JP2014046408A - Spindle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a spindle device which uses shaft bearings capable of high speed rotation with a dmn value of 1,000,000 or greater, and prevents flinger deformation due to centrifugal force, while maintaining a satisfactory waterproofing function.SOLUTION: A spindle device 10 includes: a flinger 40 which is fixed to a periphery of a rotating shaft 11 so as to be integrally rotatable with the periphery, and has a waterproofing function to restrain intrusion of fluid into front side bearings 50 and 50. A housing is formed so as to join its shaft-direction end surface 12b to an outer peripheral surface 13c through convex spherical surfaces 12c and 13d. The flinger 40 includes: a cylindrical boss part 42; and an extension part 45 which extends from the boss part 42 to an outward radial direction side. The extension part 45 has a concave spherical surface 45a on a surface facing the convex spherical surfaces 12c and 13d of the housing H. Further, the flinger 40 has a specific gravity which is small relative to the rotating shaft 11, and is made from a material with a high specific strength.

Description

  The present invention relates to a spindle device, and more particularly to a spindle device having a waterproof function and suitable for application to a machine tool.

  A rotating shaft of a spindle device applied to a machine tool or the like rotates at a high speed to perform cutting or grinding of a workpiece. In machining, a large amount of machining liquid is generally supplied to the machining unit for the purpose of lubrication and cooling of machining tools such as cutting tools and grindstones and machining sites. That is, lubrication can improve the machining characteristics, suppress wear on the cutting edge, extend the tool life, and the like. In addition, the thermal expansion of the processing tool and the workpiece is suppressed by cooling, so that the processing accuracy is improved, the thermal welding of the processing portion is prevented, the processing efficiency is improved, and the surface property of the processing surface is improved. Since the distance between the spindle device and the machining unit is close, a large amount of machining liquid is also applied to the front surface of the spindle device. This large amount of machining fluid is likely to enter the bearing that supports the rotating shaft, and if the machining fluid enters the bearing, it may cause poor lubrication or seizure of the bearing. Become. In particular, in bearings that are lubricated with grease or lubricated with grease, the inside of the bearing is at a lower pressure than oil / air lubricated or oil mist lubricated bearings that are supplied with lubricating oil along with air. It is easy to intrude into and requires higher waterproof performance.

  As a general waterproof mechanism, a contact seal such as an oil seal or a V ring is known. However, when this contact type seal is applied to a spindle device used at a high speed rotation with a dmn value of a bearing to be used of 400,000 or more (more preferably, 500,000 or more), the contact type seal from the contact portion of the contact type seal is used. There is a problem that heat generation is large, the seal member is worn, and it is difficult to maintain waterproof performance for a long period of time. For this reason, in a machine tool, a so-called labyrinth is a non-contact seal in which a flinger is fixed to a front end portion (tool side) of a spindle device so as to be able to rotate integrally with a rotary shaft, and a gap between the flinger and a housing is reduced. The seal is made to be waterproof. The flinger that rotates at a high speed has a labyrinth effect and prevents the machining fluid from entering the bearing by shaking the machining fluid that has fallen on the flinger outward in the radial direction by centrifugal force.

  The waterproofing effect using the flinger's centrifugal force and labyrinth effect increases the centrifugal force by increasing the rotation speed and using a large-diameter flinger, and the gap between the flinger and the housing is as small and long as possible. It is effective. However, when rotating at a high speed or increasing the diameter of the flinger, the centrifugal force and the hoop stress acting on the flinger also increase in proportion thereto.

  In the sealing device in the spindle device for machine tools described in Patent Document 1, a shielding plate that rotates integrally with the tip portion of the spindle is disposed so as to face the tip surface of the housing with a gap therebetween, thereby shielding the shielding device. A labyrinth portion is provided between the plate and the front end surface of the housing. With this configuration, the coolant that has bounced off the workpiece or the like is prevented from entering the inside of the housing.

