JP3452947B2 - Bearing lubrication mechanism of main shaft device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing lubrication mechanism for a spindle device of a machine tool or the like, and more specifically to an improvement of a lubricating oil supply system capable of excellent bearing lubrication at high speed.

In order to realize a high speed spindle, more accurate lubrication inside the bearing is required. When the spindle rotates at high speed,
Lubricating oil must be reliably supplied to the inside of the bearing against the high-speed air flow near the end face of the bearing caused by centrifugal force and rotation of rolling elements and cages. Is a problem.

As a bearing lubrication mechanism for lubricating the inside of such a bearing, conventionally, a so-called jet lubrication mechanism for directly injecting a large amount of lubricating oil from a gap between an inner ring and an outer ring of a bearing toward an inner ring raceway surface, and an inner ring Various so-called underrace lubrication mechanisms have been proposed in which lubricating oil is supplied from an oil supply hole formed in the inner ring raceway surface or opening in the vicinity thereof.

As a first conventional example employing the jet lubrication mechanism, there is one having a structure as shown in FIG. 4, for example. In FIG. 4, reference numeral 1 denotes an outer ring spacer arranged between the bearings 5 and 5, and an oil injection portion 2 is integrally and annularly provided on the inner peripheral surface of the outer ring spacer 1. The oil injection portion 2 is provided with an oil passage hole 4 of which one end is opened in the annular oil groove 3, and the other end of the oil passage hole 4 is provided with injection holes 6, 6 opened on both side surfaces of the oil injection portion 2. Are formed to communicate with each other, and the injection holes 6 and 6 are opposed to the side surfaces of the bearings 5 and 5. In this conventional lubrication mechanism, the lubricating oil sent to the annular oil groove 3 of the outer ring spacer 1 is injected and supplied to the inner ring raceway surface from the gap between the inner ring and the outer ring through the oil passage holes 4, the injection holes 6 and 6. .

As a second conventional example adopting the above-mentioned underrace lubrication mechanism, for example, as disclosed in Japanese Utility Model Publication No. 62-183130 and Japanese Utility Model Publication No. 3-20726, lubricating oil is formed on the inner ring. Some of the oil is introduced into the introduction hole from the side of the bearing. This is to form an oil supply hole in the inner ring so as to open at or near the inner ring raceway surface, and to introduce an introduction hole or an introduction groove communicating with the oil supply hole so as to extend in the axial direction to the inner ring and open to the inner ring side surface. It has a structure in which a jet nozzle is provided so as to face the introduction hole and the like. In this conventional example, lubricating oil is injected from the jet nozzle toward the introduction hole of the inner ring and the like, and this lubricating oil is supplied from the oil supply hole to the inner ring raceway surface.

As a third conventional example employing an underlace lubrication mechanism, as disclosed in Japanese Patent Laid-Open No. 4-57355, lubricating oil is supplied to the inner ring raceway surface from the spindle axis side. There is. This is because the drive rod inserted into the through hole of the main shaft axis is provided with an oil supply passage, and the oil supply passage is communicated with an oil supply hole opening on the inner ring raceway surface through an oil passage hole penetrating in the radial direction of the main shaft. It is designed to refuel the raceway surface.

[0007]

However, in the jet lubrication mechanism as shown in the above-mentioned first conventional example, when the main shaft rotates at high speed, the lubricating oil is agitated by the bearing rolling elements to generate heat and reduce the shaft power loss. Occurs. Therefore, a large-capacity oil cooler and a large-output motor are required, and there arises a problem that the spindle device and the machine body are enlarged and energy is wasted.

Further, in the under-race lubrication mechanism in which the lubricating oil is supplied through the introduction hole or groove inside the inner ring as shown in the second conventional example, there is a large amount of leakage when flowing into the introduction hole, and the injection is performed. The amount of oil that flows into the oil supply hole through the introduction hole or the like is limited with respect to the amount, and there is a risk of causing poor lubrication and causing a burning accident.

Furthermore, in the under-race lubrication mechanism in which the lubricating oil is supplied through the oil supply passage of the main shaft axis as shown in the third conventional example, the inner ring raceway surface can be reliably lubricated without leakage. However, since a tool attaching / detaching mechanism that acts in the axial direction is built in the spindle through hole, there is a problem that the interior of the spindle becomes complicated and the spindle inner diameter becomes large by newly providing the oil supply passage. Further, a rotational joint for supplying lubricating oil to a rotating main shaft and vibration generated by an imbalance of lubricating oil which is nonuniformly present in the main shaft are factors that limit the rotational speed of the main shaft.

