JP2003207094A - Spindle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a spindle device which sprays a super-fine quantity of lubricating oil at a sufficient discharge speed certainly to a part which requires most the lubricating oil according to the type of bearing. <P>SOLUTION: The spindle device is equipped with a lubricating device for supplying a fine quantity of lubricating oil through a nozzle 80 to an angular ball bearing 62a at a discharge speed of 10-100 m/sec, the discharging oil quantity being as less as 0.0005-0.01 ml/shot. The discharging direction of the lubricating oil from the nozzle 80 is directed to the contacting position with balls 41 of the inner ring 64 of the bearing 62a. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a spindle device used in various high speed rotating machines such as machine tools.

[0002]

2. Description of the Related Art Conventionally, for lubrication of bearings for various high-speed rotating main shafts of machine tools and the like, usually, lubricating oil is made into a fine mist,
An oil mist system that conveys compressed air in the air pipe and ejects it toward the inside of the bearing. Lubricating oil droplets (0.01 to 0.03 m1) adjusted to a fixed amount are discharged into the air pipe, and compressed air is used. An oil-air system that carries it to the nozzle and ejects it toward the inside of the bearing, or a jet that uses a high-pressure pump to increase the pressure of the lubricating oil without using an air source, and jets the lubricating oil at high speed from the nozzle with a narrow discharge diameter toward the inside of the bearing. Various methods such as the method are adopted.

However, in both the oil mist system and the oil air system lubrication, since compressed air is used, noise problems such as wind noise of the air and the work environment caused by the mist of lubricating oil being scattered into the atmosphere There is deterioration. In addition, since the amount of lubricating oil supplied into the bearing becomes uncertain because the mist of lubricating oil is scattered into the atmosphere, the air curtain is formed with the rotation of the main spindle at high speed rotation. Is hardly supplied inside the bearing,
It may cause seizure of the bearing.

The jet type lubrication is less affected by the air curtain as compared with the oil mist type and the oil air type. However, an auxiliary device including a high pressure pump is required and the oil supplied to the bearings is required. Since the stirring resistance increases due to the increase in the amount, a large motor is required for driving the main shaft, resulting in high cost. Under such circumstances, an extremely small amount of lubricating oil is directly supplied to the inside of the bearing in a pin spot manner.
The lubrication device described in Japanese Patent No. 711 has been developed.

[0005]

However, in the lubricating device described in Japanese Patent Laid-Open No. 2000-110711, since the amount of lubricating oil to be discharged is very small, the lubrication target position is important for obtaining lubricating performance. Therefore, how to accurately refuel at a predetermined target position has been a problem.

Therefore, in order to solve such a problem, the applicant of the present invention has previously proposed a spindle lubricator described in Japanese Patent Application No. 2000-327340. This main shaft lubricating device directly supplies a small amount of lubricating oil with a discharge speed of 10 m / sec or more and 100 m / sec or less and a discharge oil amount of 0.0005 ml / shot or more and 0.01 ml / shot or less to the inside of the bearing through a nozzle. In the case of spraying and supplying, the nozzle includes a nozzle body and a nozzle tip provided at a lubricating oil discharge port of the nozzle body.

According to this main shaft lubricating device, the discharge speed is 10 m / sec or more and 100 m / sec or less, and the discharge oil amount is 0.0005 ml / shot or more 0.01 with respect to the inside of the bearing.
By discharging a minute amount of lubricating oil of less than ml / shot from the nozzle tip provided in the nozzle body, the lubricating oil can be accurately and stably supplied to a predetermined target position. An ideal lubrication state can always be obtained inside, the stability of the bearing torque is enhanced, and the rise in bearing temperature can be suppressed to a low level.

10 m / se in direct injection lubrication as described above
The lubricating oil discharge speed of c or more and 100 m / sec or less had a speed of 10% or more of the inner ring peripheral speed of the bearing, and according to high-speed video observation, it was injected despite the air flow accompanying the rotation caused by the bearing. The oil travels almost linearly and reaches the inside of the bearing. It is considered that this is because the discharge speed is high and the lubricating oil has some inertial mass.

