U.S. patent application number 13/709641 was filed with the patent office on 2013-06-13 for sliding bearing and pump device using the same.
This patent application is currently assigned to Hitachi-GE Nuclear Energy, Ltd.. The applicant listed for this patent is Hitachi-GE Nuclear Energy, Ltd.. Invention is credited to Kouji AIZAWA, Masaaki HAYASHI, Tomonaga OYAMADA.
Application Number | 20130149142 13/709641 |
Document ID | / |
Family ID | 48572132 |
Filed Date | 2013-06-13 |
United States Patent
Application |
20130149142 |
Kind Code |
A1 |
OYAMADA; Tomonaga ; et
al. |
June 13, 2013 |
Sliding Bearing and Pump Device Using the Same
Abstract
In a sliding bearing, load carrying capacity and bearing
rigidity is increased without increasing a size of the bearing and
the pressure of the fluid. The sliding bearing comprises a
cylindrical-shaped sleeve supporting a rotatable shaft via fluid,
and hydrostatic pressure pockets provided in the inner periphery of
the sleeve. The hydrostatic pressure pockets constitute a plurality
of rows of circumferentially disposed hydrostatic pressure pockets
via orifices. At least one of the hydrostatic pressure pocket rows
is arranged adjacently to each of both end portions of the inner
periphery of the sleeve. And a circular cylindrical inner
peripheral surface region without the hydrostatic pressure pockets
is provided at a center portion of the sleeve. A width of the
circular cylindrical inner peripheral surface region provided in
the axial direction of the shaft is made wider than a sum of widths
of the hydrostatic pressure pocket rows.
Inventors: |
OYAMADA; Tomonaga;
(Hitachinaka-shi, JP) ; AIZAWA; Kouji;
(Hitachi-shi, JP) ; HAYASHI; Masaaki;
(Hitachinaka-shi, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Hitachi-GE Nuclear Energy, Ltd.; |
Hitachi-shi |
|
JP |
|
|
Assignee: |
Hitachi-GE Nuclear Energy,
Ltd.
Hitachi-shi
JP
|
Family ID: |
48572132 |
Appl. No.: |
13/709641 |
Filed: |
December 10, 2012 |
Current U.S.
Class: |
415/229 ;
384/114 |
Current CPC
Class: |
F04D 29/0476 20130101;
F16C 32/0685 20130101; F04D 13/08 20130101; F16C 2210/08 20130101;
F16C 32/0651 20130101; F04D 29/0473 20130101; F04D 3/00
20130101 |
Class at
Publication: |
415/229 ;
384/114 |
International
Class: |
F04D 29/047 20060101
F04D029/047 |
Foreign Application Data
Date |
Code |
Application Number |
Dec 13, 2011 |
JP |
2011-271887 |
Claims
1. A sliding bearing comprising a substantially circular
cylindrical-shaped sleeve slidingly supporting a rotatable shaft
via fluid in an inner periphery thereof, hydrostatic pressure
supplying passages penetrating through the sleeve and supplying
high pressure fluid into the sleeve inner periphery from an
external pressure source, and hydrostatic pressure pockets provided
in the inner periphery of the sleeve and having radially recessed
shapes, the hydrostatic pressure supplying passages being opened in
the hydrostatic pressure pockets, wherein the hydrostatic pressure
pockets constitute a plurality of rows of circumferentially
disposed hydrostatic pressure pockets, at least one of the
hydrostatic pressure pocket rows being arranged adjacently to each
of both end portions of the inner periphery of the sleeve in an
axial direction of the shaft, and a circular cylindrical inner
peripheral surface region in which the hydrostatic pressure pockets
are not present is provided at a center portion of the sleeve so as
to be interposed between the hydrostatic pressure pocket rows.
2. The sliding bearing according to claim 1, wherein a width of the
circular cylindrical inner peripheral surface region without the
hydrostatic pressure pockets provided in the axial direction of the
shaft is made wider than a sum of widths of the hydrostatic
pressure pocket rows provided in the axial direction of the
shaft.
3. The sliding bearing according to claim 1, wherein hydrostatic
pressure supplying passages communicating with hydrostatic pressure
pockets belonging to the same hydrostatic pressure pocket row and
hydrostatic pressure supplying passages communicating with
hydrostatic pressure pockets belonging to a different hydrostatic
pressure pocket row are independently communicated with the
pressure source supplying the high pressure fluid.
4. The sliding bearing according to claim 1, wherein an
arrangement-angle range of hydrostatic pressure pockets which
extends in a circumferential direction has a shape that is
superposed on an arrangement-angle range of adjacent hydrostatic
pressure pockets.
5. The sliding bearing according to claim 1, wherein an
arrangement-angle range of hydrostatic pressure pockets which
extends in a circumferential direction is located so as to be
superposed on an arrangement-angle range of adjacent hydrostatic
pressure pockets.
6. The sliding bearing according to claim 1, wherein each of the
hydrostatic pressure pockets has a shape in which an outer side of
the hydrostatic pressure pocket that is adjacent to an end portion
of the sleeve extends to an upstream side relative to a rotational
direction of the shaft as compared to an inner side of the
hydrostatic pressure pocket that is remote from the end portion of
the sleeve and the inner side of the hydrostatic pressure pocket
that is remote from the end of the sleeve extends to a downstream
side relative to the rotational direction of the shaft as compared
to the outer side of the hydrostatic pressure pocket that is
adjacent to the end portion of the sleeve.
7. The sliding bearing according to claim 1, wherein a region of
the sleeve inner periphery that has no hydrostatic pressure pockets
is formed with grooves in which the hydrostatic pressure supplying
passages are not opened.
