JPS62196417A - Bearing device - Google Patents

Abstract

PURPOSE:To reduce noise and abrasion between a bearing end surface and a washer by interposing a plurality of washers between a load applying portion and the bearing end surface, and forming groove portions pointing in the specified direction on the end surface of a bearing on washer side. CONSTITUTION:When a rotary shaft 19 is rotated, lubricating oil in an oil- impregnated bearing 14 oozes out to lubricate a sliding surface. Downward thrust load applied to the rotary shaft 19 is received by the end surface of the oil impregnated bearing 14 through a collar 20 and two washers 21, 22. Accordingly, the washer 21 is rotated by frictional force received from the collar 20, and the washer 22 is rotated by frictional force received from the washer 21. At this time, as a plurality of grooves 23 are formed on the end surface of the oil impregnated bearing 14 on the washer 22 side in such a manner as to point in the direction of obstructing the rotation of the washer 22, the rotating speed of the washer 22 is lowered as compared with the washer 21. Thus, sliding noise and local abrasion between the washer 22 and the oil impregnated bearing 14 can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial Application Field) The present invention relates to a bearing device in which a thrust load applied to a rotating shaft is received by an end face of the bearing.

(Prior Art) For example, in a conventional bearing device for a vertical shaft type motor used in a ceiling ventilation fan, an oil-impregnated bearing 2 is supported at the center of the end face of a frame 1, as shown in FIG. It had a structure in which the rotating shaft 3 was inserted through and supported. Regarding the thrust load, a washer 5 is interposed between the collar 4 as a load applying part fitted and fixed to the rotating shaft 3 and the end face of the oil-impregnated bearing 2.
It was designed to receive thrust loads by receiving them at the end faces of the cylinder. In this case, the end surface of the oil-impregnated bearing 2 that receives the washer 5 was a flat surface.

When the rotary shaft 3 is operated face-to-face, the lubricating oil inside the oil-impregnated bearing 2 oozes onto the sliding surface of the rotary shaft 3 due to the rise in temperature of the rotary shaft 3 and the suction effect caused by the rotation of the rotary shaft 3, and lubricates the sliding surface of the rotary shaft 3. During this operation, the washer 5 rotates at high speed to follow the thrust load applied via the collar 4 while contacting the end face of the oil-impregnated bearing 2 due to the frictional force received from the collar 4 and the rotating shaft 3. However, since the end surface of the oil-impregnated bearing 2 that receives this washer 5 is a flat surface, this end surface is inherently difficult to form a lubricating oil film, and the lubricating effect on the washer 5 becomes insufficient. A relatively large frictional force is generated. Even so, since the frictional force between the washer 5 and the collar 4 is much larger, the washer 5 follows the collar 4 and rotates at high speed even though it receives a relatively large frictional force from the oil-impregnated bearing 2 side. As a result, a relatively large sliding noise is generated between the oil-impregnated bearing 2 and the washer 5, and the sliding motion of both is locally worn out in a relatively short period of time, resulting in a shortened service life. was there.

(Problem to be Solved by the Invention) According to the above-mentioned conventional configuration, although the river action between the end face of the oil-impregnated bearing 2 and the washer 5 is inherently insufficient, the washer 5 is attached to the rotating shaft. Since it rotates at high speed following the collar 4 of No. 3, there are problems in that noise increases due to the sliding between the end face of the oil-impregnated bearing 2 and the washer 5, and that the life of the bearing is shortened due to local wear.

The present invention is intended to solve these problems, and its purpose is to reduce sliding noise during rotation, reduce local wear caused by sliding, and provide long-term use. An object of the present invention is to provide a bearing device that can extend its service life.

[Structure of the Invention] (Means for Solving the Problems) The bearing device of the present invention is configured such that the thrust load applied to the rotating shaft is received by the end face of the bearing via a load applying portion provided on the rotating shaft. A plurality of washers are interposed between the load applying portion and the end face of the bearing, and
A groove portion oriented in a direction intersecting the circumferential direction of the bearing is formed on the end surface of the bearing on the washer side.

