CN108603527B - Self-alignment type bearing supporting device - Google Patents
Self-alignment type bearing supporting device Download PDFInfo
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- CN108603527B CN108603527B CN201680082003.1A CN201680082003A CN108603527B CN 108603527 B CN108603527 B CN 108603527B CN 201680082003 A CN201680082003 A CN 201680082003A CN 108603527 B CN108603527 B CN 108603527B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/02—Sliding-contact bearings
- F16C23/04—Sliding-contact bearings self-adjusting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Support Of The Bearing (AREA)
Abstract
Self-alignment type bearing supporting device (10) supports intermediate bearing (7), and aforementioned intermediate bearing (7) can rotatably support the middle part of jackshaft (6), and intermediate bearing (7) is horizontally extending, and front-end and back-end can rotatably be supported.Self-alignment type bearing supporting device (10) has the synthesis spring constant (k) of displacement (x) relative to intermediate bearing (7) away from mounting height.Comprehensive spring constant (k) is configured to, and the supporting force (F) of intermediate bearing (7) is in setting height range (RH) in setting load range (RF).In addition, having the velocity of displacement limits device (30) of velocity of displacement of limitation intermediate bearing (7) from mounting height.Velocity of displacement limits device (30) has the displacement of the displacement of fixed intermediate bearing (7) (x) fixed device (Remote control valve (39)).
Description
Technical field
The present invention relates to adjust the height and position of bearing to the self-alignment type bearing supporting device of position appropriate.
Background technique
Device is adjusted as the alignment for adjusting the height and position of bearing to position appropriate, such as proposes patent document
1、2。
In " the bearing alignment automatic regulating apparatus " of patent document 1, has the setting value letter for generating bearing centre position
Number duty setting signal generator, the variation of measuring state amount state measuring device, calculate the arithmetic unit of deviation, basis
The position of bearings that deviation adjusts bearing centre position adjusts device.
" the alignment adjustment device " of patent document 2 is sensed by the parameter monitor of the state of axis, is monitored according to parameter
The monitoring amount of device carries out the arithmetic unit of operation to control amount, according to by the actuator structure of the control amount adjustment shaft alignement of operation
At.As parameter monitor, using the displacement meter relative to shafting, shaft vibration is found out according to the detection limit from displacement meter, is
Inhibit the alignment that shafting is adjusted by shaft vibration that arithmetic unit finds out.
Patent document 1: Japanese Unexamined Patent Publication 7-317757 bulletin.
Patent document 2: Japanese Unexamined Patent Publication 2002-213522 bulletin.
Have to support the rotary shaft of torque transfer and the case where there are three above bearings is set.In this case, each
Bearing considers the balance of respective bearing load under certain condition (such as cold conditions) and is mounted.But actual use
Under situation (such as tropical conditions), due to the effect (such as variation of drinking water) of temperature change or external force, each bearing height occurs
Displacement, significantly deviates from the counterweight balance of plan sometimes.
If bearing load becomes excessive, the face pressure of metal increases, and has the case where generating hot sticky damage, in addition, if bearing
Load becomes too small, then axis restraint declines, and the fretting in the bearing metal portion generated due to movement occurs, there is generation axis
The case where holding the removing of metal.
In the biggish situation of the displacement of each bearing height, there are above-mentioned risk, the problem of becoming shafting will be because.
In addition, control device (arithmetic unit, arithmetic unit etc.) is indispensable in the scheme of above-mentioned patent document 1,2
It is few, have due to power failure, noise and a possibility that loss of function.
Summary of the invention
The present invention makes to solve the above-mentioned problems.That is, the purpose of the present invention is to provide a kind of self-alignment types
Bearing supporting device, aforementioned self-alignment type bearing supporting device is after the installation of bearing, even if due to temperature change or external force
Effect and in the case that bearing height is subjected to displacement, also can not by have a power failure, noise is influenced in the case where by bearing
Load automatically adjusts in appropriate range.
According to the present invention, a kind of self-alignment type bearing supporting device, aforementioned self-alignment type bearing supporting device bearing are provided
Intermediate bearing, aforementioned intermediate bearing can rotatably support the middle part of jackshaft, and aforementioned jackshaft is horizontally extending,
Its front-end and back-end can rotatably be supported, and have the synthesis spring of the displacement relative to aforementioned intermediate bearing away from mounting height
Constant, aforementioned comprehensive spring constant are configured to, and the supporting force of aforementioned intermediate bearing carries in setting height range in setting
Within the scope of lotus.
With the velocity of displacement limits device for limiting velocity of displacement of the aforementioned intermediate bearing from aforementioned mounting height.
Aforementioned displacements speed limiting device has the fixed device of the displacement of fixed aforementioned displacements.
Have top tie plate, lower tie plate, guide device, force application apparatus, aforementioned top tie plate is fixed in aforementioned
Between bearing, aforementioned lower tie plate is fixed on fixed part, and aforementioned guide device is by aforementioned top tie plate relative under aforementioned
Portion's fixed plate can guide up or down in aforementioned setting height range, and aforementioned force application apparatus is held on aforementioned top tie plate
Between aforementioned lower tie plate, aforementioned top tie plate is exerted a force upwards relative to aforementioned lower tie plate, aforementioned force
The total force of device is configured to, and the aforementioned supporting force of aforementioned intermediate bearing is set within the scope of aforementioned setting height in aforementioned
Determine in load range.
Aforementioned force application apparatus has the spring being held between aforementioned top tie plate and aforementioned lower tie plate, aforementioned bullet
The spring constant of spring is configured to, and as a whole, the aforementioned supporting force of aforementioned intermediate bearing is within the scope of aforementioned setting height
In in aforementioned setting load range.
Have the top tie plate of fixed aforementioned intermediate bearing and is fixed on the lower tie plate of fixed part, aforementioned displacements
There is speed limiting device hydraulic pressure cylinder and movement speed to adjust device, and aforementioned hydraulic pressure cylinder is held on aforementioned top and fixes
Between plate and aforementioned lower tie plate, there is the piston for following movement of the aforementioned top tie plate relative to aforementioned lower tie plate
Bar, aforementioned movement speed adjustment device adjust the movement speed of aforementioned piston rod.
