the bearing 15. The inclined surface of the support member corresponds to the inner diameter surface 6a of the bearing support member 6. The inner diameter surface 6a of the bearing support member 6 is fitted to the outer diameter surface 15a of the bearing 15. The outer diameter surface 15a of the bearing 15 has a shape that changes with the same inclination as the shape change of the inner diameter surface 6a of the bearing support member 6. That is, the distance from the axis of the rotating shaft 4 to the bearing inclined surface and the distance from the axis of the rotating shaft 4 to the inclined surface of the support member increase from one side to the other side in the axial direction of the rotating shaft 4.

In order to support the bearing 15, the shape of the bearing support member 6 can be changed according to the magnitude of the radial load applied to the bearing 15. However, as the radial load applied to the bearing 15 increases, the shape of the bearing support member 6 becomes complicated. That is, in order to cope with a larger radial load applied to the bearing 5 only by the shape of the bearing support member 6, the shape of the bearing support member 6 becomes complicated, which increases the processing cost and processing time.

Therefore, the fifth embodiment includes a configuration in which the shape of the outer diameter surface 15a of the bearing 15 is changed with the same inclination as the shape change of the bearing support member 6. With such a configuration, it is possible to maintain a mechanism in which the bearing 15 is easy to slide even when the rotating shaft 4 is thermally expanded. Further, even if a large radial load is applied to the bearing 15, the bearing 15 can slide and move along the bearing support member 6 according to the inclination. Therefore, the bearing 15 can be reliably supported by the bearing support member 6, and damage to the bearing 15 can be suppressed. As a result, it is possible to cope with the case where the bearing support member 6 and the outer diameter surface 15a of the bearing 15 and the radial load are further large.

Embodiment 6.
In the fifth embodiment shown in FIG. 8, the configuration in which the shape of the outer ring of the bearing is changed with the same inclination as the shape change of the bearing support member has been described. On the other hand, in the sixth embodiment, a structure in which the bearing fixing member is further used will be described with reference to FIG. FIG. 9 is a schematic view of the bearing support structure according to the sixth embodiment of the present invention. In FIG. 9, the same reference numerals as those of the reference reference numerals of the first embodiment of FIG. 4 are the same or similar components, and detailed description thereof will be omitted.

The bearing 45 has a structure including a bearing fixing member 16 and a bearing body 35 provided inside the bearing fixing member 16. Therefore, the outer peripheral portion of the bearing fixing member 16 constitutes the outer peripheral portion of the bearing 45. The bearing fixing member 16 newly added in the sixth embodiment is arranged between the bearing support member 17 and the bearing body 35. The bearing body 35 is held by the bearing fixing member 16. The bearing 45 is held by the bearing support member 17. That is, the bearing fixing member 16 as a collar or a ring is fitted to the outer ring of the bearing body 35.

The inner diameter surface 17a of the bearing support member 17 is provided so as to be inclined in the axial direction, as in FIG. On the other hand, the outer diameter surface 16a of the bearing fixing member 16 is provided in a shape that changes with the same inclination as the shape change of the bearing support member 17.

Further, a flat portion 16b and a flat portion 17b are provided on a part of the bearing fixing member 16 where the outer diameter surface 16a and the inner diameter surface 17a of the bearing support member 17 face each other, respectively. Here, the flat portion 16b corresponds to a bearing parallel surface. The flat portion 17b corresponds to a parallel surface of the support member. The bearing parallel surface and the support member parallel surface are provided so as to be in contact with each other. The distance from the axis of the rotating shaft 4 to the parallel surface of the bearing and the distance from the axis of the rotating shaft 4 to the parallel surface of the support member are provided so as to be constant in the axial direction of the rotating shaft.

In the structure shown in FIG. 8 in the above-described fifth embodiment, when a large load in the radial direction acts on the bearing, the bearing 5 easily slides even if the rotating shaft 4 thermally expands. Further, in order to reduce the number of parts, it was effective to change the shapes of the inner diameter surface 6a of the bearing support member 6 and the outer diameter surface 15a of the outer ring of the bearing 15. However, the structure according to the fifth embodiment is costly because it is necessary to prepare a custom-made bearing 15.