  The spindle device for machine tools described in Patent Document 2 includes a labyrinth seal formed by a spindle cap and an end surface cover, and the labyrinth seal is configured to include a labyrinth chamber. By setting a large value, when the coolant liquid enters the labyrinth chamber through the gap between the spindle cap and the end surface cover, the pressure of the coolant fluid in the labyrinth chamber is reduced to attenuate the flow of the coolant liquid. Further, the coolant liquid is prevented from entering the bearing portion of the main shaft without supplying a large amount of compressed air from the gap between the main shaft and the main shaft housing of the main shaft head toward the tip end side of the main shaft.

  FIG. 10 shows a conventional motor built-in spindle device in which the rotating shaft 101 is rotatably supported with respect to the housing H by front and rear bearings 102 and 103 disposed on the front side and the rear side with respect to the motor M. 100 is shown. In the spindle apparatus 100, the cover 104 is disposed on the front side of the housing H, and a clearance between the front lid 105 and the nut 106 disposed in the inside thereof is a labyrinth structure, so that liquid from the outside can be removed from the front bearing 102. Prevents entry into the interior.

JP 2002-263882 A JP 2010-76045 A

  By the way, in the conventional spindle device 100 shown in FIG. 10, when a large amount of liquid sprays on the front surface of the spindle device 100, it passes through the labyrinth gap between the front lid 105 and the nut 106 and enters the front bearing 102. The bearing 102 may be damaged.

  In general, the flinger is made of a metal material having a relatively large specific gravity, such as an SC material, an SCM material, a SUS material, or a CU material. Therefore, if the diameter of the flinger is increased in order to apply a large centrifugal force to the working fluid falling on the flinger, a large centrifugal force acts on the flinger itself, particularly on the outer diameter side. At high speed rotation where the dmn value of the bearing used is 1 million or more, such as a rotating shaft of a machine tool, the flinger is deformed by centrifugal force, and in some cases, the original waterproof function of the flinger may be lowered. For this reason, it is necessary to limit the diameter of a flinger and the rotational speed of a rotating shaft to such an extent that the influence of centrifugal force is allowed. That is, in the conventional spindle device used in an environment where the dmn value of the bearing to be used is 1 million or more, the size of the flinger is limited in consideration of the magnitude of the centrifugal force. There was room for improvement.

  The present invention has been made in view of the above-described problems. The object of the present invention is to provide a flinger by centrifugal force while maintaining a good waterproof function and capable of rotating at a high speed with a dmn value of a bearing used of 1 million or more. It is an object of the present invention to provide a spindle device that can prevent deformation of the spindle.

The above object of the present invention can be achieved by the following constitution.
(1) a rotating shaft to which a processing tool is attached on one end side;
A housing that rotatably supports the rotating shaft via a bearing;
A flinger that is fixed around the rotary shaft so as to be integrally rotatable, and has a waterproof function to prevent liquid from entering the bearing;
A spindle device comprising:
The housing is formed so as to connect the end surface in the axial direction and the outer peripheral surface by a convex curved surface,
The flinger includes a cylindrical base portion, and an extending portion extending radially outward from the base portion,
The spindle device according to claim 1, wherein the extending portion has a concave curved surface on a surface facing the convex curved surface of the housing.
(2) The spindle apparatus according to (1), wherein the flinger has a concave spherical surface on a surface facing the housing.
(3) The spindle device according to (1) or (2), wherein a flange that extends radially outward is formed at a free end of the flinger.
(4) The spindle device according to any one of (1) to (3), wherein at least one rib is provided on the facing surface of the flinger.
(5) The spindle device according to (4), wherein a plurality of the ribs extending in the radial direction are provided at equal intervals in the circumferential direction on the facing surface of the flinger.
(6) The spindle device according to any one of (1) to (5), wherein the flinger is made of a material having a small specific gravity and a high specific strength with respect to the rotating shaft.
(7) The spindle apparatus according to (6), wherein the flinger is composed of a fiber-reinforced composite material made of either a carbon fiber composite material or an aramid fiber composite material.
(8) The spindle device according to (6), wherein the flinger is made of a light metal material made of aluminum, duralumin, or titanium.