Aforementioned movement speed adjustment device is to be set to be connected to the lid side of aforementioned hydraulic pressure cylinder with working liquid tank the 1st
1st flow rate regulating valve of connecting tube.
Aforementioned movement speed adjustment device is to be set to the 2nd connection for being connected to the lid side of aforementioned hydraulic pressure cylinder with bar side
2nd flow rate regulating valve of pipe.
Aforementioned movement speed adjustment device is set to be connected to the lid side of aforementioned hydraulic pressure cylinder with working liquid tank the 1st and connects
Adapter tube or the 2nd connecting tube that the lid side of aforementioned hydraulic pressure cylinder be connected to bar side, with can be by aforementioned 1st connecting tube or preceding
State the Remote control valve that the 2nd connecting tube completely closes in a manner of remotely controlling.
Aforementioned guide device has lower limit limit stop, ceiling restriction bolt, flexible guiding piece, and aforementioned minimum limitation stops
Moving part is held between aforementioned top tie plate and aforementioned lower tie plate, prevents aforementioned top tie plate in aforementioned setting height
The lower limit of range moves downwards, and aforementioned ceiling restriction bolt prevents aforementioned top tie plate in the upper of aforementioned setting height range
Limit is moved upward, and aforementioned flexible guiding piece guides the flexible of the up and down direction of aforementioned force application apparatus.
The gap sensor of position sensor and bearing height monitoring with the alarm of bearing height position, aforementioned axis
Hold height and position alarm position sensor be able to detect aforementioned setting height range aforementioned minimum or the aforementioned upper limit, it is aforementioned
The gap sensor of bearing height monitoring is able to detect the clearance gap of aforementioned top tie plate and aforementioned lower tie plate.
With lifting bolt, aforementioned lifting bolt is threadedly engaged with aforementioned top tie plate or aforementioned lower tie plate, phase
Aforementioned lower tie plate is pushed aforementioned top tie plate upwards.
Invention effect
According to aforementioned present invention, set comprehensive spring constant, so that the supporting force of intermediate bearing is within the scope of setting height
In setting load range.Therefore, after the installation of bearing, though due to temperature change or external force effect and bearing height
It, also can be automatic in setting load range by bearing load (supporting force of intermediate bearing) in the case where mounting height displacement
Ground adjustment.
In addition, using control device, thus can not by have a power failure, noise is influenced in the case where by bearing load (in
Between bearing supporting force) setting load range in automatically adjust.
Detailed description of the invention
Fig. 1 is the explanatory diagram for having the rotary shaft of self-alignment type bearing supporting device of the invention.
Fig. 2A is spring performance figure required by supporting the supporting part of intermediate bearing.
Fig. 2 B is the schematic diagram for supporting the supporting part of intermediate bearing.
Fig. 3 A is the portion the A enlarged drawing of Fig. 1.
Fig. 3 B is the side view of Fig. 3 A.
Fig. 4 is the portion the B enlarged drawing of Fig. 3 A, is the 1st embodiment figure of bearing supporting device.
Fig. 5 A is spring performance figure required by supporting the supporting part of intermediate bearing.
Fig. 5 B is the schematic diagram for supporting the supporting part of intermediate bearing.
Fig. 6 is the portion the B enlarged drawing of Fig. 3 A, is the 2nd embodiment figure of bearing supporting device.
Fig. 7 A is the 1st embodiment figure of velocity of displacement limits device.
Fig. 7 B is the 2nd embodiment figure of velocity of displacement limits device.
Specific embodiment
Based on attached drawing, embodiments of the present invention will be described.In addition, identical to common part mark in the various figures
Appended drawing reference, the repetitive description thereof will be omitted.
Fig. 1 is that have self-alignment type bearing supporting device 10 of the invention (following to be simply referred to as " bearing supporting device 10 ")
The explanatory diagram of rotary shaft.
In the figure, appended drawing reference 1 is ship, and appended drawing reference 1a is stern, and appended drawing reference 1b is hull bottom, appended drawing reference 1c
It is dual ground, appended drawing reference 2 is propeller, and appended drawing reference 3 is stern tube, and appended drawing reference 4 is stern tubular shaft, appended drawing reference
5 be propeller shaft, and appended drawing reference 6 is jackshaft, and appended drawing reference 7 is intermediate bearing, and appended drawing reference 8 is host output shaft, attached drawing
Label 9 is host bearing.
Propeller shaft 5, jackshaft 6 and host output shaft 8 are rotated centered on horizontally extending axle center Z-Z.
Axle center Z-Z is not limited to trunnion axis, is also possible to relative to horizontally tilted sloping shaft.
In addition the arrow E in figure indicates the axial center of host bearing 9.
In Fig. 1, the front-end and back-end of jackshaft 6 can rotate twelve Earthly Branches by host bearing 9 and stern tubular shaft 4 respectively
It holds.In addition, stern tubular shaft 4 is fixed on the hull of stern 1a.
Intermediate bearing 7 can rotatably support the middle part of jackshaft 6.The position of middle part is preferably jackshaft 6
The center of length direction is but it is also possible to be other positions.
Bearing supporting device 10 of the invention is installed on pedestal 11, is the device for supporting intermediate bearing 7.11 quilt of pedestal
It is linked to dual ground 1c securely, there is high rigidity.
In addition, the shell of ship 1, i.e. stern 1a, hull bottom 1b and dual ground 1c are reinforced muscle reinforcing, with high rigid
Property.
In the following description, as an example, by the spring constant k1 of pedestal 11, (the following are " adapting table spring constants
K1 ") be set as 85kN/mm, it is contemplated that the spring constant of the shell of ship 1 than the big units of pedestal 11 more than.
Previous construction does not use bearing supporting device 10 of the invention, and the intermediate bearing 7 of Fig. 1 is directly fixed on hull
It constructs (i.e. pedestal 11).As previous, intermediate bearing 7 is directly fixed on pedestal 11 in the case where installing, in
Between the influence coefficient (load change of the height displacement relative to 1mm) relative to the relative displacement x with hull at bearing 7 be
The biggish value of for example, about 85 (kN/mm).
