JP4015371B2 - Cylindrical roller bearing - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a cylindrical roller bearing, in particular is used in the main shaft, the lower air-oil in the printing cylinder or the like of the roll and the printing machine of the rolling machine (oil / air) Jun Namerama other oil mist lubrication (spray lubrication) of the machine tool The present invention relates to a cylindrical roller bearing.
[0002]
[Prior art]
The spindle speed of machine tools has been increasing year by year, and the lubrication method of bearings has been frequently used from grease lubrication to air oil lubrication and oil mist lubrication. Air oil lubrication is also called micro oil lubrication, and is described, for example, in Japanese Utility Model Publication No. 63-14156.
[0003]
2. Description of the Related Art Conventionally, a cage-type cage cage made of copper alloy (high-strength brass casting) has been used for a single-row cylindrical roller bearing used for a main shaft. The size of such a single-row cylindrical roller bearing, there is a track record of bearings inside diameter φ25~ φ160. The cage guide system includes a rolling element (roller) guide system in which there is a gap between the cage inner diameter and the inner ring outer diameter, and the cage outer diameter and the outer ring inner diameter.
[0004]
Hereinafter, a bearing portion of a machine tool or the like using a single row cylindrical roller bearing will be described. FIG. 7 is a partial cross-sectional view of the bearing portion. In FIG. 7, reference numeral 10 denotes a rotary shaft insertion portion, and a cylindrical roller bearing (hereinafter referred to as a bearing) 11 is disposed on the outer periphery thereof. In this bearing 11, a retainer 14 is disposed between an inner ring 12 and an outer ring 13, and a cylindrical roller (hereinafter referred to as a roller) 15 is interposed in a pocket hole of the retainer 14 so as to be able to roll. Reference numeral 16 denotes a lubricating oil supply member having a supply hole 17 inside, a nozzle hole 18 communicating with the tip thereof, and a nozzle 19 provided at the outer end of the nozzle hole 18. The nozzle 19 supplies air oil or oil mist-like lubricating oil aiming at a gap between the inner diameter surface of the cage 14 and the outer diameter surface of the inner ring 12. Reference numeral 20 denotes a used lubricating oil guide member provided on the opposite side of the lubricating oil supply member 16, and has a guide cavity portion 21 having a size equivalent to the gap (radial direction) between the inner ring 12 and the outer ring 13 of the bearing 11. Have. A discharge hole 23 for discharging used lubricating oil is provided on the circumference of the guide member 20. Accordingly, the air oil or oil mist-like lubricating oil 24 is supplied from one end of the supply hole 17 of the lubricating oil guide member 16, is ejected from the nozzle 19 and supplied to the bearing 11, and the centrifugal force and the roller 15 due to the rotation of the inner ring 12. The roller is spread in the bearing 11 by the rolling of the roller and performs a lubricating action. The used lubricating oil 24a exits from the bearing 11 and is discharged to the outside through the guide cavity portion 21 and the discharge hole 23 of the guide member 20.
[0005]
FIG. 8 is an enlarged cross-sectional view of an example of the cylindrical roller bearing 11 and shows a cage-type cage caulking cage. In FIG. 8, 31 is an inner ring and has flanges 31a and 31a at both ends in the width direction of the outer diameter surface. 32 is a outer ring are arranged in the radially outer surface a predetermined distance of the inner ring 3 1. 33 is the inner ring 3 1 and cage rivet caulking the cage interposed between the outer ring 3 2, crimping the auxiliary member 33b of the substantially annular in and comb teeth-shaped main member 33a and the annular with rivets 33c Thus, pocket holes (not shown) at regular intervals are formed. Reference numeral 34 denotes a cylindrical roller which is rotatably accommodated in a pocket hole of the cage 33.
[0006]
[Problems to be solved by the invention]
The design of main components in the single row cylindrical roller bearing will be described in detail below.
[0007]
(1) As described above, in a single row cylindrical roller bearing of a type (hereinafter referred to as N type) having a flange 31a in the inner ring 31, when the cage 33 is a rolling element guide, The setting of the outer diameter dimension is made uniform from the PCD of the roller 34 in consideration of the rigidity of the ring portion and the like.