  According to the spindle apparatus of the present invention, the housing is formed so that the axial end surface and the outer peripheral surface are connected by the convex curved surface, and the flinger extends from the base to the radially outer side. An extended portion, and the extended portion has a concave curved surface on the surface facing the convex curved surface of the housing, so that stress concentration due to centrifugal force during high-speed rotation is suppressed, and high-speed rotation is possible. The effect of shaking off the liquid can be increased and the waterproof property can be improved. Accordingly, the spindle device can prevent the flinger from being deformed due to centrifugal force while maintaining a good waterproof function and capable of rotating at a high speed with a dmn value of the bearing used of 1 million or more.

It is sectional drawing of the spindle apparatus which concerns on 1st Embodiment of this invention. It is a principal part expanded sectional view of the spindle apparatus of FIG. It is sectional drawing corresponding to FIG. 2 which shows the spindle apparatus which concerns on the modification of 1st Embodiment. It is sectional drawing for demonstrating the swing-off effect | action of the flinger of FIG. It is a principal part expanded sectional view of the spindle apparatus which concerns on 2nd Embodiment of this invention. It is a rear view of the flinger of FIG. It is a rear view corresponding to FIG. 8 which shows the flinger which concerns on the 1st modification of 2nd Embodiment. (A)-(c) is sectional drawing of the applicable rib along the VIII-VIII line of FIG. It is sectional drawing corresponding to FIG. 7 which shows the spindle apparatus which concerns on the 2nd modification of 2nd Embodiment. It is sectional drawing which shows the conventional spindle apparatus.

Hereinafter, a spindle device according to an embodiment of the present invention will be described in detail with reference to the drawings.
As shown in FIG. 1, the spindle device 10 is a motor built-in spindle device for a machine tool, and the rotating shaft 11 supports two rows of front bearings 50 and 50 that support the tool side (front side, front in the axial direction). The housing H is rotatably supported via two rows of rear bearings 60 and 60 that support the opposite tool side (rear side, rearward in the axial direction). The housing H includes a front bearing outer ring retainer 12, an outer cylinder 13, a rear housing 14, and a rear lid 5 in order from the tool side. The outer cylinder 13 is fixed to a bracket (not shown) of the spindle head by inserting a bolt through a bolt hole 13b of a flange 13a provided in the front in the axial direction.

On the tool side of the rotary shaft 11, a tool mounting hole 24 and a female screw 25 formed in the axial direction through the center of the shaft are provided. The tool attachment hole 24 and the female screw 25 are used for attaching a processing tool (not shown) to the rotary shaft 11. For example, a grinding wheel quill (not shown) is attached to the tool attachment hole 24 and the female screw 25, thereby enabling grinding.
The configuration of the rotary shaft 11 is not limited as long as a machining tool can be attached to one end side, and a draw bar is slidably inserted into the shaft core of the rotary shaft 11 instead of the tool mounting hole 24 and the female screw 25. You may do it. The draw bar includes a collet portion (not shown) that fixes the tool holder, and biases the collet portion in the counter tool side direction by the force of the disc spring.

  A rotor 26 disposed so as to be able to rotate integrally with the rotation shaft 11 and a stator 27 disposed around the rotor 26 are disposed substantially at the center in the axial direction between the front bearings 50, 50 and the rear bearings 60, 60 of the rotation shaft 11. With. The stator 27 is fixed to the outer cylinder 13 by fitting the cooling jacket 28 shrink-fitted into the stator 27 into the outer cylinder 13 constituting the housing H. The rotor 26 and the stator 27 constitute a motor M, and by supplying electric power to the stator 27, a rotational force is generated in the rotor 26 to rotate the rotating shaft 11.