Therefore, in the biggish situation of displacement x of the mounting height away from intermediate bearing 7, intermediate bearing 7 or host bearing
9 bearing load is more than to allow bearing load, a possibility that damage.
For example, it is assumed that the load range (hereinafter referred to as " setting load range RF ") of the supporting force F of intermediate bearing 7 as 12 ~
The plan supporting force F (the following are " plan installed loads ") of intermediate bearing 7 when installing is set as 63kN by 151kN.
In the case that the displacement x (direction that intermediate bearing 7 declines) of intermediate bearing 7 is 1mm, the supporting force F of intermediate bearing 7
For 63kN-85 (kN/mm) × 1mm=-22kN.I.e. in this case, intermediate bearing 7 is lifted from pedestal 11, in jackshaft 6 not by
The state of bearing generates the damage due to fretting in the metal portion of intermediate bearing 7.
Fig. 2A and Fig. 2 B is the schematic diagram of the 1st embodiment of the invention.
As concrete example, if setting load range RF as 12 ~ 151kN, it is 63kN that installed load is drawn in design, if setting height
Range RH (displacement range of the intermediate bearing 7 away from mounting height) is the range of the upper limit (x=-2mm) to lower limit (x=2mm).
Relative displacement is envisioned for twice by displacement x of the setting height range RH relative to above-mentioned 1mm with allowing some leeway.
Fig. 2A is spring performance figure required by supporting the supporting part of intermediate bearing 7.In the figure, during horizontal axis x [mm] is
Between displacement (downward distance) of the bearing 7 away from mounting height (x=0), longitudinal axis F [kN] is the supporting force of intermediate bearing 7.
The synthesis spring constant k for meeting the spring performance of this is k=25.5kN/mm.
Fig. 2 B is the schematic diagram for supporting the supporting part of intermediate bearing 7.In the figure, 10 quilt of bearing supporting device of the invention
It is held between intermediate bearing 7 and pedestal 11.The spring constant k2 of bearing supporting device 10 is referred to as below and " it is normal to support spring
Number k2 ".
Pedestal 11 and bearing supporting device 10 are located at upper and lower concatenated position, thus relational expression below (1) (2) at
It is vertical.Here, x1 is the displacement of pedestal 11, and x2 is the displacement of bearing supporting device 10.
F × x=F × x1=F × x2 (1)
X=x1+x2 (2)
From formula (1) (2) deriving (3).
1/k=1/k1+1/k2 (3)
According to formula (3), in the case where k=25.5kN/mm, k1=85kN/mm, bearing spring constant k2=is obtained
37kN/mm。
As described above, bearing supporting device 10 of the invention has relative to intermediate bearing 7 away from mounting height (x=0)
The synthesis spring constant k of displacement x.Synthesis spring constant k is configured to, and the supporting force F of intermediate bearing 7 is in height setting range
In (such as x=-2 ~ 2mm) in preset setting load range RF (such as F=12 ~ 151kN).
That is, in the above example, the spring performance of bearing supporting device 10 is set, so that bearing spring constant k2 is k2
=37kN/mm.As a result, as shown in Figure 2 A, after the installation of intermediate bearing 7 due to temperature change or external force effect and bearing is high
In the case where degree displacement, also bearing load (the supporting force F of intermediate bearing 7) can automatically be adjusted in setting load range RF
It is whole.
Fig. 3 A is the portion the A enlarged drawing of Fig. 1, and Fig. 3 B is the side view of Fig. 3 A.
In this embodiment, intermediate bearing 7 has the bearing cage of the bearing 7a of bearing jackshaft 6, the outer peripheral surface for surrounding bearing 7a
The foot 7c of the lower surface of 7b, bearing support cover 7b.
In addition, foot 7c has a pair of of horizontal support surface 7d in the lower surface at width direction both ends.
In addition, in this embodiment, bearing 7a is the bearing of journals (sliding bearing), however, the present invention is not limited thereto is also possible to it
His bearing (such as rolling bearing).
In addition, in this embodiment, pedestal 11 has pair of right and left supporting station 11a and adjustment liner 11b.
A pair of of supporting station 11a is located in the position of the width direction two sides interval of axle center Z-Z.Under supporting station 11a
Dual ground 1c is fixed on via adjustment liner 11b in surface.Adjustment liner 11b is made of multiple plates or conical plate, can be incited somebody to action
The upper level of supporting station 11a is finely tuned.
In addition, the fine tuning of the upper level for pedestal 11, preferably has lifting in the lower surface of supporting station 11a
Bolt (not shown).
The upper surface of supporting station 11a is horizontal plane, and bearing bearing is clamped between the horizontal support surface 7d of intermediate bearing 7
Device 10.
In this embodiment, a pair of bearings supporting arrangement 10 is held in upper surface and the jackshaft of pair of right and left supporting station 11a
It holds between 7 horizontal support surface 7d.
In addition, bearing supporting device 10 is not limited to a pair, it can be independent one and be also possible to three or more.
Fig. 4 is the portion the B enlarged drawing of Fig. 3 A, is the 1st embodiment figure of bearing supporting device 10.
In the figure, bearing supporting device 10 has top tie plate 12, lower tie plate 14, guide device 16 and force
Device 18.
Top tie plate 12 is horizontal heavy wall plate in this embodiment, and intermediate bearing 7 is for example fixed on by bolt or nut
The upper surface of top tie plate 12.
Lower tie plate 14 is in this embodiment horizontal heavy wall plate, and fixed part is for example fixed on by bolt or nut in lower end
Divide (being pedestal 11 in the example).In addition, fixed part is not limited to pedestal 11, as long as having high rigidity to be also possible to ship
A part of 1 shell.
In addition, in figure 3b, being separately installed with side in the width direction outer surface of pair of right and left bearing supporting device 10
Guiding piece 10a.
In this embodiment, top tie plate 12 is fixed in the upper end of side guides 10a, extends downward, lower end
Extend along the width direction outer surface of lower tie plate 14.Under on the contrary, side guides 10a is fixed on
Portion's fixed plate 14.
