JPS6026817A - Bearing device - Google Patents

Abstract

PURPOSE:To turn a revolutional shaft smoothly at a high speed and reduce power los or the like by bearing the revolutional shaft by means of an angular contact rolling bearing in both the radial and axial directions and additionally bearing the shaft by means of a magnetic bearing in the counter-axial direction. CONSTITUTION:Inside a case 1 a driving shaft 2 is disposed at the rear part thereof and supported by a ball bearing 3, A pulley 4 which is attached around the middle part of the driving shaft 2 is inserted in a window 5 formed on the peripheral wall of the case 1. The driving shaft 2 may be ready to be turned by winding a belt 6 on the pulley 4 exposed from the window 5. Inside the case 1 a revolutional shaft 7 is also disposed at the front part thereof in such a way that the front end of the shaft 7 passes through the end plate 8 disposed at the head of the case 1 and the middle part thereof is supported by an angular ball bearing 9 which is engaged inside the case 1. Permanent magnets 28 and 29 are embedded in the rear end face of the revolutional shaft 7 and the front end face of the driving shaft 2, respectively, whereby bearing the revolutional shaft 7 in the backward axial direction and applying a forward axial preload on said ball bearing 9.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a bearing device for a rotating shaft that rotates at high speed, for example, the rotating shaft of a spinning rotor in a rotor-type open-end spinning machine.

Conventionally, in rotor-type open-end spinning machines, the rotating shaft of the spinning rotor is a planetary friction machine! 7+¥ speed increase 1:! 1
If; the drive shaft is connected to the motor through the belt transmission center; bearing. However, single-row deep groove ball bearings cannot be held in the radial and axial positions of the rotating shaft due to their internal clearances, which causes large vibrations and noise and prevents the rotating shaft from moving smoothly. Does not rotate at high speed. Historically, single-row deep-groove ball bearings have low strength due to many restrictions on the construction and material of the retainer, so when the rotating shaft rotates at high speeds of 70,000 rotations per minute or more, The cage is damaged by centrifugal force.

In order to eliminate the above-mentioned drawbacks, it is conceivable to use two angular contact ball bearings in place of the single-row deep-groove ball bearing of A. In angular contact ball bearings, there are few restrictions on the structure and material of the cage, and there are some limitations that prevent damage even when the cage rotates at a high speed of 1 tjr or more. If a certain preload is applied, the radial and axial positions of the rotating shaft can be maintained at -1,jj G, so the copying shaft can be rotated smoothly at high speed.However, if two ball bearings are used, Since it is used in bearings/
The heat generation and power loss due to j'+ J■4q are large.

In view of the above-mentioned difficult circumstances, the purpose of the present invention is to provide a bearing device that rotates smoothly at high speed and that generates less heat and power loss due to friction.

The present inventor has considered eliminating the disadvantages of the device using the above two angular contact ball bearings, which has many advantages over the device using the above seven single-row deep groove ball bearings. This is caused by the use of two bearings with 9 friction rollers, so first we reduced the number of angular contact roller bearings to 7, thereby bearing the rotating shaft in the radial direction and one axial direction. I thought about it. Then, the required C is to bear the rotating shaft in the other axial direction without using rolling friction, and to apply a preload in one axial direction to the angular contact rolling bearing. These two requirements eventually boiled down to the requirement of adding force to the rotating shaft in one axial direction without using rolling friction, and it was realized that this requirement could be achieved by using a thrust magnetic bearing. Ta.

That is, in the present invention, the rotating shaft is supported in the radial direction and in one axial direction by an angular contact rolling bearing, and is laterally supported in the other axial direction by a magnetic bearing, and one side is supported in the angular contact rolling bearing 1. This is a bearing device characterized by applying preload in the axial direction.

In the bearing device of the present invention, since the angular contact rollers apply preload to the 9 bearings, the radial and axial positions of the rotating shaft must be kept constant, and the rotating shaft may generate large vibrations and noise. In addition, since only seven bearings with rolling friction are used, there is less heat generation and power loss due to friction in the bearings.

Next, examples of the present invention will be described.

