JP6318582B2 - Bearing device and spindle device - Google Patents

Description

  The present invention relates to a bearing device and a main shaft device, and more particularly to a bearing device and a main shaft device that can be stably grease lubricated over a long period of time with enclosed grease.

  The speedup of the spindle device for machine tools has been remarkably developed, and oil mist lubrication and oil-air lubrication have been the main lubrication methods for enabling speedup of the spindle. However, in recent years, there has been a strong demand for environmental measures, energy savings, and resource savings, environmental considerations due to noise and oil scattering are necessary, a large amount of air is required, oil mist lubrication equipment and oil air There are disadvantages in terms of cost, such as the need for incidental equipment such as a supply device.

  In order to avoid these problems, grease lubrication has begun to attract attention again. Since grease lubrication is performed with the grease base oil enclosed when the bearing is assembled, the amount of base oil necessary for bearing lubrication is limited, and the amount of base oil affects the lubrication life. For this reason, it is conceivable to increase the amount of grease enclosed in the bearing, but in this case, since the viscous resistance increases, bearing heat generation increases when used at high speed rotation, and conversely, the oil film breaks due to early grease deterioration. It may occur and lead to burn-in. For this reason, in consideration of the balance between the temperature rise characteristics during high-speed rotation and the life of the grease, normally, grease corresponding to approximately 10 to 20% of the internal volume of the bearing is enclosed. In addition, if excessive grease is filled, the running-in time becomes longer, so the time until the production line returns after the main bearing replacement becomes longer, which also affects the production efficiency.

  As a conventional grease lubricated bearing, a grease reservoir component and a rolling bearing are disclosed in which a grease reservoir component is formed separately from the rolling bearing and is disposed adjacent to the stationary side race (for example, , See Patent Document 1). As shown in FIG. 7, the grease reservoir component 100 described in Patent Document 1 includes an annular container portion 101 whose inside is a grease reservoir 102, and a raceway of a fixed-side bearing ring 111 of the rolling bearing 110 that protrudes from the container portion 101. And an in-bearing insertion portion 103 inserted to the vicinity of the surface 111a. A base oil bleeding port 104 is provided at the tip of the bearing insertion portion 103, and the grease G accommodated in the container portion 101 is supplied from the base oil bleeding port 104 to the rolling bearing 110.

JP 2008-240828 A

  However, the grease reservoir component 100 and the rolling bearing 110 described in Patent Document 1 are a combination of a plurality of components having a complicated structure, which causes an increase in manufacturing cost. In addition, the grease G is supplied from the grease base oil exudation port 104 by using the pressure fluctuation caused by the heat cycle in the grease reservoir 102 accompanying the operation / stop of the rolling bearing 110. ing. For this reason, there is a possibility that lubrication may be insufficient only in the pressure fluctuation due to the heat cycle in an application (dmn 500,000 or more, more preferably dmn 1,000,000 or more) that rotates at a high speed like a bearing for a spindle of a machine tool.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a bearing device and a spindle device capable of stable grease lubrication over a long period of time with a simple and inexpensive mechanism. .

The above object of the present invention can be achieved by the following constitution.
(1) An inner ring having an inner ring raceway surface on an outer peripheral surface, an outer ring having an outer ring raceway surface on an inner peripheral surface, and a predetermined contact angle so as to be freely rollable between the inner ring raceway surface and the outer ring raceway surface. A plurality of balls, and an angular ball bearing in which grease is sealed in a bearing space between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring,
An outer ring spacer that is disposed in contact with the axial end surface of the outer ring on the counter-bore side;
An inner ring spacer facing the outer ring spacer and disposed in contact with an axial end surface of the inner ring;
A bearing device comprising:
The outer ring spacer has a spacer-side grease reservoir defined by cutting out an inner peripheral surface so as to communicate with the bearing space on the inner diameter side, and grease is enclosed in the spacer-side grease reservoir,
The outer peripheral surface of the inner ring spacer includes a conical tapered outer peripheral surface that gradually increases in diameter toward the angular ball bearing, and a cylindrical portion that is formed closer to the angular ball bearing than the tapered outer peripheral surface. A bearing device.
(2) An inner peripheral surface of the outer ring spacer is disposed opposite to the tapered outer peripheral surface of the inner ring spacer via a predetermined gap, and gradually increases in diameter toward the angular ball bearing. The bearing device according to (1), which has a surface.
(3) The bearing device according to (1) or (2), wherein grease mixed with a gelling agent is sealed in at least one of the bearing space and the spacer side grease reservoir.
(4) The bearing device according to any one of (1) to (3) is provided, and the bearing device is a pair of rear surfaces arranged on both sides in the axial direction of the outer ring spacer and the inner ring spacer. A main shaft device comprising the angular ball bearing, wherein the main shaft is rotatably supported with respect to a housing via the bearing device.
(5) The outer ring spacer is provided with a vent hole for supplying air to the spacer-side grease reservoir via an air supply passage formed in the housing (4). Spindle device described in 1.