By the way, there are cases where different types of bearings such as angular contact ball bearings and inner ring flanged cylindrical roller bearings are used in the main shaft device. In angular contact ball bearings, the lubricating oil is retained in the inner ring by centrifugal force. Since it is hard to be prevented and the PV value (P: surface pressure, V: relative sliding speed) of the ball and the inner ring is large and the lubrication condition is severe, the lubricating oil is most needed at the contact portion between the ball and the inner ring, while the inner ring collar In a cylindrical roller bearing of the type, since the rib and the end surface are in sliding contact, oil is most needed between the rib and the end surface.

However, in the lubricating device for a main shaft having the above-mentioned structure, the details of the discharge direction of the lubricating oil are not disclosed, and the lubricating oil should be surely injected to the most required portion according to the type of bearing. It is desirable to have a means to do so. Therefore, an object of the present invention is to solve the above problems, and it is possible to reliably inject an extremely small amount of lubricating oil at a sufficient discharge speed to a portion that requires the most lubricating oil according to the type of bearing. It is to provide a highly reliable spindle device.

[0011]

The object of the present invention is to provide a shaft, an angular ball bearing having an inner ring fitted to the shaft, a housing fitted to an outer ring of the angular ball bearing, and a nozzle. The above angular contact ball bearing has a discharge speed of 10 m /
sec or more and 100 m / sec or less, discharge oil amount 0.000
A lubricating device for supplying a small amount of lubricating oil of 5 ml / shot or more and 0.01 ml / shot or less is provided, and the inner ring and the outer ring of the angular ball bearing are relatively rotatable via balls as rolling elements. The main spindle device is characterized in that the direction of discharge of the lubricating oil from the nozzle is directed to the contact position between the inner ring and the ball.

According to the above construction, the lubricating oil discharged from the nozzle travels almost linearly. Therefore, by directing the discharging direction to the contact position between the inner ring and the ball, the lubricating oil can be reliably transferred to the contact point between the inner ring and the ball. Can be supplied to.

Another object of the present invention is to provide a shaft, an inner ring flanged cylindrical roller bearing having an inner ring fitted to the shaft, a housing fitted to an outer ring of the cylindrical roller bearing, and a nozzle. And a lubricating device for supplying a minute amount of lubricating oil having a discharge speed of 10 m / sec or more and 100 m / sec or less and a discharge oil amount of 0.0005 ml / shot or more and 0.01 ml / shot or less to the cylindrical roller bearing. A spindle device in which an inner ring and an outer ring of a bearing are relatively rotatable via a cylindrical roller as a rolling element, and a direction in which lubricating oil is discharged from the nozzle is an exposed surface of one end surface of the cylindrical roller. And a main shaft device which is directed to a flange surface which guides an end surface opposite to the end surface.

According to the above construction, by directing the direction of discharge of the lubricating oil from the nozzle to the exposed surface of the one end surface of the cylindrical roller and the flange surface for guiding the end surface opposite to the end surface, the required position can be obtained. Lubricating oil can be reliably supplied.

[0015]

DETAILED DESCRIPTION OF THE INVENTION A spindle device according to an embodiment of the present invention will be described in detail below with reference to the accompanying drawings. 1 is a sectional view for explaining a spindle device according to a first embodiment of the present invention, FIG. 2 is an enlarged sectional view of an angular ball bearing and a nozzle, and FIG. 3 is a ball as a rolling element from the end surface side of the bearing. FIG.

First, the spindle device according to the first embodiment of the present invention will be described. As shown in FIG. 1, the spindle housing 51 includes a housing body 52 and a housing body 5.
A front bearing housing 53 internally fitted and fixed to the front end (left end in the drawing) of No. 2 and a rear bearing housing 54 internally fitted and fixed to the rear end of the housing body 52 are provided. An outer ring pressing member 55 and a front lid 57 are attached to the end of the front bearing housing 53, and the rear bearing housing 54 is
The outer ring pressing member 58 and the rear lid 60 are attached.

