WO2017199327A1

WO2017199327A1 - Self-aligning bearing support device

Info

Publication number: WO2017199327A1
Application number: PCT/JP2016/064572
Authority: WO
Inventors: 才貴西山; 政宏清水; 真吾三澤; 正史中家
Original assignee: ジャパンマリンユナイテッド株式会社
Priority date: 2016-05-17
Filing date: 2016-05-17
Publication date: 2017-11-23
Also published as: CN108603527A; JP6573296B2; JPWO2017199327A1; KR20180075661A; KR102035953B1; CN108603527B

Abstract

A self-aligning bearing support device 10 supports an intermediate bearing 7 which rotatably supports the intermediate portion of an intermediate shaft 6. The intermediate bearing 7 extends horizontally with the front and rear ends thereof being rotatably supported. The self-aligning bearing support device 10 has a total spring constant k with respect to the displacement x of the intermediate bearing 7 from the installation height. The total spring constant k is set so that the supporting force F of the intermediate bearing 7 falls within a preset load range RF in a preset height range RH. The self-aligning bearing support device 10 also has a displacement speed restriction device 30 which restricts the speed of displacement of the intermediate bearing 7 from the installation height. The displacement speed restriction device 30 has a displacement fixing device (remote control valve 39) which fixes the displacement x of the intermediate bearing 7.

Description

Self-alignment type bearing support device

The present invention relates to a self-alignment type bearing support device that adjusts the height position of a bearing to an appropriate position.

For example,

Patent Documents

1 and 2 have been proposed as alignment adjustment devices that adjust the height position of a bearing to an appropriate position.

In the “bearing alignment automatic adjustment device” of Patent Document 1, a setting value signal generator that generates a setting value signal of a bearing center position, a state quantity measuring device that measures a change in state quantity, and an arithmetic device that calculates a deviation value, And a bearing position adjusting device for adjusting the bearing center position based on the deviation value.

The “alignment adjusting device” of Patent Document 2 adjusts the alignment of the shaft by the parameter monitor for detecting the state of the shaft, the calculator for calculating the control amount from the monitored amount by the parameter monitor, and the calculated control amount. And an actuator. The displacement monitor for the shaft system is used as a parameter monitor, the shaft vibration is obtained from the detected amount from the displacement meter, and the alignment of the shaft system is adjusted so that the shaft vibration obtained by the calculator is suppressed.

JP 7-317757 A JP 2002-213522 A

∙ There are cases where three or more bearings are provided to support the rotating shaft for torque transmission. In this case, each bearing is installed in consideration of the balance of each bearing load under a certain condition (for example, a cold condition). However, under actual usage conditions (for example, hot conditions), the height of each bearing may be displaced due to a change in temperature or the action of an external force (for example, a change in draft), and may greatly deviate from the planned load balance.

If the bearing load becomes too large, the surface pressure of the metal may increase and seizure damage may occur, and if the bearing load becomes too small, the shaft restraining force will decrease, causing fretting of the bearing metal part due to behavior, The bearing metal may peel off.

¡When the displacement of each bearing height is large, there is the risk mentioned above, which causes a trouble of the shaft system.

In the means of

Patent Documents

1 and 2 described above, a control device (arithmetic unit, arithmetic unit, etc.) is indispensable, and there is a possibility that the function is lost due to a power failure or noise.

The present invention has been created to solve the above-described problems. That is, the object of the present invention is to automatically adjust the bearing load within an appropriate range without being affected by a power failure or noise even when the bearing height is displaced due to temperature change or external force after installation of the bearing. It is an object of the present invention to provide a self-alignment type bearing support device that can be used.

According to the present invention, there is provided a self-alignment type bearing support device that supports an intermediate bearing that extends in a horizontal direction and rotatably supports an intermediate portion of an intermediate shaft that is rotatably supported at its front end and rear end,
An overall spring constant for displacement from the installation height of the intermediate bearing;
A self-alignment type bearing support device is provided in which the total spring constant is set such that a support force of the intermediate bearing is within a set load range in a set height range.

· A displacement speed limiting device for limiting the displacement speed of the intermediate bearing from the installation height is provided.

The displacement speed limiting device has a displacement fixing device that fixes the displacement.

An upper fixing plate to which the intermediate bearing is fixed;
A lower fixing plate fixed to the fixing part;
A guide device that guides the upper fixing plate relative to the lower fixing plate so as to move up and down within the set height range;
An urging device sandwiched between the upper fixing plate and the lower fixing plate and urging the upper fixing plate upward with respect to the lower fixing plate;
The total urging force of the urging device is set so that the support force of the intermediate bearing is within the set load range in the set height range.

The biasing device has a spring sandwiched between the upper fixing plate and the lower fixing plate,
The spring constant of the spring is set so that the support force of the intermediate bearing as a whole is within the set load range in the set height range.