According to the bearing device of the present invention, the outer ring spacer has a spacer-side grease reservoir defined by cutting out the inner peripheral surface so as to communicate with the bearing space on the inner diameter side, and the spacer-side grease reservoir. Grease is enclosed, and the outer peripheral surface of the inner ring spacer has a conical tapered outer peripheral surface that gradually increases in diameter toward the angular ball bearing, and a cylindrical portion formed closer to the angular ball bearing than the outer peripheral surface of the taper. in order to provide a centrifugal force, the differential pressure acting, and the air flow toward the counterbore occurring angular ball bearings with a contact angle, generating a flow entering the air into the bearing toward the counter bore from the opposite counter bore Since the grease base oil in the spacer side grease reservoir moves to the bearing space, the grease life can be extended.

  Further, according to the spindle device of the present invention, the bearing device includes a pair of angular ball bearings that are arranged in combination on the back side on both sides in the axial direction of the outer ring spacer and the inner ring spacer, and the spindle is inserted through the bearing device. Since the bearing is rotatably supported with respect to the housing, the lubricating oil can be stably supplied to the pair of angular contact ball bearings combined on the back surface, and the spindle device can be increased in speed and life.

(A) is sectional drawing of 1st Embodiment of the bearing apparatus based on this invention, (b) is an effect | action explanatory drawing of the bearing apparatus shown to (a). It is sectional drawing of 2nd Embodiment of the bearing apparatus which concerns on this invention. It is sectional drawing of 3rd Embodiment of the bearing apparatus which concerns on this invention. It is sectional drawing of 4th Embodiment of the bearing apparatus which concerns on this invention. It is sectional drawing of 5th Embodiment of the bearing apparatus which concerns on this invention. It is principal part sectional drawing of the main axis | shaft apparatus incorporating the bearing apparatus which concerns on this invention. It is sectional drawing of the conventional bearing apparatus.

  Hereinafter, each embodiment of a bearing device and a spindle device according to the present invention will be described in detail with reference to the drawings.

(First embodiment)
First, a first embodiment of a bearing device according to the present invention will be described with reference to FIG.
A bearing device 10 according to this embodiment shown in FIG. 1A includes an angular ball bearing 11, an outer ring spacer 12, and an inner ring spacer 13.

  The angular ball bearing 11 is held by an inner ring 14 having an inner ring raceway surface 14a on an outer peripheral surface, an outer ring 15 having an outer ring raceway surface 15a on an inner peripheral surface, and a cage 17, and has an inner ring raceway surface 14a having a predetermined contact angle α. And a plurality of balls 16 arranged so as to roll freely between the outer raceway surface 15a and the outer ring raceway surface 15a. A counter bore 15b is provided on the inner peripheral surface of one of the outer rings 15 in the axial direction (left side in FIG. 1). In the angular ball bearing 11, grease G is sealed in a bearing space S <b> 1 between the outer peripheral surface of the inner ring 14 and the inner peripheral surface of the outer ring 15.