On the other hand, in the sixth embodiment, a structure in which the bearing fixing member 16 is arranged between the bearing 5 and the bearing support member 17 is used. The outer diameter surface 16a of the bearing fixing member 16 is formed in a shape that allows the bearing 5 to slide easily. As a result, it is possible to realize a mechanism in which a non-custom-made inexpensive bearing 5 can easily slide without changing the shape of the outer ring of the bearing 5.

Further, by providing the flat portions 16b and 17b on a part of the contact surfaces of the bearing support member 17 and the bearing fixing member 16, the bearing 5 can be supported by the flat portions 16b and 17b even when the load in the radial direction is large. ..

Embodiment 7.
In the sixth embodiment shown in FIG. 9, a configuration that is easy to slide and can be supported even when the radial load is large has been described. On the other hand, in the seventh embodiment, a configuration for restricting the sliding range of the bearing will be described with reference to FIG. FIG. 10 is a schematic view of a bearing support structure according to a seventh embodiment of the present invention. In FIG. 10, the same reference numerals as those of the reference reference numerals of the first embodiment of FIG. 4 are the same or similar components, and detailed description thereof will be omitted.

The bearing 46 has a structure including a bearing fixing member 18 and a bearing body 36 provided inside the bearing fixing member 18. Therefore, the outer peripheral portion of the bearing fixing member 18 constitutes the outer peripheral portion of the bearing 46. A bearing fixing member 18 is fitted to the outer ring of the bearing body 36. The outer diameter surface 18a of the bearing fixing member 18 is provided with a stepped shape. On the other hand, the inner diameter surface 19a of the bearing support member 19 is provided with a stepped shape similar to the shape change of the outer diameter surface 18a of the bearing fixing member 18.

The temperatures of the bearing 5 and the rotating shaft 4 fluctuate up and down depending on the operating status of the elevator. Therefore, in the case of a mechanism in which the bearing 5 slides easily, the bearing 5 returns to its original position due to the temperature decrease of the bearing 5 and the rotating shaft 4 after the bearing 5 slides due to the temperature rise of the bearing 5 and the rotating shaft 4. Try to. That is, a force for returning to the origin position acts on the bearing 5.

In such a case, as in the seventh embodiment, the bearing 5 has a rotating shaft 4 by forming the inner diameter surface 19a of the bearing support member 19 and the outer diameter surface 18a of the bearing fixing member 18 into a stepped shape. Even if it tries to return to the contraction direction of the bearing 5, it can be regulated so that the bearing 5 does not slide in the contraction direction of the rotating shaft 4 from the reference position. Further, the above structure makes it unnecessary to adjust the bearing 5 at the time of maintenance, and the maintenance cost can be suppressed. Further, in order to make the bearing easy to slide, a slippery material may be used for the outer diameter surface 18a of the bearing fixing member 18 and the inner diameter surface 19a of the bearing support member 19.

Embodiment 8.
In the eighth embodiment, a configuration that can support the bearing 5 even when the width of the bearing 5 is small will be described with reference to FIG. FIG. 11 is a schematic view of a bearing support structure according to the eighth embodiment of the present invention. In FIG. 11, the same reference numerals as those of the reference reference numerals of the first embodiment of FIG. 4 are the same or similar components, and detailed description thereof will be omitted.

The bearing 47 has a structure including a bearing fixing member 20 and a bearing body 37 provided inside the bearing fixing member 20. Therefore, the outer peripheral portion of the bearing fixing member 20 constitutes the outer peripheral portion of the bearing 47. A bearing fixing member 20 is fitted to the outer ring of the bearing 5. A second bearing fixing member 21 as a collar or a ring is further provided between the inner diameter surface 22a of the bearing support member 22 and the outer diameter surface 20a of the bearing fixing member 20 into which the bearing 5 is fitted. Here, the second bearing fixing member 21 corresponds to a spacer formed in an annular shape.

A second bearing fixing member 21 is fitted to the outer diameter surface 20a of the bearing fixing member 20. Further, the outer diameter surface 20a of the bearing fixing member 20 and the inner diameter surface 21a of the second bearing fixing member 21 are fitted. Further, the outer diameter surface 21b of the second bearing fixing member 21 and the inner diameter surface 22a of the bearing support member 22 are fitted.

The outer diameter surface 20a of the bearing fixing member 20, the inner diameter surface 21a and the outer diameter surface 21b of the second bearing fixing member 21, and the inner diameter surface 22a of the bearing support member 22 are all provided with inclinations in the rotation axis direction. ing. All of these slopes are provided in the same changing shape.