  Each front bearing 50 is an angular ball bearing having an outer ring 51, an inner ring 52, a ball 53 as a rolling element arranged with a contact angle, and a cage (not shown). Is an angular ball bearing having an outer ring 61, an inner ring 62, balls 63 as rolling elements, and a cage (not shown). The front bearings 50 and 50 (parallel combination) and the rear bearings 60 and 60 (parallel combination) are arranged to cooperate with each other to form a back combination.

  The outer rings 51, 51 of the front bearings 50, 50 are fitted in the outer cylinder 13, and are axially directed to the outer cylinder 13 via the outer ring spacer 54 by the front bearing outer ring retainer 12 bolted to the outer cylinder 13. It is fixed to the position. Inner rings 52, 52 of the front bearings 50, 50 are externally fitted to the rotary shaft 11, and are attached to the rotary shaft 11 by an nut 16 fastened to the rotary shaft 11 via an inner ring spacer 55 and a flinger 40 described later. It is positioned and fixed in the axial direction.

  The outer rings 61 and 61 of the rear bearings 60 and 60 are fitted into a sleeve 18 that is slidably fitted in the rear housing 14 so as to be slidable in the axial direction, and are integrally fixed to the sleeve 18 with bolts 66. The rear bearing outer ring presser 19 is positioned and fixed in the axial direction with respect to the sleeve 18 via the outer ring spacer 64.

  Inner rings 62 and 62 of the rear bearings 60 and 60 are externally fitted to the rotary shaft 11, and are axially directed to the rotary shaft 11 via the inner ring spacer 65 by another nut 21 fastened to the rotary shaft 11. It is fixed to the position. A coil spring 23 is disposed between the rear housing 14 and the rear bearing outer ring retainer 19, and the spring force of the coil spring 23 presses the rear bearing outer ring retainer 19 together with the sleeve 18 backward. Thereby, a preload is applied to the rear bearings 60 and 60.

  Here, in the grinding process as in this embodiment, generally, a large amount of grinding liquid is supplied to the processing part, and the processing part is cooled and the processing powder is removed. The flinger 40 is fixed so as to be integrally rotatable around the rotary shaft 11 on the tool side (left side in the drawing) of the front bearings 50 and 50 so that the machining fluid does not enter the front bearings 50 and 50. A labyrinth seal is formed between the outer ring retainer 12 and the outer cylinder 13 to provide a waterproof function to suppress the penetration of the liquid into the front bearings 50 and 50 by shaking off the grinding fluid from the outside along with the rotation of the rotating shaft 11.

  Referring also to FIG. 2, the flinger 40 has a cylindrical boss portion 42 as a base portion, and an extending portion 45 extending radially outward from the axial front end portion of the boss portion 42. The flinger 40 is fixed to the rotary shaft 11 so as to be integrally rotatable by fitting the boss portion 42 to the rotary shaft 11 and tightening the nuts 16 together with the inner rings 52 and 52 in the axial direction.

  Convex spherical surfaces 12 c and 13 d are formed on the front bearing outer ring retainer 12 and the outer cylinder 13 so as to connect between the axial front end surface 12 b of the front bearing outer ring retainer 12 and the outer peripheral surface 13 c of the outer cylinder 13. Yes.

  On the other hand, the inner surface of the extending portion 45 of the flinger 40 has a concave spherical surface 45a on the opposing surface of the front bearing outer ring retainer 12 and the convex spherical surfaces 12c and 13d of the outer cylinder 13, and the front bearing outer ring retainer 12 has an inner surface. A flat surface 45b is provided on the surface facing the axial front end surface 12b, and a cylindrical surface 45c is provided on the facing surface 13c with the outer peripheral surface 13c of the outer cylinder 13. Further, the outer surface of the extending portion 45 has a convex spherical surface 45g having a curvature center substantially equal to the concave spherical surface 45a formed on the inner surface between the front end surface 45d and the outer peripheral surface 45e. By configuring the flinger 40 in this manner, the thickness of the extended portion 45 becomes substantially uniform, so that stress concentration can be further suppressed.