A spindle (shaft) is provided in the spindle housing 51.
61 is inserted and arranged, and the main shaft 61 has two front and rear angular ball bearings 62a and 62b axially spaced from each other in a front bearing housing 53, and one main bearing 61 arranged in a rear bearing housing 54. It is rotatably supported by the inner ring flange type cylindrical roller bearing 63.

The angular ball bearings 62a and 62b are
A plurality of balls 4 as rolling elements between the inner ring 64 and the outer ring 67
1 are arranged at substantially equal intervals in the circumferential direction via the cage 40,
A fixed position preload is applied, and each outer ring 67 is internally fitted and fixed to the front bearing housing 53, and each inner ring 64 is externally fitted and fixed to the main shaft 61.

On the other hand, the inner ring collar type cylindrical roller bearing 63 is
A plurality of cylindrical rollers 31 as rolling elements are arranged between the inner ring 69 and the outer ring 73 at substantially equal intervals in the circumferential direction via the retainer 30, and the outer ring 73 is internally fitted and fixed to the rear bearing housing 54. In addition, the inner ring 69 is externally fitted and fixed to the main shaft 61.

The cylindrical roller bearing 63 is, as in this example,
It is used as a rear side bearing for the main shaft 61 whose front side is preloaded with a fixed position. At this time, since the rear cylindrical roller bearing 63 is not positively loaded, the inner diameter is usually set to be 10 to 20% smaller than the front angular contact ball bearings 62a and 62b. Also,
The maximum speed of the main shaft 61 of this type is regulated by the angular position ball bearings 62a and 62b of pre-positioned preload, and as a result, the maximum rotational speed of the cylindrical roller bearing 63 is dm · n (d
m: rolling element pitch circle diameter (mm), n: rotational speed (rp
m)) is about 2.2 million.

An inner ring spacer 66 is interposed between the inner rings 64 of the two front and rear angular ball bearings 62a, 62b in the front bearing housing 53, and the inner ring 64 of the rear angular ball bearing 62b is The inner ring 64 of the front angular contact ball bearing 62a is axially pressed rearward by the inner ring pressing member 56 while being locked to the stepped portion 65 of the main shaft 61.

Two front and rear angular ball bearings 62 are also provided.
An outer ring spacer 70 is interposed between the outer rings 67 of a and 62b, the outer ring 67 of the rear angular ball bearing 62b is locked to the step 68 of the front bearing housing 53, and the front angular ball The outer ring 67 of the bearing 62a is axially pressed rearward by the outer ring pressing member 55.

A rotor 76 is externally fitted and fixed to a substantially central portion of the main shaft 61 in the axial direction, and a stator 77 is coaxially arranged on the outer peripheral surface side of the rotor 76. Stator 77
Is attached to the inner peripheral surface of the housing body 52 by the stator sleeve 7
It is fixed via 8. Nozzles 80 and 81 are arranged to penetrate the outer ring spacer 70 on the front bearing housing 53 side, and nozzles 90 are arranged to penetrate to the outer ring spacer 75 on the rear bearing housing 54 side. ，
Lubricating oil is supplied to 90 from a small amount lubrication device 82 via an oil supply passage 91 formed in the spindle housing 51.

The micro-lubrication device 82 has a discharge port 80a for the nozzles 80, 81, 90 controlled by a controller (not shown).
The discharge speed, the supply interval, the supply amount, etc. of the lubricating oil discharged from 81a, 90a toward the bearings 62a, 62b, 63 are controlled to be predetermined values.

In the present embodiment, the nozzles 80, 8
1, 90 discharge ports 80a, 81a, 90a to each bearing 6
The discharge speed of the lubricating oil discharged toward 2a, 62b, 63 is 10 m / sec or more and 100 m / sec or less, and the discharge oil amount is 0.0005 ml / shot or more and 0.01 ml / shot or less. Since it does not use the noise, it is possible to eliminate noise problems such as wind noise of the air and deterioration of the work environment due to the scattering of mist of lubricating oil into the atmosphere, and the discharging speed of the lubricating oil discharged from the nozzle is 10 to 100 m. Since it is as fast as / sec, lubricating oil can be reliably supplied to the inside of the bearing without being affected by the air curtain generated during high-speed rotation, and the amount of lubricating oil discharged is 0.0005 ml / shot or more 0.01 ml. Since it is a minute amount less than / shot, the rise in bearing temperature can be suppressed to a low level, and an auxiliary device including a high-pressure pump such as a jet system can be used. Does not, without an increase in agitation resistance due to become much amount of oil supplied to the bearings, it can be used as inexpensive small motor for driving the spindle.