An upper fixing plate to which the intermediate bearing is fixed;
A lower fixing plate fixed to the fixing portion,
The displacement speed limiting device is a hydraulic cylinder having a piston rod that is sandwiched between the upper fixed plate and the lower fixed plate and follows the movement of the upper fixed plate with respect to the lower fixed plate;
A moving speed adjusting device for adjusting a moving speed of the piston rod.

The moving speed adjusting device is a first flow rate adjusting valve provided in a first connecting pipe communicating the head side of the hydraulic cylinder and the hydraulic fluid tank.

The moving speed adjusting device is a second flow rate adjusting valve provided in a second connecting pipe communicating the head side and the rod side of the hydraulic cylinder.

The moving speed adjusting device is provided in a first connection pipe that communicates the head side of the hydraulic cylinder and the hydraulic fluid tank, or a second connection pipe that communicates the head side and the rod side of the hydraulic cylinder, A remote control valve capable of fully closing the first connection pipe or the second connection pipe by remote control;

The guide device is sandwiched between the upper fixing plate and the lower fixing plate, and at the lower limit of the set height range, a lower limit limiting stopper for preventing the upper fixing plate from moving downward,
An upper limit bolt that prevents the upper fixing plate from moving upward at the upper limit of the set height range;
A telescopic guide for guiding the vertical expansion and contraction of the urging device.

A position sensor for bearing height position alarm capable of detecting the lower limit or the upper limit of the set height range;
A bearing height monitoring gap sensor capable of detecting a gap gap between the upper fixing plate and the lower fixing plate.

A jack bolt that is screwed to the upper fixing plate or the lower fixing plate and presses the upper fixing plate upward with respect to the lower fixing plate.

According to the present invention, the total spring constant is set so that the support force of the intermediate bearing is within the set load range in the set height range. Therefore, even if the bearing height is displaced from the installation height due to temperature change or external force after the bearing is installed, the bearing load (supporting force of the intermediate bearing) can be automatically adjusted within the set load range. .

Also, since no control device is used, the bearing load (supporting force of the intermediate bearing) can be automatically adjusted within the set load range without being affected by power failure or noise.

It is explanatory drawing of the rotating shaft provided with the self-alignment type bearing support apparatus of this invention. It is a spring characteristic figure requested | required of the support part which supports an intermediate bearing. It is a schematic diagram of the support part which supports an intermediate bearing. It is the A section enlarged view of FIG. FIG. 3B is a side view of FIG. 3A. It is a B section enlarged view of Drawing 3A, and is a 1st embodiment figure of a bearing support device. It is a spring characteristic figure requested | required of the support part which supports an intermediate bearing. It is a schematic diagram of the support part which supports an intermediate bearing. It is a B section enlarged view of Drawing 3A, and is a 2nd embodiment figure of a bearing support device. It is a 1st embodiment figure of a displacement speed limiting device. It is a 2nd embodiment figure of a displacement speed limiting device.

Embodiments of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the common part in each figure, and the overlapping description is abbreviate | omitted.

FIG. 1 is an explanatory view of a rotary shaft provided with a self-alignment type bearing support device 10 of the present invention (hereinafter simply referred to as “bearing support device 10”).

In this figure, 1 is a ship, 1a is stern, 1b is bottom, 1c is double floor, 2 is propeller, 3 is stern tube, 4 is stern tube bearing, 5 is propeller shaft, 6 is intermediate shaft, and 7 is intermediate A bearing, 8 is a main machine output shaft, and 9 is a main machine bearing.
The propeller shaft 5, the intermediate shaft 6, and the main engine output shaft 8 rotate around an axis ZZ extending in the horizontal direction. The axis ZZ is not limited to the horizontal axis, and may be an inclined axis inclined with respect to the horizontal.
Note that an arrow E in the figure indicates the axial center position of the main engine bearing 9.

In FIG. 1, the front end and the rear end of the intermediate shaft 6 are rotatably supported by a main engine bearing 9 and a stern tube bearing 4, respectively. The stern tube bearing 4 is fixed to the hull of the stern 1a.
The intermediate bearing 7 rotatably supports an intermediate portion of the intermediate shaft 6. The position of the intermediate portion is preferably the center of the intermediate shaft 6 in the length direction, but may be other positions.

The bearing support device 10 of the present invention is a device that is attached to the bearing stand 11 and supports the intermediate bearing 7. The bearing stand 11 is firmly connected to the double floor 1c and has high rigidity.
Further, the hull of the ship 1, that is, the stern 1 a, the ship bottom 1 b, and the double floor 1 c are reinforced by a stiffener and have high rigidity.
In the following description, the spring constant k1 of the bearing base 11 (hereinafter referred to as “the receiving spring constant k1”) is 85 kN / mm as an example, and the spring constant of the hull of the ship 1 is one digit larger than that of the bearing base 11. Assumes that.

