U.S. patent application number 15/503135 was filed with the patent office on 2017-08-10 for centrifugal rotary machine.
This patent application is currently assigned to MITSUBISHI HEAVY INDUSTRIES, LTD.. The applicant listed for this patent is MITSUBISHI HEAVY INDUSTRIES, LTD.. Invention is credited to Nobuyori YAGI.
Application Number | 20170226896 15/503135 |
Document ID | / |
Family ID | 55304044 |
Filed Date | 2017-08-10 |
United States Patent
Application |
20170226896 |
Kind Code |
A1 |
YAGI; Nobuyori |
August 10, 2017 |
CENTRIFUGAL ROTARY MACHINE
Abstract
Provided is the centrifugal rotary machine including: a rotor
having a rotary shaft rotating around an axis and impellers
rotating together with the rotary shaft; a casing surrounding the
rotor from an outer peripheral side; a plurality of diaphragms
stacked between the rotor and the casing in a direction of the axis
and configured to define a flow channel of a fluid fed under
pressure using the impellers; and the restraining members
configured to restrain the diaphragms from the outer peripheral
side.
Inventors: |
YAGI; Nobuyori; (Tokyo,
JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
MITSUBISHI HEAVY INDUSTRIES, LTD. |
Tokyo |
|
JP |
|
|
Assignee: |
MITSUBISHI HEAVY INDUSTRIES,
LTD.
Tokyo
JP
|
Family ID: |
55304044 |
Appl. No.: |
15/503135 |
Filed: |
January 16, 2015 |
PCT Filed: |
January 16, 2015 |
PCT NO: |
PCT/JP2015/051049 |
371 Date: |
February 10, 2017 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04D 29/083 20130101;
F04D 17/122 20130101; F04D 29/162 20130101; F05D 2300/432 20130101;
F04D 29/4206 20130101; F01D 25/164 20130101; F01D 25/246 20130101;
F01D 25/24 20130101; F04D 17/10 20130101 |
International
Class: |
F01D 25/24 20060101
F01D025/24; F01D 25/16 20060101 F01D025/16 |
Foreign Application Data
Date |
Code |
Application Number |
Aug 13, 2014 |
JP |
2014-164735 |
Claims
1. A centrifugal rotary machine comprising: a rotor having a rotary
shaft rotating around an axis and impellers rotating together with
the rotary shaft; a casing surrounding the rotor from an outer
peripheral side; a plurality of diaphragms stacked between the
rotor and the casing in an axial direction and configured to form a
flow channel of a fluid fed under pressure using the impellers; and
restraining members configured to restrain the diaphragms from the
outer peripheral side, wherein the restraining members are annular
rings fitted to outer peripheral surfaces of the diaphragms, and
outer peripheral surfaces of the rings are formed to come into
contact with an inner peripheral surface of the casing, and concave
grooves formed at regular intervals in a peripheral direction are
formed in outer peripheral surfaces of the restraining members.
2. (canceled)
3. The centrifugal rotary machine according to claim 1, wherein the
restraining members are made of a resin.
4.-5. (canceled)
6. The centrifugal rotary machine according to claim 1, wherein the
impellers include: a first impeller group disposed at a first side
in an axial direction and causing the fluid to flow toward a
central position in an axial direction of the rotary shaft; a
second impeller group disposed at a second side opposite to the
first side in the axial direction and causing the fluid to flow
toward the central position in the axial direction of the rotary
shaft; and bearings provided at both ends of the rotary shaft and
configured to rotatably support the rotary shaft, wherein the
restraining members are provided at positions of the diaphragms
near the central position.
7. The centrifugal rotary machine according to claim 3, wherein the
impellers include: a first impeller group disposed at a first side
in an axial direction and causing the fluid to flow toward a
central position in an axial direction of the rotary shaft; a
second impeller group disposed at a second side opposite to the
first side in the axial direction and causing the fluid to flow
toward the central position in the axial direction of the rotary
shaft; and bearings provided at both ends of the rotary shaft and
configured to rotatably support the rotary shaft, wherein the
restraining members are provided at positions of the diaphragms
near the central position.
Description
TECHNICAL FIELD
[0001] The present invention relates to a centrifugal rotary
machine having a plurality of vane wheels.