8. A pump device comprising an impeller arranged at a midway of a
fluid passage and transferring fluid according to rotational
movement thereof, a shaft connected to an rotation power source and
rotation-driving the impeller, a substantially circular
cylindrical-shape sleeve slidingly supporting an outer peripheral
surface of the shaft via the fluid, hydrostatic pressure supplying
passages penetrating through the sleeve and supplying high pressure
fluid into an inner periphery of the sleeve from an outlet side of
the fluid passage, and a sliding bearing having hydrostatic
pressure pockets which are provided in the inner periphery of the
sleeve and have radially recessed shapes, the hydrostatic pressure
supplying passages being opened in the hydrostatic pressure
pockets, wherein the hydrostatic pressure pockets constitute a
plurality of rows of circumferentially disposed hydrostatic
pressure pockets, at least one of the hydrostatic pressure pocket
rows being arranged adjacently to each of both end portions of the
inner periphery of the sleeve in an axial direction of the shaft,
and a circular cylindrical inner peripheral surface region in which
the hydrostatic pressure pockets are not present is provided at a
center portion of the sleeve so as to be interposed between the
hydrostatic pressure pocket rows.
9. The pump device according to claim 8, wherein a width of the
circular cylindrical inner peripheral surface region which is
provided in an axial direction of the shaft is made wider than a
sum of widths of the hydrostatic pressure pocket rows which is
provided in the axial direction of the shaft.
10. The pump device according to claim 8, wherein hydrostatic
pressure supplying passages communicating with hydrostatic pressure
pockets belonging to a hydrostatic pressure pocket row and
hydrostatic pressure supplying passages communicating with
hydrostatic pressure pockets belonging to a different hydrostatic
pressure pocket row are independently communicated with the outlet
side of the fluid passage.
11. The pump device according to claim 8, wherein the fluid that
flows through the fluid passage is fluid metal.
Description
CLAIM OF PRIORITY
[0001] The present application claims priority from Japanese
application serial No. 2011-271887 filed on Dec. 13, 2011, the
content of which is hereby incorporated by reference into this
application
BACKGROUND OF THE INVENTION
[0002] 1. Field of the Invention
[0003] The present invention relates to a sliding bearing provided
with a hydrostatic pressure bearing structure in which high
pressure fluid is supplied into a gap between the outer periphery
of a shaft and the inner periphery of a sleeve from the outside and
which supports rotational movement of the shaft, and a pump device
provided with a mechanism which supports, through the sliding
bearing, the rotational movement of the shaft connected to an
impeller.
[0004] 2. Description of the Related Art
[0005] As a large-sized pump device used in, for example, a
circulative cooling system of a fast-breeder reactor, there has
been generally used a mechanical-type vertical axial pump device in
which an impeller attached to a longitudinal shaft is
rotation-moved in a casing, to thereby transfer fluid, such as
fluid metal, that is a cooling medium.
[0006] In this pump device, for the purposes of preventing
impinging of the impeller on the casing or the like due to
centrifugal whirling and/or earth quake, and suppressing vibration
of the shaft, a journal bearing is arranged adjacently to the
impeller of the shaft. As this journal bearing, there is often
employed a sliding bearing. A shaft outer periphery is slid
relative to a substantially cylindrical-shaped sleeve inner
periphery of the sliding bearing while being lubricated via the
fluid, whereby the rotational movement of the shaft is
supported.
[0007] In the sliding bearing used in such a pump device, for the
purpose of allowing thermal deformation and manufacturing
tolerances of the shaft and casing, a gap between the shaft outer
periphery and the bearing inner periphery is required to be
increased relative to that in a general sliding bearing. Moreover,
for the purpose of preventing the entrance of foreign material,
fluid that can be used for the lubrication of the sliding bearing
is limited to fluid of the same kind as the fluid to be transferred
by the pump. In the pump device for the fast-breeder reactor, use
of low-viscosity fluid metal or the like is required.
[0008] In the aforesaid situation, the sliding bearing itself which
is used in the pump device is subjected to conditions where it is
hard to obtain high dynamic pressure as compared to an oil
lubricating sliding bearing used in a general mechanical device.
Therefore, in order to stably support the shaft against high load
even under such conditions, there has been often employed a
hydrostatic pressure bearing structure in which high pressure fluid
is introduced onto a sliding surface from the outside of the
bearing and used to support a load.
[0009] Generally, in a journal bearing-type sliding bearing having
the hydrostatic pressure bearing structure, several recess portions
called "hydrostatic pressure pockets" are provided in a
substantially circular cylindrical-shaped sleeve inner periphery in
a circumferential direction or in a shaft axial direction and
occupy the most part of the sleeve inner periphery. A passageway
which communicates with an external pressure source is opened in
each of the hydrostatic pressure pockets. High pressure fluid which
is introduced via the passageways into the hydrostatic pressure
pockets from the external pressure source fills hydrostatic
pressure pocket interiors and a gap between the bearing and the
shaft and flows to a low-pressure outside from an opened end
portion of the gap.
[0010] If the shaft is radially pressed by a load and made
eccentric in the bearing, a deviation of the gap is partially
produced, so that the amount of fluid flowing out of a part of the
gap present in an eccentric direction is reduced and pressure in
the part rises, while the amount of fluid flowing out of a part of
the gap present in a direction opposite to the eccentric direction
is increased and pressure in the part drops. Pressure difference
between both parts generates a restoring force tending to return
the shaft to a center of the bearing, whereby the load of the shaft
is supported.
[0011] In recent years, according to capacity enlargement of the
pump device, demand has been raised for improving a load carrying
capacity that is a supportable load for the sliding bearing, and a
bearing rigidity that is a load carrying capacity change relative
to a minimum gap change due to shaft eccentricity.
[0012] JP-A No. 61-236921 disclosing the background art in this
technical field describes a hydrostatic pressure bearing which
includes pockets in a bearing inner peripheral surface and in which
high pressure oil is adapted to be supplied between the pockets and
the outer peripheral surface of a rotating shaft. A plurality of
pocket rows are formed in a circumferential direction arranged in
an axial direction and the phases of the pockets between the
respective rows are shifted in the circumferential direction.