(Function) Since the groove formed on the end face of the bearing on the washer side is oriented in a direction that intersects the circumferential direction, that is, in a direction that prevents rotation of the washer, the sliding resistance between the end face of the bearing and the washer increases. As a result, the rotational speed of the washer that contacts the end face of the bearing can be kept low. As a result, during operation, the rotational speed of the plurality of washers interposed between the end face of the bearing and the 6:1 load applying part gradually decreases from the load applying part side to the bearing side. The speed difference between each sliding surface between the load-applying part and the washer that contacts this, between each washer, and between the load applying part and the washer that contacts this becomes small.

(Embodiment) An embodiment in which the present invention is applied to a vertical shaft type motor will be described below with reference to FIGS. 1 to 3. Reference numeral 11 denotes a motor frame in which a stator 12 is fitted, and a tapered cylindrical bearing support part 13 is formed at the center of the end face of this motor frame. An oil-impregnated bearing 14, which will be described later, is supported on the bearing support portion 13, and an oil core 15 made of felt, for example, impregnated with lubricating oil is in contact with the oil-impregnated bearing 14 on the outer peripheral portion of the oil-impregnated bearing 14. It is arranged. The oil wick 15 is housed in a stepped cylindrical oil pan case 16 fixed to the inner side of the end surface of the motor frame 11, and the stepped portions 1.6 of the oil pan case 16.
The oil-impregnated bearing 1
4 is pressed against the bearing support portion 13 side. On the other hand, an annular collar 20 serving as a load applying portion is fitted and fixed to the rotating shaft 19 of the rotor 18, and a collar 20 is fitted to the rotating shaft 19.
A plurality of washers 21 and 22, for example, two washers, are rotatably inserted between the oil-impregnated bearing 14 and the oil-impregnated bearing 14. In this state, the movement of the two washers 21 and 22 in the axial direction (in the upward direction in the figure) is restricted by the collar 20. In this case, the washers 21 and 22 are made of a resin with relatively high wear resistance, such as nylon. The rotating shaft 19, into which the two washers 21.
22 is located inside the oil bearing case 16, and the thrust load applied to the rotating shaft 19 is received by the end face of the oil bearing 14 via the collar 20 and two washers 21 and 22.

Now, to explain in detail about the oil-impregnated bearing 14, this oil-impregnated bearing 14 is made by impregnating a porous member such as sintered metal with lubricating oil, and its outer peripheral surface is formed into a spherical shape to allow self-alignment. It makes it seem possible. Historically, the end face of the oil-impregnated bearing 14 on the washer 22 side has four grooves 23 oriented in a direction intersecting the circumferential direction (sliding direction), for example, in a radial direction, as shown in FIGS. 2 and 3. is forming. In this embodiment, a similar groove 23 is formed on the opposite end surface of the oil-impregnated bearing 14 to eliminate the directionality, so that neither end surface of the oil-impregnated bearing 14 can be directed toward the washer 22 during assembly. It is constructed in such a way that it has a good set-γ property.

Next, the operation of the L configuration will be explained. When the rotating shaft 19 rotates, the lubricating oil inside the oil-impregnated bearing 14 leaks onto the sliding surface of the rotating shaft 19 to lubricate it.

Also, during this operation, the downward thrust load applied to the rotating shaft 19 is applied to the collar 20 and the two washers 21 and 22.
Since the lower washer 22 is in contact with the end face of the oil-impregnated bearing 14 and the washer 21 on the i-1- side is in contact with the collar 20 in FIG. . At this time, the washer 21 on the -I- side rotates at a relatively high speed due to the frictional force received from the collar 20 so as to follow this. On the other hand, the washer 22 on the F side also rotates without contacting the end surface of the oil-impregnated bearing 14 due to the frictional force caused by the rotation of the washer 21 on the second side. Due to the suction of the lubricating oil as the washer 22 rotates, a small amount of the lubricating oil inside the oil-impregnated bearing 4 oozes out to the end face on the washer 22 side, lubricating the washer 22 to some extent. However, in this embodiment, four grooves 23 are formed on the end face of the oil-impregnated bearing 14 on the washer 22 side so as to be oriented in a direction intersecting the circumferential direction (sliding direction), that is, in a direction that prevents the rotation of the washer 22. The presence of these grooves 23 increases the sliding resistance to the washer 22, and the rotational speed of the washer 22 becomes lower than that of the washer 21 on the -1- side. Therefore, since the washer 22 rotates at a relatively low speed on the end face -1- of the oil-impregnated bearing 14, the sliding noise and local wear between the two are significantly reduced.

