JPS6252198B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a bearing lubrication device, and more particularly to a device for pumping and supplying lubricating oil using an oil disk.

[Technical background of the invention and its problems]

It is well known that a disc-shaped oil disk is widely used as a self-lubricating method for bearings. Unlike an oil ring, this oil disk rotates integrally with the shaft, so it is extremely reliable in terms of oil supply reliability.

By the way, as the circumferential speed of the bearing surface and the applied load increase, there is naturally a limit to the amount of oil supplied by the oil disk, so there is a so-called forced oil supply method that uses an electric pump to exceed this limit.

However, the forced lubrication system has a complicated structure and is troublesome to maintain, and also has extremely disadvantageous factors in terms of labor and resource conservation, such as failure of the electric pump or backup in the event of a power outage.

Therefore, there is an extremely strong desire to expand the applicable range of self-lubricating using an oil disk, which is advantageous in this respect. The disadvantage of oil discs is that as the outer circumferential speed of the disk increases, the amount of pumped lubricating oil that is thrown away increases, and when a certain circumferential speed is exceeded, the desired amount of pumped oil cannot be obtained. For example, curve a in FIG. 4 shows the relationship between rotational speed and pumping amount for a bearing with a diameter of 140 mm and an oil disk with a diameter of 290 mm. As is clear from this figure, when the circumferential speed of the oil disk exceeds approximately 4 m/sec, the pumping amount begins to decrease. Therefore, in the case of a rotating machine that is trying to obtain the desired oil flow rate of 2.5/min, the rotation speed range is
Limited to the range of 120-500r.pm.

In order to transport this scattered oil as far above the oil disk as possible, various proposals have been made to provide an oil guiding cover that includes the outer periphery of the oil disk (Japanese Utility Model Publication No. 82596/1983). However, the rate of increase in the pumped amount was at most 10 to 20%, which was not satisfactory. Additionally, there is a problem in that the bearing device becomes larger due to the attachment of the oil guiding cover.

In addition, a plurality of rolling elements are placed around the outer circumference of the rotating shaft, making contact with the shaft and the bearing box, and as the shaft rotates, the rolling elements rotate and revolve, drawing up the lubricating oil from the bearing box. There is something. (Jikko Sho 35-
(Japanese Patent Publication No. 15316) According to this configuration, even if the rotating shaft rotates at high speed, the revolution speed of the rolling elements is reduced, so oil can be effectively supplied.

However, since the rolling elements are in contact with the rotating shaft and the stationary bearing box, there is a problem in that the rotating shaft does not allow rocking and cannot be applied to high-speed rotating machines.

[Purpose of the invention]

The present invention has been made in view of the above points, and
The purpose is to provide a self-lubricating device for bearings that can effectively supply pumped oil by making the rotational speed of the oil pumping part lower than the rotational speed of the shaft, and that can also tolerate rocking of the rotating shaft. be.

[Summary of the invention]

In order to achieve the above object, the bearing self-lubricating device of the present invention includes a plurality of rolling elements disposed around the outer periphery of a rotating shaft, which revolve while rotating due to the rotation of this shaft,
This is an improved oil supply device in which the lubricating oil in the bearing box is scraped up by the rolling elements and supplied to the bearing, and the rotating shaft is provided with a flange having a diameter larger than the bearing diameter, and the outer periphery of the flange is formed on the rotating shaft. The rolling element is disposed on the rotary shaft, and an outer ring for holding the rolling element is provided, and the outer ring is locked to the stationary side member with some play, thereby allowing the rotating shaft to swing. .

[Embodiments of the invention]

An embodiment of the present invention will be described below with reference to the drawings. 1 and 2 show a bearing device equipped with a self-lubricating device, in which an oil disk 3 is mounted on one side of a sliding bearing 2 that supports a rotating shaft 1, and an oil disk 3 is mounted on one side of a sliding bearing 2 that surrounds these members. 2
A bearing housing 4 is shown supporting the bearing housing 4.

The structure of the oil disc 3 will be described later, but this oil disc 3 rotates together with the rotating shaft 1 and pumps up lubricating oil 5 stored in the lower part of the bearing box 4, and an oil paddle 6 attached to the upper part of the sliding bearing 2. The oil is directed to the bearing side and flows into the oil filler port 7 of the bearing.

Next, the oil disk 3 will be explained with reference to FIG. A protruding flange portion 8 is formed on a part of the rotating shaft 1. An annular inner ring 9 is fitted onto the outer periphery of this collar portion 8 by shrink fitting. A concave raceway 9a is formed on the outer periphery of the inner ring 9. An outer ring 13 is provided on the outside of the inner ring 9 with an annular layer 10 in between. A concave raceway 13a is also formed on the inner peripheral side of the outer ring 13. The annular layer 10 is disposed between the inner and outer rings 9 and 13, and has a plurality of rolling elements 11 which are fitted into raceways and are made of spheres that can roll in the circumferential direction. and an annular retainer 12 that slidably envelops the retainer 12 from both sides.

A groove 14 extending in the axial direction is provided in the upper part of the outer ring 13, and a pin 15 protruding from the oil paddle 6 described above is loosely inserted into this groove.
This prevents the outer ring 13 from rotating.