[0013] According to the background art disclosed in JP-A No.
61-236921, the plurality of pocket rows in which the hydrostatic
pressure pockets are formed in the circumferential direction is
arranged in the axial direction and the phases of the pockets
between the respective rows are shifted in the circumferential
direction, whereby when the shaft is made eccentric in a certain
radial direction, a force which acts in a radial direction
perpendicular to this is cancelled and it can be anticipated that
stability of the bearing at the time of high speed rotation is
improved.
[0014] However, even if the phases of the hydrostatic pressure
pockets are shifted in the circumferential direction and the
pockets are merely arranged in the plurality of rows as described
in the patent literature 1, this structure has little influence on
the load carrying capacity and bearing rigidity of the bearing and
it is hard for the structure to increase the load carrying capacity
without increasing the pressure of an oil supplied from the
outside, or without increasing the size of the bearing.
[0015] Moreover, JP-A No. 57-200699 describes a pump for fluid
metal which is provided with a bearing for an impeller shaft,
arranged just adjacently to an impeller provided between an inlet
port and an outlet port in a casing and in which plural pockets are
circumferentially arranged in a bearing inner surface and a portion
of fuel metal pressed out by the impeller is introduced into the
pockets, in which circumferential recess grooves that contain the
fluid metal and allow the fluid metal to be present therein are
provided in annular-band portions which axially interpose the
pockets and are provided so as to be relatively-rotated with liquid
sealing properties.
[0016] Moreover, JP-A No. 57-200699 describes a pump in which
ring-shaped circumferential vacancies having the fluid metal always
contained therein are additionally provided in annular-band
portions which are provided so as to axially interpose the pockets
constituting a hydrostatic pressure bearing for supporting the
impeller and have liquid sealing properties.
[0017] According to the background art disclosed in JP-A No.
57-200699, the structure in which the circumferential recess
grooves are provided in the annular-band portions that are provided
so as to axially interpose the hydrostatic pressure pockets into
which high pressure liquid metal is supplied from the outside is
employed, whereby it is anticipated that even when metal contact is
produced between the shaft and the bearing, the fluid metal is easy
to be supplied to the circumference of the contacted portions and
damage occurring due to seizure or the like is reduced by the
effects of lubrication and cooling.
[0018] However, even if the circumferential recess grooves are
provided in the annular-band portions as described in JP-A No.
57-200699, change in pressure distribution on a bearing inner
periphery is small and the effects of improving the load carrying
capacity and bearing rigidity of the bearing cannot be anticipated
at all. Therefore, it is hard to improve the load carrying capacity
without increasing the pressure of an oil supplied from the outside
or without increasing the size of the bearing.
[0019] Moreover, JP-A No. 60-37329 describes a fluid bearing device
in which a plurality of pressure generating band regions are formed
in the circumferential direction of a bearing surface that supports
an axial load and is provided at a bearing member fixed relative to
a rotatable shaft member and each of the pressure generating band
regions comprises a hydrostatic pressure generating portion
including a pair of pockets formed so as to be axially spaced and
having excretion mechanisms, a dynamic pressure generating portion
including a land portion formed at a middle between the both
pockets, and a supply groove formed along a side of the land which
is parallel to axial lines of the both pockets, interconnecting the
both pockets, and supplying pressure fluid to the both pockets via
a throttle, and a bearing gap of the dynamic pressure generating
portion is made smaller than a bearing gap of the hydrostatic
pressure generating portion.
[0020] According to the fluid bearing device disclosed in JP-A No.
60-37329, it can be anticipated that in addition to the generation
of hydrostatic pressure by the pressure fluid that is introduced
into the external supply groove and also supplied to the pockets,
the generation of the dynamic pressure in the dynamic pressure
generating portion surrounded by the pockets and the supply groove
can be also anticipated.
[0021] However, in the fluid bearing device disclosed in JP-A No.
60-37329, even if the dynamic pressure that is higher than the
pressure of the pressure fluid supplied from the outside is
produced in the dynamic pressure generating portion, the pressure
is easy to escape through the supply groove and supporting by the
dynamic pressure is restricted. Therefore, the load carrying
capacity considerably depends upon the hydrostatic pressure.
[0022] Moreover, if the shaft is deformed or inclined to thereby
make a certain part of the gap between the shaft and the bearing
wider and an amount of fluid flowing out of the widened part of the
gap is increased, an entire pressure in the pockets and the supply
groove which communicate with each other is reduced and the load
carrying capacity is easy to be lowered. In the vertical-type pump
device, the shaft rotates in a state inclined relative to the
bearing inner periphery in many cases. Therefore, it is difficult
to apply the structures disclosed in the patent literatures to the
vertical-type pumps or the like.
[0023] The present invention has been made with a view of the
aforesaid background and it is an object of the present invention
to provide a journal bearing-type sliding bearing provided with a
hydrostatic pressure bearing structure in which high pressure fluid
is supplied into a gap between an outer periphery of a shaft and an
inner periphery of a substantially circular cylindrical shaped
bearing from an outside and which supports rotational movement of
the shaft, and a pump device having the sliding bearing enclosed,
in which dynamic pressure produced in the gap at the time of
rotation of the shaft is increased and utilized to the fullest,
whereby it is possible to increase the load carrying capacity and
bearing rigidity of the bearing without increasing a size of the
bearing and the pressure of the fluid supplied from the
outside.