[0002] Priority is claimed on Japanese Patent Application No.
2014-164735, filed Aug. 13, 2014, the content of which is
incorporated herein by reference.
BACKGROUND ART
[0003] In centrifugal rotary machines such as centrifugal
compressors, generally, there are gaps between rotating bodies such
as rotary shaft and impellers (vane wheels), and stationary bodies
such as diaphragms in the vicinity of the rotating bodies. For this
reason, sealing devices configured to prevent a working fluid from
flowing into the gaps between the rotating bodies and the
stationary bodies may be provided in some cases. In the case of a
centrifugal compressor, sealing devices are provided at ferrule
portions of inlets of impellers, portions between stages of
multi-stage impellers, a balance piston portion provided at the
last stage of multi-stage impellers, and the like. For example, a
damper seal, a labyrinth seal, or the like is used for such sealing
devices.
[0004] In order to minimize a leakage in sealing devices, gaps
between seal members such as seal fins and rotating bodies are set
to a small dimension (for example, 0.1 mm to several mm). When a
centrifugal compressor is operated, deformation occurs in internal
components such as diaphragms, impellers, and the like of the
centrifugal compressor due to heat, stress, or a centrifugal force.
Thus, the rotating bodies may come into contact with a stationary
body in accordance with gaps between the sealing devices, which
causes unstable vibration of a rotary shaft.
[0005] In recent years, for example, in a centrifugal compressor
for a gas field, a discharge pressure has significantly
increasingly become higher. For example, a high pressure compressor
of which a discharge pressure is 20 MPa or more may be required.
For this reason, deformation of the stationary body or the rotating
bodies has tended to increase.
[0006] Also, for example, an absolute value of a differential
pressure of a pressure distribution occurring in the vicinity of
internal components such as diaphragms also increases along with an
increase in pressure of a centrifugal compressor. Thus, the
internal components are likely to be displaced. When gaps between
sealing devices are enlarged in consideration of such deformation
or displacement so that contact is prevented, this leads to
deterioration of performance of the centrifugal compressor. Thus,
it is difficult to set the gaps between the sealing devices.
[0007] Patent Literature 1 describes a centrifugal compressor
including anti-deformation rings of the sealing devices to suppress
deformation of the sealing devices.
CITATION LIST
Patent Literature
[0008] Patent Literature 1
[0009] Japanese Unexamined Patent Application, First Publication
No. 2011-32908
SUMMARY OF INVENTION
Technical Problem
[0010] However, in the structure disclosed in Patent Literature 1,
deformation or displacement of diaphragms cannot be suppressed.
Thus, gaps between sealing devices become non-uniform due to the
deformation or displacement of the diaphragms, which causes
unstable vibration of a rotary shaft.
[0011] An objective of the present invention is to provide a
centrifugal rotary machine in which deformation or displacement of
diaphragms is suppressed and thus unstable vibration of a rotary
shaft of the centrifugal rotary machine can be prevented.
Solution to Problem
[0012] According to a first aspect of the present invention, a
centrifugal rotary machine includes: a rotor having a rotary shaft
rotating around an axis and impellers rotating together with the
rotary shaft; a casing surrounding the rotor from an outer
peripheral side; a plurality of diaphragms stacked between the
rotor and the casing in an axial direction and configured to form a
flow channel of a fluid fed under pressure using the impellers; and
restraining members configured to restrain the diaphragms from the
outer peripheral side.
[0013] With such a constitution, restraining members serve to
suppress deformation or displacement of diaphragms so that a change
in relative position of a stationary body and a rotating body along
with deformation or displacement of the diaphragms is suppressed,
and thus contact between the stationary body and the rotating body
can be prevented.
[0014] In the centrifugal rotary machine, the restraining members
may be annular rings fitted to outer peripheral surfaces of the
diaphragms, and outer peripheral surfaces of the rings may be
formed to come into contact with an inner peripheral surface of the
casing.
[0015] With such a constitution, gaps between the diaphragms and
the casing can be kept constant. In other words, the diaphragms can
be prevented from being displaced in a radial direction. Also,
deformation of the diaphragms can also be suppressed. Thus, when
sealing devices are provided at diaphragms, the sealing devices can
be prevented from coming into contact with the rotating body at the
gaps.