The immersion positional relationship between the oil disk 3 and the lubricating oil 5 configured as described above is such that the oil level OL is set so that the outer peripheral surface of the lowest part of the inner ring 9 is slightly lower than that.

Next, the action will be explained. As the rotating shaft 1 rotates, the inner ring 9 also rotates at the same rotational speed. When the inner ring 9 rotates, the rolling elements 11 in contact with the inner ring 9 rotate on their own axis and revolve around the orbit at a rotation speed slower than that of the rotating shaft. As the rolling elements 11 revolve, the cage 12 attached thereto also revolves at the same rotational speed as the rolling elements 11. In other words, the annular layer 10 composed of the rolling elements 11 and the cage 12 has its lower part immersed in lubricating oil, so it pumps up oil at a rotation speed slower than the rotation speed of the rotating shaft 1.

This number of revolutions can be expressed by an equation for determining the number of revolutions of the rolling elements in a rolling bearing. In other words, if the number of revolutions is n, then n=(1-dcosα/dm)N/2(rpm)...(1) where d: Diameter of rolling element (mm) α: Contact angle of rolling element (°) dm: Pitch diameter of rolling element (mm) N: Rotation speed of rotating shaft (rpm). By using the above-mentioned rolling elements, the rotational speed of the annular layer 10 can be suppressed to about 40% of the rotational speed of the rotating shaft.

FIG. 4 shows the relationship between the amount of lubricating oil pumped up and the rotational speed of the rotating shaft in an experiment using the oil supply device according to this embodiment. For comparison, the pumping characteristics a of a conventional integral disk-shaped oil disk are also shown, and the dimensions of the oil disk are set to be the same. (In this experiment, the wall diameter of the outer ring was made approximately the same as the outer diameter of the conventional oil disc, 290 mm,
(The rolling element has eight balls arranged at equal intervals.) As is clear from this figure, the pumping characteristic b greatly exceeds the high speed range. For example, if we look at bearings that currently require an oil pumping rate of 2.5/min, conventional discs were limited to a range of 120 to 500 rpm, but with the disc of this embodiment, the range is 230 rpm.
It can be used in the range of ~1200rpm. Although a certain unusable range in the low-speed range is unavoidable due to the characteristics of the revolution number, the expanded range in the high-speed range is large, so it is extremely effective in greatly expanding the range in which the bearing can be operated with self-lubrication. .

In addition, since the outer ring 13 is locked with the oil paddle pin 15, which is a stationary side member, with some play, the rotating shaft 1
Does not restrict floating, whirling or axial movement of the

In the above embodiment, the inner ring 9 is fitted to the flange 8 of the rotating shaft 1, but the flange 8 and the inner ring 9 may be integrated. The pin 15 of the oil paddle 6 is engaged with the groove 14, but a round hole is provided in the upper part of the outer ring 13, and the pin 15 is passed through this hole loosely to prevent the outer ring from moving in the axial direction. Either raceway (9a or 13a) of the inner ring may be omitted to form a smooth surface.

Further, the rolling elements 11 are not limited to spheres, and may be rollers.

When this roller is used as a rolling element, an annular relief groove 13b is provided in a part of the raceway of the outer ring 13 as shown in FIGS. It is also possible to provide a hole 13c that opens toward the outer circumference in the upper part, and to eject lubricating oil from this hole. In this way, in addition to the oil scraped up on the side surface of the annular layer 10, the hole 1
Since the oil ejected from 3c is added, it is effective in further increasing the bearing oil supply amount.

〔Effect of the invention〕

As described in detail above, according to the self-lubricating device of the present invention, since the rotating shaft is provided with rolling elements that revolve while rotating due to the rotation of the shaft, it is possible to lubricate effectively even in high-speed ranges, and it also makes contact with the rolling elements. The outer ring was locked on the stationary side to allow swinging, so
This has an excellent quality effect in that no unreasonable force is generated between the rotating side and the stationary side.

[Brief explanation of the drawing]

Fig. 1 is a front view of a bearing device showing an embodiment of the present invention, Fig. 2 is a sectional view taken along the - line in Fig. 1 and seen in the direction of the arrow, and Fig. 3 is an oil disk of Fig. 1. Fig. 4 is a characteristic curve diagram showing the relationship between the rotational speed of the rotating shaft and the amount of pumped oil in comparison with a conventional one, and Fig. 5 is a modification of this embodiment. FIG. 6 is a sectional view of an example oil disk, and FIG. 6 is a side view of a rotating shaft on which the oil disk of FIG. 5 is mounted. DESCRIPTION OF SYMBOLS 1... Rotating shaft, 2... Bearing, 3... Oil disk, 4... Bearing box, 10... Annular layer, 11...
Rolling element, 12... Cage, 13... Outer ring, 16...
...slip ring.

Claims (1)

[Scope of Claims] 1. A plurality of rolling elements are arranged on the outer periphery of a rotating shaft, and the rolling elements rotate and revolve around the axis as the shaft rotates, and the rolling elements scrape up lubricating oil from the bearing box and supply it to the bearings. In the self-lubricating device, a flange having a diameter larger than the bearing diameter is formed on the rotating shaft, the rolling elements are disposed on the outer periphery of the flange, and an outer ring for holding the rolling element is provided, and the outer ring is connected to the stationary side member. A self-lubricating device for a bearing, characterized in that the bearing is locked with play.