The conventional structure does not use the bearing support device 10 of the present invention, and directly fixes the intermediate bearing 7 in FIG. 1 to the hull structure (that is, the bearing stand 11). When the intermediate bearing 7 is fixed and installed directly on the bearing base 11 as in the prior art, the influence coefficient (load change with respect to a height displacement of 1 mm) with respect to the relative displacement x with the hull at the intermediate bearing 7 is, for example, A large value of about 85 (kN / mm) is obtained.
Therefore, when the displacement x from the installation height of the intermediate bearing 7 is large, the bearing load of the intermediate bearing 7 or the main engine bearing 9 may exceed the allowable bearing load, and damage may occur.

For example, assuming that the load range of the support force F of the intermediate bearing 7 (hereinafter referred to as “set load range RF”) is 12 to 151 kN, the planned support force F of the intermediate bearing 7 during installation (hereinafter “planned installation load”) Is 63 kN.
When the displacement x of the intermediate bearing 7 (the direction in which the intermediate bearing 7 is lowered) is 1 mm, the support force F of the intermediate bearing 7 is 63 kN−85 (kN / mm) × 1 mm = −22 kN. In other words, in this case, the intermediate bearing 7 is lifted from the bearing base 11 and the intermediate shaft 6 is not supported, and the metal portion of the intermediate bearing 7 is damaged by fretting.

2A and 2B are principle diagrams of the first embodiment of the present invention.
As a specific example, the set load range RF is 12 to 151 kN, the planned installation load is 63 kN, and the set height range RH (displacement range from the installation height of the intermediate bearing 7) is changed from the upper limit (x = -2 mm) to the lower limit (x = 2 mm).
The set height range RH assumes that the relative displacement is doubled with a margin with respect to the above-mentioned displacement x of 1 mm.

FIG. 2A is a spring characteristic diagram required for the support portion that supports the intermediate bearing 7. In this figure, the horizontal axis x [mm] is the displacement (downward distance) from the installation height (x = 0) of the intermediate bearing 7, and the vertical axis F [kN] is the supporting force of the intermediate bearing 7.
The total spring constant k that satisfies the spring characteristics of this example is k = 25.5 kN / mm.

FIG. 2B is a schematic view of a support portion that supports the intermediate bearing 7. In this figure, the bearing support device 10 of the present invention is sandwiched between an intermediate bearing 7 and a bearing base 11. The spring constant k2 of the bearing support device 10 is hereinafter referred to as “support spring constant k2”.

Since the bearing stand 11 and the bearing support device 10 are positioned in series in the vertical direction, the following relational expressions (1) and (2) are established. Here, x1 is the displacement of the bearing stand 11, and x2 is the displacement of the bearing support device 10.

F × x = F × x1 = F × x2 (1)
x = x1 + x2 (2)
Equation (3) is derived from equations (1) and (2).
1 / k = 1 / k1 + 1 / k2 (3)

From equation (3), when k = 25.5 kN / mm and k1 = 85 kN / mm, a support spring constant k2 = 37 kN / mm is obtained.

As described above, the bearing support device 10 of the present invention has the total spring constant k with respect to the displacement x from the installation height (x = 0) of the intermediate bearing 7. The total spring constant k is such that the supporting force F of the intermediate bearing 7 is within a preset load range RF (eg, F = 12 to 151 kN) in a height setting range (eg, x = −2 to 2 mm). It is set to be.

That is, in the above-described example, the spring characteristics of the bearing support device 10 are set so that the support spring constant k2 is k2 = 37 kN / mm. As a result, as shown in FIG. 2A, the bearing load (supporting force F of the intermediate bearing 7) is kept within the set load range RF even when the bearing height is displaced due to a temperature change or an external force after the intermediate bearing 7 is installed. It can be adjusted automatically.

3A is an enlarged view of a part A in FIG. 1, and FIG. 3B is a side view of FIG. 3A.

In this example, the intermediate bearing 7 includes a bearing 7a that supports the intermediate shaft 6, a bearing case 7b that surrounds the outer peripheral surface of the bearing 7a, and a leg portion 7c that supports the lower surface of the bearing case 7b.
The leg portion 7c has a pair of horizontal support surfaces 7d on the lower surfaces at both ends in the width direction.
In this example, the bearing 7a is a journal bearing (sliding bearing), but the present invention is not limited to this, and may be another bearing (for example, a rolling bearing).

In this example, the bearing stand 11 has a pair of left and right support tables 11a and an adjustment liner 11b.
The pair of support bases 11a are located at intervals on both sides in the width direction of the axis ZZ. The lower surface of the support base 11a is fixed to the double floor 1c via the adjustment liner 11b. The adjustment liner 11b is composed of a plurality of flat plates or tapered plates, and can finely adjust the height of the upper surface of the support base 11a.
In order to finely adjust the height of the upper surface of the bearing base 11, it is preferable to have jack bolts (not shown) on the lower surface of the support base 11a.

