JPS6155498A - Self oil supply device of bearing - Google Patents

Abstract

PURPOSE:To suppress scattering of lubricating oil, by providing an annular layer rotated at relatively low speed in an oil disc, in the case of a device sucking lubricating oil, accumulated in the bottom part of a bering case, by the oil diex of a rotary shft to be supplied to a bearing surface. CONSTITUTION:A bearing device, equipping a self oil supply device, rotatably mounts an oil disc 3 in one side of a sliding bearing 2 supporting a rotary shaft 1, and these members are enveloped by a bearing case 4 enebling the sliding bearing 2 to be supported. Here the oil disc 3 is constituted by an annular innder ring 9 fitted to the periphery of a flange part 8 formed in a part of the rotary shaft 1, outer ring 13 provided outside the inner ring 9 and held unable to rotate ty engaging a pin 15 protruded from the oil scraper 6, and an annular layer 10 interposed between the both rings 9, 13. The annular layer 10, being constituted by a plurality of rolling balls 11 fitted to a track 9a of the inner ring 9 and an annular holder 12 holding these rolling balls 11, serves so as to enable lubricating oil 5 to be sucked and flow into supply oil port 7.

Description

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

[Technical background of the invention and its problems]

It is well known that disc-shaped oil discs are widely used as a self-lubricating method for bearings. Unlike an oil ring, this oil disc 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 system 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 backup in case of failure of the electric pump or power outage.

Therefore, there is a strong desire to expand the scope of application of self-lubricating using an oil disk, which is advantageous in this respect. A disadvantage of oil disks is that as the outer circumference of the disk becomes higher, the amount of pumped lubricating oil that is thrown away increases, and if the circumferential speed exceeds the desired amount of pumped oil, it becomes impossible to obtain the desired amount of pumped oil. For example, curve a in Figure 4
Bearing diameter 140", oil disc diameter 290"
This figure shows the relationship between rotational speed and pumping amount for mm. As is clear from this figure, when the circumferential speed of the oil disk exceeds approximately 4 m7kc, the pumping amount begins to decrease. So now, the desired oil amount is 2.5'/ml.
In the case of a rotating machine intended to obtain n, its rotational speed range is limited to a range of 120 to 500 r, p, m.

Conventionally, in order to transport the δS scattered oil as far as possible above the oil disk, various proposals have been made to provide an oil guide cover that wraps around the outer periphery of the oil disk (Utility Model No. 55-8
Publication No. 2596). However, the rate of increase in the pumped amount was only about 10 to 20% at most, 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.

[Purpose of the invention]

The present invention provides a self-lubricating device that suppresses scattering of pumped oil by making the rotational speed of the oil pumping part of the oil disk lower than the rotational speed of the shaft, and expands the self-cooling efficiency of the bearing to a high-speed range. The purpose is to

[Summary of the invention]

According to the present invention, an annular layer that rotates at a rotation speed slower than the rotation speed of the rotating shaft is provided in the lubricating oil-immersed portion of the oil disk, thereby suppressing scattering of the lubricating oil even when the rotating shaft rotates at high speed. This effectively supplies lubricating oil to the bearings.

[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. A bearing housing 4 supporting 2 is shown.

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

Next, the oil disc 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 continuous casting. The outer periphery of this inner ring 9 is formed by a concave raceway 9a.

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 located between the inner and outer rings 9 and 13, and includes a plurality of rolling elements 11 made of spheres that are fitted into the raceway and are movable in the circumferential direction.In order to maintain the distance between these adjacent rolling elements, the rolling elements 11 are separated from both sides. It is composed of an annular retainer 12 that is slidably encased.

A groove 14 extending in the axial direction is provided in the upper part of the outer ring 13, and a pin 1 protruding from the oil paddle 6 described above is inserted into this groove.
5 is inserted loosely, and this pin 15 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 to be at or slightly lower than the outer peripheral surface of the lowest part of the inner ring 9.

Next, the effect 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.

d: Diameter of the rolling element (to) α: Contact angle of the rolling element (0) dm: Diameter of the pin of the rolling element (mm) N: Number of rotations of the rotating shaft (rpm). By using the above-mentioned rolling elements, the rotational speed for the annular layer can be suppressed to around 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 inner diameter of the outer ring was made approximately the same as the outer diameter of a conventional oil disk, 290", and the rolling elements were made of eight balls arranged at equal intervals.) As is clear from this figure, the pumping characteristics are For example, if we look at bearings that currently require a pumping oil rate of 2.5'/min, conventional disges were limited to a range of 120 to 500 rpm, but with this implementation According to the example disk, 230-1200
It can be used in the rpm range. 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 extremely effective for greatly expanding the range in which the bearing can be operated with self-lubricating. It is.