  Further, the boss portion 42 is disposed to face the inner peripheral surface 12a of the front bearing outer ring retainer 12 in the radial direction with a slight gap, and the extending portion 45 extends from the axial front end surface 12b of the front bearing outer ring retainer 12. The front bearing outer ring holder 12 and the convex spherical surfaces 12c and 13d of the outer cylinder 13 are arranged to face each other through a slight gap to the outer peripheral surface 13c of the outer cylinder 13. As described above, the flinger 40 is disposed so as to face the front bearing outer ring presser 12 and the outer cylinder 13 constituting the housing H through a slight gap, for example, a gap of about 0.5 mm, and constitutes a so-called labyrinth seal.

  In particular, an air curtain is formed between the cylindrical surface 45c of the extending portion 45 and the outer peripheral surface 13c of the outer cylinder 13 due to the difference in peripheral speed, and the processing liquid that falls on the spindle device 10 when processing the workpiece. Constitutes a waterproof mechanism for suppressing the front bearing 50, 50 from entering.

  Further, the flinger 40 configured as described above is made of a material having a low specific gravity and a high specific strength (tensile strength / specific gravity) with respect to the material used for the rotating shaft 11. It is comprised by the fiber reinforced composite material which consists of either a fiber composite material (CFRP) and an aramid fiber composite material (AFRP), or the light metal material which consists of either aluminum, duralumin, or titanium.

  For example, as a carbon fiber composite material, for example, a woven fabric (sheet-like) formed of carbon fibers made of PAN (polyacrylonitrile) as a main raw material or a fiber made of carbon fibers. It is manufactured by laminating a plurality of sheets impregnated with a thermosetting resin such as an epoxy resin containing a curing agent, wrapping the sheet around a cored bar and the like, followed by heat curing. Moreover, the carbon fiber which used pitch system as the main raw material can also be used. By optimizing the fiber direction and angle, the carbon fiber composite material can optimize physical properties such as tensile strength, tensile elastic modulus, and linear expansion coefficient according to the application.

As the characteristics of the carbon fiber composite material, for example, carbon fiber mainly composed of PAN having a tensile strength of 1800 to 3500 MPa, a tensile elastic modulus of 130 to 280 GPa, and a specific gravity of 1.5 to 2.0 g / cc is used. When used, the tensile strength is equal to or higher than that of conventional high-strength steel and the like, and the specific gravity is about 1/5 (the specific strength is about three times that of a normal metal material). Moreover, since the thermal expansion coefficient can be made −5 to + 12 × 10 ⁻⁶ K ⁻¹ by optimizing the fiber direction and angle, it is about 1 to 1/10 compared with the conventional carbon steel. can do.

  As described above, by using a carbon fiber composite material having a higher specific strength than a general metal, the centrifugal force acting on the flinger 40 can be significantly reduced if the diameter is the same, and the housing Since the surface facing H is formed by the concave spherical surface 45a having no curved surface, stress concentration due to centrifugal force is alleviated. Therefore, the restriction on the rotational speed of the rotating shaft 11 and the restriction on the size (radial direction) of the flinger 40 can be greatly relaxed.

  This makes it possible to increase the rotation speed of the flinger 40, which has been difficult to achieve in the past, or to increase the size of the flinger 40. It can be swung away to prevent intrusion into the bearing. Further, since the centrifugal force acting on the extending portion 45 of the flinger 40 is reduced, the opening side (the right side in the drawing) of the extending portion 45 having a cantilever structure with relatively low strength is expanded radially outward. Can be suppressed. Thereby, the radial direction length and axial direction length of the extension part 45 are set long, and the length of a labyrinth seal becomes long and the waterproofing effect improves.