The upper surface of the support base 11 a is a horizontal plane, and the bearing support device 10 is sandwiched between the horizontal support surface 7 d of the intermediate bearing 7.
In this example, a pair of bearing support devices 10 are sandwiched between the upper surfaces of a pair of left and right support bases 11 a and a horizontal support surface 7 d of the intermediate bearing 7.
The bearing support device 10 is not limited to one pair, and may be single or three or more.

FIG. 4 is an enlarged view of a portion B in FIG. 3A and is a first embodiment diagram of the bearing support device 10.
In this figure, the bearing support device 10 includes an upper fixing plate 12, a lower fixing plate 14, a guide device 16, and an urging device 18.

The upper fixing plate 12 is a horizontal thick plate in this example, and the intermediate bearing 7 is fixed to the upper surface of the upper fixing plate 12 by, for example, bolts or nuts.
The lower fixing plate 14 is a horizontal thick flat plate in this example, and the lower end is fixed to a fixing portion (bearing base 11 in this example) by, for example, a bolt or a nut. The fixed portion is not limited to the bearing stand 11 and may be a part of the hull of the ship 1 as long as it has high rigidity.

In FIG. 3B, side guides 10a are attached to the outer surfaces in the width direction of the pair of left and right bearing support devices 10, respectively.
In this example, the side guide 10 a has an upper end fixed to the upper fixing plate 12 and extending downward, and a lower end extending along the outer surface in the width direction of the lower fixing plate 14. Conversely, the side guide 10 a may be fixed to the lower fixing plate 14.
With this configuration, it is possible to guide the vertical movement of the intermediate bearing 7 by the pair of side guides 10a and to prevent the intermediate bearing 7 from moving in the left and right lateral direction (width direction).

In FIG. 4, the guide device 16 guides the upper fixing plate 12 relative to the lower fixing plate 14 so as to move up and down within a set height range RH (x = −2 to +2 mm in FIG. 2A).
The set height range RH includes the allowable bearing load of the bearing that supports the intermediate shaft 6 (in this example, the main engine bearing 9, the stern tube bearing 4, and the intermediate bearing 7) and the usage status after installation (for example, temperature change or external force). It is possible to set in advance from the relative displacement of each bearing height assumed by the above action.

In addition to the pair of side guides 10a described above, the guide device 16 includes a lower limit stopper 20, a stopper fixing bolt 21, an upper limit bolt 22, and an extendable guide 24 in this example.

The lower limit limiting stopper 20 is sandwiched between the upper fixing plate 12 and the lower fixing plate 14 and prevents the upper fixing plate 12 from moving downward at the lower limit (x = 2 mm) of the set height range RH. The lower limit limiting stopper 20 is a hollow cylindrical member in this example.
The lower end of the stopper fixing bolt 21 is fixed to the lower fixing plate 14 through the center hole of the lower limit limiting stopper 20, and the head of the bolt is fixed with a gap from the upper surface of the upper fixing plate 12. The stopper fixing bolt 21 holds the position of the lower limit limiting stopper 20.

The upper limit bolt 22 prevents the upper fixing plate 12 from moving upward at the upper limit (x = -2 mm) of the set height range RH. In this example, the upper limit limiting bolt 22 is a bolt that passes through the center hole of the urging device 18, the lower end is fixed to the lower fixing plate 14, and the head of the bolt is fixed with a gap from the upper surface of the upper fixing plate 12. ing.

The expansion / contraction guide 24 guides the vertical expansion / contraction of the urging device 18. In this example, the telescopic guide 24 is a concentric double tube surrounding the biasing device 18, and one is fixed to the upper fixing plate 12 and the other is fixed to the lower fixing plate 14.

The above-described guide device 16 can guide the upper fixing plate 12 to the lower fixing plate 14 such that the upper fixing plate 12 can move up and down within a set height range RH.

In FIG. 4, the biasing device 18 is sandwiched between the upper fixing plate 12 and the lower fixing plate 14 and biases the upper fixing plate 12 upward with respect to the lower fixing plate 14.
The total urging force (total urging force) of the urging device 18 is such that the supporting force F of the intermediate bearing 7 is within a set load range RF set in advance in the set height range RH (x = −2 to +2 mm). It is set to be.
The set load range RF can be set in advance within a range in which the allowable bearing load of the intermediate bearing 7 is a maximum value and the supporting force F of the intermediate bearing 7 is not negative. The range in which the supporting force F is not negative is set such that an excessive tensile force acts on the above-described upper limit bolt 22 (and the stopper fixing bolt 21), the intermediate bearing 7 is lifted, and the function of the intermediate bearing 7 is lost. This is to prevent it.

In FIG. 4, the urging device 18 includes a spring 26 that is sandwiched between the upper fixing plate 12 and the lower fixing plate 14. In this example, the spring 26 is a disc spring laminated body in which a plurality of disc springs and a plurality of flat washers are laminated. The spring 26 is not limited to this configuration, and may be a coil spring or another spring (for example, a leaf spring).
The spring constant (that is, the support spring constant k2) of the spring 26 (disc spring laminated body) is set so that the support force F of the intermediate bearing 7 as a whole is within the set load range RF in the set height range RH. Yes.