FIRST EXAMPLE (See FIGS. 1 to 5) A drive device 1.1 of a loaf type open-end spinning frame equipped with a bearing device d of this example has a cylindrical case ( 1) in the rear of the drive shaft (2), both of which are %r?
A ball bearing (blade, (30 pieces) is fitted in the case (1) at the H part, and is placed in the same position and bears in the radial and axial directions, and the central part G of the drive shaft (2) Fitted pulley (4)
is installed through the peripheral wall of the case (1) so as to face the fc window (5),
A belt (6) connected to a motor (not shown) is wrapped around a pulley (4) exposed through a window (5) to rotate the drive shaft (2). In addition, in the front part of the case (1), as shown in FIG. Angular contact ball bearing fitted inside the case (
9), and is disposed coaxially at the front side of the drive shaft (2), and is supported in the radial direction and the forward axial direction by the angular ball bearing (9). In history, Figures 1 and 2
As shown in 1, a circumferential groove 0Q is formed on the outer circumferential surface of the base AHA portion of the rotating shaft (7), and a support ring 0υ connected to the tip of the drive shaft (2) is inserted into the circumferential groove (10 A fixed ring 0η was fitted into the case (1) at the outer circumferential position of the drive shaft support ring (1υ), and a fixed ring 0η was placed around the drive shaft support ring aυ at equal intervals along the axial direction. A planetary friction wheel 0< with a cylindrical rotor is slid into each recess (13), and each planetary friction wheel q angle having a diameter larger than the wall thickness of the support ring (1υ) is fixed between the inner peripheral surface of the slope lamp 4 and the rotating shaft. Appropriate pressure is applied to the four circumferential grooves of the drive shaft (7), and each planetary friction wheel α4 revolves and rotates on its own axis, causing the rotating shaft (7) to rotate at an increased speed. It constitutes a planetary friction military aircraft (Inano speed increaser) 14. Also, as shown in Figures 1 and 3, the opposing end face of the rotating shaft (7) and the leading end face of the drive shaft (2) Annular permanent magnets (4) and 2) were installed on the coaxial core, respectively, and fixed to the rear end surface of the 14-output permanent magnet (to) fixed to the rotating shaft (7) and the drive shaft (2). Permanent magnets (all exposed front end faces are the same polarity and open space ′?r) are provided to face each other and repel each other to form a magnetic bearing. ), (rotated by allllll1l
I (7) is supported in the rearward axial direction, and a preload is applied to the angular ball bearing (9) in the axial direction in the Iiil direction. Drive shaft +21 arranged coaxially and rotation III
As shown in Figures 1 and 2, (7) is provided with an oil supply passage (LF-) at its axial position,
Multiple oil supply passages reaching the circumferential groove of the I rotating shaft, and oil supply passages (
1. A plurality of oil supply passages αη reaching the inner circumference of the inner ring of the angular ball bearing (9) of the rotating shaft are provided along the radial direction, and lubricating oil is driven from an oil supply source (not shown).
I (Foundation of force W: M [Refueling fi'6 opened at 111
Supply Qi, History, Note rllll Road 1. The oil is supplied to the speed increasing mechanism Tachibana, (1η, 04. I4, 0 fathoms,
The lubricating oil flowing out from the U-shaped bearing and the angular contact ball bearing (9) is returned to the oil supply source through oil drain holes provided through the peripheral wall of the case (1). At the tip of the rotor 1i1111 (7) protruding from the end plate (8) at the tip of the case (1), a substantially cup-shaped spinning rotor (crucible) is attached to the workpiece 9 shown in FIG. The spinning rotor ( lCjV3 is the opening Q at its tip
A device is used to generate air flow from υ to the exhaust hole (e). At the tip of the case (1) that supports the spinning rotor 01 and its rotating shaft (7), there is a cylindrical container shape made of a material with high thermal conductivity and heat dissipation properties. Cover (2) formed in the case (2), so that the end plate (c) at the tip of No. 4 faces the opening (21) of the spinning rotor, and the base end of the opening of the gutter (c) is placed at the tip of the case (1). Attach the spinning rotor (1'J) and its rotating shaft (A) to the case (1) on the coaxial core, and attach the fiber supply path (C) to the end plate (C) of the cover. Attach the pipes that form the f! The pipe is installed through H, and the yarn pull-out path (C) faces the middle 11'rs of the spinning rotary 9.
Fiber supply caused by rotation of spinning rotor u9? 6
(Open the inside of the ijj thread rotor Q9 through (4)
) to the exhaust hole (2), an air passageway (5) is formed through which the air flow passes through the cover (■) and is discharged from an outlet 09 penetrating the proximal side of the peripheral wall of the cover, 4+, lj, air oil 1
The airflow flowing through the scratches Qθ eliminates the heat generated by the rotation G of the spinning rotor a9.
When operating the drive 9jh device of a rotor-type open-end spinning frame equipped with the bearing device of this example, lubricating oil is supplied to the oil supply path 0■, as in the conventional case, while! Trial oil (
2) to rotate the rotating shaft (7) and thus the spinning rotor θ.
Rotate 9 at increased speed. Then, unlike in the past,
The rotating shaft (7) and the spinning rotor 09 rotate smoothly at high speed without producing large scale vibrations or noise, and have little heat generation and power loss due to friction.

In order to confirm the effect of reducing frictional heat and power loss in bearing device a of this example, a flow rate of lubricating oil was added to the container, and in each case, the rotating shaft (7) was rotated 100,000 revolutions per minute, and the angular When the temperature rise of the outer ring of the ball bearing (9) and the gutter tip power were measured, the results were obtained as shown by the solid lines with circles in the diagrams of Fig. 3 and Fig. 5, respectively. Next, in order to compare this result, for the conventional device using the two angular contact ball bearings mentioned above, the flow rate of the lubricating oil was similarly set to 700,000 yen per minute. When the bearing was rotated and the temperature rise and power loss of the outer ring of the angular contact ball bearing were measured, the results were obtained as shown by the dashed lines with triangle marks in the diagrams in Figure 3 and Figure 5, respectively.