By the way, when the number of washers interposed between the oil-impregnated bearing 14 and the collar 20 is set to one, when this washer is rotated at a low speed as in this embodiment, on the contrary, this washer and the collar 20 As the speed difference between the parts increases, the sliding noise and wear in this part increase significantly, making it impossible to reduce the noise and extend the service life as a whole.

However, in this embodiment, the oil-impregnated bearing 14 end face and the collar 20
Since two washers 21 and 22 are interposed between the two washers 21 and 22, the rotational speed is stepped in the order of the collar 20, the upper washer 21, and the lower washer 22 by causing slippage between the washers 21 and 22. This causes the gap between washer 22 and collar 20 and between both washers 21
．． The speed difference between 22 becomes small. For this reason, between the washer 22 and the collar 20 and both washers 21.2
The sliding noise generated between the two parts can also be suppressed to a low level, and the overall noise can be reduced.

Moreover, by reducing the speed difference between the washers 21 and 22 and between the washer 21 and the collar 20, local wear in those areas can be suppressed, thereby extending the service life.

Although only four grooves 23 are formed in a radial manner in this embodiment, the grooves 23 are not limited to this, but may be three or less, or five or more as in another embodiment of the present invention shown in FIG. It is also possible to form a configuration. Further, the grooves do not necessarily have to be formed radially as in this embodiment, but may be formed so as to be oriented in any direction as long as they intersect with the circumferential direction of the end face of the bearing. For example, as in still another embodiment of the present invention shown in FIG. 5, a plurality of grooves 24 may be formed parallel to each other so that the grooves are oriented in the direction J that intersects the circumferential direction. It is something. Alternatively, the groove may be formed only on one end surface of the bearing. Furthermore, three or more washers may be interposed between the bearing and the load applying section. In addition, the present invention can be modified in various ways without departing from the spirit, such as being applicable to a horizontal shaft type motor.

[Effects of the Invention] As is clear from the explanation below, the present invention provides a load (= f
A plurality of washers are interposed between the 'j part and the end face of the bearing, and a groove part oriented in a direction intersecting the circumferential direction is formed on the end face of the bearing on the washer side -10=. , the sliding resistance acting on the washer from the bearing end surface increases, and the rotational speed of the multiple washers gradually decreases from the load application side to the bearing side, which causes contact with the bearing end surface. The speed difference between each sliding surface between the washer and the washer that is in contact with the washer, and between the load applying part and the washer in contact with it is reduced, resulting in lower overall noise and less localized wear. It is possible to provide a bearing device that has the excellent effect of increasing the lifespan by reducing the number of bearings.

[Brief explanation of drawings]

1 to 3 show an embodiment in which the present invention is applied to a vertical shaft type motor, in which FIG. 1 is a longitudinal sectional front view of the lower part of the motor, FIG. Figure 3 is the same plan view,
4 and 5 are views corresponding to FIG. 3 showing other different embodiments of the present invention, and FIG. 6 is a longitudinal sectional front view showing a conventional bearing device. In the drawing, 14 is an oil-impregnated bearing (bearing), 19 is a rotating shaft, and 20
is a collar (load applying part), 21 and 22 are washers, 2
3 and 24 are grooves.

Claims (1)

[Claims] 1. A rotary shaft is inserted into and supported by a bearing, and a thrust load applied to the rotary shaft is received by an end face of the bearing via a load applying portion provided on the rotary shaft, wherein the load applying portion and the A bearing device characterized in that a plurality of washers are interposed between the bearing and the end face of the bearing, and a groove portion oriented in a direction intersecting the circumferential direction of the bearing is formed in the end face of the bearing on the washer side.