  The outer ring spacer 12 is disposed in contact with the axial end surface 15c of the outer ring 15 on the counter-bore side. The outer ring spacer 12 has an annular shape in which the inner peripheral surface is cut into a substantially rectangular cross section so that the inner diameter of the contact surface 12 a that contacts the axial end surface 15 c of the outer ring 15 is substantially equal to the inner diameter of the outer ring 15. The outer ring spacer 12 is formed in a substantially L-shaped cross section. Thus, a spacer-side grease reservoir S2 is defined on the inner diameter side of the outer ring spacer 12 on the angular ball bearing 11 side. The spacer side grease reservoir S <b> 2 communicates with the bearing space S <b> 1 of the angular ball bearing 11.

  The inner ring spacer 13 faces the outer ring spacer 12 and is disposed in contact with the axial end surface 14 b of the inner ring 14. The outer peripheral surface of the inner ring spacer 13 is formed of a cylindrical portion 13a parallel to the shaft center and a conical tapered outer peripheral surface 13b that gradually expands at an angle θ toward the angular ball bearing 11. The ridgeline D where the cylindrical portion 13a and the tapered outer peripheral surface 13b intersect is disposed in the vicinity of the inner peripheral edge 12b1 of the notched portion 12b of the outer ring spacer 12.

  In such a bearing device 10, the outer ring 15 and the outer ring spacer 12 of the angular ball bearing 11 are fixedly fitted in the mounting holes 31 of the housing 30, and the inner ring 14 and the inner ring spacer 13 of the angular ball bearing 11 are fixed. The rotary shaft 32 is fitted on the outside. That is, the outer ring 15 is a fixed wheel and the inner ring 14 is a rotating wheel.

  Therefore, when the bearing device 10 is assembled in the housing 30, an appropriate amount of grease G is sealed in the bearing space S1 and the spacer-side grease reservoir S2. As the grease G to be enclosed, a grease G mixed with a gelling agent is suitable. The amount of grease G enclosed in the bearing space S1 is based on the balance between the temperature rise due to viscous resistance accompanying rotation and the grease life. The space volume of the bearing space S1 is preferably 10 to 20%. Thereby, the running-in time can be shortened, and the production line return time after the bearing replacement can be shortened. The grease G mixed with the gelling agent may be enclosed in either the bearing space S1 or the spacer side grease reservoir S2.

  The grease G in which the gelling agent is mixed has a characteristic that it easily becomes oily from a gel state due to a shearing force generated with rotation, and quickly recovers to a gel state when the shearing force is lost. For this reason, when the grease G is supplied to the rolling contact surface of the angular ball bearing 11, it is changed from gel to oil and supplied, so that momentary torque fluctuation due to the engagement of the grease G is prevented, and low Torque operation is possible. Further, the oily formation of the grease G in the vicinity of the rolling surface improves the fluid connection with the grease G slightly away from the rolling surface, and the replenishment of the base oil from the peripheral portion is further promoted. As a result, the lubrication efficiency is improved and the break-in operation time can be shortened. In particular, an effect can be expected in applications having a dmn of 500,000 or more, or a dmn of 1 million or more, such as a machine tool spindle bearing.

  The grease G in which the gelling agent is mixed is preferably gelling agent: thickener = 50-80: 50-20, and a consistency of 265-275. As the gelling agent, a benzylidene sorbitol derivative or an amino acid gelling agent having a high gelling ability is suitable. In addition, when using the general grease which does not contain a gelatinizer, it is desirable to set it as the consistency 220-295.

  The base oil of the grease G is held by a thickener having a fiber structure, and moves between the fibers of the thickener by capillary action. The grease G sealed in the bearing space S1 and the spacer side grease reservoir S2 is brought into contact with each other by the running-in operation, so that a thickener necessary for the movement of the base oil is connected. As a result, the angular ball bearing 11 is lubricated. The amount of grease G to be increased can be greatly increased. In addition, when rotating at high speed as in the spindle device of a machine tool, the temperature of the grease G in the vicinity rises and softens as the temperature around the bearing rises. Extends grease life.