The present invention has been made in order to solve the above-mentioned conventional drawbacks, and an object thereof is to enable efficient and reliable lubrication with a small amount of lubricating oil even at high speed rotation. It is an object of the present invention to provide a bearing lubrication mechanism for a main spindle device that enables high-speed rotation by reducing heat generation and shaft power loss due to oil agitation.

[0011]

According to a first aspect of the present invention, a main shaft for lubricating a bearing that axially supports a main shaft is provided by arranging a large number of rolling elements at equal intervals between an inner ring and an outer ring. In the bearing lubrication mechanism of the device, a nozzle that protrudes in the axial direction from the side of the bearing is provided, and the tip opening of the nozzle is closer to the inner ring raceway surface than the nozzle side end surface of the cage on the inner ring side of the cage. And open so as to face the inner ring raceway surface.
Causes, connect the nozzle to the lubricating oil supply source, also
Therefore, the lubricating oil is directly supplied to the inner ring raceway surface .

According to a second aspect of the present invention, the nozzle is a spindle axis line.
Parallel to and parallel to the parallel part and perpendicular to the spindle axis
And a right-angled portion,
According to a third aspect of the present invention , the inner ring is formed so that a nozzle side end surface of the inner ring is located closer to an inner ring raceway surface side than a nozzle side end surface of the retainer, and the nozzle is inserted between the retainer and a main shaft. The invention of claim 4 is further characterized in that a taper surface for guiding the lubricating oil to the inner ring raceway surface is formed at the outer peripheral surface nozzle side edge portion of the inner ring.

[0013] A fifth aspect of the present invention, to form a stepped portion on the outer peripheral surface nozzle side edge of the inner ring, characterized in that inserted between the stepped portion and the retainer of the nozzle, claim The invention of No. 6 is further characterized in that a tapered surface for guiding the lubricating oil to the inner ring raceway surface is formed following the step portion.

Here, the inner ring raceway surface in the present invention means a track surface on which the rolling elements on the outer surface of the inner ring actually contact. In the invention of claim 3 , inserting the nozzle between the retainer and the main shaft includes the case where, for example, the inner ring spacer is located between the main shaft and the nozzle.

[0015]

According to the bearing lubrication mechanism of the main shaft device of the first aspect of the invention, the tip opening of the nozzle is brought closer to the inner ring raceway surface than the nozzle side end surface of the cage, and the lubricating oil is supplied from the position closest to the inner ring raceway surface. Since it is jetted and oil is directly supplied to the inner raceway surface, it is possible to reduce the influence of the air flow generated at the bearing end by the rotation of the cage, etc., and to reliably lubricate the inner ring raceway surface with a small amount of lubricating oil supply. Can be generated, and the
Ru can prevent the heat.

According to the invention of claim 2 , the nozzle is provided with a parallel portion.
Since it is composed of a minute part and a right angle part, it can be manufactured by machining.
It's easy. According to the invention of claim 3, since the nozzle-side end surface of the inner ring is shortened, and according to the invention of claim 5 , since the step portion is formed on the outer peripheral surface nozzle side edge portion of the inner ring, the nozzle interferes with the inner ring. It is possible to easily approach the inner ring raceway surface without the need.

Further, according to the inventions of claims 4 and 6 ,
Since the tapered surface that guides the lubricating oil is provided on the inner ring raceway surface,
The injected lubricating oil receives a centrifugal force and reliably flows into the inner ring raceway surface connected to the tapered surface.

[0018]

Embodiments of the present invention will be described below with reference to the drawings. 1 and 2 are views for explaining a first embodiment according to the invention of claims 1 to 4 , FIG. 1 is a vertical cross-sectional front view of a spindle device having a mechanism of this embodiment, and FIG. It is an enlarged vertical cross-sectional front view of a part.

In the figure, reference numeral 11 is a main spindle device, and the main spindle device 11 includes a main spindle 12 arranged in a horizontal direction, and a pair of angular ball bearings 13 and 13 rotatably supporting a front portion of the main spindle 12. , A cylindrical roller bearing 14 for rotatably supporting the rear portion of the main shaft 12, and the bearings 13, 14
A housing 15 for supporting the main shaft 12 and a motor 21 for rotationally driving the main shaft 12 are provided.