SUMMARY OF THE INVENTION
[0024] In accordance with an aspect of the present invention, there
is provided a sliding bearing which comprises a substantially
circular cylindrical-shaped sleeve slidingly supporting a rotatable
shaft via fluid in an inner periphery thereof, hydrostatic pressure
supplying passages penetrating through the sleeve and supplying
high pressure fluid into the sleeve inner periphery from an
external pressure source, and hydrostatic pressure pockets provided
in the inner periphery of the sleeve and having radially recessed
shapes, the hydrostatic pressure supplying passages being opened in
the hydrostatic pressure pockets, in which the hydrostatic pressure
pockets constitute a plurality of rows of circumferentially
disposed hydrostatic pressure pockets, at least one of the
hydrostatic pressure pocket rows being arranged adjacently to each
of both end portions of the inner periphery of the sleeve in an
axial direction of the shaft, and a circular cylindrical inner
peripheral surface region in which the hydrostatic pressure pockets
are not present is provided at a center portion of the sleeve so as
to be interposed between the hydrostatic pressure pocket rows.
[0025] In a sliding bearing according to a preferred embodiment of
the present invention, a width of the circular cylindrical inner
peripheral surface region without the hydrostatic pressure pockets
which is provided in the axial direction of the shaft may be made
wider than a sum of widths of the hydrostatic pressure pocket rows
which is provided in the axial direction of the shaft.
[0026] In a sliding bearing according to a preferred embodiment of
the present invention, hydrostatic pressure supplying passages
communicating with hydrostatic pressure pockets belonging to the
same hydrostatic pressure pocket row and hydrostatic pressure
supplying passages communicating with hydrostatic pressure pockets
belonging to a different hydrostatic pressure pocket row may be
independently communicated with the pressure source supplying the
high pressure fluid.
[0027] In a sliding bearing according to a preferred embodiment of
the present invention, an arrangement-angle range of hydrostatic
pressure pockets which extends in a circumferential direction may
have a shape that is superposed on an arrangement-angle range of
adjacent hydrostatic pressure pockets.
[0028] In a sliding bearing according to a preferred embodiment of
the present invention, an arrangement-angle range of hydrostatic
pressure pockets which extends in a circumferential direction may
be located so as to be superposed on an arrangement-angle range of
adjacent hydrostatic pressure pockets.
[0029] In a sliding bearing according to a preferred embodiment of
the present invention, each of the hydrostatic pressure pockets may
have a shape in which an outer side of the hydrostatic pressure
pocket that is adjacent to an end portion of the sleeve extends to
an upstream side relative to a rotational direction of the shaft as
compared to an inner side of the hydrostatic pressure pocket that
is remote from the end portion of the sleeve and the inner side of
the hydrostatic pressure pocket that is remote from the end of the
sleeve extends to a downstream side relative to the rotational
direction of the shaft as compared to the outer side of the
hydrostatic pressure pocket that is adjacent to the end portion of
the sleeve.
[0030] In a sliding bearing according to a preferred embodiment of
the present invention, a region of the sleeve inner periphery that
has no hydrostatic pressure pockets may be formed with grooves in
which the hydrostatic pressure supplying passages are not
opened.
[0031] According to another aspect of the present invention, there
is provided a pump device which comprises an impeller arranged at a
midway of a fluid passage and transferring fluid according to
rotational movement thereof, a shaft connected to an rotation power
source and rotation-driving the impeller, a sliding bearing
provided with a substantially circular cylindrical-shape sleeve
slidingly supporting an outer peripheral surface of the shaft via
the fluid, hydrostatic pressure supplying passages penetrating
through the sleeve and supplying high pressure fluid into an inner
periphery of the sleeve from an outlet side of the fluid
passage.
[0032] The sliding bearing has hydrostatic pressure pockets which
are provided in the inner periphery of the sleeve and have radially
recessed shapes, the hydrostatic pressure supplying passages being
opened in the hydrostatic pressure pockets, in which the
hydrostatic pressure pockets constitute a plurality of rows of
circumferentially disposed hydrostatic pressure pockets, at least
one of the hydrostatic pressure pocket rows being arranged
adjacently to each of both end portions of the inner periphery of
the sleeve in an axial direction of the shaft, and a circular
cylindrical inner peripheral surface region in which the
hydrostatic pressure pockets are not present is provided at a
center portion of the sleeve so as to be interposed between the
hydrostatic pressure pocket rows.
[0033] In a pump device according to a preferred embodiment of the
present invention, a width of the circular cylindrical inner
peripheral surface region which is provided in an axial direction
of the shaft may be made wider than a sum of widths of the
hydrostatic pressure pocket rows which is provided in the axial
direction of the shaft.
[0034] In a pump device according to a preferred embodiment of the
present invention, hydrostatic pressure supplying passages
communicating with hydrostatic pressure pockets belonging to a
hydrostatic pressure pocket row and hydrostatic pressure supplying
passages communicating with hydrostatic pressure pockets belonging
to a different hydrostatic pressure pocket row may be independently
communicated with the outlet side of the fluid passage.
[0035] In a pump device according to a preferred embodiment of the
present invention, the fluid that flows through the fluid passage
may be fluid metal.
[0036] According to the present invention, in the sliding bearing
that comprises the substantially circular cylindrical-shaped sleeve
slidingly supporting the rotatable shaft via fluid in the inner
periphery thereof, the hydrostatic pressure supplying passages
penetrating through the sleeve and supplying high pressure fluid
into the sleeve inner periphery from the external pressure source,
and the hydrostatic pressure pockets provided in the inner
periphery of the sleeve and having radially recessed shapes, the
hydrostatic pressure supplying passages being opened in the
hydrostatic pressure pockets, the hydrostatic pressure pockets
constitute the plurality of rows of circumferentially disposed
hydrostatic pressure pockets, the at least one of the hydrostatic
pressure pocket rows is arranged adjacently to each of both end
portions of the inner periphery of the sleeve in the axial
direction of the shaft, and the circular cylindrical inner
peripheral surface region in which the hydrostatic pressure pockets
are not present is provided at the center portion of the sleeve so
as to be interposed between the hydrostatic pressure pocket
rows.
[0037] Therefore, the shaft that is rotated in the inner periphery
of the sleeve is supported by the hydrostatic pressure supplied in
the hydrostatic pressure pockets from the outside and dynamic
pressure produced on the circular cylindrical inner peripheral
surface region. When the dynamic pressure is produced, large
pressure is obtained as compared to the conventional example, and
the loading capability and bearing rigidity of the entire sliding
bearing can be increased.