[0016] In the centrifugal rotary machine, the restraining members
may be made of a resin.
[0017] With such a constitution, slidability between the casing and
the restraining members can be improved.
[0018] In the centrifugal rotary machine, concave grooves formed at
regular intervals in a circumferential direction may be formed in
outer peripheral surfaces of the restraining members.
[0019] With such a constitution, slidability between the casing and
the restraining members can be improved.
[0020] In the centrifugal rotary machine, the restraining members
may be key grooves formed to continue to the diaphragms which are
adjacent to each other and key members fitted into the key
grooves.
[0021] With such a constitution, the diaphragms joined in an axial
direction can be firmly coupled using the key members. Thus,
displacement of the diaphragms can be suppressed. In addition, when
sealing devices are provided at the diaphragms, the sealing devices
can be prevented from coming into contact with the rotating body at
the gaps.
[0022] In the centrifugal rotary machine, the impellers may
include: a first impeller group disposed at a first side in an
axial direction and causing the fluid to flow toward a central
position in an axial direction of the rotary shaft; a second
impeller group disposed at a second side opposite to the first side
in the axial direction and causing the fluid to flow toward the
central position in the axial direction of the rotary shaft; and
bearings provided at both sides of the rotary shaft and configured
to rotatably support the rotary shaft, wherein the restraining
members may be provided at positions of the diaphragms near the
central position.
[0023] With such a constitution, deformation or displacement of
diaphragms near the central position farthest away from the
bearings serving as supporting portions of the rotary shaft can be
effectively suppressed.
Advantageous Effects of Invention
[0024] According to the present invention, restraining members
serve to suppress deformation or displacement of diaphragms so that
a deformation or change in relative position of a stationary body
and a rotating body along with displacement of the diaphragms is
suppressed, and thus contact between the stationary body and the
rotating body can be prevented.
BRIEF DESCRIPTION OF DRAWINGS
[0025] FIG. 1 is a schematic cross-sectional view of a centrifugal
compressor of a first embodiment of the present invention.
[0026] FIG. 2 is a partially enlarged view of the centrifugal
compressor of the first embodiment of the present invention.
[0027] FIG. 3 is a view when a deformation restraining ring of a
modified example of the first embodiment of the present invention
is viewed in an axial direction thereof.
[0028] FIG. 4 is a view when a spacer of the modified example of
the first embodiment of the present invention is viewed in an axial
direction thereof.
[0029] FIG. 5 is a partially enlarged view of a centrifugal
compressor of a second embodiment of the present invention.
DESCRIPTION OF EMBODIMENTS
First Embodiment
[0030] Hereinafter, a centrifugal compressor serving as a
centrifugal rotary machine related to a first embodiment of the
present invention will be described.
[0031] As shown in FIG. 1, a centrifugal compressor 1 in this
embodiment is a single axis multistage type centrifugal compressor
including a plurality of impellers 3 (vane wheels).
[0032] The centrifugal compressor 1 has a rotor 2 rotating around
an axis P, a cylindrical casing 7 surrounding the rotor 2 from an
outer peripheral side, and a plurality of diaphragms 6 stacked
between the rotor 2 and the casing 7 in an axial direction and
configured to form a flow channel of a process gas G (a fluid) fed
under pressure using impellers 3.
[0033] The rotor 2 has a rotary shaft 4 and the plurality of
impellers 3 rotating together with the rotary shaft 4. The
impellers 3 are vane wheels attached to the rotary shaft 4 and
configured to compress the process gas G using a centrifugal
force.
[0034] A driver (not shown) such as a motor is coupled to the
rotary shaft 4, and the rotor 2 is rotatably driven by the
driver.
[0035] The rotary shaft 4 has a columnar shape and extends in an
axial direction P. The rotary shaft 4 is rotatably supported by
bearings 16 at both ends thereof in the axial direction P. Sealing
devices 5 are appropriately provided between the rotary shaft 4 and
the plurality of impellers 3 constituting the rotating bodies and
the diaphragms 6.
