JPS58207520A - Guide bearing pad - Google Patents

Abstract

PURPOSE:To prevent burn-out of a guide bearing pad by forming an oil storage sump in a welled form on the surface of the pad which slidingly contacts with a rotor, thus increasing the thickness of oil membrane on the slide surface and reducing the shear angle of lubricating oil due to inclination of the pad. CONSTITUTION:An oil storage sump 18 of welled form is provided on the surface of a guide bearing pad 1b, which slidingly contacts with a rotor 2 in a vertical spindle water turbine generator etc. Owing to said oil storage sump 18, the thickness of oil film increases, and the shear angle of lubricating oil reduces even if the slide surface of the bearing pad 1b tilts with respect to the surface of a rotor 2, so the calorific value reduces, and burn-out of the guide bearing pad 1a can be prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a guide-flfU bearing band which is threaded onto a culvert bearing band and which is arranged symmetrically with the rotor at a predetermined spacing.

In the case of an axle-type water turbine generator, an axle-type guide bearing device (hereinafter referred to as a guide bearing device) that uses lubricating oil for lubrication is installed so that the rotating body, that is, the rotor, is all at a predetermined position. ing. Particularly in high-speed, high-load guide bearing devices, multiple guide shelf bands are often used. Conventional examples of guide bearing devices using this guide bearing pad are shown in Figures 1 and 2. ing. As shown in these figures, a plurality of guide bearing bands 1 are arranged at predetermined intervals on the outer circumference of the rotor 2, and the guide bearing pads 1 that slide on the rotor 2 are attached to the rotor 2. 41 means 4 for adjusting the fence receiving gap 3 is provided.

That is, the adjustment means 4 is formed by the adjustment bolt 4, the bearing gap 3 supports the back surface of the guide bearing band 1, and the oil passage 5
The head of the adjustment bolt 40 is rounded so that the guide 4i receiving pad l can slide. An oil film is formed between the bearing pJj and the guide bearing pad 1 and the rotor 2. A guide bearing support 7 is provided to prevent the guide bearing support 26 from falling downward, and the guide support 6 is supported on a base 8. An oil tank is formed on the guide bearing pad 1vd, but the oil
Row Hao Ilframe 9. Oil dam10. Oil pan 11. There is a groove formed from Manil Tower 12 etc., and ζ oil cover 13 is thrown on the upper surface J of oil frame 9)
In the oil 11: 'ii lubricant lubricant lubricant 14 what?
In addition, since the oil cooler tube 15 is installed, a rib 16 is provided that connects the guide shelf receiving coos 6 and the oil frame 9. In addition, the 17d adjustment bolt 4 is already cut.

In the beam 173 having the bearing body configured in this way, the guide shelf support band 1 is formed on a smooth surface with the rotor 2 as shown in Figures 3 to 51.
○For example, if there is a smooth 7-cedar or a broken surface like this, 7-
Puppy-shaped hydraulic power (in some machines, 5D type 7 and 2. Since the shear load is very large, the guide bearing hand 17) is used to disperse the thick fx load.
Due to the number of installations, υ load t per 101 guide bearing bands,
However, I tried to reduce my virginity! - When the diameter of the cylinder 2 becomes smaller, the circumferential speed of the sliding surface V increases, leading to the following disadvantages.

That is, as shown in FIG. 12, lubricating oil 1 is applied between the rotor 2 and the guide bearing band 1, that is, in the bearing gap.
This lubricating oil 14, which is filled with oil 4, has a viscosity of M, and depending on the relative speed between the rotor 2 and the guide bearing pad 1 in the bearing gap, the thickness of the bearing gap increases due to the resistance caused by the viscosity. A deviation angle θ0 (all required θ.) is generated in the lubricating oil 14 between the sides, starting from the support point Δ of the A bolt. This total angle θ. a. It is related to the circumferential speed U of the rotor 2, which is the size of the relative speed, and the size of the bearing clearance, and is expressed as θo = u/h, and the reason why the circumferential speed U is small is that Required θ. As the temperature increases, the heat generated also decreases. However, as this generated heat increases, the viscosity of the lubricating oil 14 decreases by an order of magnitude, making it easier to move relative to the weight of the rotor 2/':l:f'i. Due to this fL, the sliding surface of the rotor 2 approaches the sliding surface of the guide shelf support band l, and the bearing clearance becomes smaller, resulting in a shear angle θ. If the guide bearing pad 1 is made thicker, the rise in temperature will cause the guide bearing pad 1 to sink too much and burn out.