BRIEF DESCRIPTION OF THE DRAWINGS
[0038] FIG. 1 is a structure view of a vertical-type pump device
according to an embodiment 1 of the present invention;
[0039] FIG. 2 is an enlarged view of a circumference of a sliding
bearing in the vertical-type pump device according to the
embodiment 1 of the present invention;
[0040] FIG. 3 is a perspective view of a sleeve in the sliding
bearing according to the embodiment 1 of the present invention;
[0041] FIG. 4 is a graph showing a loading capability in the
sliding bearing according to the embodiment 1 of the present
invention;
[0042] FIG. 5 is a graph showing a bearing rigidity in the sliding
bearing according to the embodiment 1 of the present invention;
[0043] FIG. 6 is a sectional view of a sliding bearing according to
an embodiment 2 of the present invention;
[0044] FIG. 7 is a sectional view of a sliding bearing according to
an embodiment 3 of the present invention;
[0045] FIG. 8 is a sectional view of a sliding bearing according to
an embodiment 4 of the present invention;
[0046] FIG. 9 is a sectional view of a sliding bearing according to
an embodiment 5 of the present invention; and
[0047] FIG. 10 is a sectional view of a sliding bearing according
to an embodiment 6 of the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0048] Embodiments of the present invention will be explained
hereinafter with reference to the drawings.
Embodiment 1
[0049] An embodiment 1 of the present invention will be explained
with reference to a vertical-type pump device 100 having a journal
bearing-type sliding bearing according to the present invention
incorporated therein.
[0050] FIG. 1 is a structure view of the vertical-type pump device
100 according to this embodiment. A passage 104 which communicates
between an inlet port 102 and an outlet port 103 is formed in the
interior of a casing 101. At the midway of the passage 104, an
impeller 105 is provided at a tip end of a shaft 106 connected to
an external rotation power source 107.
[0051] The shaft 106 is rotatably supported, on a side thereof
adjacent to the rotation power source 107, by a bearing 108, and is
rotatably supported, on a side thereof adjacent the impeller 105,
by a sliding bearing 109. Supply of power from the rotation power
source 107 causes the shaft 106 to be rotated to rotation-move the
impeller 105, whereby fluid such as fluid metal which flows into an
interior of the pump device 100 from the inlet port 102 is
transferred through the passage 104 and then discharged out of the
outlet port 103. Pressure head is produced at a downstream side of
the passage 104 relative to the impeller 105, as compared to an
upstream side of the passage 104 relative to the impeller 105, and
pressure at the upstream side is increased.
[0052] The bearing 108 of the two bearings rotatably supports the
shaft 106 and supports load produced in a vertical direction of
FIG. 1, i.e., in an axial direction of the shaft 106. On the other
hand, the sliding bearing 109 is fixed to a support portion 110 and
suppresses centrifugal whirling of the shaft in a radial direction,
to thereby suppress vibration produced according to the rotational
movement of the shaft 106 and impeller 105, in addition to
preventing impingement of the impeller 105 against a wall surface
of the passage 104, the casing 101, etc.
[0053] FIG. 2 is an enlarged view of a circumference of a sliding
bearing 109. In the sliding bearing 109, several hydrostatic
pressure pockets 112A that have concavities recessed in the radial
direction are formed in an inner periphery of a substantially
circular cylindrical-shaped sleeve 111A. Hydrostatic pressure
supplying passages 113 which penetrate through the support portion
110 and the sleeve 111A from the outlet port side of the passage
104 are opened in the respective hydrostatic pressure pockets 112A
via orifices 114.
[0054] Thereby, portions of high pressure fluid that have been
transferred to the downstream side of the passage 104 by the
rotation of the impeller 105 pass through the hydrostatic pressure
supplying passages 113 and the orifices 114, are introduced into
the hydrostatic pressure pockets 112A, and fill a gap between the
outer periphery of the shaft 106 and the inner periphery of the
sleeve 111A.
[0055] The hydrostatic pressure pockets 112A constitute a plurality
of rows of circumferentially disposed hydrostatic pressure pockets
112A in the inner periphery of the sleeve 111A. One row of
hydrostatic pressure pockets is formed adjacently to each of the
both end portions of the inner periphery of the sleeve 111A in the
axial direction of the shaft 106. Moreover, a circular cylindrical
inner peripheral surface region 115 in which a row of hydrostatic
pressure pockets is not present is provided at a center portion of
the inner periphery of the sleeve 111A so as to be interposed
between the rows of hydrostatic pressure pockets.
[0056] FIG. 3 is a perspective view illustrating a detail of the
sleeve 111A. The inner periphery of the sleeve 111A is provided at
each of the both end portions thereof with the one row 116 of
circumferentially disposed hydrostatic pressure pockets 112A, while
the outer periphery of the sleeve 111A is provided with the
hydrostatic pressure supplying passages 113.
[0057] A hydrostatic pressure supplying passage 113 communicating
with one of the hydrostatic pressure pocket rows 116 and a
hydrostatic pressure supplying passage 113 communicating with the
other of the hydrostatic pressure pocket rows 116 are provided
independently from each other and separately communicate with the
downstream side of the passage 104 as also shown in FIG. 2.
[0058] The inventor of the present invention made the sliding
bearing according to the present invention, performed an evaluation
on loading capability and bearing rigidity, verified improvement
effects of the loading capability and bearing rigidity by the
application of the present invention, and investigated a
relationship between the hydrostatic pressure pockets 112A capable
of effectively achieving load reduction and effectively improving
the bearing rigidity, and the circular cylindrical inner peripheral
surface region 115 interposed by the hydrostatic pressure rows 116.
Next, the results will be explained with reference to FIGS. 4 and
5.