Here, in this embodiment, the nozzles 80, 8
The direction of discharge of the lubricating oil discharged from No. 1 toward the angular ball bearings 62a and 62b is directed to the contact position between the inner ring 64 and the ball 41, and is discharged from the nozzle 90 toward the cylindrical roller bearing 63. The direction of discharge of the lubricating oil is directed toward the exposed surface of the one end surface of the cylindrical roller 31 and the flange surface 69a of the inner ring 69 that guides the end surface on the opposite side of the end surface. It is possible to reliably inject a very small amount of lubricating oil at a required portion at a sufficient discharge speed.

FIG. 2 shows the angular ball bearing 62 on the left side of FIG.
3A and the nozzle 80, the target position of the nozzle 80 is the center of the contact ellipse between the inner ring 64 and the ball 41. The nozzle angle θ is preferably 5 to 20 ° in order to reliably aim at the contact position between the inner ring 64 and the ball 41. It should be noted that, considering that the contact angle α varies due to temperature or centrifugal force during high-speed rotation, the target position may be set in advance according to the variation. Since the discharge port 80a is thin and foreign matter is easily clogged, a filter 80b is built in the nozzle body to prevent this.

FIG. 3 is a view of the ball 41 as seen from the bearing end face side. When the ball 41 is rolling in the zone (Z) in the drawing, the ball 4 is moved.
1 is lubricated, and the inner ring 64 is lubricated in the section (Y). Now, consider the conditions for the lubricating oil to reach the contact position 1 in FIG. While the balls 41 are rolling in the section (Y) of FIG. 3, the lubricating oil needs to travel at least the distance (X) of FIG. This relationship is determined by the rotation speed, the ball diameter of the bearing, the number of balls, PCD, the contact angle α, and the nozzle angle θ. In the angular ball bearing used for high speed rotation, it is calculated that the discharge speed of 8 to 10% or more of the inner ring peripheral speed is the minimum required.

As an example, nozzle angle: θ = 10 °, bearing: inner diameter 70 mm, ball diameter 8.73 mm, number of balls 22, PC
D88mm, contact angle α = 15 °, rotation speed 40000m
In the case of in ^-1 , the minimum required ejection speed from the nozzle 80 is about 14 m / sec. In direct-injection lubrication, the speed is sufficiently realizable. Further, as an example at this time, 0.0
Consider that discharge was performed at 03 ml / shot, 40 m / sec, and an inner diameter of 0.1 mm of the discharge port 80a of the nozzle. At this time, the discharge time of one sailboat is about 5 msec, during which the lubricating oil collides with the balls 41 and the inner ring 64 about 60 times each. As a result, it can be seen that the lubricating oil is injected almost all around the balls 41 and the inner ring 64, and it can be seen that a stable lubrication state can be secured.

FIG. 4 shows an example of an outer ring hooking type angular contact ball bearing according to a second embodiment of the present invention. The outer ring bearing allowance type bearing may have a larger outer diameter of the inner ring 64 than the inner ring bearing allowance type angular contact ball bearing of FIG. 2, but in such a case, by increasing the nozzle angle θ, The contact point between the inner ring 64 and the ball 41 can be aimed at. At that time, the cage 40 may block the target position. In this example, the inner diameter of the cage 40 is processed into a tapered shape as shown in FIG. 4, thereby making it possible to aim at the contact position between the balls 41 and the inner ring 64.

5 and 6 show an example of the nozzle 100 according to the third embodiment of the present invention, which is a modification of the nozzle 80. The specifications of the nozzle 100 are as follows:
1, 90 can also be applied. The nozzle 100
Includes a nozzle body 101 and a nozzle tip 102 fitted in the nozzle body 101, and the nozzle tip 102 has a discharge port 100a formed therein. The discharge port 100a has a narrowed tip, and the discharge port diameter d is preferably 0.1 to 0.3 mm because the small amount of oil is jetted at high speed.