The housing 15 is a concentric small-diameter cylindrical portion 1.
5a and a large-diameter cylindrical portion 15b having a small diameter,
A flange 1 is provided on the outer peripheral surface of the boundary between the large-diameter cylindrical portions 15a and 15b.
6 is formed. A front cover 17 is fixed to the front end surface of the small diameter cylindrical portion 15a, and a rear cover 18 is fixed to the rear end surface of the large diameter cylindrical portion 15b.

The motor 21 is incorporated in the large-diameter cylindrical portion 15b of the housing 15. This motor 21
Has a structure in which the stator 21a is inserted and fixed to the inner circumference of the large-diameter cylindrical portion 15b via the sleeve 22, and the rotor 21b is fixed to the outer circumference of the main shaft so as to face the stator 21a. A spiral cooling liquid passage 23 is provided on the outer periphery of the sleeve 22, and the stator 21a is cooled from the outer peripheral side by the cooling liquid supplied to the cooling liquid passage 23 from an external cooling liquid source (not shown). To do.

The large-diameter cylindrical portion 15b of the housing 15
The cylindrical roller bearing 14 that supports the rear portion of the main shaft 12 is disposed in the through hole of the rear cover 18 fixed to the rear end. The outer ring 14 a of the bearing 14 is the rear cover 1
It is sandwiched in the axial direction by the inner diameter stepped portion 18a of 8 and the outer ring retainer 24, and is fixed by pressure to the inner periphery of the rear cover 18. The inner ring 14b of the bearing 14 is fitted to the main shaft 12 together with the short spacer 25 and the long spacer 26, and is screwed to the outer diameter step portion 12c of the main shaft 12 and the male screw 12d formed on the rear portion of the main shaft 12. It is clamped in the axial direction by the fixing nut 27 and fixed to the outer circumference of the main spindle by pressure.

Further, the outer ring retainer 24 is provided with a nozzle 24a which opens to the side of the bearing 14, and the nozzle 24a is connected to an external lubricating device (not shown) through a pipe 28. There is. Oil air, which is a lubricating oil obtained by mixing oil and air, is supplied to the bearing 14 through the nozzle 24a.

A tool mounting taper hole 12e is formed at the tip of the main shaft 12, and a through hole 12f for extending the taper hole 12e to the main shaft rear end surface is axially provided in the shaft center. . A tool attaching / detaching mechanism (not shown) or the like is inserted into the through hole 12f.

Inside the small-diameter cylindrical portion 15a of the housing 15, the pair of angular ball bearings 13, 13 for supporting the front portion of the main shaft 12 are arranged in a back face combination with an axial interval. Outer ring 13 of these bearings 13, 13
a and 13a are connected to the housing 15 via the outer ring spacer 19.
It is pressed and held in the axial direction by the inner diameter stepped portion 15c and the front cover 17, and is fixed by pressure contact with the inner circumference of the small diameter cylindrical portion 15a. The inner rings 13b and 13b of the bearings 13 and 13 are
Through the inner ring spacer 20, the outer diameter stepped portion 12a of the main shaft 12 and the holding nut 32 screwed to the male screw 12b formed on the front portion of the main shaft 12 are pressed and clamped in the axial direction,
As a result, the rolling element 13c and the raceway surface are pressed against and fixed to the outer periphery of the main shaft in a state where a preload is applied.

An annular oil groove 15h is formed between the bearings 13 and 13 on the outer circumference of the small-diameter cylindrical portion 15a of the housing 15, and a cylindrical cooling cylinder 30 is fitted therein.
A cooling liquid is supplied from an external cooling liquid source (not shown) to the space formed between the oil groove 15h and the cooling cylinder 30, and the cooling liquid cools the small diameter cylindrical portion 15a from the outer periphery.

The lubrication mechanism of this embodiment will be described in more detail with reference to FIG. As shown in the figure, the front bearing portion of the main shaft 12 includes a pair of angular contact ball bearings 13, 13 for connecting the outer ring spacer 19 to the outer ring spacer 19.
Also, the inner ring spacer 20 is disposed so as to be interposed therebetween, and is configured symmetrically in the drawing. The bearing 13 includes a pair of outer races 13a and inner races 13b, a large number of rolling elements 13c interposed between the outer raceway surfaces 13g and inner raceway surfaces 13e of the two wheels 13a and 13b, and guides and holds the rolling bodies 13c at equal intervals. And a holder 13d for

The end surface of the inner ring 13b which is in contact with the inner ring spacer 20 is axially shortened toward the inner ring raceway surface 13e, and the rolling element 1 is located closer to the spacer side end surface of the cage 13d.
It is located on the 3c side. Further, a taper surface 13f continuous with the inner ring raceway surface 13e is formed on the outer peripheral edge portion on the shortening side of the inner ring 13b.