[0008]
(2) On the other hand, on the outer diameter surface of the inner ring 31, there are flanges 31a, 31a for guiding the axial movement of the roller 34 on both sides, and the height of the flange 31a is a roller diameter reference (20% of the normal roller diameter). ). Thereby, the inner ring outer diameter (径 outer diameter) dimension is set.
[0009]
(3) The oil supply position for air oil lubrication or oil mist lubrication is determined by considering the lubrication of the rollers 34 and 31a and the flow of oil due to centrifugal force during high speed rotation (inner ring rotation), and the inner diameter of the retainer 33 and the inner ring 31 Aims for a gap with the outer diameter.
[0010]
Here, in the bearing design, in order to give priority to the above settings (1) and (2), the clearance (radial direction) dimension between the inner diameter of the cage 33 and the outer diameter of the inner ring 31 is the nozzle diameter (usually φ0. 8 to φ1.5), which is usually 0.3 to 0.8 times the nozzle diameter.
[0011]
For the reason (3), the oil supply position (nozzle position) is aimed at the gap between the inner diameter of the cage on the narrow side and the outer diameter of the inner ring. In that case, in order to make it easy to supply the lubricating oil diffused from the nozzle to the inside of the bearing, as shown in the drawing, a tapered guide portion is provided on the outer diameter portion of the inner ring.
[0012]
However, the conventional cylindrical roller bearing has a high temperature rise during operation, and a peak of temperature rise is observed in the vicinity of dn = 400,000 to 800,000. Since keeping the operating temperature as low as possible for the bearing is advantageous for stability of machining accuracy in the machine tool and seizure resistance of the main shaft, a low temperature rise of the bearing is always required.
[0013]
Therefore, the problem to be solved by the present invention is to make the temperature rise during operation of the cylindrical roller bearing as low and flat as possible in the practical range of dn.
[0014]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, the present invention ejects air oil or oil mist-like lubricating oil from a nozzle arranged toward the gap between the inner diameter surface of the cage and the outer diameter surface of the inner ring and supplies the lubricant to the gap. In cylindrical roller bearings operated under air oil lubrication or oil mist lubrication, the clearance between the inner diameter surface of the cage and the outer diameter surface of the inner ring is 0.8 to 1.6 times the nozzle diameter to which the lubricating oil is supplied. It is characterized by being set to.
[0015]
The present invention is also characterized in that, in the above configuration, the nozzle diameter is φ0.8 to φ1.5.
[0016]
According to the present invention configured as described above, air oil or oil mist-like lubricating oil supplied from the nozzle is efficiently supplied into the bearing from the gap between the inner diameter surface of the cage and the outer diameter surface of the inner ring. Thus, the lubricating oil spreads between the inner ring, the outer ring, the rollers and the cage, and the frictional resistance between them is reduced, so that a low temperature rising operation can be achieved.
[0017]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings.
[0018]
FIG. 1 shows a cross-sectional view of the main part of a single row cylindrical roller bearing embodying the present invention. In FIG. 1, reference numeral 1 denotes an inner ring made of a high-strength brass casting, and roller guide ribs 1a, 1a are formed on both sides in the width direction (axial direction) of the outer diameter surface, and between the both ribs 1a, 1a. A recess is formed. Reference numeral 2 denotes an outer ring made of a high-strength brass casting disposed at a predetermined interval along the outer peripheral surface of the inner ring 1. Reference numeral 3 denotes a cage-type rivet caulking cage made of a high-strength brass casting disposed between the inner ring 1 and the outer ring 2, 3a is an annular and comb-shaped main member, and 3b is an annular auxiliary member. Is fixed by caulking 3c, and pocket holes (not shown) are formed at regular intervals by the main member 3a and the auxiliary member 3b. The inner diameter of the cage 3 is larger than the outer diameter of the flanges 1a, 1a of the inner ring 1, and the outer diameter is set smaller than the inner diameter of the outer ring 2, and in combination with a roller (4) described later, The inner ring 1 and the outer ring 2 are not in contact with each other. 4 is a cylindrical roller fitted into the pocket hole of the cage 3 so as to be able to roll, and a part of the peripheral surface portion is accommodated and guided between the flanges 1a, 1a of the inner ring 1, Another part of the peripheral surface portion is in contact with the inner surface of the outer ring 2. The inner ring 1 is rotatably held with respect to the outer ring 2 by the rolling of the rollers 4.