When the width of the bearing is small, when the bearing slides due to the thermal expansion of the rotating shaft, the area in contact between the bearing support member and the bearing or the bearing fixing member in which the bearing is fitted is small. Therefore, the radial load may not be supported.

On the other hand, as in the eighth embodiment, by further providing the second bearing fixing member 21, the inner diameter surface 21a of the second bearing fixing member 21 and the bearing support member 22 are brought into contact with each other, and the bearing support member 22 is brought into contact with each other. The outer diameter surface 21b of the bearing fixing member 21 of 2 and the bearing fixing member 20 can be brought into contact with each other. As a result, the radial load can be supported with the contact area increased.

FIG. 12 is a modified example of the bearing support structure of FIG. 11, and is a schematic view in which a flat portion is provided on the bearing fixing member. The bearing 48 has a structure including a bearing fixing member 23 and a bearing body 38 provided inside the bearing fixing member 23. Therefore, the outer peripheral portion of the bearing fixing member 23 constitutes the outer peripheral portion of the bearing 48.

In FIG. 12, the bearing fixing member 23 inclined in the axial direction is provided with a flat portion 23c parallel to the axial direction in a part of the inclined outer diameter surface 23a. Similarly, the inner diameter surface 24a and the outer diameter surface 24b of the second bearing fixing member 24, which are inclined in the axial direction, are provided with a flat portion 24c and a flat portion 24d, respectively, in a portion of the inclination. Here, the second bearing fixing member 24 corresponds to a spacer formed in an annular shape. Further, the bearing support member 25 inclined in the axial direction is provided with a flat portion 25c on a part of the inclined inner diameter surface 25a.

That is, each of the flat portion 23c, the flat portion 24c, the flat portion 24d, and the flat portion 25c is provided so as to form a surface parallel to each other. The distance from the axis of the rotating shaft 4 to the flat portion 23c and the distance from the axis of the rotating shaft 4 to the flat portion 24c are provided so as to be constant in the axial direction of the rotating shaft. Further, the distance from the axis of the rotating shaft 4 to the flat portion 24d and the distance from the axis of the rotating shaft 4 to the flat portion 25c are provided so as to be constant in the axial direction of the rotating shaft. Therefore, the structure shown in FIG. 12 can support a larger radial load by having these flat portions.

Embodiment 9.
In the seventh embodiment shown in FIG. 10, the inner diameter surface 19a of the bearing support member 19 and the outer diameter surface 18a of the bearing fixing member 18 are formed into a stepped shape so that the sliding range of the bearing 5 can be regulated. explained. On the other hand, in the ninth embodiment, a configuration in which the sliding range of the bearing can be more regulated will be described with reference to FIG. FIG. 13 is a schematic view of a bearing support structure according to a ninth embodiment of the present invention. In FIG. 13, the same reference numerals as those of the reference reference numerals of the first embodiment of FIG. 4 are the same or similar components, and detailed description thereof will be omitted.

In FIG. 13, the bearing support member 27 is fitted to the outer diameter surface 26a, which is the outer ring of the bearing 26. The outer diameter surface 26a, which is the outer peripheral portion of the bearing 26, is provided with a convex portion 26b at the center of the rotating shaft 4 in the axial direction. On the other hand, a recess 27b is provided on the inner diameter surface 27a which is the inner peripheral portion of the bearing support member 27. The concave portion 27b has convex portions 27c at both ends in the axial direction of the rotating shaft 4. The convex portions 27c at both ends of the concave portion 27b are in contact with the outer diameter surface 26a of the bearing 26. As a result, there are gaps between the convex portions 27c at both ends of the inner diameter surface of the bearing support member 27 and the convex portions 26b, respectively.

If the heat generated by the bearing and the rotating shaft is larger than expected, the rotating shaft may thermally expand beyond the range in which the bearing and the bearing support member are fitted, and the bearing may be derailed from the bearing support member. On the other hand, as in the ninth embodiment, when the convex portion 26b is provided on the bearing 26 side and the concave portion 27b is provided on the bearing support member 27 side, the bearing 26 slides due to thermal expansion of the rotating shaft 4. It is possible to prevent the bearing 26 from coming off from the bearing support member 27. Further, even when the bearing 26 slides in the contraction direction of the rotating shaft 4, it is possible to prevent the wheel from coming off in the same manner.