  Further, in the angular ball bearing 11 in which the outer ring 15 has the counterbore 15b, the clearance between the cage 17 and the outer ring 15 is large on the counterbore 15b side and is small on the counter-counterbore side. For this reason, the grease G sealed in the angular ball bearing 11 tends to accumulate on the counterbore 15b side and decreases on the counter-counterbore side. In the case of the outer ring guide retainer that guides the retainer 17 on the surface, the gap between the outer ring 15 and the retainer 17 is small, so that bias tends to occur). However, according to the bearing device 10 of this embodiment, the balance of the base oil supply between the counterbore side and the counter-counterbore side is improved, the unevenness of lubrication is eliminated, and the lubrication efficiency is improved.

  Further, in the bearing device 10 of the present embodiment, as shown in FIG. 1B, when the inner ring spacer 13 rotates together with the inner ring 14, the centrifugal force generated on the tapered outer peripheral surface 13b is larger when the diameter is larger. Further, the speed of the air flow that is accompanied by the tapered outer peripheral surface 13b is also increased on the large diameter side. For this reason, a pressure difference is generated in a direction along the tapered outer peripheral surface 13b, and an air flow F is generated along the tapered outer peripheral surface 13b from the small diameter side to the large diameter side.

  In addition, since the pressure decreases when the gap through which the air flow passes is reduced, the gap between the outer and inner ring spacers 12 and 13 is narrowed toward the angular ball bearing 11, so that a differential pressure is more easily generated. A pressure difference from the larger one toward the smaller gap between the inner ring spacers 12 and 13 occurs (from the high pressure region to the low pressure region), and the air flow along the tapered outer peripheral surface 13b increases. If the angle θ of the tapered outer peripheral surface 13b of the inner ring spacer 13 is too small, the differential pressure effect is reduced, and it is difficult to generate an air flow that causes the lubricating oil to flow into the angular ball bearing 11 side. If the angle exceeds 45 °, the position of the ridge line D where the cylindrical portion 13a and the taper outer peripheral surface 13b intersect increases to the outer diameter side. Therefore, the volume of the spacer-side grease reservoir S2 becomes smaller and less grease G can be held. Become. For this reason, the angle θ should be 5 ° or more and 45 ° or less, more preferably 10 ° or more and 30 ° or less.

  Further, in the angular ball bearing 11 having the counter bore 15b on the outer ring 15, a phenomenon (so-called pump action) of sucking air toward the counter bore 15b occurs.

  As a result of the above action, the air flow generated on the taper outer peripheral surface 13b passes through the spacer-side grease reservoir S2 and the bearing space S1 from the gap between the outer and inner ring spacers 12 and 13, as indicated by an arrow A, and the outer ring 15 rotates. Since it flows into the running surface, the base oil of the grease G in the spacer-side grease reservoir S2 moves to the bearing space S1 and is replenished to the grease G in the bearing space S1.

  As described above, according to the bearing device 10 of the present embodiment, the outer ring spacer 12 has the spacer-side grease reservoir S2 defined to communicate with the bearing space S1 on the inner diameter side. Grease G is sealed in the seat-side grease reservoir S2, and the outer peripheral surface of the inner ring spacer 13 is provided with a conical tapered outer peripheral surface 13b that gradually increases in diameter toward the angular ball bearing 11, so that centrifugal force and differential pressure action are provided. And the air flow toward the counter bore 15b that occurs in the angular ball bearing 11 having a contact angle causes a flow of air that enters the bearing from the counter-bore side toward the counter-bore side, thereby generating a spacer-side grease reservoir S2. Since the base oil of the grease G moves to the bearing space S1, the grease life can be extended.

  In addition, since grease G mixed with a gelling agent is sealed in at least one of the bearing space S1 and the spacer-side grease reservoir S2, the gel-like state easily becomes oily due to the shearing force generated with rotation, Torque fluctuation due to the engagement of the grease G can be prevented, low torque operation can be performed, and the break-in operation time can be shortened.

(Second Embodiment)
Next, a second embodiment of the bearing device according to the present invention will be described with reference to FIG. In the following embodiments, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals in the drawings, and the description thereof is omitted or simplified.