In the outer ring 13a, a plurality of oil supply holes 13h penetrating radially outward from the vicinity of the outer ring raceway surface 13g are radially provided at predetermined angular intervals.

An annular injection convex portion 19a is integrally provided on the inner peripheral surface of the outer ring spacer 19 interposed between the outer rings 13a and 13a, and the injection convex portion 19a is the outer peripheral surface of the inner ring spacer 20. It projects to the vicinity. Further, the jet convex portion 19a
An annular injection portion 19b is provided on each side surface of the bearing 13
It is provided so as to project to the side. The injection portion 19b extends to the inner ring raceway surface 13e side from the retainer 13d through the inner ring side, and its tip is located in the vicinity of the tapered surface 13f of the inner ring 13b and the rolling element 13c.

A plurality of oil passage holes extending in the radial direction are provided at the front and rear portions in the axial direction corresponding to the bearings of the injection projection 19a.
(Right angle portion) 19c is radially provided at predetermined angular intervals. One end of this oil passage hole 19c is provided with the injection projection 19
A nozzle (parallel portion) 19d that is opened in the outer periphery of a and is axially bored in the injection portion 19b communicates with the other end. The nozzle opening (tip opening) 19e of the nozzle 19d is open toward the inner ring raceway surface 13e and the tapered surface 13f. Here, since the spacer contact side of the bearing inner ring 13b is shortened, the injection portion 19b is the cage 1 of the bearing 13.
Nozzle port 19e without interfering with 3d and inner ring 13b
Can be disposed in the immediate vicinity of the inner ring raceway surface 13e.

An oil supply passage 15f extending in the axial direction is formed in the upper portion of the small-diameter cylindrical portion 15a of the housing 15 in the figure.
Further, an annular oil groove 15d is formed on the inner circumference of the small-diameter cylindrical portion 15a at a position corresponding to the oil supply holes 13h of the outer rings 13a and the oil passage holes 19c of the outer ring spacers 19, respectively. The hole 13h and the oil passage hole 19c communicate with the oil supply passage 15f by the oil grooves 15d and a plurality of branched oil supply passages 15e formed in the radial direction.

An axially extending drainage passage 15g is cut out at the lower portion of the small-diameter cylindrical portion 15a of the housing 15 in the figure. Further, oil discharge ports 29 are provided at the ends of the outer ring spacer 19 that come into contact with the outer rings 13a, the front cover 17, and the inner diameter stepped portion 15c of the small-diameter cylinder part. The oil air that has communicated with the oil drain passage 15g through the oil drain passage 31 or directly and is accumulated in the lower portion of the bearing is discharged to the outside from the rear portion of the oil drain passage 15g.

Next, the function and effect of this embodiment will be described. In the above configuration, the oil air supplied from the external lubricating oil supply device is supplied to the oil supply passage 15f in the housing 11.
To branch and flow into each branch oil supply passage 15e, and then flow into each oil groove 15d on the inner circumference of the small-diameter cylindrical portion. This oil air enters the nozzle 19d through the oil groove 15c from the oil groove 15d corresponding to the oil hole 19c of the outer ring spacer 19, and the nozzle opening 19e.
It jets out toward the inner ring raceway surface 13e and the tapered surface 13f.

Here, the jetted oil air is subjected to the action of centrifugal force, propagates through the tapered surface 13f, reliably flows into the inner ring raceway surface 13e, and is also supplied to the rolling elements 13c. The oil air flowing into the oil groove 15d is the oil groove 1 corresponding to the oil supply hole 13h of the bearing outer ring 13a.
Oil is directly supplied to the outer ring raceway surface 13g and the rolling elements 13c from 5d through the oil supply hole 13h.

The oil-air supplied to each part of the bearing is collected in the lower part of the small-diameter cylindrical part of the housing 15 and quickly discharged from the oil discharge port 29 of each bearing side through each branch oil discharge path 31 to the oil discharge path 15g. It is discharged to the outside via.