According to this structure, by a pair of of side guides 10a, moving up and down for intermediate bearing 7 can be guided, and can be prevented
The only movement in the port and starboard direction (width direction) of intermediate bearing 7.
In Fig. 4, guide device 16 is by top tie plate 12 relative to lower tie plate 14 in setting height range RH (figure
X=-2 ~+2mm in 2A) it can guide up or down.
Setting height range RH can (be in this embodiment host bearing 9, stern tube according to the bearing of bearing jackshaft 6
Bearing 4 and intermediate bearing 7) permission bearing load and by the behaviour in service (such as effect of temperature change or external force) after installing
The relative displacement for each bearing height imagined is preset.
Guide device 16 has lower limit limit stop other than above-mentioned a pair of of side guides 10a in this embodiment
20, retainer fixing bolt 21, ceiling restriction bolt 22 and flexible guiding piece 24.
Lower limit limit stop 20 is held between top tie plate 12 and lower tie plate 14, prevents top tie plate
12 move downwards in the lower limit (x=2mm) of setting height range RH.Lower limit limit stop 20 is hollow cylinder in this embodiment
Shape component.
Retainer fixing bolt 21 passes through the centre bore of lower limit limit stop 20, and lower tie plate is fixed in lower end
14, the head of bolt is separated from the upper surface of top tie plate 12 to be fixed with gap.Retainer fixing bolt 21 keeps lower limit limit
Prevent the position of moving part 20.
Ceiling restriction bolt 22 prevents top tie plate 12 from moving upwards in the upper limit (x=-2mm) of setting height range RH
It is dynamic.Ceiling restriction bolt 22 is the bolt across the centre bore of force application apparatus 18 in this embodiment, and lower tie plate is fixed in lower end
14, the head of bolt is separated from the upper surface of top tie plate 12 to be fixed with gap.
Flexible guiding piece 24 guides the flexible of the up and down direction of force application apparatus 18.Flexible guiding piece 24 is to surround in this embodiment
The concentric double pipe of force application apparatus 18, a side are fixed on top tie plate 12, and another party is fixed on lower tie plate 14.
By above-mentioned guide device 16, can relative to lower tie plate 14 by top tie plate 12 in setting height model
Enclosing RH can guide up or down.
In Fig. 4, force application apparatus 18 is held between top tie plate 12 and lower tie plate 14, solid relative to lower part
Fixed board 14 exerts a force top tie plate 12 upwards.
The total force (whole active force) of force application apparatus 18 is set to, and the supporting force F of intermediate bearing 7 is in setting height
In range RH (x=-2 ~+2mm) in the setting load range RF being preset.
The permission bearing load of intermediate bearing 7 can be set as maximum value by setting load range RF, in the branch of intermediate bearing 7
Load F is preset in the range of not being negative.Setting is to prevent to the above-mentioned upper limit in the range of supporting force F is not negative
It limits bolt 22 (and retainer fixing bolt 21) and acts on excessive drawing force, intermediate bearing 7 lifts, and loses intermediate bearing 7
Function.
In Fig. 4, force application apparatus 18 has the spring 26 being held between top tie plate 12 and lower tie plate 14.
Spring 26 is the disc spring laminated body that multiple disc springs and multiple plain washers are laminated in this.In addition, spring 26 is not limited to the structure,
It can be helical spring, be also possible to other springs (such as leaf spring).
The spring constant (i.e. bearing spring constant k2) of spring 26 (disc spring laminated body) is configured to, as a whole, intermediate
The supporting force F of bearing 7 is in setting height range RH in setting load range RF.
In this embodiment, 3 groups of springs 26 are held between top tie plate 12 and lower tie plate 14.But the present invention is not
It is limited to the structure, is set to, as a whole, supporting force F is in setting height range RH in setting load range RF.
For example, intermediate bearing 7 is supported by pair of right and left bearing supporting device 10, in each bearing as shown in Fig. 3 B and Fig. 4
In the case that supporting arrangement 10 has 3 groups of springs 26 respectively, spring 26 is equipped at two sides of a ship at 6 positions.In this case, every
Spring constant (the following are " single spring constants ") k3 of the spring 26 at one position is as described below.
Single spring constant k3=supports spring constant k2/6=37/6 ≒ about 6.2kN/mm.
According to the above-mentioned present invention, with the supporting force F of intermediate bearing 7 for setting load range in setting height range RH
Mode set comprehensive spring constant k in RF.Therefore, due to the effect of temperature change or external force after the installation of intermediate bearing 7
And bearing height from mounting height be displaced in the case where, also can by bearing load (the supporting force F of intermediate bearing 7) setting carry
It is automatically adjusted in lotus range RF.
In addition, do not use control device, so can not had a power failure, noise effect in the case where by bearing load (in
Between bearing 7 supporting force F) setting load range RF in automatically adjust.
In Fig. 4, bearing supporting device 10 is also with position sensor 27A, 27B, the axis of bearing height position alarm
Hold the gap sensor 28 and lifting bolt 29 of height monitoring.
In this embodiment, position sensor 27A detects the lower limit of setting height range RH, position sensor 27B detection setting
The upper limit of altitude range RH.Position sensor 27A, 27B are, for example, limit switch, close switch, laser sensor, ultrasonic wave biography
Sensor etc..
According to this structure, alarm can be exported in the lower limit or the upper limit of setting height range RH.
The clearance gap of gap sensor 28 detection top tie plate 12 and lower tie plate 14.Gap sensor 28 is for example
It is laser sensor, ultrasonic sensor etc..
By the way that the gap sensor 28 is set to many places (such as 4 positions), the bearing shape of jackshaft 6 can be grasped
State.
Lifting bolt 29 is threadedly engaged with top tie plate 12 or lower tie plate 14, by top tie plate 12 relative under
Portion's fixed plate 14 pushes upwards.Lifting bolt 29 is connect with the internal thread hole screw thread for penetrating through top tie plate 12 in this embodiment
The bolt of conjunction.