In this example, three sets of springs 26 are sandwiched between the upper fixing plate 12 and the lower fixing plate 14. However, the present invention is not limited to this configuration, and as a whole, it is sufficient that the support force F is set so as to be within the set load range RF in the set height range RH.

For example, as shown in FIGS. 3B and 4, when the intermediate bearing 7 is supported by a pair of left and right bearing support devices 10, and each bearing support device 10 includes three sets of springs 26, the springs 26 are connected to both sides. It will be equipped with 6 places. In this case, the spring constant (hereinafter referred to as “individual spring constant”) k3 of the spring 26 at one place is as follows.
Individual spring constant k3 = support spring constant k2 / 6 = 37 / 6≈about 6.2 kN / mm

According to the present invention described above, the total spring constant k is set so that the supporting force F of the intermediate bearing 7 is within the set load range RF in the set height range RH. Therefore, even if the bearing height is displaced from the installation height due to temperature change or external force after installation of the intermediate bearing 7, the bearing load (supporting force F of the intermediate bearing 7) is automatically adjusted within the set load range RF. can do.

Also, since no control device is used, the bearing load (supporting force F of the intermediate bearing 7) can be automatically adjusted within the set load range RF without being affected by power failure or noise.

4, the bearing support device 10 further includes bearing height position

alarm position sensors

27A and 27B, a bearing height monitoring clearance sensor 28, and a jack bolt 29.

In this example, the position sensor 27A detects the lower limit of the set height range RH, and the position sensor 27B detects the upper limit of the set height range RH. The

position sensors

27A and 27B are, for example, limit switches, proximity switches, laser sensors, ultrasonic sensors, and the like.
With this configuration, an alarm can be output at the lower limit or the upper limit of the set height range RH.

The gap sensor 28 detects a gap interval between the upper fixing plate 12 and the lower fixing plate 14. The gap sensor 28 is, for example, a laser sensor, an ultrasonic sensor, or the like.
By providing the gap sensors 28 at a plurality of locations (for example, 4 locations), it is possible to always grasp the support state of the intermediate shaft 6.

The jack bolt 29 is screwed into the upper fixing plate 12 or the lower fixing plate 14 and presses the upper fixing plate 12 upward against the lower fixing plate 14. In this example, the jack bolt 29 is a bolt that is screwed into a female screw hole penetrating the upper fixing plate 12.
With this configuration, the height of the intermediate shaft 6 can be manually adjusted when the urging device 18 is damaged.

5A and 5B are principle diagrams of the second embodiment of the present invention.
As a specific example, the set load range RF, the planned installation load, and the set height range RH are the same as in the first embodiment.

FIG. 5A is a spring characteristic diagram required for the support portion that supports the intermediate bearing 7. In this figure, the horizontal axis x [mm] and the vertical axis F [kN] are the same as in the first embodiment.
In this figure, the solid line indicates the total spring constant k = 25.5 kN / mm, and the broken line indicates the total spring constant k = 85 kN / mm. In the second embodiment, the total spring constant can be adjusted in the range of k = 25.5 to 85 kN / mm.

FIG. 5B is a schematic diagram of a support portion that supports the intermediate bearing 7. In this figure, in the bearing support device 10 of the present invention, an urging device 18 having a support spring constant k2 and a displacement speed limiting device 30 for moving resistance f are arranged in parallel on the bearing base 11.
Since the bearing stand 11 and the bearing support device 10 are positioned in series vertically, the following relational expressions (4) and (5) are established. Here, x1 is the displacement of the bearing stand 11, and x2 is the displacement of the bearing support device 10.

F × x = F × x1 = (F−f) × x2 (4)
x = x1 + x2 (5)
Equation (6) is derived from Equations (4) and (5).
1 / k = 1 / k1 + (1-f / F) / k2 (6)

From equation (6), k2 = 37 kN / mm is obtained when k = 25.5 kN / mm, k1 = 85 kN / mm, and f = 0.
Further, when k = 25.5 kN / mm, k1 = 85 kN / mm, and f = F, k2 = 85 kN / mm is obtained.

That is, in FIG. 5A, when f / F is sufficiently small, the total spring constant k≈25.5 kN / mm, and when f / F is close to 1, the total spring constant k≈85 kN / mm. Therefore, the total spring constant k can be variably adjusted according to the magnitude of f / F (ie, f).

The displacement speed limiting device 30 has a function of limiting the displacement speed from the installation height (x = 0) of the intermediate bearing 7.
With this configuration, after the intermediate bearing 7 is installed, when the bearing height is displaced from the installation height in a long cycle (for example, a cycle of 1 hour or more, such as a change in draft) due to a temperature change or an external force, a displacement speed limit is set. The device 30 can follow the displacement with a small movement resistance f.