This book-i@mei is unscrupulous in the above points, and its purpose is to provide a guide bearing hand that prevents burnout.

That is, in the present invention, at least 11 concave oil reservoirs are fixedly provided on the surface of the guide bearing pad that slides on the rotor.
t features.

Hereinafter, the present invention will be explained based on the illustrated four rows. An embodiment of the present invention is shown in FIGS. 6-8. Note that parts that are the same as those in the conventional model are given the same reference numerals, and therefore their explanations will be omitted. In this embodiment, at least one concave oil reservoir 17 is provided on the surface of the guide bearing pad 1a that is adjacent to the D rotor 2.
11 were established. By pouring the oil reservoir 17 in this manner, the thickness of the oil film becomes smaller, and the amount of 1-threshold oil used at the wellhead becomes smaller, and the heat generated becomes smaller. It is possible to obtain a guide shelf support band la that prevents burnout.

That is, as shown in FIG. 13, at the support point Δ of the adjustment bolt, the bearing clearance h2 is larger than the conventional bearing clearance by the depth of the oil reservoir 17, so that the support of the adjustment bolt is The shear angle θ1 of the lubricating oil 14 starting from point Δ is the conventional shear angle θ. (See Fig. 412). Therefore, it is possible to reduce the generated heat and reduce the temperature rise of the guide bearing band 1a.

The depth hl of the oil reservoir 17 is between the rotor 2 and the guide bearing pad 1.
It is formed to be equal to or smaller than the bearing clearance between a and a. In this way, the amount of lubricating oil 14 transferred from the sliding surface of rotor 2 is large, so that r
The lubricating oil 14 is exposed to the i-shield, and the load capacity decreases.
-No harm done.

9 to 11 show practical examples of Hon@Akinoya. In this embodiment, the oil reservoir 1st is formed into a rectangular shape extending in the circumferential direction. In this case as well, the same effects as in the above case can be achieved. In other words, such an oil pond 1
The guide bearing pad 1b having the number 8 can also be made to have a low temperature rise similar to the above-mentioned guide shelf support pad la (see FIGS. 6 to 8).

According to the present invention, since a concave oil reservoir is provided on the sliding surface of the guide bearing pad, the size of the oil film on the sliding surface is increased, and the amount of lubricating oil used during this period is reduced. It is smaller and generates less heat, making it possible to obtain an inner bearing pad that prevents burnout.

M of the drawing? Figure 1 is a cross-sectional side view of a vertical cedar bearing device with a conventional guide bearing band, and Figure 2 is a cross-sectional side view of a vertical cedar bearing device with a conventional guide bearing band. , Fig. 3A is a front view of seven guide bearing pads for one holder, Fig. 4 is a conventional XJ diagram of one guide bearing pad, and Fig. 5 is a conventional guide case holder D sliding with the rotor and large vibrations. Fig. 6 is a front view of five Komei guide bearing pads (not shown); Fig. 6 is a front view of one guide bearing pad of the present invention; Fig. 8 is a side view of one guide bearing pad of the present invention; Cross-sectional view showing the friction point with the rotor of a case of leprosy, No. 9
Fig. 411 is a front view of one row of Ikeno-seed of the recreational bearing pad of the present invention, Fig. 10, d is also a side view of Ike-no-setsu row of Ikeno-setsu row, Fig. 411 is the present invention, 7) 4-circle sleeve support. Ike no Mi of the pad, the moving dog collar with the collapsing rotor, 12th A, the guide bearing pad of the engineering and hokimae @ Soharama l slip oil ri-kun use. FIG. 13 is an explanatory diagram illustrating the use of lubricating oil in the bearing gap of an embodiment of the guide bearing pad of the present invention.

la, Ib...Guide bearing pad, -2...Rotor, 3
・Bearing clearance, 17.18...Oil sump agent Patent attorney Akio Takahashi

Claims (1)

[Claims] 1. In the east gate bearing band which is arranged in the oil tank and in the same manner as the rotor with a predetermined gap τ, a concave oil is provided on the surface of the guide bearing band that slides on the rotor. A guide bearing pad patented as having at least a reservoir. 2. A load which is formed into a rectangular shape extending around the circumference of the oil reservoir; ff - The guide bearing pad according to claim 1. F. The guide bearing band according to claim 1, wherein the oil is formed so that the depth thereof is equal to or smaller than the gap between the rotor and the guide bearing pad. .