As described above, even if the heat generated by the bearing and the rotating shaft becomes larger than expected, an overload is not applied to the bearing, and a highly reliable support structure can be obtained.

An example of utilizing the support structure of the present invention is to apply it to an elevator hoist, but the present invention is not limited thereto. The present invention can be used not only for industrial electric motors but also for hoists, agricultural machinery and the like.

1 motor, 4 rotating shafts, 5, 15, 26, 45, 46, 47, 48 bearings, 9 support pedestal (winding machine support pedestal), 6, 7, 12, 13, 14, 17, 19, 22, 25 , 27 Bearing support member, 6b, 12b, 13b, 14b gap, 12c, 14c protrusion, 26b, 27c convex part, 27b concave part, 16, 18, 20, 23 bearing fixing member, 21, 24 second bearing fixing member ( (Aspherical spacer), 6a, 12a, 13a, 14a, 17a, 19a, 21a, 22a, 24a, 25a Inner diameter surface, 15a, 16a, 18a, 20a, 21b, 23a, 24b, 26a Outer diameter surface, 16b, 23c Flat Parts (bearing parallel surface), 17b, 25c Flat part (support member parallel surface), 24c, 24d Flat part, 35, 36, 37, 38 Bearing body.

Claims (6)

Bearings that support the rotating shaft and
A bearing support member for accommodating the bearing is provided.
Since the inner peripheral portion of the bearing support member is partially in contact with the outer peripheral portion of the bearing, a gap exists between the inner peripheral portion of the bearing support member and the outer peripheral portion of the bearing .
The inner peripheral portion of the bearing support member has a plurality of convex portions aligned in the axial direction of the rotating shaft.
The plurality of convex portions are in contact with the outer peripheral portion of the bearing.
The gap is a support structure of a hoisting machine existing between the plurality of convex portions. Bearings that support the rotating shaft and
A bearing support member for accommodating the bearing is provided.
Since the inner peripheral portion of the bearing support member is partially in contact with the outer peripheral portion of the bearing, a gap exists between the inner peripheral portion of the bearing support member and the outer peripheral portion of the bearing .
The inner peripheral portion of the bearing support member has convex portions at both ends in the axial direction of the rotating shaft.
The convex portions at both ends are in contact with the outer peripheral portion of the bearing.
The outer peripheral portion of the bearing has a convex portion at the center in the axial direction of the rotating shaft.
The convex portion at the central portion is located between the convex portions at both ends in the axial direction of the rotating shaft, and is in contact with the inner peripheral portion of the bearing support member.
The gap is a support structure of a hoisting machine existing between the convex portions at both ends and the convex portions at the central portion. Bearings that support the rotating shaft and
A bearing support member for accommodating the bearing is provided.
A bearing inclined surface is formed on the outer peripheral portion of the bearing.
A support member inclined surface that comes into contact with the bearing inclined surface is formed on the inner peripheral portion of the bearing support member.
The distance from the axis of the rotating shaft to the bearing inclined surface and the distance from the axis of the rotating shaft to the inclined surface of the support member are increased from one side to the other side in the axial direction of the rotating shaft. Machine support structure. The bearing has a bearing fixing member and a bearing body provided inside the bearing fixing member.
The support structure for a hoist according to claim 3 , wherein the outer peripheral portion of the bearing fixing member is an outer peripheral portion of the bearing. A bearing parallel surface is formed on the outer peripheral portion of the bearing.
A parallel surface of the support member that contacts the parallel surface of the bearing is formed on the inner peripheral portion of the bearing support member.
The third or fourth aspect, wherein the distance from the axis of the rotating shaft to the parallel surface of the bearing and the distance from the axis of the rotating shaft to the parallel surface of the support member are constant in the axial direction of the rotating shaft. Support structure of the hoisting machine. An annular spacer provided between the outer peripheral portion of the bearing and the inner peripheral portion of the bearing support member is provided.
The inner peripheral portion of the spacer is in contact with the outer peripheral portion of the bearing, and the inner peripheral portion thereof is brought into contact with the outer peripheral portion of the bearing.
The hoisting machine support structure according to any one of claims 3 to 5 , wherein the outer peripheral portion of the spacer is in contact with the inner peripheral portion of the bearing support member.

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