Further, when the intermediate bearing 7 is displaced by a vertical movement of a short cycle (for example, a cycle of 10 seconds or less), such as a vertical vibration by a main machine (for example, a swing of a crankshaft), the displacement speed limiting device 30 is a damper device. (Or a shock absorber). As a result, vertical vibrations with a short period can be prevented, the life of the spring can be extended, and replacement is unnecessary (maintenance-free).

Furthermore, the displacement speed limiting device 30 preferably has a displacement fixing device (not shown, which will be described later) for fixing the displacement of the intermediate bearing 7.
With this configuration, after the intermediate bearing 7 is installed, the displacement x of the intermediate bearing 7 is fixed after the bearing height is displaced from the installation height due to a change in temperature or the action of an external force to reach a steady state. 7 can be substantially fixed at a position (ie height) suitable for steady state.

FIG. 6 is an enlarged view of part B of FIG.
In this figure, the bearing support device 10 has the displacement speed limiting device 30 described above.
Other configurations are the same as those of the first embodiment.

FIG. 7A is a diagram showing a first embodiment of the displacement speed limiting device 30, and FIG. 7B is a diagram showing a second embodiment of the displacement speed limiting device 30.
7A and 7B, the displacement speed limiting device 30 includes a hydraulic cylinder 32 and a moving speed adjusting device 34.

The hydraulic cylinder 32 is preferably a hydraulic cylinder, and has a piston rod 33 that is sandwiched between the upper fixing plate 12 and the lower fixing plate 14 and follows the movement of the upper fixing plate 12 relative to the lower fixing plate 14. In this example, the piston rod 33 is fixed to the upper fixing plate 12 with, for example, a bolt 31a, and the main body of the hydraulic cylinder 32 is fixed to the lower fixing plate 14 with, for example, a bolt 31b.
Conversely, the piston rod 33 may be fixed to the lower fixing plate 14 and the main body of the hydraulic cylinder 32 may be fixed to the upper fixing plate 12.

In FIG. 7A, the hydraulic cylinder 32 is a ram cylinder, and hydraulic fluid (for example, hydraulic fluid) is supplied to only one (head side) of the piston rod 33 (that is, the ram).
In FIG. 7B, the hydraulic cylinder 32 is a normal hydraulic cylinder that can move up and down, and hydraulic fluid is supplied to both the head side and the rod side.

The moving speed adjusting device 34 adjusts the moving speed of the piston rod 33.

In FIG. 7A, the moving speed adjustment device 34 is a first flow rate adjustment valve 37 A provided in a first connection pipe 36 A that communicates the head side of the hydraulic cylinder 32 and the hydraulic fluid tank 35.
The hydraulic fluid in the hydraulic fluid tank 35 is held at a constant pressure (for example, atmospheric pressure).
The first flow rate adjustment valve 37A is, for example, a needle valve or an orifice for flow rate adjustment, and controls the flow rate (that is, the flow rate) flowing through the first connection pipe 36A to adjust the moving speed of the piston rod 33.

With this configuration, when the bearing height is displaced downward with a long cycle (for example, a cycle of 1 hour or more) after the intermediate bearing 7 is installed, the pressure (positive pressure) generated in the hydraulic cylinder 32 is low. The rod 33 follows this displacement with a small movement resistance f. Further, when displacing upward in a long cycle, the piston rod 33 rises following the movement of the upper fixing plate 12 by the urging force of the spring 26, and the pressure (negative pressure) generated in the hydraulic cylinder 32 at this time ) Is also low, the piston rod 33 follows this displacement with a small movement resistance f.

Further, when the intermediate bearing 7 is displaced by the vertical movement of a short cycle (for example, a cycle of 10 seconds or less), the pressure (positive pressure) generated in the hydraulic cylinder 32 when displaced downward is increased. Therefore, the moving speed adjusting device 34 functions as a damper device (or shock absorber), and vertical vibrations with a short period can be effectively prevented.

In FIG. 7B, the moving speed adjusting device 34 is a second flow rate adjusting valve 37B provided in a second connecting pipe 36B that communicates the head side and the rod side of the hydraulic cylinder 32.
The second flow rate adjusting valve 37B is, for example, a needle valve or an orifice for adjusting the flow rate, and controls the flow rate (that is, the flow rate) flowing through the second connection pipe 36B to adjust the moving speed of the piston rod 33.
Further, in this example, the moving speed adjusting device 34 has a fixed throttle 38 provided in the third connection pipe 36 C that communicates the second connection pipe 36 B and the hydraulic fluid tank 35. The fixed throttle 38 controls the flow rate (that is, the flow velocity) flowing through the third connection pipe 36C to be smaller than that of the second connection pipe 36B, and compensates for excess and deficiency of hydraulic fluid on the head side and the rod side of the hydraulic cylinder 32. Instead of the fixed throttle 38, a needle valve for adjusting the flow rate or an orifice may be used.