[0019]
Then, air oil or oil mist-like lubricating oil is supplied from a nozzle (not shown) to a gap 5 between the inner diameter surface of the cage 3 and the outer diameter surfaces of the flanges 1a and 1a of the inner ring 1. I am doing so. Therefore, the inner ring 1 freely rotates with a small frictional resistance with respect to the outer ring 2 by the rolling action of the rollers 4 and the cooperative action with the lubricating oil supplied in the form of air oil or oil mist.
[0020]
Here, as described above, the normal nozzle diameter is φ0.8 to φ1.5, and the dimension of the gap 5 between the inner diameter surface of the cage 3 and the outer diameter surface of the flange 1a of the inner ring 1 is g. Then, the gap size g0 of the conventional cylindrical roller bearing is less than 0.3 to 0.8 of the nozzle diameter. Therefore, in the conventional cylindrical roller bearing, the lubricating oil injected from the nozzle is not efficiently supplied to the inside of the bearing 11 from the gap 5, and the lubrication action is not sufficient, so that the low temperature rise is not achieved. It is considered a thing.
[0021]
In the present invention, the dimension g of the gap 5 is set to be 0.8 to 1.6 times the nozzle diameter by making it larger than the conventional one. As a result, the air oil or oil mist-like lubricating oil injected from the nozzle is efficiently supplied into the bearing through the gap 5, and a sufficient lubricating action is obtained to achieve low temperature operation of the bearing.
[0022]
【Example】
Examples of the present invention will be described below.
[0023]
FIG. 2 shows a single-row cylindrical roller bearing in the first embodiment in which the gap 5 is larger than that of the conventional product and the gap dimension g1 is set to 0.8 times the nozzle diameter (φ0.8 to φ1.5). It is sectional drawing of the principal part.
[0024]
FIG. 3 shows a single row cylindrical roller bearing in which the gap 5 is made larger than that of the first embodiment, and the gap dimension g2 is set to 1.6 times the nozzle diameter (φ0.8 to φ1.5). It is sectional drawing of the principal part in 2 Examples.
[0025]
FIG. 4 is a main view in a comparative example in which the gap 5 is the same as that of the conventional product in a single row cylindrical roller bearing, that is, the gap dimension g3 is set to 0.4 times the nozzle diameter (φ0.8 to φ1.5). It is sectional drawing of a part.
[0026]
In the first embodiment, the second embodiment, and the comparative example, in order to avoid complication of the drawings, the main member 3a, the auxiliary member 3b, and the hook 3c of the cage 3 are omitted, and FIG. 1 shows a pocket hole 3d that cannot be seen.
[0027]
The test results of the first example, the second example and the comparative example will be described below. The test conditions are as follows: Lubrication method: Air oil Lubricating lubricant: VG32
Nozzle diameter: φ0.8, φ1.5
Air amount: 20n1 / min. Lubrication amount: 0.02ml / 5min Nozzle target position: Radial internal gap after assembly of inner ring outer diameter and cage inner diameter gap: 0μm
FIG. 5 is a temperature rise characteristic diagram of the outer ring 2 in the first embodiment, the second embodiment, and the comparative example when the nozzle diameter is φ0.8. The vertical axis is the temperature rise value (° C.) of the outer ring 2, the horizontal axis is dn (× 10 ⁴ ), d is the inner diameter of the outer ring 2, and n is the rotational speed.
[0028]
FIG. 6 shows a temperature rise characteristic diagram of the outer ring 2 in the first, second, and comparative examples when the nozzle diameter is φ1.5. The vertical axis is the temperature rise value (° C.) of the outer ring 2, the horizontal axis is dn (× 10 ⁴ ), d is the inner diameter of the outer ring 2, and n is the rotational speed.
