Spindle device

Abstract

An object of the present invention is to provide a spindle device for stabilizing a retainer with a minimum quantity of air to be supplied to the bearing. A spindle device includes: supplying unit which supplies air from three or more points spaced in a circumferential direction between outer races and inner races of bearings supporting a spindle; and control unit which controls a supply quantity of air supplied by the supplying unit in such a manner as to independently vary the supply quantity at each of the supplying points.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a vertically cross-sectional view showing a spindle device according to the present invention;

FIG. 2 is a laterally cross-sectional view showing the spindle device;

FIG. 3 is a cross-sectional view showing a part of FIG. 1 in enlargement;

FIG. 4 is a cross-sectional view showing a modification of a part shown in FIG. 3, being equivalent to FIG. 3;

FIG. 5 is a table illustrating an air supplying quantity; and

FIG. 6 is a diagram explanatory of inclination angles of a spindle.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

A detailed description will be given below of a preferred embodiment according to the present invention in reference to the attached drawings.

In the description below, a left side in reference to FIG. 1 is referred to as the left, and further, a side opposite to the left side is referred to as a right. In addition, the left is a front side while the right is a rear side.

A spindle device is provided with a hollow spindle 11 having an axis in a horizontal direction, a horizontally cylindrical sleeve 12 fitted around the spindle 11, a first bearing 21 and a second bearing 22 which support the spindle 11 on the left side thereof with an axial interval, a third bearing 23 which supports the spindle 11 on the right side thereof, a left housing 24 which surrounds the first bearing 21 and the second bearing 22 and is fixed to an inner surface of the sleeve 12, and a right housing 25 which surrounds the third bearing 23 and is fixed to the inner surface of the sleeve 12.

At an outer surface of the spindle 11 are formed a large-diameter portion 31, a middle-diameter portion 32 and a small-diameter portion 33 in sequence via steps from left to right.

A stator 35 for a motor 34 is secured to the inner surface of the sleeve 12 between the second bearing 22 and the third bearing 23. Furthermore, a rotor 36 for the motor 34 is secured to the outer surface of the spindle 11 in such a manner as to correspond to the stator 35.

At a left end of an inner surface of the left housing 24 is disposed a left inward annular projection 37. In the meantime, at a right end of an inner surface of the right housing 25 is disposed a right inward annular projection 38.

The first to third bearings 21 to 23 have the same structure. FIG. 3 particularly shows the second bearing 22. The second bearing 22 includes an outer race 41 secured to the inner surface of the left housing 24, an inner race 42 secured to the outer surface of the spindle 11, a plurality of rolling elements 43 interposed between the outer race 41 and the inner race 42, and a retainer 44 which is rotated together with the rolling elements 43 under a guidance of an inner surface of the outer race 41 so as to retain the rolling elements 43 at predetermined intervals.

Referring to FIG. 1 again, an outer race inter-seat 45 secured to the inner surface of the left housing 24 is interposed between the outer races 41 of the first bearing 21 and the second bearing 22. In the meantime, an inner race inter-seat 46 secured to the outer surface of the spindle 11 is interposed between the inner races 42 of both of the bearings 21 and 22.

A left opening of the sleeve 12 is capped with a left presser cap 51. The left presser cap 51 presses the outer races 41 of the first bearing 21 and the second bearing 22 toward the left inward annular projection 37 together with the outer race inter-seat 45. A left pressing nut 52 is screwed on a right side of the second bearing 22. The left pressing nut 52 presses the inner races 42 of the first bearing 21 and the second bearing 22 against the step of the large-diameter portion 31 and the middle-diameter portion 32 together with the inner race inter-seat 46. A right opening of the sleeve 12 is capped with a right presser cap 53. The right presser cap 53 presses the outer race 41 of the third bearing 23 toward the right inward annular projection 38. A right pressing nut 54 is screwed on a right side of the third bearing 23. The right pressing nut 54 presses the inner race 42 of the third bearing 23 against the step of the middle-diameter portion 32 and the small-diameter portion 33.

Referring to FIG. 3 again, an inward opening annular groove 61 is formed at the right side surface of the outer race inter-seat 45 in such a manner as to face a clearance defined between the outer race 41 and the inner race 42 in the second bearing 22. At a portion just a left side of the second bearing 22, an outer air supplying hole 62 are formed at the sleeve 12 and an inner air supplying hole 63 are formed at the left housing 24, respectively, in such a manner that an inner air supplying hole 64 is formed at the outer race inter-seat 45 continuously in alignment inward and outward. The annular groove 61 and a bottom of the inner air supplying hole 64 are connected to each other via a communication hole 65. These outer air supplying holes 62, inner air supplying holes 63, inner air supplying holes 64 and communication holes 65 are formed in the same manner on a right side of the first bearing 21 and on a left side of the third bearing 23, respectively. The outer air supplying hole 62, inner air supplying hole 63, inner air supplying hole 64 and communication hole 65 corresponding to each of the bearings 21 to 23 are formed at four points I to IV quartered on the sleeve 12, the housing and the outer race inter-seat 45, as shown in FIG. 2.

FIG. 4 shows a modification of the annular groove 61, the outer air supplying hole 62, the inner air supplying hole 63, the inner air supplying hole 64 and the communication hole 65. In this modification, air is supplied directly to between the outer race 41 and the inner race 42 in the second bearing 22 without any connection between the annular groove 61 and the communication hole 65. An outer air supplying hole 66, an inner air supplying hole 67 and another inner air supplying hole 68 are formed in such a manner as to pass between the outer race 41 and the inner race 42 in the second bearing 22. The inner air supplying hole 68 penetrates inward and outward of the outer race 41 in the second bearing 22.

