Patent Document

This application is a continuation of now abandoned application Ser. No. 576,406, filed Feb. 2, 1984. 
    
    
     BACKGROUND OF THE INVENTION 
     The present invention relates to a roller bearing lubricating device for a lateral rotary machine. 
     A conventional bearing lubricating device for a rotary machine of this kind is shown in FIGS. 1 and 2. In the drawings, reference numeral 1 designates a rotary shaft, reference numeral 2 designates a roller bearing which supports the rotary shaft 1, reference numerals 2a, 2b, and 2c designate an outer race, an inner race, and rollers (ball bearings), respectively, reference numeral 3 designates a bearing housing, reference numeral 4 designates an oil tank which is provided in the housing 3 and stores lubricating oil 6, and reference numeral 5 designates an oil gauge mounted in the tank 4. 
     The conventional lubricating device lubricates the bearing by immersing the rollers 2c of the bearing 2 directly in the lubricating oil 6 in the tank 4. In this case, the inner race 2b of the bearing 2 rotates together with the shaft 1. Thus, the rollers 2c rotate and the oil 6 is stirred due to the rotation of the rollers 2c. This stirring produces heat, oil splashes A, and waves B on the oil surface. As a result, when the rollers 2c are immersed directly in the lubricating oil in the tank 4, more oil than necessary for the purpose of lubrication is supplied to the bearing 2. When the shaft 1 is accelerated in rotation, the heat produced by stirring abruptly increases and the bearing temperature thus remarkably increases. In addition, oil splashing increases and oil leakage results. Further, surface waviness is also increased, causing great variation in the oil surface level, and as a result the gauge 5 is unable to accurately measure the oil level. 
     Thus, the above-described conventional lubricating device can be applied only in the low and middle speed ranges in which the D m  N value which designates the empirical speed limit of the roller bearing is at most 300,000 to 400,000 or less. D m , shown in FIG. 1, is the average in mm of the inner and outer diameters of the bearing, and N is the rotational speed in RPM of the shaft. 
     SUMMARY OF THE INVENTION 
     This invention has been made in view of the disadvantages described above, and has for its object to provide a roller bearing lubricating device wherein a lubricating oil reservoir which dips a roller bearing is isolated from an oil tank, and the lubricating oil of the oil tank is caused to flow in a predetermined amount to the oil reservoir through an oil supply passage, whereby the temperature rise of the bearing can be lowered. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a longitudinal sectional view showing a conventional roller bearing lubricating device; 
     FIG. 2 is a transverse sectional view taken along the line II--II of FIG. 1; 
     FIGS. 3 and 7 are longitudinal sectional views showing the roller bearing lubricating device according to one embodiment of the present invention, FIG. 3 showing the device in a stationary state and FIG. 7 showing the device in a rotating state; 
     FIG. 4 is a sectional view taken along the line IV--IV of FIG. 3; 
     FIG. 5 is a sectional view taken along the line V--V of FIG. 4; 
     FIG. 6 is an enlarged view of portion C of FIG. 3; 
     FIG. 8 is a sectional view showing another embodiment of the invention; and 
     FIG. 9 is a diagram showing the relationship between the diameter of an orifice, the bearing oil supply amount, and the bearing temperature in the present invention. 
     In the drawings, the same symbols indicate the same or corresponding parts. 
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENT 
     An embodiment of the present invention will now be described with reference to FIGS. 3 to 6. FIG. 3 is a longitudinal sectional view showing the stationary state of a rotary shaft. FIG. 4 is a sectional view taken along the line IV--IV in FIG. 3. (FIG. 3 corresponds to the view taken along line III--III of FIG. 4). FIG. 5 is a sectional line taken along the line V--V of FIG. 4, and FIG. 6 is an enlarged view of portion C of FIG. 3. 