According to this structure, in the case where force application apparatus 18 damages, the height adjustment of jackshaft 6 can manually be carried out.
Fig. 5 A and Fig. 5 B are the schematic diagrams of the 2nd embodiment of the invention.
As concrete example, load range RF, plan installed load and setting height range RH and the 1st embodiment are set
It is identical.
Fig. 5 A is spring performance figure required by supporting the supporting part of intermediate bearing 7.In the figure, horizontal axis x [mm] and vertical
Axis F [kN] is identical as the 1st embodiment.
In the figure, solid line indicates that comprehensive spring constant k=25.5kN/mm, dotted line indicate comprehensive spring constant k=
85kN/mm.In the 2nd embodiment, comprehensive spring constant can be adjusted in the range of k=25.5 ~ 85kN/mm.
Fig. 5 B is the schematic diagram for supporting the supporting part of intermediate bearing 7.In the figure, bearing supporting device 10 of the invention
Support spring constant k2 force application apparatus 18 and moving resistance f velocity of displacement limits device 30 by pedestal 11 side by side
Configuration.
Pedestal 11 and bearing supporting device 10 are located at upper and lower concatenated position, thus relational expression below (4) (5) at
It is vertical.Here, x1 is the displacement of pedestal 11, and x2 is the displacement of bearing supporting device 10.
F × x=F × x1=(F-f) × x2 (4)
X=x1+x2 (5)
From formula (4) (5) deriving (6).
1/k=1/k1+ (1-f/F)/k2 (6)
K2=37kN/mm is obtained in the case where k=25.5kN/mm, k1=85kN/mm, f=0 according to formula (6).
In addition, obtaining k2=85kN/mm in the case where k=25.5kN/mm, k1=85kN/mm, f=F.
That is, in fig. 5, f/F ten divides hour, when comprehensive spring constant k ≒ 25.5kN/mm, f/F are close to 1, comprehensive spring
Constant k ≒ 85kN/mm.It therefore, can (comprehensive spring constant k be variably adjusted by size i.e. f) according to f/F.
Velocity of displacement limits device 30 has the function of limiting velocity of displacement of the intermediate bearing 7 from mounting height (x=0).
According to this structure, after the installation of intermediate bearing 7, due to temperature change or external force effect and bearing height from installation
When height is with longer period (such as variation of drinking water etc., one hour or more period) displacement, velocity of displacement limits device 30
Displacement can be followed with lesser moving resistance f.
In addition, as the up-down vibration as caused by host (such as whirling of crank axle), by shorter period (example
Such as 10 seconds periods below) move up and down in the case that intermediate bearing 7 is displaced, velocity of displacement limits device 30 is used as vibration damping
Device (or buffer) functions.Thereby, it is possible to prevent more short-period up-down vibration, extends the service life of spring, do not need
Replaced (non-maintaining).
In turn, velocity of displacement limits device 30 is preferably with the fixed device of the fixed displacement of the displacement by intermediate bearing 7
(not shown, in aftermentioned explanation).
According to this structure, after the installation of intermediate bearing 7, due to temperature change or external force effect and bearing height from installation
After height displacement becomes standing state, the displacement x of fixed intermediate bearing 7 is suitable thus, it is possible to which intermediate bearing 7 to be actually fixed on
Close the position (i.e. height) of standing state.
Fig. 6 is the portion the B enlarged drawing of Fig. 3 A, is the 2nd embodiment figure of bearing supporting device 10.
In the figure, bearing supporting device 10 has above-mentioned velocity of displacement limits device 30.
Other structures are identical as the 1st embodiment.
Fig. 7 A is the 1st embodiment figure of velocity of displacement limits device 30, and Fig. 7 B is the 2 of velocity of displacement limits device 30
Embodiment figure.
There is velocity of displacement limits device 30 hydraulic pressure cylinder 32 and movement speed to adjust device 34 in Fig. 7 A and Fig. 7 B.
Hydraulic pressure cylinder 32 is preferably oil pressure pressure cylinder, is held between top tie plate 12 and lower tie plate 14,
With the piston rod 33 for following movement of the top tie plate 12 relative to lower tie plate 14.In this embodiment, 33, piston rod
It such as is fixed on top tie plate 12 by bolt 31a, it is solid that the main body of hydraulic pressure cylinder 32 is for example fixed on lower part by bolt 31b
Fixed board 14
Alternatively, it is also possible to which on the contrary, piston rod 33 is fixed on lower tie plate 14, the main body of hydraulic pressure cylinder 32 is consolidated
Due to top tie plate 12.
In fig. 7, hydraulic pressure cylinder 32 is plunger type pressure cylinder, only to a side (lid side) for piston rod 33 (i.e. plunger)
It supplies working solution (such as working oil).
In addition, in figure 7b, hydraulic pressure cylinder 32 is the common oil pressure pressure cylinder that can be moved up and down, working solution by
Lid side and bar side both sides supply.
Movement speed adjusts the movement speed that device 34 adjusts piston rod 33.
In fig. 7, movement speed adjustment device 34 is set to the lid side of hydraulic pressure cylinder 32 and working liquid tank 35
The 1st flow rate regulating valve 37A of 1st connecting tube 36A of connection.
The working solution of working liquid tank 35 keeps certain pressure (such as atmospheric pressure).
1st flow rate regulating valve 37A is, for example, the needle-valve or throttle orifice of flow adjustment, and control is flowed in the 1st connecting tube 36A
Flow (i.e. flow velocity), adjust piston rod 33 movement speed.
According to this structure, after the installation of intermediate bearing 7, bearing height is with (such as one hour or more week in longer period
Phase) when being displaced downwards, it is lower in the pressure (positive pressure) that hydraulic pressure cylinder 32 generates, so piston rod 33 is with lesser mobile resistance
Power f follows the displacement.In addition, due to the active force of spring 26, piston rod 33 is followed when being displaced upwards with the longer period
The movement of portion's fixed plate 12 and rise, the pressure (negative pressure) for resulting from hydraulic pressure cylinder 32 at this time is relatively low, so piston rod 33
The displacement is followed with lesser moving resistance f.