The discharge port length L is preferably 100 to 300% of the discharge port diameter d. If the ejection port length L is too short, the ejection direction will not be stable, and if the ejection port length L is long, it will be difficult to process the hole of the ejection port 100a, foreign matter will be easily clogged, and the ejection speed will be affected by the flow path resistance. Problems such as deterioration occur. Since the discharge port 100a is thin and foreign matter is likely to be clogged, the nozzle body 101 has a filter 10
3 is built in to prevent this.

The throttle portion 104 of the nozzle tip 102 is
The cross-section has a taper shape in which the diameter is reduced toward the discharge port 100a side. With such a taper shape, bubbles are stagnant in the throttle portion 104 and the loss of discharge energy due to contraction flow is reduced. Can be made. Although the narrowed portion 104 has a linear tapered cross-section in consideration of workability in this example, the narrowed portion 10 having a curved cross-section as shown in FIG.
It may be 4a.

Further, the nozzle 10 shown in FIGS.
In the example of No. 0, the nozzle body 102 has the nozzle chip 102 in which the narrowed portion 104 is processed, and is press-fitted into the nozzle body 101.
As shown in FIG. 7, the throttle portion 105 may be bored from the side opposite to the nozzle outlet, and the opening may be sealed with a stopper 106 made of the same material as the main body. In this case, it is difficult to secure the processing accuracy, but the nozzle body can be downsized.

The material of the nozzle is C365 in consideration of workability.
It is desirable to use brass such as 4 or HBSC1. Others, copper, aluminum, aluminum alloys, iron, steel,
It is also possible to use various materials such as stainless steel and resin. In particular, the inner diameter of the nozzle tip is 0.1 to 0.
A brass material is preferably used for drilling a hole of a 3 mm discharge port.

The material of the nozzle body is not limited in terms of processing, but it is preferable to use the same material as the nozzle tip so that the tightening margin for press fitting does not change with temperature. Further, when a resin having a large thermal expansion is used, it is possible to prevent a phenomenon in which a small amount of air enters from the tip of the nozzle when the temperature decreases and the volume of oil decreases after the spindle is operated. Usually, in order to prevent such a phenomenon, a shot is taken for a while after the operation. Further, if the surface roughness of the hole which is the flow path is bad, foreign matter is caught and the nozzle is clogged. Therefore, the roughness of the flow path is preferably set to 3.2 μmRa or less in terms of center line average roughness.

FIG. 9 shows the structure of a nozzle according to the fourth embodiment of the present invention, which is one angular ball bearing 62.
Two nozzles 80 and 110 are used for a, and one nozzle 1
The discharge direction of 10 is directed to the guide surface of the cage 40, and the discharge direction of the other nozzle 80 is directed to the contact point between the ball 41 and the inner ring 64.

Further, as shown in FIG. 10, the nozzle 80 defines an aiming position by making an angle φ with the axis of the bearing in the same direction as the rotation direction. When the rotation direction is fixed, this can improve the oil supply efficiency. Normally, the injection speed of direct injection lubrication is fast, but due to the characteristics of the pump and the compressibility of the oil, the discharge speed is slow between the very early and the last hundreds of microseconds of discharge in one shot (the discharge time of one shot is Thousands of microseconds).

At this time, if the discharge direction of the nozzle is oriented in the rotation direction, even oil having a slow discharge speed can reach the inside of the bearing. The angle φ is usually about 0 to 20 °. In addition, it is also effective when using a micro-lubrication pump whose discharge speed is not so fast. The discharge direction of the nozzle 110 is substantially parallel to the bearing axis.
By aiming at the guide surface, the lubricating oil can be relatively injected to the inside of the guide surface.

FIG. 11 shows the structure of a nozzle according to the fifth embodiment of the present invention. In order to reduce the cost, one nozzle 120 is used for two opposing angular ball bearings 62a, 62b. This is an example of lubrication. In this case, since the pipe resistance increases and the discharge speed decreases, the pipe is used in applications where the rotation speed is not very high.

