JPS5846260Y2 - damper bearing - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a damper bearing that can reduce vibrations of a rotating shaft.

In order to effectively damp the vibration of the rotating shaft with a damper bearing, it is necessary to adjust the gap between the primary bearing and the secondary bearing, that is, the thickness of the squeeze oil film supplied into this gap, as appropriate. .

In conventional damper bearings, in order to adjust the above-mentioned gap, the gap is adjusted by replacing the primary bearing one by one, but this adjustment is very cumbersome and time-consuming.

Therefore, the present invention provides a damper bearing that solves these problems.

An embodiment of the present invention will be described below based on the drawings.

1 is a rotating shaft, 2 is a two-split primary bearing [tailing pad journal bearing] that supports the rotating shaft 1, and 3 is a 2-split primary bearing that supports the rotating shaft 1.
This is a split commercial secondary bearing.

The secondary bearing 2 is composed of the following components.

That is, there is a retainer ring 4 surrounding the rotating shaft 1, and an appropriate number of rings (5 in this embodiment) that are irremovably fitted into an annular groove 4a formed on the inner peripheral surface of the retainer ring 4 and in contact with the rotating shaft 1. ) journal pad 5,
The journal pad, whose threaded portion is screwed into the screw hole of the retainer ring 4 and whose tip end is fitted into the hole 5a of each journal pad 5, is fitted with a setscrew 6 and a circumferentially appropriate part on one end surface of the retainer ring 4. An appropriate number (eight in this embodiment) of bar spring parts 7 protruding at each interval, a ring part 8 fixed to the end of each bar spring part 7, and an edge of the outer peripheral surface of the ring part 8. A flange portion 8a is formed at the portion.

Further, the outer circumferential surface 4b of the retainer ring 4 is formed into a tapered surface that widens outward in the direction of arrow A.

The small-diameter inner circumferential surface 3a of the secondary bearing 3 is formed into a tapered surface parallel to the outer circumferential surface 4b of the retainer ring 4, and the large-diameter inner circumferential surface 3b of the secondary bearing 30 is externally fitted onto the ring portion 8. ing.

Reference numeral 9 denotes a two-piece liner disposed between the end surface of the secondary bearing 3 and the flange 8a, and the thickness L of this liner 9 allows the liner 9 to be separated from the small diameter inner surface 3a of the secondary bearing 3. The gap C1 between the retainer ring 4 and the outer peripheral surface 4b, that is, the thickness of the squeeze oil film is determined.

Reference numeral 10 is a bolt whose threaded portion is screwed into a threaded hole formed in the end face of the secondary bearing 3 through the hole in the flange 8a and the liner 9, and is used to connect the primary bearing 2 to the secondary bearing 3. It is fixed.

Even in this state, the primary bearing 2 is
is capable of vibrating along a direction perpendicular to the axis of the rotating shaft 1.

11 is an annular groove formed approximately at the center of the small-diameter inner circumferential surface 3a of the secondary bearing 3; 12 is a through hole that passes through the retainer ring 4 and communicates with the annular groove 11; 13 is a through hole that passes through the secondary bearing 3; This is a primary bearing lubricating oil supply port that communicates with the annular groove 11.

Therefore, when lubricating oil is injected into the supply port 13, this lubricating oil passes through the annular groove 11 and the through hole 12 to the rotating shaft 1.
is supplied to

Reference numeral 14 denotes four annular grooves formed on the outer circumferential surface 4b of the retainer ring 4, and 15 an O-ring disposed in each of the annular grooves 14 and mounted on the small diameter inner circumferential surface 3a of the secondary bearing 3. As a result, two ring-shaped sealed spaces 16 are formed between both bearings 2 and 3.

17 is a squeeze oil film lubricating oil supply port formed at a suitable location on the outer peripheral surface of the secondary bearing 3, and 18 is an oil supply port formed in the secondary bearing 3 from the supply port 17 to each of the ring-shaped sealed spaces 16. It is a road.

Therefore, when lubricating oil is injected into the supply port 17, the lubricating oil is supplied into the two ring-shaped spaces 16 through the oil passage 18, and a squeeze oil film is formed in the ring-shaped sealed spaces 16.

Reference numerals 19 and 20 indicate parallel bottles, and 21 and 22 indicate bolts for tightening the two-split retainer ring 4 and the secondary bearing 3.

In the above configuration, when the rotating shaft 1 is rotated, vibrations generated by the rotation are transmitted to the primary bearing 2 and then to the secondary bearing 3, but the vibrations are transmitted to the primary bearing 2 and then to the secondary bearing 3. Since a squeeze oil film is formed, vibrations are reduced by this squeeze oil film.

Next, if you want to change the thickness of the squeeze oil film, you can do the following.