Further, since the feelings that shorter moving up and down for period (such as 10 seconds periods below) and intermediate bearing 7 are displaced
Under condition, the pressure (positive pressure) that the hydraulic pressure cylinder 32 when being displaced downwards generates is got higher.Therefore, movement speed adjustment device 34 is made
It is functioned for vibration absorber (or buffer), the up-down vibration in shorter period can be effectively prevented.
In figure 7b, movement speed adjustment device 34 is to be set to be connected to the lid side of hydraulic pressure cylinder 32 with bar side the
The 2nd flow rate regulating valve 37B of 2 connecting tube 36B.
2nd flow rate regulating valve 37B is, for example, the needle-valve or throttle orifice of flow adjustment, and control is flowed in the 2nd connecting tube 36B
Flow (i.e. flow velocity), adjust piston rod 33 movement speed.
In addition, in this embodiment, movement speed adjustment device 34, which has, to be set to the 2nd connecting tube 36B and working liquid tank 35
The fixed restrictive valve 38 of 3rd connecting tube 36C of connection.Fixed restrictive valve 38 (flows the flow flowed in the 3rd connecting tube 36C
Speed) control at smaller than the 2nd connecting tube 36B, compensates the excessive or insufficient of the lid side of hydraulic pressure cylinder 32 and the working solution of bar side.Separately
Outside, it also can replace fixed restrictive valve 38 and using the needle-valve or throttle orifice of flow adjustment.
According to this structure, after the installation of intermediate bearing 7, in (such as one hour or more week in bearing height longer period
Phase) to when upper and lower displacement, piston rod 33 can follow the displacement with lesser moving resistance f.
Further, since the feelings that shorter moving up and down for period (such as 10 seconds periods below) and intermediate bearing 7 are displaced
Under condition, movement speed adjustment device 34 is functioned as vibration absorber (or buffer), can prevent the upper of shorter period
Lower vibration.
In fig. 7, movement speed adjustment device 34, which has, is set to the lid side of hydraulic pressure cylinder 32 and working liquid tank 35
The Remote control valve 39 of 1st connecting tube 36A of connection.
In figure 7b, movement speed adjustment device 34, which has to be set to, is connected to the lid side of hydraulic pressure cylinder 32 with bar side
The Remote control valve 39 of 2nd connecting tube 36B.
Remote control valve 39 is, for example, solenoid valve, is configured to remotely to control and completely close the 1st connecting tube 36A.
Remote control valve 39 is equivalent to the fixed device of above-mentioned displacement.
According to this structure, after the installation of intermediate bearing 7, due to temperature change or external force effect and bearing height from installation
Height displacement after becoming standing state, can completely close Remote control valve 39 by the instruction from remote control room.
It, can be by intermediate bearing 7 in suitable standing state thereby, it is possible to fix the displacement of the displacement of piston rod 33, i.e. intermediate bearing 7
Position (i.e. height) be actually fixed on pedestal 11.
As described above, bearing supporting device 10 of the invention has relative to intermediate bearing 7 away from mounting height (x=0)
The synthesis spring constant k of displacement x.Synthesis spring constant k is set to, and the supporting force F of intermediate bearing 7 is in height setting range
For in preset setting load range RF (such as F=12 ~ 151kN) in (such as x=-2 ~ 2mm).
That is, in the above example, setting bearing supporting device in a manner of supporting spring constant k2 as k2=37kN/mm
10 spring performance.As a result, as shown in Figure 2 A, even if due to the effect of temperature change or external force after the installation of intermediate bearing 7
And in the case that bearing height is displaced, it also can be by bearing load (the supporting force F of intermediate bearing 7) in setting load range RF
Automatically adjust.
In addition, by the structure for having velocity of displacement limits device 30, after the installation of intermediate bearing 7, bearing height with compared with
When the long period (such as one hour or more period) is displaced, piston rod 33 can follow the displacement with lesser moving resistance f.
Further, since the feelings that shorter moving up and down for period (such as 10 seconds periods below) and intermediate bearing 7 are displaced
Under condition, movement speed adjustment device 34 is functioned as vibration absorber (or buffer), can prevent the upper of shorter period
Lower vibration.
And then structure according to the present invention, obtain following subsidiary effect.
(1) the counterweight balance adjust automatically of each bearing, reliability can be improved.
That is, setting has the bullet in the displacement of respective relative altitude between bearing (intermediate bearing 7) and pedestal 11
The bearing supporting device 10 of spring characteristic, thus, it is possible to automatically adjust so that always be in counterweight balance appropriate, system it is reliable
Property improve.
(2) the hot sticky damage of bearing metal can be prevented.
In the case where the displacement of the relative altitude of bearing (intermediate bearing 7) and pedestal 11 becomes larger, if the bearing of a part
Load is more than allowable load, then has the hot sticky damage there is a situation where metal.But by the way that bearing supporting device 10 is arranged, from
The balance for adjusting each bearing load dynamicly, thus, it is possible to prevent the hot sticky damage of bearing metal.
(3) metal-stripping due to caused by the fretting of bearing metal can be prevented.
If being got higher with respect to bearing height for part and bearing load becomes too small, the supporting force of bearing is reduced, so producing
The fretting in raw bearing metal portion, the reason of the removing of bearing metal occurs, becomes the significant problem of system.But pass through
Bearing supporting device 10 is set, automatically adjusts the balance of each bearing load, thus, it is possible to prevent due to caused by fretting
Metal-stripping.
(4) inhibit the dynamic change power due to caused by the external force to shafting, be able to carry out stable bearing bearing.
By equipping spring 26 (disc spring laminated body), displacement speed as illustrated in fig. 6 between intermediate bearing 7 and pedestal 11
Limits device 30 is spent, can prevent bearing entirety rocks or generate vibration, is able to carry out stable operating.
In addition, being equipped in connecting tube 36A, 36B of hydraulic pressure cylinder 32 as Fig. 7 A, Fig. 7 B it can be considered that changing outer
The ground such as the period of power carry out flow rate regulating valve 37A, 37B (such as needle-valve) of flow adjustment, and thus, it is possible to carry out more stable fortune
Turn.