As described above, in this embodiment, the end surface of the inner ring 13b on the nozzle side is shortened from the end surface of the retainer 13d on the inner ring raceway surface 13e side, and the injection portion 19b is located on the inner ring 13b side of the retainer 13d on the inner ring raceway side. Since it is projected to the surface 13e side, the nozzle opening 19e can be provided at the position closest to the inner ring raceway surface 13e while avoiding the retainer 13d, the influence of the airflow is reduced, and the bearing 13 is provided even at the time of high speed rotation. The appropriate amount of oil is reliably supplied to improve the lubrication performance and cooling effect. Further, since the tapered surface 13f is provided on the outer peripheral edge of the inner ring 13b, the lubricating oil flows into the inner ring raceway surface 13e along the tapered surface 13f by the centrifugal force, and the lubricating performance is improved also from this point.

Further, since the lubricating oil can be effectively introduced into the inner ring raceway surface 13e, the amount of oil supply can be minimized, the heat generation due to the agitation of the lubricating oil is small, and the heat generation from the bearing inner ring 13b is also reduced. Thermal displacement can be suppressed. Also, since the amount of lubricating oil can be minimized, the motor 2
Since there is no need to increase the output of No. 1 or to provide a large-capacity oil cooler, it is not necessary to upsize the spindle device or machine body, and energy and cost can be reduced.

Furthermore, in this embodiment, the housing 1
As the structure for supplying the lubricating oil from the 5 side, the lubricating oil flow path is provided in the outer ring spacer 19, so that the number of parts can be reduced.
Easy to assemble and maintain.

In the above embodiment, one oil supply passage 15f is used.
Although the oil air is supplied to each oil supply port by the above method, the oil supply paths may be independent from each other and the optimum oil supply amounts may be set.

FIG. 3 shows the second aspect of the invention according to claims 1, 5 , and 6 .
FIG. 2 is a vertical sectional front view of a main part of a spindle device according to an example. The angular ball bearing 49 includes a pair of outer ring 50 and inner ring 51,
A plurality of rolling elements 52 interposed between the outer ring 50 and the inner ring 51 and a cage 53 for guiding and holding the rolling elements 52 at equal intervals on the circumference are provided. The inner ring 51 is the main shaft 5
4, the outer ring 50 is fitted on the inner periphery of the housing 55, and is pressed in the axial direction to preload the rolling elements 52, the outer ring, and the inner ring raceway surfaces 56, 57. The inner ring spacer 58 and the outer ring spacer 59 are sandwiched and fixed in the axial direction.

The inner ring 51 is set to be slightly longer than the cage 53, and a step portion 60 is formed on the outer peripheral edge of one of the spacers, and the inner ring raceway surface 57 is formed on the rolling element side of the step portion 60. Is provided with a tapered surface 61.

An annular injection convex portion 62 is integrally provided on the inner peripheral surface of the outer ring spacer 59, and the injection convex portion 62 projects to the vicinity of the outer periphery of the inner ring spacer. One end of the injection convex portion 62 is opened to the outer peripheral oil groove 63, and a plurality of oil passage holes 64 extending in the radial direction are radially provided at predetermined angular intervals. Further, the side surface of the injection convex portion 60 communicates with the other end of the oil passage 64, and the inner ring raceway surface 57 and the tapered surface 6 are formed.
A plurality of nozzle cylinders 65 that open toward 1 are projected and fixed to the space between the cage 53 and the inner ring step portion 60 at predetermined angular intervals.

Next, the function and effect of the second embodiment will be described. In the above configuration, the oil air supplied from the housing side to the oil groove 63 on the outer periphery of the outer ring spacer is supplied to the oil passage holes 6
No. 4 flows into each nozzle cylinder 65 and is jetted from the nozzle port 66 toward the bearing inner ring raceway surface 57 and the tapered surface 61.

Also in the second embodiment, similarly to the first embodiment, oil air can be reliably supplied to the inner ring raceway surface 57, and reliable lubrication can be performed with a minimum amount of oil supply. in this case,
According to this embodiment, since the step portion 60 is provided on the inner ring 51,
The nozzle cylinder 65 can be inserted into the lower portion of the retainer 53 to bring the nozzle port 66 closer to the inner ring raceway surface 57 without shortening the inner ring width, and reliable oil supply to the inner ring raceway surface 57 is possible.

Although the nozzle cylinder 65 is a separate component in the second embodiment, it may be formed integrally with the outer ring spacer 59. Further, although oil air is adopted in the first and second embodiments, it is not limited to oil air, and other lubrication methods such as oil mist may be used.

In the first and second embodiments, the case of the ball bearing has been described, but the present invention can be applied to the case of the roller bearing. Furthermore, in the above-mentioned first and second embodiments, the case of the pair of angular contact ball bearings used in the rear combination has been described, but the present invention can of course be applied to the case of the front combination. In the front combination, the nozzle is formed by utilizing the front cover 17 and the inner diameter step portion 15c of the housing 15.