  The outer ring spacer 12 of the present embodiment has a tapered inner peripheral surface 12c inclined in the same direction at the same angle θ as the tapered outer peripheral surface 13b of the inner ring spacer 13, and the inner ring spacer 13 has a predetermined gap C therebetween. It faces the taper outer peripheral surface 13b. Thereby, the labyrinth part 18 with a narrow gap is formed between the tapered outer peripheral surface 13b and the tapered inner peripheral surface 12c.

  When the gap C through which the airflow passes is reduced, the circumferential airflow is likely to be generated in the labyrinth portion 18 by the rotation of the inner ring spacer 13. In addition, since the peripheral speed of the air flow on the large diameter side is faster than the peripheral speed of the air flow on the small diameter side, the pressure difference between the large diameter side and the small diameter side causes the pressure to decrease toward the large diameter side. An air flow is generated, and the differential pressure effect can be further enhanced. Thus, the centrifugal force described in the first embodiment and the pump action of the angular ball bearing 11 and the air flow generated by the differential pressure effect pass from the labyrinth portion 18 through the spacer-side grease reservoir S2 and the bearing space S1. Then, it flows into the rolling surface of the outer ring 15 and replenishes the base oil of grease G. It is effective that the gap C of the labyrinth portion 18 is narrow. However, in consideration of interference between the outer and inner ring spacers 12 and 13 and part machining accuracy, the gap C is at a radial distance perpendicular to the axial direction. 0.15 to 1.0 mm is desirable.

As described above, according to the bearing device 10 of the present embodiment, the inner peripheral surface of the outer ring spacer 12 is disposed to face the tapered outer peripheral surface 13b of the inner ring spacer 13 with a predetermined gap C therebetween. Since it has a conical tapered inner peripheral surface 12c that gradually increases in diameter toward the bearing 11, and the tapered outer peripheral surface 13b and the tapered inner peripheral surface 12c form the labyrinth portion 18, due to the differential pressure effect at the labyrinth portion 18. Thus, it is possible to efficiently generate the air flow and promote the movement of the base oil of the grease G in the spacer side grease reservoir S2 to the bearing space S1.
About another structure and an effect, it is the same as that of the said 1st Embodiment.
In the case of the present embodiment, if the angle θ of the tapered outer peripheral surface 13b of the inner ring spacer 13 exceeds 45 °, the right inner end of the outer ring spacer 12 becomes a sharp edge, which may cause defects such as burrs and chips. Is not preferable.

(Third embodiment)
Next, a third embodiment of the bearing device according to the present invention will be described with reference to FIG.
Similar to the inner ring spacer 13 of the first embodiment, the inner ring spacer 13 of the present embodiment is a cylindrical portion 13a that is parallel to the shaft center and a cone that gradually expands at an angle θ toward the angular ball bearing 11. And a tapered outer peripheral surface 13b. Further, the outer ring spacer 12 has a conical shape that gradually decreases in diameter toward the angular ball bearing 11 at the same angle θ as the tapered outer peripheral surface 13 b on the inner peripheral surface facing the tapered outer peripheral surface 13 b of the inner ring spacer 13. A tapered inner peripheral surface 12d is formed. As a result, an annular space 20 having a substantially V-shaped cross section is formed between the outer and inner ring spacers 12 and 13, and the distance between the two gradually decreases toward the angular ball bearing 11.

In the bearing device 10 of the present embodiment, a space between the outer and inner ring spacers 12 and 13 is provided on the inner peripheral surface of the outer ring spacer 12 by providing a tapered inner peripheral surface 12 d that is reduced in diameter toward the angular ball bearing 11. The volume can be increased, and in addition to the operation described in the first embodiment, more air flows into the angular ball bearing 11 and the grease base oil in the spacer-side grease reservoir S2 moves to the bearing space S1. Can be made.
About another structure and an effect, it is the same as that of the said 1st Embodiment.
Note that the angle θ on the inner ring spacer side and the angle θ on the outer ring spacer side do not have to be the same, and the angle θ is set to 10 to 45 °, preferably θ = 10 to 30 °.