FIG. 12 relates to a sixth embodiment of the present invention and is on the side opposite to the normal nozzle position, that is, the angular ball bearing 62.
This is an example in which the nozzle 80 is arranged on the front side of a. The angular ball bearing 62a is affected by the rotation of the ball 41, and
Since an air flow is generated from the right side to the left side of the above, there is a problem in the conventional oil-air lubrication or the like that lubrication failure occurs when discharging from the front side. With direct-injection lubrication, the discharge speed is high and it is difficult to be affected by the air flow.

FIG. 13 shows the inner ring flange type cylindrical roller bearing 63 and the nozzle 90 on the right side of FIG. 1. The target position of the nozzle 90 is from the discharge port 90a of the nozzle 90 to the cylindrical roller bearing 63. The direction in which the lubricating oil is discharged is
It is set so as to face the exposed surface 31a of one end surface of the cylindrical roller 31 and the flange surface 69a of the inner ring 69 that guides the end surface on the opposite side of the end surface.

The nozzle angle θ is preferably 5 to 15 ° in order to aim at the exposed surface 31a and the collar surface 69a. When the cage 30 blocks the target position, the inner diameter T portion of the cage 30 is processed into a taper shape to secure the target position. Similar to the angular ball bearing, the end surface of the cylindrical roller 31 is lubricated in the section (Z) in FIG. 14, and the flange surface 69a is lubricated in the section (Y). The required discharge speed for the lubricating oil to reach the flange surface 69a is determined by the roller diameter of the bearing, the number of rollers, the roller length, the roller chamfer R, the nozzle angle θ, and the rotation speed.

A calculation of a normally used cylindrical roller bearing for high speed rotation is calculated to be about 45% of the inner ring peripheral speed. Although this speed is higher than the speed of the angular ball bearing, the practical maximum rotation speed of the cylindrical roller bearing is slower than that of the angular ball bearing for the reasons described below, so it is a practical speed. That is, the cylindrical roller bearing 63 is used as a support bearing on the rear side of the main shaft 61 whose front side is preloaded in a fixed position, and the cylindrical roller bearing 63 on the rear side is used.
Does not receive the load positively, so that the inner diameter is normally 10 to that of the front side angular contact ball bearings 62a and 62b.
It is set to be 20% smaller. In addition, the maximum speed of this type of spindle 61 is the fixed position preload angular contact ball bearing 62.
a, 62b, resulting in cylindrical roller bearing 6
The maximum rotation speed of No. 3 is about 2.2 million in dm · n (dm: rolling element pitch circle diameter (mm), n: rotation speed (rpm)).

Therefore, as an example in which the cylindrical roller bearing 63 is used at high speed, nozzle angle θ = 10 °, bearing: inner diameter 55 mm, roller diameter 3 mm, roller length 8 mm, number of rollers 18
Piece, chamfering R 0.5 mm, PCD 73 mm, rotation speed 3
When 0000 min ⁻¹ is considered, the required minimum ejection speed is about 40 m / sec, which is a practical speed.

FIG. 15 relates to the seventh embodiment of the present invention and is an example in which short rollers are used as rolling elements. The cylindrical roller 31 of the commonly used inner ring flanged cylindrical roller bearing 63 has the same roller diameter and length. However, in the inner ring flanged cylindrical roller bearing 163 shown in FIG.
The length is about 60% of the roller diameter.

This cylindrical roller bearing 163 has a feature that the heat generation due to the rolling friction resistance is small and the moment for skewing the cylindrical roller 31 is small, so that the seizure resistance of the collar is high. When this bearing is applied to direct injection lubrication,
Since the distance (X) is shorter than that in FIG. 13, the collar surface 69
It is possible to provide the advantage that the lubricating oil reaching a'is increased and the seizure resistance of the collar is further improved. The minimum required lubricating oil discharge speed to reach the flange surface 69a 'is about 25% of the inner ring peripheral speed. It is needless to say that the spindle device of the present invention is not limited to the configuration of each of the above-described embodiments and can take various forms based on the spirit of the present invention.