Returning to FIG. 1, each of the outer air supplying holes 62 is connected to a compressor 72 in an air supplying apparatus via a flow rate regulator 71. Each of the flow rate regulators 71 is controlled by a controller 73.

A rotational speed detecting sensor 74 is attached to a side surface of the right presser cap 53 in such a manner as to expose a right side end of the spindle 11. In addition, an acceleration detecting sensor 75 is attached to an intermediate portion in a longitudinal direction of the outer surface of the sleeve 12.

Next, description will be made on an air supplying operation.

First of all, the rotational speed detecting sensor 74 detects the rotational speed of the spindle 11. Incidentally, the rotational speed may be detected by using a spindle control command value. Upon the detection of the rotational speed, an air flow rate is determined in reference to a previously created table, as illustrated in FIG. 5. The table shows supplying quantities per rotational speed (rpm) of the spindle at the positions I to IV in FIG. 2 at the outer air supplying hole 62, the inner air supplying hole 63 and the inner air supplying hole 64 corresponding to each of the bearings 21 to 23 on six levels 0 to 5. Although the supplying quantity is set per 2000 rpm in the table illustrated in FIG. 5, it may be further divisionally set. Otherwise, in the case of an intermediate rotational speed such as 0 to 2000 rpm or 2000 to 4000 rpm, 0 to 999 rpm, for example, is set to 0 rpm or 1000 to 1999 rpm, for example, is set to 2000 rpm. Set values in the table illustrated in FIG. 5 are set such that an increased air flow rate in one direction keeps a balance since the vibration of the retainer 44 and the imbalance are liable to occur by the large clearance between the outer race 41 and the retainer 44 due to a small centrifugal force of the retainer 44 or a small thermal expansion during low-speed rotation of 0 to 6000 rpm. The air flow rate is set in such a manner as to become small since the vibration of the retainer 44 becomes small caused by the small clearance between the outer race 41 and the retainer 44 during high-speed rotation of 8000 rpm or higher. A command as to the set value is sent to each of the flow rate regulators 71 from the controller 73, to thus regulate the air flow rate.

FIG. 6 illustrates the attitude of the spindle 11, that is, inclination angles θ1 to θ4. The inclination angles θ1 to θ4 indicate angles in reference to a vertically downward state of the spindle 11. First, the inclination angles θ1 to θ4 of the spindle 11 are detected. The inclination angle may be detected based on a spindle angle command value or a detection value from an angle detecting sensor fixed to the spindle device. Upon the detection of the inclination angles θ1 to θ4, the air flow rate is determined in reference to a previously created table, not illustrated, in conformance with FIG. 5.

In order to create the table, the following is taken into consideration. The attitude of the retainer 44 for guiding the outer race 41 is varied due to its own weight since the clearance is defined between the inner circumferential surface of the outer race 41 and the rolling element 43. When the inclination angle of the spindle 11 is, for example, 90°, that is, θ2 or θ4, the center of the rotation of the retainer 44 is moved downward. If the rotation is continued as it is, imbalance occurs, thereby possibly generating an abnormal noise or an abnormal vibration. In order to prevent any occurrence of such abnormality, the air flow rate at each of the positions I to IV is set. The table may be created in consideration of the rotational speed. Alternatively, the table illustrated in FIG. 5 created per rotational speed also may be used at the same time.

Subsequently, in the case where the vibration generated in the spindle is detected and the air flow rate is set so as to suppress the vibration, a description will be given by way of one example in which the air flow rate at each of the positions I to IV is set by the use of the rotational speed detecting sensor 74 and the acceleration detecting sensor 75.

The acceleration detecting sensor 75 detects the axis of the sleeve 12 and a vertical acceleration. A frequency of a signal obtained from the acceleration detecting sensor 75 is analyzed at real time or a signal is stored in a memory, and then, its frequency is analyzed, so that only a multiple component of a rotational frequency is extracted. Multiple component to be extracted may be arbitrarily determined. The rotational speed detecting sensor 74 gives the rotational frequency component of the spindle 11. In the case where the size of the signal indicating the extracted multiple component is greater than a predetermined threshold as a result of comparison, a phase having a larger vibration in the spindle rotational direction is specified by the rotational speed detecting sensor 74, and then, the flow rate and direction of the air are determined in such a manner as to reduce the vibration of the phase. In the case of the consideration of both of the axis and the horizontal vibration, each of values may be set to become smaller by the use of the biaxial acceleration detecting sensor 75. Furthermore, several kinds of air supplying patterns are prepared in order to reduce the vibration, and then, the flow rate and direction of the air may be determined by testing the patterns in sequence. Alternatively, the air flow rate may be manually regulated in such a manner as to reduce the value of the vibration sensor while monitoring the value of the vibration.

Although the acceleration detecting sensor 75 is used as one example for obtaining the vibration in the present preferred embodiment, a sound pressure sensor and a displacement sensor may be used singly or in combination as unit for detecting information relating to the vibration.

Claims

1. A spindle device comprising: supplying unit which supplies fluid from three or more points spaced in a circumferential direction between an outer race and an inner race of a bearing supporting a spindle; andcontrol unit which controls a supply quantity of fluid supplied by the supplying unit in such a manner as to independently vary the supply quantity at each of the supplying points.

2. A spindle device according to claim 1, wherein the supply quantity of fluid controlled by the control unit is determined based on a rotational speed of the spindle.

3. A spindle device according to claim 1, wherein the supply quantity of fluid controlled by the control unit is determined based on an inclination angle of the spindle.

4. A spindle device according to claim 1, further comprising: a sensor which detects vibration of the spindle,the supply quantity of fluid controlled by the control unit being determined based on a value detected by the sensor.