     Referring now to FIGS. 3 to 6, reference numeral 7 designates a weir formed in the bearing housing 3 for isolating the roller bearing 2 and the oil tank 4. The upper end of the weir 7 is formed slightly higher than the level of the oil gauge 5. An oil reservoir 8 formed by the weir 7 has a volume capable of reserving an amount of lubricating oil which is small when compared with the volume of the tank 4. An oil supply passage 9 passes through the lower part of the weir 7 and provides communication between the oil tank 4 and the reservoir 8. At the bottom end of the oil supply passageway 9 is an inlet which opens onto the oil tank 4. A liner 10 is detachably threaded into the inlet of the bottom of the passage 9 and has a predetermined diameter 11. An oil exhaust runner 12 is secured to the shaft 1. An oil exhaust passage 13, one end of which opens upon the runner 12 and the other end of which opens above the surface of the oil in the tank 4, is formed on each side of the bearings 2. 
     As shown in FIGS. 3 and 4, the tank 4 is filled with lubricating oil 6 so as not to overflow the weir 7 when the shaft 1 is stationary. Since the tank 4 and the reservoir 8 are partitioned by the weir 7, the bearing 2 is not immersed directly in the lubricating oil in the tank 4 and only a small portion of the outer race 2a and a plurality of rollers 2c are dipped in a small amount of lubricating oil of the reservoir 8 when the shaft 1 is stationary as described above. 
     When the shaft 1 is rotated, the lubricating oil which lubricates the bearing 2 is radially splashed due to the rotation of the runner 12 as shown in FIG. 5, and exhausted through the passage 13 into the tank 4 from the opening 13a. The lubricating oil of the reservoir 8 is scattered due to the rotation of the bearing 2 as shown in FIG. 7, splashes over the upper end of the weir 7, and returns to the tank 4. As a result, there occurs a difference between the oil levels of the tank 4 and the reservoir 8, and the lubricating oil in the tank 4 is automatically supplied through the liner 10 and the passage 9 into the reservoir 8, as designated by the arrow D, due to the differential pressure thus produced, and the bearing 2 is lubricated to maintain sufficient oil level in reservoir 8 to cover only the lowermost part of the lowermost roller as illustrated in FIG. 7. 
     FIG. 9 is a diagram showing the relationship between the oil amount supplied to the bearing and the bearing temperature, wherein the diameter 11 of the liner 10 is the abscissa and the bearing temperature and oil amount are the ordinate. 
     If the diameter 11 of the liner 10 is varied from E 1  to E 2  when a roller bearing of a predetermined size is rotated at a predetermined rate, if the diameter 11 of the liner 10 is small, the oil supply amount Q 2  is less than the minimum amount Q 1  necessary to cool the bearing as designated by the range F, with the result that the bearing temperature T rises. On the contrary, if the diameter 11 of the liner 10 is excessively large, the oil supply amount Q 2  becomes excessive as designated by the range H, with the result that the bearing temperature T becomes high due to the stirring of excess oil. In the range J of a conventional oil bath lubricating structure, the bearing temperature T abruptly rises due to the excess lubricating oil. 
     When the diameter 11 of the liner 10 is within the range designated by G, the oil supply amount Q 2  is appropriate, with the result that the bearing temperature T decreases. From experiments using a bearing of a predetermined size, it is known that when the diameter 11 of the liner 10 is from 3 to 6 mm, the roller bearing lubricating device can be applied in a high speed range in which the D m  N value of the roller bearing is 500,000 to 800,000. 
     Since oil stirring is almost eliminated in the above-described lubricating device, oil splashing can be reduced, thereby preventing oil leakage. Further, since the oil reservoir and the oil tank are partitioned by the weir, surface waves in the oil and variations in the oil level can be substantially eliminated with the result that a normal oil level indication can be obtained with an oil gauge. 
     In the embodiment described above, a liner 10 is provided in the inlet at the bottom of the oil supply passage 9. However, the liner 10 may be dispensed with (eliminated), as shown in FIG. 8, in which case the predetermined diameter 11 becomes the diameter of the inlet of the bottom of the passageway 9. 
     Thus, it will be appreciated that according to the present invention since the oil reservoir and the oil tank in which the roller bearing is partly dipped are isolated by the weir and communication between the tank and the reservoir is through an oil supply passage, a part of which has a predetermined cross-sectional area, a predetermined amount of lubricating oil is supplied from the tank to the reservoir. Since excess oil is not supplied to the bearing, the temperature rise in the bearing can be decreased.

Technology Category: 2