That is, it is clear from the drawing that the bearing device of this example has the following features:
Compared to the conventional device of the comparative example described above, if the flow rate of lubricating oil is the same, the temperature rise and power loss of the angular ball bearing (9) are small.

When replaced, the allowable rise in angular contact ball bearing (9) τg%
If the temperature is the same, the flow rate of lubricating oil will be small, and therefore the loss of power will be small. After all, if the allowable temperature rise of the angular contact ball bearing (9) and the flow rate of lubricating oil are the same,
The rotational speed of the rotating shaft (7) can be increased to an unprecedented level.

Second Example The only difference in the bearing device of this example from that of the previous example is that the directions of the axial support by the angular ball bearing (9) and magnetic bearings (2) and (c) are reversed. It is. That is, the rotating shaft inside the front part of the case is supported in the radial and rearward axial directions by angular contact ball bearings fitted inside the case, and the end of the rotating shaft and the tip of the drive shaft inside the rear part of the case are By two fixed permanent magnets that attract each other?
With a +8 air bearing, if you bear it in the forward hl + direction, will it be angular to the east? A rearward axial preload is applied to the ball bearing.

Note that if one of the end of the rotation shaft and the tip of the drive shaft is a Ca-based body that is attracted to a magnet fixed to the other, one of the magnets may be omitted.

Third embodiment (see Fig. 6) The only difference in the bearing device of this embodiment from that of the first embodiment is that the mounting position of the magnetic bearing has been changed.
As shown in the figure, a circular plate-shaped permanent (weight Cat) is placed on the outer bottom surface of the spinneret θ9 facing the force side and on the front surface of the end plate (8) at the tip of the case (1), and on the iD 2 coaxial core. The rear surface of the permanent magnet (1) fixed to the spinning rotor 09 and the front surface of the permanent magnet 0υ fixed to the end plate (8) are made of the same polarity and face each other with a gap 2 provided, and both permanent magnets C repel each other. Power, O
By J)? In other words, the rotating shaft (7) in the j3iT section of the case (1) is rotated in the radial direction by the angular ball bearing (9) fitted in the case (1). and a forward axial bearing, and also a magnetic bearing (RI) above.

()0 applies a preload in the forward axial direction to the angular ball bearing (9) while bearing in the rearward axial direction. The other points are the same as those in the example/example, so the explanation will be omitted by adding the title ``No.
do.

In the bearing device of this example, the magnetic 1jQ11 bearing, l-
8"j's value masterpiece/IJ face is the first. The reason is to make it wider than that in the second embodiment. Good health, magnetic bearings (
(1).

It is possible to increase the axial force of C3υ, or to use a permanent magnet with a weaker magnetic force per unit area for C3υ.

First Embodiment The only difference in the bearing device of this example from that of the previous example is that the direction of the axial support between the angular contact ball bearing (9) and the magnetic bearing and by 0υ was reversed, and inside the case. NolL! The wide shaft is supported in the radial and rearward axial directions by angular ball bearings fitted into the case, and is also supported by two mutually suction bearings fixed to the outer bottom J of the spinning rotor and the front surface of the end plate at the tip of the case. A permanent magnet bearing is used to support the bearing in the axial direction facing the cutting direction, and also applies preload in the axial direction facing backwards to the angular contact ball bearing.

In addition, if one of the bottom plate of the spinning rotor and the end plate at the base end of the case is a magnetic material that is attracted to the 711 stone fixed to the other,
One of the magnets may be omitted.

Although the bearing device of the above-mentioned /6 embodiment uses an angular contact ball bearing as the anogular contact C rolling bearing, an angular tapered roller bearing may also be used.

Furthermore, although the bearing devices of each example are used as bearings for drive devices for rotor-type oven-end spinning, they can also be used for bearings for high-speed rotating machines such as turbochargers and turpinoes.

[Brief explanation of the drawing]

FIG. 1 shows a longitudinal 11;
Figure 2 is a cross-sectional view along the ■-kawawata line in Figure 1. Figure 3 is an enlarged view of the magnetic bearing part in Figure 1. Figure 7 is the bearing temperature rise and lubricating oil flow rate in the same drive device. The line diagram S shows the relationship between power loss and lubricating oil flow rate in the same drive device. Vertical II of spinning-like drive device (this is a side view); Rotating shaft 9: Angular ball j: Senke 2 B, 2
9: i; χ magnetic bearing 30, 31: magnetic bearing 2nd
Figure 3

Claims (1)

[Claims] The rotating shaft is supported in the radial direction and in one axial direction by an angular contact rolling bearing, and in the other axial direction by a twisted magnetic bearing, and in one axial direction by an angular contact roller bearing. A bearing device characterized by a preload of 0 and 0.