  A circumferential groove 13e is formed on the outer peripheral surface 13c of the outer cylinder 13 at a position facing the free end 45z of the flinger 40 over the entire circumference. Therefore, even if the machining fluid enters the labyrinth gap, the machining fluid accumulates in the circumferential groove 13e, so that the penetration of the machining fluid into the front bearing 50 can be suppressed. The free end 45z of the flinger 40 is provided so as to cover the circumferential groove 13e, and is preferably located on the side opposite to the tool (on the right side in the drawing) from the circumferential groove 13e.

  Further, the front bearing outer ring retainer 12 has an annular groove 85 recessed in the inner circumferential surface 12a radially facing the boss portion 42 of the flinger 40 so as to extend outward in the radial direction, A first extending hole 89 extending radially outward from the annular groove 85. Further, the outer cylinder 13 is connected to the radially outer end portion of the first extending hole 89 and extends in the axially rearward direction, and the axially rearward end portion of the second extending hole 90. And a third extending hole 91 that extends radially outward and communicates with the outer peripheral surface of the flange 13a. The first, second, and third extending holes 89, 90, and 91 constitute a drain hole 88 as a communication hole that communicates the annular groove 85 and the outer peripheral surface of the flange portion 13a. Therefore, even when the grinding fluid enters between the boss portion 42 of the flinger 40 and the inner peripheral surface 83 of the front bearing outer ring retainer 12, the grinding fluid is accumulated in the annular groove 85 and is passed through the drain hole 88. Therefore, it is possible to further suppress the penetration of the grinding fluid into the front bearing 50.

  In addition, in order to demonstrate waterproof performance more, the spindle apparatus 10 of this embodiment is a horizontal direction (a state where the axial direction is perpendicular to the gravitational direction) and the opening of the drain hole 88 provided in the flange portion 13a. It is desirable to use so that 88a is directed in the direction of gravity. By using the spindle device 10 sideways, it becomes difficult for the grinding fluid to enter the labyrinth gap, and the effect of discharging the grinding fluid from the labyrinth can be enhanced by directing the opening 88a of the drain hole 88 in the direction of gravity. it can.

As described above, according to the spindle device 10 of the present embodiment, the flinger 40 is
A concave spherical surface 45 a is provided on the surface facing the housing H. Thereby, the stress concentration of the flinger 40 due to the centrifugal force at the time of high-speed rotation is suppressed, high-speed rotation is possible, the effect of swinging off the liquid is increased, and waterproofness can be improved. Therefore, the spindle device 10 is capable of high-speed rotation with a dmn value of the bearings 50 and 60 used for the main shaft (particularly, the dmn value of the front bearing 50 in which the flinger 40 is disposed in front) being 1 million or more, and good. While maintaining the waterproof function, deformation of the flinger 40 due to centrifugal force can be prevented.

  The housing H is formed so that the axial end surface 12b of the front bearing outer ring retainer 12 and the outer peripheral surface 13c of the outer cylinder 13 are connected by convex spherical surfaces 12c and 13d, and the flinger 40 has a cylindrical boss portion 42. And an extending portion 45 extending radially outward from the boss portion 42, and the extending portion 45 has a concave spherical surface 45 a on a surface facing the convex spherical surfaces 12 c and 13 d of the housing H. Thereby, the labyrinth seal of a uniform clearance gap can be comprised between the flinger 40 and the housing H, and a waterproofing effect can be improved.

  Further, the flinger 40 is made of a material having a small specific gravity and a high specific strength with respect to the rotating shaft 11 such as a fiber reinforced composite material or a light metal material, so that stress concentration due to centrifugal force during high speed rotation can be suppressed. Compared to the case where the rotating shaft 11 is made of the same member such as iron, the outer diameter of the flinger can be increased, the front surface of the spindle device 10 can be covered, and a liquid such as grinding fluid is blown to the outer diameter side by centrifugal force. Waterproofness can be improved.