As apparent from FIGS. 5 and 6, the outer ring temperature rise value of the comparative example is as high as 9 to 11.5 ° C. in the practical range where dn is 400,000 to 800,000, and the temperature rises at the center of the practical range. Whereas peaks (peaks) are observed, the outer ring temperature rise values in the first and second embodiments of the present invention are 6 to 8 ° C. in the practical range of dn, and 3 ° C. relative to the comparative example. It is low enough and is almost flat throughout the practical range of the dn. Therefore, it is clear that the cylindrical roller bearing of the present invention is superior to the comparative example in increasing the outer ring temperature.
[0029]
The present inventors made and tested similar products not only for the nozzle diameters shown in the above examples but also for various nozzle diameters (greater than φ0.8 and less than φ1.5). Similar results were obtained.
[0030]
When the gap dimension g is smaller than 0.8 times the nozzle diameter, the amount of lubricating oil injected from the nozzle enters the bearing from the gap 5 is reduced. If the effect is not sufficiently obtained and the gap dimension g is larger than 1.6 times the nozzle diameter, the rigidity of the ring portion (radial direction) of the cage 3 may not be ensured. Therefore, the gap dimension g is limited to a range of 0.8 to 1.6 times the nozzle diameter.
[0031]
Moreover, although the said Example demonstrated the case where all the material of the inner ring | wheel 1, the outer ring | wheel 2, and the roller 4 was a copper alloy (high-strength brass casting), high carbon chromium bearing steel, carburized steel, high speed steel, stainless steel The same effect can be obtained even in the case of steel, ceramics, or resin.
[0032]
Furthermore, although the said Example demonstrated the case where the material of the holder | retainer 3 was a copper alloy (high-strength brass casting), cold or hot rolled steel plate, stainless steel plate, carbon steel for machine structures, aluminum alloy, nickel It may be made of a heat-resistant polyamide resin reinforced with chromium molybdenum steel, glass fiber or carbon fiber.
[0033]
【The invention's effect】
In the cylindrical roller bearing operated under air-oil lubrication or oil mist lubrication as described above, the clearance dimension between the inner diameter surface of the cage and the outer diameter surface of the inner ring is equal to 0 of the nozzle diameter to which the lubricating oil is supplied. .8 to 1.6 times allows the lubricating oil injected from the nozzle to be efficiently supplied into the bearing, providing a sufficient lubricating action and reducing the temperature rise of the bearing during operation. Can be suppressed.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a main part of a single-row cylindrical roller bearing of the present invention. FIG. 2 is a cross-sectional view of a main part of a single-row cylindrical roller bearing of a first embodiment of the present invention. FIG. 4 is a cross-sectional view of the main part of the single-row cylindrical roller bearing of the embodiment. FIG. 4 is a cross-sectional view of the main part of the single-row cylindrical roller bearing of the comparative example. FIG. 6 is a temperature rise characteristic diagram of the outer ring in the single-row cylindrical roller bearing of the second embodiment and the comparative example. FIG. 6 is a single row of the first and second embodiments of the present invention and the comparative example when the nozzle diameter is φ1.5. Temperature rise characteristics diagram of outer ring in cylindrical roller bearing [Fig. 7] Partial cross-sectional view of the main part of machine tool etc. using cylindrical roller bearing [Fig. 8] Expansion of cylindrical roller bearing using cage cage Sectional view [Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Inner ring 1a Inner ring flange 2 Outer ring 3 Retainer 3a Retainer main member 3b Retainer auxiliary member 3c Reed 3d Pocket hole 4 Cylindrical 2 roller 5 Gap g, g0, Retainer inner diameter surface and inner ring outer diameter surface g1, g2 Clearance dimension

Claims (2)

It is operated under air oil lubrication or oil mist lubrication , in which air oil or oil mist-like lubricating oil is jetted from a nozzle arranged toward the clearance between the inner diameter surface of the cage and the outer diameter surface of the inner ring and supplied to the clearance. In the cylindrical roller bearing, a cylindrical roller bearing characterized in that a clearance between the inner diameter surface of the cage and the outer diameter surface of the inner ring is set to 0.8 to 1.6 times the nozzle diameter to which the lubricating oil is supplied. The cylindrical roller bearing according to claim 1, wherein the nozzle diameter is φ0.8 to φ1.5.

Images