With this configuration, after the intermediate bearing 7 is installed, the piston rod 33 can follow the displacement with a small movement resistance f when the bearing height is displaced vertically with a long period (for example, a period of 1 hour or more). it can.
Further, when the intermediate bearing 7 is displaced by a vertical movement of a short cycle (for example, a cycle of 10 seconds or less), the moving speed adjustment device 34 functions as a damper device (or a shock absorber) to prevent a short cycle of vertical vibration. can do.

In FIG. 7A, the moving speed adjustment device 34 has a remote control valve 39 provided in a first connection pipe 36 A that communicates the head side of the hydraulic cylinder 32 and the hydraulic fluid tank 35.
In FIG. 7B, the moving speed adjusting device 34 has a remote control valve 39 provided in a second connection pipe 36 B that communicates the head side and the rod side of the hydraulic cylinder 32.
The remote control valve 39 is, for example, an electromagnetic valve, and is configured so that the first connection pipe 36A can be fully closed by remote control. The remote control valve 39 corresponds to the displacement fixing device described above.

With this configuration, after the intermediate bearing 7 is installed, the remote control valve 39 is fully closed by a command from the remote control room after the bearing height is displaced from the installation height due to a change in temperature or the action of external force and becomes a steady state. can do. Thereby, the displacement of the piston rod 33, that is, the displacement of the intermediate bearing 7 can be fixed, and the intermediate bearing 7 can be substantially fixed to the bearing base 11 at a position (that is, height) suitable for the steady state.

Further, with the configuration including the displacement speed limiting device 30, when the bearing height is displaced with a long cycle (for example, a cycle of 1 hour or more) after the intermediate bearing 7 is installed, the piston rod 33 has a small movement resistance f. It can follow the displacement.
Further, when the intermediate bearing 7 is displaced by a vertical movement of a short cycle (for example, a cycle of 10 seconds or less), the moving speed adjustment device 34 functions as a damper device (or a shock absorber) to prevent a short cycle of vertical vibration. can do.

Further, according to the configuration of the present invention, the following accompanying effects can be obtained.
(1) The load balance of each bearing can be automatically adjusted to improve reliability.
In other words, by providing a bearing support device 10 having a spring characteristic corresponding to the relative height displacement between the bearing (intermediate bearing 7) and the bearing base 11, an automatic load balance is ensured. System reliability can be improved.

(2) The seizure damage of the bearing metal can be prevented.
When the relative height displacement between the bearing (intermediate bearing 7) and the bearing base 11 becomes large, if a part of the bearing load exceeds the allowable load, metal seizure damage may occur. However, by providing the bearing support device 10, it is possible to prevent seizure damage of the bearing metal by automatically adjusting the balance of each bearing load.

(3) Metal peeling due to fretting of bearing metal can be prevented.
If the relative bearing height becomes too high and the bearing load becomes too small, the bearing support force will decrease, causing fretting of the bearing metal part, peeling of the bearing metal, and serious system trouble. Cause. However, by providing the bearing support device 10, it is possible to prevent metal peeling due to fretting by automatically adjusting the balance of each bearing load.

(4) Stable bearing support can be achieved by suppressing dynamic fluctuating force due to external force applied to the shaft system.
As shown in FIG. 6, between the intermediate bearing 7 and the bearing base 11, the spring 26 (disc spring laminated body) and the displacement speed limiter 30 are provided, so that the entire bearing can be prevented from shaking and vibrating. Stable operation is possible.
Further, as shown in FIGS. 7A and 7B, the

connection pipes

36A and 36B of the hydraulic cylinder 32 are equipped with flow

rate adjusting valves

37A and 37B (for example, needle valves) that can adjust the flow rate in consideration of the cycle of the fluctuating external force. Thus, more stable operation can be performed.

(5) Along with the flow

rate adjusting valves

37A and 37B (needle valves) for adjusting the flow rate, a remote control valve 39 (as shown in FIGS. 7A and 7B is provided so that the flow of hydraulic oil can be controlled remotely from the control room. Equipped with a solenoid valve), it can be controlled according to the system movement.

(6) In a device in which the shaft system is installed at each bearing and then the height of each bearing mounting base is displaced due to a disturbance factor, the bearing load is unbalanced and the bearing is damaged. By using it, the bearing can be prevented from being damaged, and the reliability of the apparatus can be improved.

(7) Even when the relative displacement between the bearing and the bearing mounting base is large, the installation and adjustment can be easily performed, and the readjustment after the installation is not required, so that the maintenance can be made free.

The present invention is not limited to the above-described embodiment, and various changes can be made without departing from the scope of the present invention.