[0059] FIG. 4 shows the loading capability of the bearing in a case
where the pressure of the fluid supplied to the hydrostatic
pressure pockets 112A is made constant and the widths of the
hydrostatic pressure pockets 112A and the width of the circular
cylindrical inner peripheral surface region 115 in the inner
periphery of the sleeve 111A are varied. When the width of the
circular cylindrical inner peripheral surface region 115 is
increased relative to the sum of the widths of the hydrostatic
pressure pocket rows 116 provided adjacently to the both ends of
the sleeve 111A so as to interpose the circular cylindrical inner
peripheral surface region 115 therebetween, the increase has
resulted in particular in improvement of a loading capability
increasing rate of the bearing as compared to a case of being equal
to or lower than it.
[0060] FIG. 5 shows the bearing rigidity in the case where the
pressure of the fluid supplied to the hydrostatic pressure pockets
112A is made constant and the widths of the hydrostatic pressure
pockets 112A and the width of the circular cylindrical inner
peripheral surface region 115 in the inner periphery of the sleeve
111A are varied. When the width of the circular cylindrical inner
peripheral surface region 115 is increased relative to the sum of
the widths of the hydrostatic pressure pocket rows 116 provided
adjacently to the both ends of the sleeve 111A so as to interpose
the circular cylindrical inner peripheral surface region 115
therebetween, the increase has resulted in particular in
improvement of a bearing rigidity increasing rate as compared to a
case of being equal to or lower than it.
[0061] When the hydrostatic pressure pockets rows 116 to be
arranged adjacently to the both end portions of the inner periphery
of the sleeve 111A and the circular cylindrical inner peripheral
surface region 115 to be interposed between the hydrostatic
pressure pocket rows 116 are formed, if the width of the circular
cylindrical inner peripheral surface region 115 in the axial
direction of the shaft 106 is increased, in this way, relative to
the sum of the widths of the hydrostatic pressure pocket rows 116
interposing the circular cylindrical inner peripheral surface
region, it has been verified that the load carrying capacity and
the bearing rigidity can be more effectively increased.
Embodiment 2
[0062] The main purpose of providing the hydrostatic pressure
pocket rows adjacently to the both end portions of the inner
periphery of the sleeve lies in that pressure at the both ends of
the circular cylindrical inner peripheral surface region arranged
so as to be interposed between the hydrostatic pressure pocket rows
is kept in a high state and a level of the dynamic pressure
produced on the circular cylindrical inner peripheral surface
region is kept.
[0063] FIG. 6 shows an embodiment 2 of a sleeve portion of a
sliding bearing that more positively attains this purpose. Two
hydrostatic pressure pocket rows 116 are arranged adjacently to
each of the both end portions of the inner periphery of a sleeve
111B. In the two adjacent hydrostatic pressure pocket rows 116,
hydrostatic pressure pockets 112B are arranged so as to be
staggered in the circumferential direction.
[0064] A circular cylindrical inner peripheral surface region 115
in which the hydrostatic pressure pockets 112B are not present is
formed at a center portion of the inner periphery of the sleeve
111B. The width of the circular cylindrical inner peripheral
surface region 115 in the axial direction of the shaft 106 is wider
than the sum of the widths of the four hydrostatic pressure pocket
rows 116 interposing the circular cylindrical inner peripheral
surface region 115 on the both sides thereof.
[0065] When such a structure is employed, at a circumferentially
angular position in which the hydrostatic pressure pocket is not
present in one hydrostatic pressure row 116, the hydrostatic
pressure pockets 112B which belong to another adjacent hydrostatic
pressure pocket row 116 are located, and the supply of the
hydrostatic pressure by the hydrostatic pressure pockets 112B is
uniformly successively performed in the whole circumferences of the
both end portions of the sleeve 111B. Thereby, the pressure on the
circular cylindrical inner peripheral surface region 115 is kept in
a higher state and it is possible to provide high loading
capability and bearing rigidity to the sliding bearing.
Embodiment 3
[0066] FIG. 7 shows an embodiment 3 of a sleeve portion of a
sliding bearing which increases pressure on neighborhoods of the
both end portions of a sleeve 111C, i.e., the both ends of the
circular cylindrical inner peripheral surface region 115.
Hydrostatic pressure pockets 112C have shapes asymmetrical in the
circumferential direction and in the axial direction of the shaft
106. Hydrostatic pressure pocket-extending portions 117 are
partially provided at the both ends of the hydrostatic pressure
pockets 112C in the circumferential direction. Hydrostatic pressure
pocket-extending portions 117 of a hydrostatic pressure pocket 112C
are separated from hydrostatic pressure pocket-extending portions
117 of a circumferentially adjacent hydrostatic pressure pocket
112C but are partially superposed on them within a fixed
circumferential arrangement-angle range.
[0067] Each hydrostatic pressure pocket 112C is formed with a
hydrostatic pressure pocket-extending portion 117 extending to the
upstream side of a rotational direction 118 of the shaft 106 on the
outer side adjacent to the end portion of the sleeve 111C, and a
hydrostatic pressure pocket-extending portion 117 extending to the
downstream side of the rotational direction 118 of the shaft 106 on
the inner side apart from the end portion of the sleeve 111C.
[0068] When such a structure is employed, the supply of the
hydrostatic pressure by the hydrostatic pressure pockets 1120 is
uniformly successively performed in the whole circumferences of the
both end portions of the sleeve 111C. Thereby, the pressure on the
circular cylindrical inner peripheral surface region 115 is kept in
a high state and it is possible to provide high load carrying
capacity and bearing rigidity to the bearing.
[0069] Moreover, small regions of the circumferential end portions
of the hydrostatic pressure pockets 112C may be merely machined to
thereby form the hydrostatic pressure pocket-extending portions
117, so that the manufacturing cost of this embodiment is reduced
as compared to the embodiment of FIG. 6 in which the four
hydrostatic pressure pocket rows in total are provided.