(5) ordinatedly can remotely be controlled from control room with flow rate regulating valve 37A, 37B (needle-valve) of flow adjustment
The mode of the flowing of working oil processed, as Fig. 7 A, Fig. 7 B, equip Remote control valve 39 (solenoid valve), thus, it is possible to carry out with
The control of the movement cooperation of system.
(6) after by shafting by the installation of each bearing, the height in each bearing erecting bed side is displaced due to disturbing factor
At device, the balance of bearing load is deteriorated, and to position use as damage of the bearing is occurring, thus, it is possible to prevent the damage of bearing
Wound, can be improved the reliability of device.
(7) the relative displacement of bearing and bearing erecting bed compared in the case where, also can simply mounting and adjusting, and install
After do not need to adjust again, can be realized non-maintaining.
The present invention is not limited to the above embodiments, it is clear that can apply without departing from the scope of spirit of the present invention various
Change.
Description of symbols
The axial center of E host bearing
The supporting force of F intermediate bearing
F moving resistance
RF sets load range
RH setting height range
K integrates spring constant
K1 adapting table spring constant
K2 supports spring constant
The single spring constant of k3
Displacement of the x away from mounting height
The displacement of x1 pedestal
The displacement of x2 bearing supporting device
The axle center Z-Z
1 ship
1a stern
1b hull bottom
The dual ground 1c
2 propellers
3 stern tubes
4 stern tubular shafts
5 propeller shafts
6 jackshafts
7 intermediate bearings
7a bearing
7b bearing cage
7c foot
7d horizontal support surface
8 host output shafts
9 host bearings
10 self-alignment type bearing supporting devices (bearing supporting device)
10a side guides
11 pedestals
11a supporting station
11b adjustment liner
12 top tie plates
14 lower tie plates
16 guide devices
18 force application apparatus
20 lower limit limit stops
21 retainer fixing bolts
22 ceiling restriction bolts
24 flexible guiding pieces
26 springs (disc spring laminated body)
27A, 27B position sensor
28 gap sensors
29 lifting bolts
30 velocity of displacement limits devices
31a, 31b bolt
32 hydraulic pressure cylinders
33 piston rods
34 movement speeds adjust device
35 working liquid tanks
The 1st connecting tube of 36A
The 2nd connecting tube of 36B
The 3rd connecting tube of 36C
The 1st flow rate regulating valve of 37A
The 2nd flow rate regulating valve of 37B
38 fixed restrictive valves
39 Remote control valves.
Claims (11)
1. a kind of self-alignment type bearing supporting device, aforementioned self-alignment type bearing supporting device supports intermediate bearing, aforementioned centre
Bearing can rotatably support the middle part of jackshaft, and aforementioned jackshaft is horizontally extending, and front-end and back-end are by energy
It is enough rotatably to support, which is characterized in that
Synthesis spring constant with the displacement relative to aforementioned intermediate bearing away from mounting height,
Aforementioned comprehensive spring constant is configured to, and the supporting force of aforementioned intermediate bearing is in setting height range in setting load
In range,
Aforementioned self-alignment type bearing supporting device has top tie plate, lower tie plate, guide device, force application apparatus,
The fixed aforementioned intermediate bearing of aforementioned top tie plate,
Aforementioned lower tie plate is fixed on fixed part,
Aforementioned guide device by aforementioned top tie plate relative to aforementioned lower tie plate aforementioned setting height range can on
Under movably guide,
Aforementioned force application apparatus is held between aforementioned top tie plate and aforementioned lower tie plate, and aforementioned top tie plate is opposite
It exerts a force upwards in aforementioned lower tie plate,
The total force of aforementioned force application apparatus is configured to, and the aforementioned supporting force of aforementioned intermediate bearing is in aforementioned setting height range
It is interior to be in aforementioned setting load range.
2. self-alignment type bearing supporting device as described in claim 1, which is characterized in that
With the velocity of displacement limits device for limiting velocity of displacement of the aforementioned intermediate bearing from aforementioned mounting height.
3. self-alignment type bearing supporting device as claimed in claim 2, which is characterized in that
Aforementioned displacements speed limiting device has the fixed device of the displacement of fixed aforementioned displacements.
4. self-alignment type bearing supporting device as described in claim 1, which is characterized in that
Aforementioned force application apparatus has the spring being held between aforementioned top tie plate and aforementioned lower tie plate,
The spring constant of aforementioned spring is configured to, and as a whole, the aforementioned supporting force of aforementioned intermediate bearing is high in aforementioned setting
It spends in range in aforementioned setting load range.
5. a kind of self-alignment type bearing supporting device, aforementioned self-alignment type bearing supporting device supports intermediate bearing, aforementioned centre
Bearing can rotatably support the middle part of jackshaft, and aforementioned jackshaft is horizontally extending, and front-end and back-end are by energy
It is enough rotatably to support, which is characterized in that
Synthesis spring constant with the displacement relative to aforementioned intermediate bearing away from mounting height,
Aforementioned comprehensive spring constant is configured to, and the supporting force of aforementioned intermediate bearing is in setting height range in setting load
In range,
With the velocity of displacement limits device for limiting velocity of displacement of the aforementioned intermediate bearing from aforementioned mounting height, aforementioned autoregistration
Formula bearing supporting device has the top tie plate of fixed aforementioned intermediate bearing and is fixed on the lower tie plate of fixed part,
There is aforementioned displacements speed limiting device hydraulic pressure cylinder and movement speed to adjust device,
Aforementioned hydraulic pressure cylinder is held between aforementioned top tie plate and aforementioned lower tie plate, solid with aforementioned top is followed
Piston rod of the fixed board relative to the movement of aforementioned lower tie plate,
Aforementioned movement speed adjustment device adjusts the movement speed of aforementioned piston rod.
6. self-alignment type bearing supporting device as claimed in claim 5, which is characterized in that
Aforementioned movement speed adjustment device is to be set to the 1st connection for being connected to the lid side of aforementioned hydraulic pressure cylinder with working liquid tank
1st flow rate regulating valve of pipe.