[0048]

As described above, according to the bearing lubrication mechanism of the main shaft device according to the invention of claim 1, the tip opening of the nozzle is made closer to the inner ring raceway surface than the nozzle side end surface of the retainer,
The lubricating oil ejected from the position closest to the inner ring raceway surface, the inner race
Since the raceway surface is directly lubricated, it is possible to efficiently and reliably lubricate a proper amount with a small amount of lubricating oil even at the time of high speed rotation, and it is possible to reduce heat generation and shaft power loss due to stirring of the lubricating oil.

According to the second aspect of the invention , the nozzle is provided with a parallel portion.
Since it is composed of a minute part and a right angle part, it can be manufactured by machining.
According to the invention of claim 3, since the end surface of the inner ring on the nozzle side is shortened, and according to the invention of claim 5 , the step is formed on the outer peripheral surface of the inner ring on the nozzle side. It is possible to easily approach the inner ring raceway surface without interfering with the inner ring and there is an effect that the lubricating oil can be efficiently supplied to the inner ring raceway surface.

Further, according to the inventions of claims 4 and 6 ,
Since the tapered surface that guides the lubricating oil is provided on the inner ring raceway surface,
The injected lubricating oil receives a centrifugal force and reliably flows into the inner ring raceway surface connected to the tapered surface, and from this point also, there is an effect that the influence of the air flow is reduced and a small amount of lubricating oil can be efficiently lubricated.

[Brief description of drawings]

1 is a longitudinal sectional front view showing a bearing lubrication mechanism of the spindle apparatus according to the first embodiment according to the invention of claims 1 to 4.

FIG. 2 is a vertical cross-sectional front view of a main part in the first embodiment.

3 is a longitudinal sectional front view of a main part of the bearing lubrication system of the spindle device according to a second embodiment according to the invention of claim 1,5,6.

FIG. 4 is a vertical cross-sectional front view of a main part of a bearing lubrication mechanism of a spindle device according to a conventional technique.

[Explanation of symbols]

11 Spindle device 12,54 Spindle 13,49 bearings 13a, 50 outer ring 13b, 51 inner ring 13c, 52 rolling elements 13d, 53 cage 13e, 57 Inner ring raceway 13f, 61 taper surface 19d, 65 nozzles, nozzle tube 19e, 66 Nozzle mouth (tip opening) 60 steps

─────────────────────────────────────────────────── ─── Continuation of the front page (58) Fields surveyed (Int.Cl. ⁷ , DB name) F16C 33/00-33/82

Claims (6)

(57) [Claims] 1. A bearing lubrication mechanism of a main spindle device, wherein a plurality of rolling elements are arranged at equal intervals between a inner ring and an outer ring by a cage to lubricate a bearing supporting a main shaft. A nozzle projecting in the axial direction from one side, the tip opening of the nozzle being closer to the inner ring raceway surface than the nozzle side end surface of the retainer on the inner ring side of the retainer , and on the inner ring raceway surface.
While opening so as to face each other , connect the nozzle to the lubricating oil supply source, and thus supply the lubricating oil directly to the inner ring raceway surface.
A bearing lubrication mechanism for a spindle device, characterized in that 2. The shaft according to claim 1, wherein the nozzle is a spindle shaft.
The parallel part that is parallel to the line and the part that is connected to the parallel part is directly connected to the spindle axis.
A bearing lubrication mechanism for a spindle device, characterized in that the bearing lubrication mechanism is composed of an angular right angle portion . 3. The inner ring according to claim 1 or 2,
The end surface of the inner ring on the nozzle side is closer to the end surface of the retainer on the nozzle side.
It is formed so that it is located on the inner ring raceway side, and the nozzle is
A bearing lubrication mechanism for a spindle device, characterized by being inserted between a cage and a spindle. 4. The method according to claim 1, wherein
Lubrication oil is proposed on the inner ring raceway on the outer edge of the inner ring on the nozzle side.
A bearing lubrication mechanism for a spindle device, characterized in that an inner tapered surface is formed . 5. The outer ring of the inner ring according to claim 1 or 2.
A step is formed on the peripheral edge of the peripheral nozzle, and the nozzle is provided with the step.
And a cage, the bearing lubrication mechanism of the main spindle device is inserted between the cage and the cage . 6. The inner ring raceway surface according to claim 5,
That the tapered surface that guides to the
Bearing lubrication mechanism of the main spindle device.