(Fourth embodiment)
Next, a fourth embodiment of the bearing device according to the present invention will be described with reference to FIG. The outer peripheral surface of the inner ring spacer 13 of the present embodiment includes a large diameter cylindrical portion 13a formed on the angular ball bearing 11 side, a small diameter cylindrical portion 13d formed on the opposite side of the angular ball bearing 11, and a large diameter cylindrical portion. 13a and a small-diameter cylindrical portion 13d, and a tapered outer peripheral surface 13b that expands toward the angular ball bearing 11 at an angle θ.

  By providing a small-diameter cylindrical portion 13d having a length L in parallel with the inner peripheral surface of the outer ring spacer 12 on the outer peripheral surface of the inner ring spacer 13 opposite to the angular ball bearing 11, the inner ring spacer 13 has a smaller diameter side ( The volume of the space 20 between the inner ring spacer 13 and the outer ring spacer 12 can be increased while ensuring the wall thickness on the right side in FIG. 4, thereby increasing the amount of air flowing into the angular ball bearing 11. Thus, the base oil of grease G can be supplied efficiently.

(Fifth embodiment)
Next, a fifth embodiment of the bearing device according to the present invention will be described with reference to FIG. The inner ring spacer 13 of the present embodiment has a large diameter cylindrical portion 13a, a small diameter cylindrical portion 13d, and a tapered outer peripheral surface 13b, similarly to the inner ring spacer 13 of the fourth embodiment shown in FIG. Moreover, the inner peripheral surface of the outer ring spacer 12 has a short-length small-diameter cylindrical portion 12e formed on the angular ball bearing 11 side, and a large-diameter cylindrical portion of length L formed on the opposite side of the angular ball bearing 11. 12f, a small-diameter cylindrical portion 12e, and a large-diameter cylindrical portion 12f are connected, and a tapered inner peripheral surface 12g that decreases in diameter toward the angular ball bearing 11 at an angle θ is provided.

The outer and inner ring spacers 12 and 13 are each provided with a tapered inner peripheral surface 12g and a tapered outer peripheral surface 13b that are reduced in diameter toward the angular ball bearing 11, and further, a large-diameter cylindrical portion 12f having a length L, and By providing the small diameter cylindrical portion 13d, the volume of the space 20 between the outer ring spacer 12 and the inner ring spacer 13 is increased, and the amount of air flowing into the angular ball bearing 11 is increased.
Also in this embodiment, the angle θ on the inner ring spacer side and the angle θ on the outer ring spacer side do not have to be the same, and the angle θ is 10 to 45 °, preferably θ = 10 to 30 °. Is set.

(Sixth embodiment)
Next, a spindle device for a machine tool in which the bearing device according to the present invention is incorporated will be described with reference to FIG.

  The spindle device 40 of the present embodiment incorporates the bearing device 10 described in the first embodiment, and the spindle 32 is rotatably supported by a pair of angular ball bearings 11 arranged in a back surface combination. A pair of angular ball bearings 11 arranged in a rear combination is positioned by an inner ring spacer 13 and positioning sleeves 13A and 13B arranged between a pair of inner rings 14, and is fastened and fixed to a main shaft 32 by an inner ring fixing nut 33. Yes. The outer ring 15 of the pair of angular ball bearings 11 is fitted into the housing 30 and positioned by the outer ring spacer 12 disposed between the pair of outer rings 15 and the positioning sleeve 14 </ b> A. It is fixed to the position.

  In addition, the inner ring spacer 13 of the present embodiment is formed by expanding the tapered outer peripheral surface 13b from the valley portion of the axially intermediate portion toward the angular ball bearings 11 on both the left and right sides. Further, the outer ring spacer 12 is provided with annular notches 12b on the inner diameter sides of the left and right side surfaces which respectively contact the outer rings 15 of the pair of angular ball bearings 11, and a radially extending portion extending in the axial direction. A pore 35 is formed. The vent hole 35 is open at a valley portion of the inner ring spacer 13 and communicates with an air supply path 36 formed in the housing 30.

  The base oil of the grease G sealed in the bearing space S1 and the spacer-side grease reservoir S2 is caused together with the airflow by the airflow (see FIG. 1) generated in the direction of the arrow A generated with the rotation of the main shaft 32. Flow into the rolling surface and lubricate. Air sucked into the pair of angular ball bearings 11 through the gap between the outer and inner ring spacers 12 and 13 is constantly supplied from the air supply path 36.