E Center position in the axial direction of the bearing for the main engine F Bearing force of the intermediate bearing f Movement resistance RF Set load range RH Set height range k Total spring constant k1 Receiving spring constant k2 Support spring constant k3 Individual spring constant x From installation height Displacement x1 Bearing stand displacement x2 Bearing support device displacement ZZ Axle 1 Ship 1a Stern

1b Ship bottom

1c Double floor 2 Propeller 3 Stern tube 4 Stern tube bearing 5 Propeller shaft 6 Intermediate shaft 7 Intermediate bearing 7a Bearing 7b Bearing Case 7c Leg 7d Horizontal support surface 8 Main machine output shaft 9 Main machine bearing 10 Self-alignment type bearing support device (bearing support device)
10a Side guide 11 Bearing base

11a Support base

11b Adjustment liner 12 Upper fixing plate 14 Lower fixing plate 16 Guide device 18 Biasing device 20 Lower limit stopper 21 Stopper fixing bolt 22 Upper limit bolt 24 Extension guide 26 Spring (disc spring laminated body)
27A, 27B Position sensor 28 Gap sensor 29 Jack bolt 30 Displacement

speed limiting device

31a, 31b Bolt 32 Hydraulic cylinder 33 Piston rod 34 Moving speed adjustment device 35 Hydraulic fluid tank 36A First connection pipe 36B Second connection pipe 36C Third connection Pipe 37A First flow rate adjustment valve 37B Second flow rate adjustment valve 38 Fixed throttle 39 Remote control valve

Claims

A self-alignment type bearing support device that supports an intermediate bearing that rotatably supports an intermediate portion of an intermediate shaft that extends in a horizontal direction and whose front and rear ends are rotatably supported,
An overall spring constant for displacement from the installation height of the intermediate bearing;
The self-alignment type bearing support device, wherein the total spring constant is set so that a support force of the intermediate bearing is within a set load range in a set height range.
2. The self-alignment type bearing support device according to claim 1, further comprising a displacement speed limiting device that limits a displacement speed of the intermediate bearing from the installation height.
The self-alignment type bearing support device according to claim 2, wherein the displacement speed limiting device includes a displacement fixing device that fixes the displacement.
An upper fixing plate to which the intermediate bearing is fixed;
A lower fixing plate fixed to the fixing part;
A guide device that guides the upper fixing plate relative to the lower fixing plate so as to move up and down within the set height range;
An urging device sandwiched between the upper fixing plate and the lower fixing plate and urging the upper fixing plate upward with respect to the lower fixing plate;
2. The self-alignment type bearing support according to claim 1, wherein the total biasing force of the biasing device is set so that the support force of the intermediate bearing is within the set load range in the set height range. apparatus.
The biasing device has a spring sandwiched between the upper fixing plate and the lower fixing plate,
The self-alignment type bearing support device according to claim 4, wherein the spring constant of the spring is set so that the support force of the intermediate bearing as a whole is within the set load range in the set height range. .
An upper fixing plate to which the intermediate bearing is fixed;
A lower fixing plate fixed to the fixing portion,
The displacement speed limiting device is a hydraulic cylinder having a piston rod that is sandwiched between the upper fixed plate and the lower fixed plate and follows the movement of the upper fixed plate with respect to the lower fixed plate;
The self-alignment type bearing support device according to claim 2, further comprising a moving speed adjusting device that adjusts a moving speed of the piston rod.
The self-alignment type bearing support device according to claim 6, wherein the moving speed adjusting device is a first flow rate adjusting valve provided in a first connecting pipe that communicates a head side of the hydraulic cylinder and a hydraulic fluid tank. .
The self-alignment type bearing support device according to claim 6, wherein the moving speed adjusting device is a second flow rate adjusting valve provided in a second connecting pipe communicating the head side and the rod side of the hydraulic cylinder.
The moving speed adjusting device is provided in a first connection pipe that communicates the head side of the hydraulic cylinder and the hydraulic fluid tank, or a second connection pipe that communicates the head side and the rod side of the hydraulic cylinder, The self-alignment type bearing support device according to claim 6, further comprising a remote control valve capable of fully closing the first connection pipe or the second connection pipe by remote control.
The guide device is sandwiched between the upper fixing plate and the lower fixing plate, and at the lower limit of the set height range, a lower limit limiting stopper for preventing the upper fixing plate from moving downward,
An upper limit bolt that prevents the upper fixing plate from moving upward at the upper limit of the set height range;
The self-alignment type bearing support device according to claim 4, further comprising: an extension / contraction guide that guides the extension / contraction of the urging device in the vertical direction.
A position sensor for bearing height position alarm capable of detecting the lower limit or the upper limit of the set height range;
The self-alignment type bearing support device according to claim 10, further comprising a bearing height monitoring gap sensor capable of detecting a gap gap between the upper fixing plate and the lower fixing plate.
The self-alignment type bearing support device according to claim 4, further comprising a jack bolt that is screwed into the upper fixing plate or the lower fixing plate and presses the upper fixing plate upward with respect to the lower fixing plate.