7. self-alignment type bearing supporting device as claimed in claim 5, which is characterized in that
Aforementioned movement speed adjustment device is to be set to the 2nd connecting tube for being connected to the lid side of aforementioned hydraulic pressure cylinder with bar side
2nd flow rate regulating valve.
8. self-alignment type bearing supporting device as claimed in claim 5, which is characterized in that
Aforementioned movement speed adjustment device is set to the 1st connecting tube for being connected to the lid side of aforementioned hydraulic pressure cylinder with working liquid tank
Or the 2nd connecting tube for being connected to the lid side of aforementioned hydraulic pressure cylinder with bar side, having can be by aforementioned 1st connecting tube or aforementioned the
The Remote control valve that 2 connecting tubes are completely closed in a manner of remotely controlling.
9. self-alignment type bearing supporting device as described in claim 1, which is characterized in that
Aforementioned guide device has lower limit limit stop, ceiling restriction bolt, flexible guiding piece,
Aforementioned minimum limit stop is held between aforementioned top tie plate and aforementioned lower tie plate, prevents aforementioned top solid
Fixed board moves downwards in the lower limit of aforementioned setting height range,
Aforementioned ceiling restriction bolt prevents aforementioned top tie plate to be moved upward in the upper limit of aforementioned setting height range,
Aforementioned flexible guiding piece guides the flexible of the up and down direction of aforementioned force application apparatus.
10. self-alignment type bearing supporting device as claimed in claim 9, which is characterized in that
The gap sensor of position sensor and bearing height monitoring with the alarm of bearing height position,
The position sensor of aforementioned bearings height and position alarm is able to detect the aforementioned minimum or preceding of aforementioned setting height range
The upper limit is stated,
The gap sensor of aforementioned bearings height monitoring is able to detect between aforementioned top tie plate and aforementioned lower tie plate
Gap interval.
11. self-alignment type bearing supporting device as described in claim 1, which is characterized in that
With lifting bolt, aforementioned lifting bolt is threadedly engaged with aforementioned top tie plate or aforementioned lower tie plate, relative to
Aforementioned lower tie plate pushes aforementioned top tie plate upwards.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2016/064572 WO2017199327A1 (en) | 2016-05-17 | 2016-05-17 | Self-aligning bearing support device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108603527A CN108603527A (en) | 2018-09-28 |
| CN108603527B true CN108603527B (en) | 2019-09-20 |
Family
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680082003.1A Active CN108603527B (en) | 2016-05-17 | 2016-05-17 | Self-alignment type bearing supporting device |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6573296B2 (en) |
| KR (1) | KR102035953B1 (en) |
| CN (1) | CN108603527B (en) |
| WO (1) | WO2017199327A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2019105352A (en) * | 2017-12-14 | 2019-06-27 | 株式会社Ｓｕｂａｒｕ | Shaft support structure |
| KR102138461B1 (en) * | 2019-03-11 | 2020-07-28 | 주식회사 금화피에스시 | Jig for adjusting step for journal bearing |
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| CN201196219Y (en) * | 2008-05-27 | 2009-02-18 | 丁郁华 | Large-specific pressure intermediate bearing for vessel |
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| CN104677631A (en) * | 2013-12-03 | 2015-06-03 | 上海船厂船舶有限公司 | Hydraulic force-measuring device, system and measuring method of intermediate bearing |
| CN104816126A (en) * | 2015-03-16 | 2015-08-05 | 南京东泽船舶制造有限公司 | Shaft system above-water centering and mounting process |
| CN105235850A (en) * | 2015-10-23 | 2016-01-13 | 上海海事大学 | Bearing supporting device with height capable of being adjusted automatically |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JP3499001B2 (en) | 1994-05-24 | 2004-02-23 | 株式会社東芝 | Automatic bearing alignment adjustment device |
| JP2002213522A (en) | 2001-01-15 | 2002-07-31 | Mitsubishi Heavy Ind Ltd | Alignment adjusting device |
| JP4064786B2 (en) * | 2002-10-31 | 2008-03-19 | 三菱重工業株式会社 | Main shaft support structure, machine tool |
| JP6239392B2 (en) * | 2014-01-24 | 2017-11-29 | 三菱重工業株式会社 | Rotation axis alignment adjustment method and alignment measurement apparatus |
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2016
- 2016-05-17 JP JP2018517961A patent/JP6573296B2/en active Active
- 2016-05-17 WO PCT/JP2016/064572 patent/WO2017199327A1/en active Application Filing
- 2016-05-17 CN CN201680082003.1A patent/CN108603527B/en active Active
- 2016-05-17 KR KR1020187015426A patent/KR102035953B1/en active IP Right Grant
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201196219Y (en) * | 2008-05-27 | 2009-02-18 | 丁郁华 | Large-specific pressure intermediate bearing for vessel |
| JP2013047515A (en) * | 2011-08-29 | 2013-03-07 | Honeywell Internatl Inc | Annular bearing support dampers, gas turbine engines including the same, and methods for the manufacture thereof |
| CN202752818U (en) * | 2012-08-07 | 2013-02-27 | 浙江增洲造船有限公司 | Centering and auxiliary installation device of ship propeller shaft |
| CN102815370A (en) * | 2012-09-04 | 2012-12-12 | 中船桂江造船有限公司 | One-step centering ship shafting mounting method |
| CN104677631A (en) * | 2013-12-03 | 2015-06-03 | 上海船厂船舶有限公司 | Hydraulic force-measuring device, system and measuring method of intermediate bearing |
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| CN105235850A (en) * | 2015-10-23 | 2016-01-13 | 上海海事大学 | Bearing supporting device with height capable of being adjusted automatically |
Also Published As
| Publication number | Publication date |
|---|---|
| KR102035953B1 (en) | 2019-10-23 |
| JP6573296B2 (en) | 2019-09-11 |
| WO2017199327A1 (en) | 2017-11-23 |
| KR20180075661A (en) | 2018-07-04 |
| JPWO2017199327A1 (en) | 2018-08-30 |
| CN108603527A (en) | 2018-09-28 |
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