[0070] Moreover, the inner side of the sleeve 111C extends on the
downstream side of the rotational direction of the shaft 106, so
that a sucking force that tends to draw the fluid in the
hydrostatic pressure pockets 112C toward the center side of the
sleeve 111C acts according to the rotation of the shaft 106 and
higher pressure is easy to be kept on the circular cylindrical
inner peripheral surface region 115.
Embodiment 4
[0071] Similarly, FIG. 8 shows an embodiment 4 of a sleeve portion
of a sliding bearing which increases pressure on neighborhoods of
the both end portions of the inner periphery of a sleeve 111D,
i.e., the both ends of a circular cylindrical inner peripheral
surface region 115. Forming of hydrostatic pressure pockets 112D
into rhombus shapes is performed in lieu of forming the hydrostatic
pressure pocket-extending portions 117 at the hydrostatic pressure
pockets 112D as in the embodiment shown in FIG. 7. The hydrostatic
pressure pockets 112D are smoothly extended to the upstream side of
the rotational direction 118 of the shaft 106, according to
progressing toward the outer sides thereof that are adjacent to the
end portions of the sleeve 111D, and are smoothly extended to the
downstream side in the circumferential direction according to
progressing toward the inner sides thereof that are remote from the
end portions of the sleeve 111D.
[0072] When such a structure is employed, a sucking force that
tends to draw the fluid in the hydrostatic pressure pockets 112D
toward the center side of the sleeve 111D is easier to act as
compared to the embodiment shown in FIG. 7, so that higher pressure
is easy to be kept on the circular cylindrical inner peripheral
surface region 115.
Embodiment 5
[0073] Moreover, FIG. 9 shows an embodiment in which foreign
material discharging grooves 119 are formed in portions of the
inner periphery of a sleeve 111E in which hydrostatic pressure
pockets 112E are not present. The foreign material discharging
grooves 119 are provided in a circular cylindrical inner peripheral
surface region 115 occupying the center portion of the sleeve 111E,
and regions of the both end portions of the sleeve 111E in which
the hydrostatic pressure pockets 112E are not present. The foreign
material discharging grooves 119 are grooves which are recessed in
a radial direction different from a recessed direction of the
hydrostatic pressure pockets 112E and in which the orifices 114 are
not opened.
[0074] If any foreign material, wear particles, etc. flow into and
remain in a gap between the outer periphery of the shaft 106 and
the inner periphery of the sleeve 111E, the shaft 106 and/or the
sleeve 111E may be subject to wear and/or damage. When the
structure shown in FIG. 9 is employed, discharging of the foreign
material, wear particles, etc. flowing into the gap between the
outer periphery of the shaft 106 and the inner periphery of the
sleeve 111E is facilitated.
[0075] The orifices 114 are not opened in the foreign material
discharging grooves 119, and the foreign material discharging
grooves 119 do not communicate directly with hydrostatic pressure
supplying passages 113, so that dynamic pressure that is produced
on the circular cylindrical inner peripheral surface region 115
escapes via the hydrostatic pressure supplying passages 113,
resulting in less effect on the reduction in the pressure on the
circular cylindrical inner peripheral surface region 115.
[0076] Moreover, the sizes of the foreign material, the wear
particles, etc. flowing into the gap between the outer periphery of
the shaft 106 and the inner periphery of the sleeve 111E are sizes
at most equal to the size of the gap, so that the depths of the
foreign material discharging grooves 119 may be also about equal to
the size of the gap. Therefore, when the depths of the foreign
material discharging grooves 119 are made about equal to the size
of the gap, even if they extend up to the ends of the sleeve 111E,
enlargement of clearance sectional areas in the end portions is
small and escapement of the pressure through this route can be
reduced.
[0077] Thereby, it is possible to configure a high reliable bearing
in which the shaft 106 and/or the sleeve 111E is unlikely to be
subject to damage due to the foreign material, the wear particles,
etc., while providing high loading capability and bearing rigidity
to the sliding bearing.
Embodiment 6
[0078] Moreover, FIG. 10 shows an embodiment 6 in which grooves 120
in which the orifices 114 are not opened are formed in the circular
cylindrical inner peripheral surface region 115. Each groove 120 is
extended, on the outer side thereof more adjacent to the end
portion of a sleeve 111F, to the upstream side in the rotational
direction 118 of the shaft 106, and is extended, on the inner side
thereof away from the end portion of the sleeve 111F, to the
downstream side in the rotational direction 118 of the shaft
106.
[0079] When such a structure is employed, a flow of the fluid is
easy to become turbulence on the circular cylindrical inner
peripheral surface region 115, or a sucking force that tends to
draw the fluid toward the center portion of the sleeve 111F is
easier to act according to the rotation of the shaft 106, so that
an effect of generating dynamic pressure is increased.
[0080] Moreover, it is possible to configure a high reliable
sliding bearing which may not be subject to the damage of the shaft
106 and/or sleeve 111F which occurs due to the accumulation of the
foreign material, wear particles, etc. in the grooves 120.
[0081] As apparently noted from the above embodiments, the sliding
bearing according to the present invention employs the structure in
which the fixed circular cylindrical inner peripheral surface
region is obtained at the center portion of the inner periphery of
the sleeve and the hydrostatic pressure pocket rows are disposed at
the both end portions of the sleeve so as to interpose the circular
cylindrical inner peripheral surface region therebetween, whereby
the pressure on the circular cylindrical inner peripheral surface
region on which the dynamic pressure is produced at the time of the
shaft rotation is increased and high pressure is kept by the
circular cylindrical inner peripheral surface region, to thereby
improve the loading capability and the bearing rigidity.
[0082] Moreover, the hydrostatic pressure supplying passages are
independently provided at the both end portions of the sleeve and
are separately communicated with the pressure source that can
supply the adequate quantity of high pressure fluid, whereby the
effect of the reduction of the pressure in the specific hydrostatic
pressure pocket row on other pocket rows is restricted and high
loading capability and bearing rigidity are obtained even if the
shaft is brought to a state where it is inclined relative the inner
periphery of the sleeve or deformed.