That is, if you want to increase the thickness of the squeeze oil film, first remove the bolt 10 and tighten the primary bearing 2 in the direction of arrow A.
The liner 9 may be replaced with a thicker one by slightly moving the liner 9 in the direction shown in FIG.

In this case, the outer peripheral surface 4b of the retainer ring 4 and the secondary bearing 3
Since both of the small diameter inner circumferential surface 3a are formed into parallel tapered surfaces, when the primary bearing 2 is moved in the direction of arrow A as described above, the gap between the above outer circumferential surface 4b and the small diameter inner circumferential surface 3a increases. C increases, and the thickness of the squeeze oil film increases.

On the other hand, if it is desired to reduce the thickness of the squeeze oil film, the liner 9 may be replaced with a thinner one using substantially the same procedure as described above.

Next, a more detailed explanation will be given based on FIG. 4.

In other words, the primary bearing 2
Dynamic characteristics generally have a modeled effect on the elastic coefficient of 1 and damping coefficient B1, whereas the squeeze oil film of the secondary bearing 3 has a damping coefficient B2 and the rod spring part 7 has an elastic coefficient of 2. exerts a certain effect.

Further, assuming that the mass of the rotating shaft 1 is Ml and the mass of the bearing is M2, the vibration characteristics of the entire damper bearing that affect the whirling vibration of the rotating shaft 1 can be modeled as shown in FIG.

Here, the thickness of the damping coefficient B2 due to the squeeze oil film is directly related to the gap C in which the squeeze oil film is formed.

This relational expression is generally given by Boc-.

Therefore, the thickness C of the squeeze oil film is changed and the damping coefficient B
By changing the size of 2, the vibration characteristics of the damper bearing as a whole can be optimized.

As stated above (according to the damper bearing of the present invention, by using the liner 9 with an appropriate thickness L, the gap C between both bearings 2 and 3, that is, the ring-shaped sealed space 16 formed in this gap C) The thickness of the squeeze oil film supplied can be adjusted as appropriate, and there is no need to replace the primary bearing 2 every time as in the conventional case.

Since the thickness of the squeeze oil film can be easily changed as described above, the vibration damping effect of the damper bearing can be easily controlled.

Also, due to the action of the rod spring portion 70, the primary bearing 2 is
It is possible to vibrate along a direction perpendicular to the axis of .

Therefore, vibrations can be damped from this point as well.

[Brief explanation of the drawing]

The figures show one embodiment of the present invention, with Figure 1 being a longitudinal sectional view and Figure 2 being a longitudinal sectional view.
The left half of the figure is a partially cutaway side view, and the right half of Figure 2 is the first
3 is a view taken along arrows III--III in FIG. 1, and FIG. 4 is a diagram showing the principle. 1...Rotating shaft, 2...Primary bearing, 3.
...Secondary bearing, 3a...Small diameter inner peripheral surface (tapered surface), 4...Retainer link, 4b...
...Outer circumferential surface (tapered surface), 5...Journal pad, 7...Bar spring part, 9...Liner 15...O ring, 16・・・・・・Ring-shaped closed space.

Claims (1)

[Scope of utility model registration request] A primary bearing 2 that supports the rotating shaft 1 and a secondary bearing 3 that further supports the secondary bearing 2 are provided. an appropriate number of journal pads 5 fixed to the inner circumferential surface and in contact with the rotating shaft 1; an appropriate number of rod spring portions 7 protruding from one end surface of the retainer ring 4 at appropriate intervals in the circumferential direction; , a ring part 8 fixed to the end of each rod spring part 7, and a flange part 8a formed at the end of the outer peripheral surface of the ring part 8, and the outer peripheral surface 4 of the retainer ring 4.
b is formed into a tapered surface, and the inner peripheral surface 3a of the secondary bearing 3 facing the retainer ring 4 is formed into a tapered surface parallel to the outer peripheral surface 4b of the retainer ring 4, and the end surface of the secondary bearing 3 and the It is inserted between the collar part 8a of the ring part 8 and the primary,
A liner 9 with an appropriate thickness L is provided to appropriately set the gap C between the two secondary bearings 2 and 3, and the ring portion 8 is connected to the secondary bearing 3.
A lubricating oil supply port 13 for the primary bearing is formed in the secondary bearing 3 to pass through the retainer ring 4 and communicate between each journal butt 5. A plurality of O-rings 15 are arranged between the inner circumferential surface 3a of the secondary bearing 3 to form an appropriate number of ring-shaped sealed spaces 16 between both bearings 2 and 3, and a ring-shaped sealed space is provided in the secondary bearing 3. Lubricating oil supply port 17 for squeeze oil film connected to 16
A damper bearing characterized by forming.