  3 and 4 show a spindle device according to a modification of the first embodiment. In this modification, the flanger 40 has a flange portion 45 h that extends radially outward from the outer peripheral surface 45 e at the free end 45 z of the extending portion 45.

  As a result, as shown in FIG. 4, the liquid adhering to the outer surface of the flinger 40 moves to the outer diameter side on the surface of the flinger 40 by the action of centrifugal force and surface tension (corresponding to surface adhering force). It diffuses radially outward from the flange 45h located at the outermost peripheral surface portion. The splashed liquid becomes a kind of curtain shielding film, and the film prevents the oil splashed directly from the processing site from entering the opening of the labyrinth.

  Further, the amount of deformation in the radial direction due to the centrifugal force of the flinger 40 is the largest at the free end 45z of the extending portion 45, and the stress is also maximized. Therefore, as in this modification, by appropriately increasing the thickness of the free end 45z by the flange 45h, the stress of the free end 45z can be relieved and the strength of the flinger 40 can be enhanced. it can.

(Second Embodiment)
Next, a spindle device according to a second embodiment of the present invention will be described with reference to FIGS. In this embodiment, as in the first embodiment, the flinger 40 has a substantially uniform wall extending portion 45 by a convex spherical surface 45g formed on the outer surface and a concave spherical surface 45a formed on the inner surface. On the other hand, on the surface facing the housing H, a plurality of ribs 46 are provided at equal intervals in the circumferential direction. Further, the front outer ring retainer 12 and the outer cylinder 13 form convex spherical surfaces 12c and 13d. Each rib 46 extends outward in the radial direction from the outer peripheral surface of the boss portion 42 and is formed so as to gradually become thinner toward the outer side in the radial direction. A concave surface is formed on the surface facing the housing H. It has a spherical surface 46a. Therefore, in the present embodiment, the gap between the inner surface of the flinger 40 and the outer surface of the housing H is formed wide by the plate thickness of the rib 46, but the cylindrical surface 45 c of the flinger 40 and the outer cylinder 13 are formed. The rib 46 is not formed between the outer peripheral surface 13c and the outer peripheral surface 13c.

  The material of the rib 46 is also made of a material having a small specific gravity with respect to the rotating shaft 11 and a high specific strength. For this reason, the flinger 40 and the rib 46 may be formed separately or integrally.

  Therefore, according to this embodiment, since the plurality of ribs 46 are provided at equal intervals in the circumferential direction on the surface of the flinger 40 facing the housing H, the strength of the flinger 40 can be further improved.

  The number of the ribs 46 is preferably arranged at equal intervals in the circumferential direction so as not to cause imbalance, and at least two or more, more preferably four as shown in FIG. It is preferable that there are at least four places such as six places as in the first modification shown in FIG. Moreover, in order to suppress the air resistance by rotation of the flinger 40, the cross-sectional shape of the rib 46 is good also as any shape of a rectangular shape, a trapezoid shape, and a curved surface shape, as shown to Fig.8 (a)-(c). .

  FIG. 9 shows a spindle device according to a second modification of the second embodiment. In this embodiment, the rib 46 extending along the radial direction is formed from the concave spherical surface 45a portion of the extending portion 45 to the cylindrical surface 45c. Therefore, in the case of this embodiment, a gap is formed wide by the plate thickness of the rib 46 between the cylindrical surface 45c of the flinger 40 and the outer peripheral surface 13c of the outer cylinder 13, while the flat surface 45b of the flinger 40 is formed. And the front end face 12b in the axial direction of the front bearing outer ring retainer 12 are not provided with ribs 46, and a gap is formed narrowly. Each rib 46 has a concave spherical surface 46 a on the surface facing the housing H.