  As described above, according to the spindle device 40 of the present embodiment, the bearing device 10 is a pair of angular ball bearings 11 that are arranged in combination on the back side on both sides in the axial direction of the outer ring spacer 12 and the inner ring spacer 13. And the spindle 32 is rotatably supported with respect to the housing 30 via the bearing device 10. Therefore, the grease is stably supplied to the pair of angular ball bearings 11 combined on the back surface, and the spindle device 40 is increased in speed. Long service life is possible.

  The bearing device 10 incorporated in the main shaft device 40 is not limited to that of the above-described embodiment, and the bearing devices 10 of the second to fifth embodiments can be similarly applied and have the same effects. Further, when the outer ring spacer 12 and the inner ring spacer 13 of the second to fifth embodiments are applied to the main shaft device 40, the shafts separated from the bearings of the spacers 12 and 13 as in the first embodiment. What is necessary is just to form symmetrically centering | focusing on a direction end surface (namely, an outer ring | wheel spacer is formed in T shape). However, in the case of the second embodiment, the inner ring spacer 13 needs to be divided and formed.

In addition, this invention is not limited to each embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.
For example, in the above embodiment, the spacer-side grease reservoir S2 is defined by the notch 12b formed in an L shape by the inner peripheral surface having a uniform inner diameter and the end surface in the axial direction, but the notch 12b. The shape is not limited to this, and any configuration is possible as long as the grease G can be enclosed and the grease G can be moved to the bearing space S1 by an air flow.

DESCRIPTION OF SYMBOLS 10 Bearing apparatus 11 Angular ball bearing 12 Outer ring spacer 12c, 12d, 12g Tapered inner peripheral surface 13 Inner ring spacer 13b Tapered outer peripheral surface 14 Inner ring 14a Inner ring raceway surface 14b Inner ring axial end face 15 Outer ring 15a Outer ring raceway surface 15c Anti-counter bore Side axial end face 16 ball 30 housing 32 rotating shaft (main shaft)
40 Spindle device C Gap G Grease S1 Bearing space S2 Spacer-side grease reservoir α Contact angle

Claims (5)

An inner ring having an inner ring raceway surface on an outer peripheral surface, an outer ring having an outer ring raceway surface on an inner peripheral surface, and a plurality of rolls arranged between the inner ring raceway surface and the outer ring raceway surface with a predetermined contact angle. An angular ball bearing in which grease is sealed in a bearing space between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring,
An outer ring spacer that is disposed in contact with the axial end surface of the outer ring on the counter-bore side;
An inner ring spacer facing the outer ring spacer and disposed in contact with an axial end surface of the inner ring;
A bearing device comprising:
The outer ring spacer has a spacer-side grease reservoir defined by cutting out an inner peripheral surface so as to communicate with the bearing space on the inner diameter side, and grease is enclosed in the spacer-side grease reservoir,
The outer peripheral surface of the inner ring spacer includes a conical tapered outer peripheral surface that gradually increases in diameter toward the angular ball bearing, and a cylindrical portion that is formed closer to the angular ball bearing than the tapered outer peripheral surface. A bearing device.   The inner peripheral surface of the outer ring spacer has a conical tapered inner peripheral surface that is disposed to face the tapered outer peripheral surface of the inner ring spacer via a predetermined gap and gradually increases in diameter toward the angular ball bearing. The bearing device according to claim 1.   The bearing device according to claim 1, wherein grease mixed with a gelling agent is sealed in at least one of the bearing space and the spacer side grease reservoir.   A pair of angular balls, comprising the bearing device according to any one of claims 1 to 3, wherein the bearing device is arranged in a back-side combination on both sides in the axial direction of the outer ring spacer and the inner ring spacer. A main shaft device comprising a bearing and rotatably supporting the main shaft with respect to a housing via the bearing device.   5. The outer ring spacer is formed with a vent hole for supplying air to the spacer-side grease reservoir via an air supply passage formed in the housing. Spindle device.

Images