[0083] Moreover, the circular cylindrical inner peripheral surface
region in the inner periphery of the sleeve is arranged so as to be
interposed in the shaft axial direction by the hydrostatic pressure
pocket rows, in which the pressure is higher than the pressure in
the opened end portions of the sleeve, and the width of the
circular cylindrical inner peripheral surface region is made wider
than the sum of the widths of the hydrostatic pressure pocket rows
that are provided in the shaft axial direction, whereby in addition
to the increase in the pressure on the circular cylindrical inner
peripheral surface region at the time of the shaft rotation, a
ratio of dependency of the load carrying capacity on the pressure
produced on the circular cylindrical inner peripheral surface
region at the time of the eccentricity of the shaft is
increased.
[0084] Therefore, even if the supply pressure from the outside is
not increased, or even if the gap between the outer periphery of
the shaft and the inner periphery of the sleeve is not made narrow,
or even if the size of the sleeve is not increased, the loading
capability and bearing rigidity of the entire sliding bearing can
be effectively increased.
[0085] Moreover, according to the structure in which the
hydrostatic pressure pocket rows are respectively provided
adjacently to the both end portions of the sleeve, and the
hydrostatic pressure supplying passages that are respectively
communicated with the pocket rows are made independent from one
another and connected to the pressure source capable of supplying
the adequate quantity of high pressure, even if a specific part of
the gap is widened by the inclination of the shaft and the pressure
in the hydrostatic pressure pockets around the specific part of the
gap is reduced.
[0086] The reduction does not effect on other hydrostatic pressure
pocket rows, in addition to producing of a moment force tending to
return the posture of the shaft to its original posture even if the
shaft is inclined in the sleeve, so that it is possible to obtain
high loading capability and bearing rigidity even at the time of
the inclination of the shaft.
[0087] Moreover, the pump device according to the present invention
has the structure which encloses the sliding bearing according to
the present invention and supplies the pressure fluid to the
hydrostatic pressure pockets from the outlet port side of the pump
device, so that an additional pump device for supplying the
pressure fluid to the hydrostatic pressure pockets is not required,
thus making it possible to miniaturize the system.
[0088] Moreover, even if the gap between the outer periphery of the
shaft and the inner periphery of the sleeve is made wider in a
certain degree, or the shaft is inclined at a certain degree in the
sleeve, it is possible to produce and keep, on the circular
cylindrical inner peripheral surface region, the dynamic pressure
higher than the pressure of the fluid supplied to the hydrostatic
pressure pockets from the pump device.
[0089] Thereby, even in the large-sized pump device, in which the
rotational movement of the shaft is required to be stably supported
against the large thermal deformation, the manufacturing
tolerances, etc., such as the vertical axial pump device used in
the circulative cooling system of the fast breeder reactor, the
high loading capability and bearing rigidity of the bearing can be
obtained and the high reliability can be obtained.
[0090] For example, in the circulative cooling system of the fast
breeder reactor, fluid such as liquid sodium or the like is often
used as a cooling medium. In the pump device for transferring fluid
metal, the same fluid metal is required to be used for lubrication
in order that it is prevented from being mixed with other
substances.
[0091] Generally, the fluid metal has a nature exhibiting a
viscosity lower than that of a lubricating oil for a general
machine or water at a high temperature, and is poor in
lubricity.
[0092] Moreover, in the pump device, in addition to the requirement
of making the shaft for rotating the impeller longitudinal in order
to provide a shielding portion for radiation, it is hard to avoid
the inclination and deformation of the shaft in a certain degree
due to the thermal deformation and/or manufacturing tolerance since
the pump device handles high temperature fluid metal.
[0093] In the pump device according to the present invention, the
fluid that is brought into the high pressure by the impeller of the
pump device is supplied to the hydrostatic pressure pockets of the
sliding bearing enclosed, so that other substances may not get
mixed with the cooling medium in the pump device.
[0094] Moreover, according to the structure in which the fixed
circular cylindrical inner peripheral surface region is obtained at
the center of the sleeve inner periphery in the sliding bearing and
the hydrostatic pressure pocket rows are arranged at the both end
portions of the sleeve so as to interpose the circular cylindrical
inner peripheral surface region, the pressure on the circular
cylindrical inner peripheral surface region on which the dynamic
pressure is produced at the time of the shaft rotation is increased
and the high pressure is kept by the circular cylindrical inner
peripheral surface region, whereby it is possible to obtain the
high load carrying capacity and bearing rigidity even in the case
where a low viscosity fluid such as fluid metal which is poor in
lubricity is used.
[0095] The load carrying capacity of the sliding bearing
considerably depends upon the dynamic pressure particularly at the
time when the shaft is made eccentric and it is unnecessary to
externally install any device for particularly increasing the
pressure of the fluid supplied to the bearing, in order to obtain
the loading capability. Therefore, it is possible to make the pump
device simple and small-sized.
[0096] Moreover, even if the gap between the shaft outer periphery
and the sleeve inner periphery is made relatively wide, or in the
case where the shaft is brought to the posture inclined relative to
the sleeve inner periphery or deformed, the high loading capability
and bearing rigidity are obtained, so that the thermal deformation
and/or tolerance at the time of manufacturing are allowed and the
stable supporting of the shaft rotation is performed.
[0097] Moreover, the hydrostatic pressure pockets are arranged
adjacently to the end portions of the sleeve inner periphery, so
that even in a case where excessive load acts on the shaft and the
shaft that is inclined relative to the neighborhoods of the end
portions of the sleeve inner periphery is directly brought into
contact with the sleeve inner periphery, the fluid is supplied to
the circumference to perform cooling and lubrication, thus making
it to reduce damage due to wearing and/or seizure.
* * * * *