In the above embodiment, the inner ring 9 is fitted to the flange 8 of the rotary shaft 1, but the flange 8 and the inner ring 9 may be integrated. Groove 1 of outer ring 13
4 is engaged with the pin 15 of the oil paddle 6, but the outer ring 13
A round hole is provided in the upper part of the ring, and the pin 15 is passed through the round hole loosely to prevent the outer ring from moving in the axial direction. may be formed.

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

When using the rollers as rolling elements, as shown in FIGS. 5 and 6, an annular relief groove 13b is provided in a part of the raceway of the outer ring 13, and the outer ring It is also possible to provide a hole 13c that opens toward the outer circumference in the upper part of the lubricating oil so that the lubricating oil can be spouted from this hole. In this way, in addition to the oil scraped up by the side surface of the annular layer 10, the amount spouted from the hole 13c is added, which is effective in further increasing the amount of oil supplied to the bearing.

Next, another embodiment of the present invention shown in FIG. 7 will be described. Annular layer 10 of oil disc 3 in this embodiment
is formed by a sliding ring 16 that rotates at a slower rotational speed than the inner ring 9 (rotating shaft) while slidingly contacting the inner ring 9 and the outer ring 13, and preferably a plurality of recesses 17 provided on the side surface of the sliding ring 16.

This sliding ring 16 must be made of a material with excellent wear resistance. For example, polytetrafluoroethylene (
There is a type of filler added to DuPont (trade name: Teflon). This material contains 20 to 30% (by weight) of glass fiber, graphite, carbon, bronze, molybdenum disulfide, or a composite thereof as a filler, and is a well-known material already used in various mechanical parts. .

This material reduces wear by 11,500 to 1,000 times more than pure Teflon, which has a good anti-friction effect. In order to make the annular layer 10 rotate at a predetermined speed that is slower than the rotating shaft, it is achieved by setting the fit between the sliding ring 16 and the inner and outer rings 9, 13 to appropriate values.

This fitting allowance can also be made adjustable. 8th
The figure shows this embodiment, in which a shallow circumferential groove is provided on the inner peripheral surface of the outer ring 13, and a band 18 is divided into a plurality of parts in the circumferential direction within the circumferential groove.
is provided in contact with the outer peripheral surface of the sliding ring 16, and each divided piece of this band 18 is attached to the outer ring 13.
9 is used for pressing. According to such a configuration, not only can the loosening of the sliding ring 16 due to wear over time be easily restored, but also the desired annular layer rotation can be achieved in response to the rotational speed of a rotating machine such as an electric motor that operates at a variable speed. You can pay homage to speed.

〔Effect of the invention〕

According to the present invention, an oil disc that scoops up lubricating oil from a bearing box and supplies it to the bearing surface of a rotating shaft is provided with an outer ring that does not rotate on its outer periphery, and a lower part that is formed between the outer ring and the rotating shaft and that supplies the lubricating oil to the bearing surface of the rotating shaft. The structure is composed of an annular layer that rotates at a rotation speed slower than the rotation speed of the immersed rotating shaft, so even if the rotating shaft rotates at high speed, lubricating oil is suppressed from scattering and can be effectively supplied to the bearings. It has an effect that can be expanded to a larger area.

[Brief explanation of drawings]

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 viewed in the direction of the arrow. Figure 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 oil disc. 6 is a sectional view of an oil disk showing a modification of the embodiment, FIG. 6 is a side view of a rotating shaft equipped with the oil disk of FIG. 5, and FIGS. 7 and 8 each show other embodiments of the present invention. It is a sectional view of an oil disk. 1... Rotating shaft, 2... Bearing. 3... Oil disk, 4... Bearing box. 10... Annular layer, 11... Rolling element. 12... ... Cage, 13 ... Outer ring. 16 ... Sliding ring. Agent: Patent attorney Noriyuki Chika (and one other person) Fig. 2 Fig. 3 (u'ulh) 4 Clothes; 41'lq> 71st 8th V

Claims (1)

[Claims] 1) An oil supply device in which lubricating oil stored in the lower part of the bearing box is supplied to the bearing surface of the rotating shaft by an oil disk of the rotating shaft, wherein the oil disk is provided on the outer periphery of the oil disk. A self-lubricating device for a bearing, comprising a non-rotating outer ring and an annular layer formed between the outer ring and a rotating shaft, the lower part of which is immersed in lubricating oil and rotating at a rotation speed slower than the rotation speed of the rotating shaft. 2) The bearing according to claim 1, wherein the annular layer is constituted by a plurality of rolling elements that revolve while rotating due to rotation of a rotating shaft, and a retainer that holds these rolling elements at a predetermined interval in the circumferential direction. self-lubricating device. 3) The self-lubricating device for a bearing according to claim 1, wherein the annular layer is constituted by a sliding ring that rotates while slidingly contacting the rotating shaft and the outer ring as the rotating shaft rotates. 4) The self-lubricating device for a bearing according to claim 3, wherein the sliding ring is made of polytetrafluoroethylene with a filler added to improve wear resistance.