  Therefore, also in this modified example, the strength of the flinger 40 can be further improved by providing the plurality of ribs 46, and each rib 46 has a cylindrical surface 45 c from the concave spherical surface 45 a portion of the extending portion 45. Since it is partially formed on the surface facing the housing H, the axial dimension of the spindle device 10 can be suppressed.

  In this modified example as well, as in the second modified example of the first embodiment, the flinger 40 has a flange 45h that extends radially outward from the outer peripheral surface 45e to the free end 45z of the extending portion 45. Is formed.

  In the present embodiment, the plurality of ribs 46 are formed to extend in the radial direction. However, the present invention is not limited to this, and at least one rib may be provided on the surface of the flinger 40 facing the housing H. . For example, it suffices that at least one rib extending in the circumferential direction is provided, a single rib may be formed over the entire circumference in the circumferential direction, or a plurality of ribs extending in the circumferential direction may be provided in the circumferential direction. May be provided at equal intervals.

  In addition, this invention is not limited to each embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the present invention can be applied in appropriate combinations within a practicable range.

  In the present embodiment, the flinger 40 has a concave spherical surface 45a on the surface facing the housing H. However, the present invention is not limited to this, for example, a housing such as a concave curved surface having an elliptical cross section. It may have a concave curved surface on the surface facing H. The housing may also be formed so that the axial end surface and the outer peripheral surface are connected by a convex curved surface corresponding to the concave curved surface of the flinger 40.

  In the present embodiment, the entire flinger is made of a material having a small specific gravity with respect to the rotating shaft and a high specific strength, such as a fiber reinforced composite material or a light metal material. May be used. However, it is preferable that the extended portion on which the centrifugal force acts is made of the material.

  Further, although the motor built-in type spindle device has been described, the present invention is not limited to this, and the present invention can be similarly applied to a belt drive type spindle device and a motor direct connection drive type spindle device coupled to a rotation shaft of a motor. Further, the present invention is not limited to a spindle device for machine tools, and can be applied to a spindle device of other high-speed rotating equipment that requires a waterproof function.

DESCRIPTION OF SYMBOLS 10 Spindle apparatus 11 Rotating shaft 12 Front side bearing outer ring holder 12c Convex spherical surface 13 Outer cylinder 13d Convex spherical surface 40 Flinger 42 Boss part (base part)
45 Extension part 45a Concave spherical surface (concave curved surface)
46 Rib 50 Front bearing (bearing)
60 Rear bearing (bearing)
H housing

Claims (8)

A rotating shaft to which a processing tool is attached on one end side;
A housing that rotatably supports the rotating shaft via a bearing;
A flinger that is fixed around the rotary shaft so as to be integrally rotatable, and has a waterproof function to prevent liquid from entering the bearing;
A spindle device comprising:
The housing is formed so as to connect the end surface in the axial direction and the outer peripheral surface by a convex curved surface,
The flinger includes a cylindrical base portion, and an extending portion extending radially outward from the base portion,
The spindle device according to claim 1, wherein the extending portion has a concave curved surface on a surface facing the convex curved surface of the housing.   The spindle apparatus according to claim 1, wherein the flinger has a concave spherical surface on a surface facing the housing.   The spindle device according to claim 1, wherein a flange portion extending radially outward is formed at a free end portion of the flinger.   4. The spindle device according to claim 1, wherein at least one rib is provided on the opposing surface of the flinger. 5.   5. The spindle device according to claim 4, wherein a plurality of the ribs extending along a radial direction are provided at equal intervals in the circumferential direction on the facing surface of the flinger.   The spindle apparatus according to claim 1, wherein the flinger is made of a material having a small specific gravity and a high specific strength with respect to the rotating shaft.   The spindle apparatus according to claim 6, wherein the flinger is made of a fiber-reinforced composite material made of either a carbon fiber composite material or an aramid fiber composite material.   The spindle apparatus according to claim 6, wherein the flinger is made of a light metal material made of aluminum, duralumin, or titanium.

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