[0048]

As described above, according to the above-described spindle device of the present invention, since the lubricating oil discharged from the nozzle travels almost linearly, the contact position between the inner ring and the ball and the exposed surface of the one end surface of the cylindrical roller. And on the collar surface that guides the end surface on the opposite side of the end surface,
By directing the discharge direction, it is possible to reliably supply an extremely small amount of lubricant oil at a sufficient discharge speed to a portion that requires the most lubricant oil depending on the type of bearing.

Therefore, it is possible to prevent noise problems such as wind noise of the air and deterioration of the working environment due to scattering of mist of lubricating oil in the atmosphere, and to supply lubricating oil to the lubricated surface of the bearing reliably. The bearing temperature can be minimized and the seizure resistance is high.
It is possible to provide a highly reliable spindle device.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view for explaining a spindle device according to a first embodiment of the present invention.

FIG. 2 is an enlarged sectional view of the angular contact ball bearing and nozzle shown in FIG.

FIG. 3 is an explanatory view of a ball as a rolling element shown in FIG. 2 viewed from an end surface side of a bearing.

FIG. 4 is a sectional view for explaining an angular contact ball bearing and a nozzle according to a second embodiment of the present invention.

FIG. 5 is a sectional view for explaining a nozzle according to a third embodiment of the present invention.

FIG. 6 is an enlarged view of a main part of FIG.

7 is a cross-sectional view showing a modified example of the nozzle shown in FIG.

8 is a sectional view showing another modified example of the nozzle shown in FIG.

FIG. 9 is a sectional view for explaining an angular contact ball bearing and a nozzle according to a fourth embodiment of the present invention.

10 is a view taken in the direction of arrow A in FIG.

FIG. 11 is a sectional view for explaining an angular contact ball bearing and a nozzle according to a fifth embodiment of the present invention.

FIG. 12 is a sectional view for explaining an angular contact ball bearing and a nozzle according to a sixth embodiment of the present invention.

13 is an enlarged cross-sectional view of an inner ring flanged cylindrical roller bearing and a nozzle shown in FIG.

FIG. 14 is an explanatory view of the cylindrical roller as the rolling element shown in FIG. 13 as seen from the end face side of the bearing.

FIG. 15 is a sectional view for explaining an inner ring flanged cylindrical roller bearing and a nozzle according to a seventh embodiment of the present invention.

[Explanation of symbols]

41 balls 51 housing 61 Spindle 62a, 62b angular contact ball bearings 63 Inner ring collar type cylindrical roller bearing 64 inner ring 67 outer ring 69 inner ring 69a Brim surface 73 outer ring 80, 81 nozzles 82 Lubricator 90 nozzles

Claims (2)

[Claims] 1. A shaft, an angular ball bearing having an inner ring fitted to the shaft, a housing fitted to an outer ring of the angular ball bearing, and a discharge speed of 10 m / sec to the angular ball bearing through a nozzle. Above 100 m / sec, discharge oil amount 0.0005 ml / shot above 0.01 ml /
A spindle device comprising a lubricating device that supplies a small amount of lubricating oil of shots or less, wherein the inner ring and the outer ring of the angular ball bearing are relatively rotatable via balls as rolling elements, A spindle device, wherein a direction of discharging lubricating oil from a nozzle is directed to a contact position between the inner ring and the ball. 2. A shaft, an inner ring flanged cylindrical roller bearing having an inner ring fitted to the shaft, a housing fitted to the outer ring of the cylindrical roller bearing, and a nozzle that discharges to the cylindrical roller bearing. Speed 10m / sec or more and 100m / sec or less, discharge oil amount 0.0005ml / shot or more 0.01ml /
A spindle device comprising a lubricating device that supplies a small amount of lubricating oil below a shot, wherein the inner ring and the outer ring of the cylindrical roller bearing are relatively rotatable via cylindrical rollers as rolling elements, A spindle device, wherein the direction of discharge of the lubricating oil from the nozzle is directed to a flange surface that guides an exposed surface of one end surface of the cylindrical roller and an end surface opposite to the end surface.