[0036] The plurality of impellers 3 are arranged between the
bearings 16 provided at both ends of the rotary shaft 4 in the
axial direction P. Furthermore, the plurality of impellers 3
constitute two-set three-stage impeller groups 3A and 3B in which
directions of blades face opposite sides in the axial direction P
of the rotary shaft 4. A first impeller group 3A and a second
impeller group 3B are attached to the rotary shaft 4 in a state in
which rear sides thereof face a central position C in the axial
direction P.
[0037] The first impeller group 3A is disposed at a first side (the
left side of FIG. 1) in the axial direction. The second impeller
group 3B is disposed at a second side (the right side of FIG. 1)
opposite to the first side in the axial direction. The impeller
groups 3A and 3B include three-stage compressor stages to
correspond to the impellers 3 arranged in the axial direction.
[0038] The impellers 3 include a substantially discoid disk 8 of
which a diameter gradually increases outward in a radial direction
with respect to the axis P toward the central position C of the
rotary shaft 4 in the axial direction P, a plurality of blades 9
radially provided at the disk 8 at intervals in a circumferential
direction with respect to the axis P, and a shroud 10 provided to
face the disk 8 and covering the plurality of blades 9.
[0039] The process gas G is compressed when it flows through the
first impeller group 3A and the second impeller group 3B toward the
central position C in the axial direction P.
[0040] The bearings 16 are provided at both ends of the rotary
shaft 4 one by one, and rotatably support the rotary shaft 4. As
the bearings 16, for example, journal bearings having a plurality
of bearing pads can be adopted.
[0041] The casing 7 is formed in a cylindrical shape, and a central
axis thereof coincides with the axis P. The casing 7 accommodates
the plurality of diaphragms 6 therein. The plurality of diaphragms
6 are provided to be stacked in the axial direction.
[0042] The plurality of diaphragms 6 are provided to correspond to
the compressor stages of the centrifugal compressor 1. To be
specific, the plurality of diaphragms 6 are constituted of a
plurality of diaphragms 6A corresponding to the first impeller
group 3A and a plurality of diaphragms 6B corresponding to the
second impeller group 3B. The plurality of diaphragms 6A
corresponding to the first impeller group 3A are connected via step
portions. The plurality of diaphragms 613 corresponding to the
second impeller group 3B are also connected via step portions. Note
that the diaphragms 6A and the diaphragms 6B, which are adjacent to
each other near the central position C, are in contact with each
other, but are not connected via the step portions.
[0043] Predetermined gaps S are formed between the cylindrical
casing 7 and the plurality of diaphragms 6. In other words, an
inner peripheral surface of the casing 7 and outer peripheral
surfaces of the plurality of diaphragms 6 are spaced apart from
each other via the predetermined gaps S. The gaps S are uniformly
provided in the axial direction and the peripheral direction.
[0044] Annular suction ports 11A formed at an outside in the radial
direction of an end at the first side in the axial direction are
formed inside the stacked diaphragms 6. Furthermore, connection
flow channels 12A are formed between the suction ports 11A and flow
channels of the impellers 3 positioned at one side of the
three-stage impeller group 3A and connect the flow channels of the
impellers 3 and the suction ports 11A. Thus, the process gas G can
be introduced from the outside into the three-stage impeller group
3A.
[0045] Connection flow channels 14A connected to the flow channels
of the impellers 3 positioned at the second side of the three-stage
impeller group 3A and extending outward in the radial direction are
formed inside the diaphragms 6. Annular discharge ports 15A
connected to the connection flow channels 14A and formed on an
outside in the radial direction of the central position C in the
axial direction are formed inside the diaphragms 6.
[0046] Also at a position at which the three-stage impeller group
3B is attached, casing flow channels 13B, suction ports 11B,
connection flow channels 12B and 14B, and discharge ports 15B are
formed inside the diaphragms 6. Furthermore, the casing flow
channels 13B, the suction ports 11B, the connection flow channels
12B and 14B, and the discharge ports 15B are disposed at positions
symmetrical with casing flow channels 13A, the suction ports 11A,
the connection flow channels 12A and 14A, and the discharge ports
15A, respectively, in the axial direction using the central
position C in the axial direction as a boundary.
[0047] A balance piston 17 configured to adjust thrust of the
impellers 3 is provided at an outer peripheral surface of the
rotary shaft 4 and between the three-stage impeller group 3A and
the three-stage impeller group 3B. In the centrifugal compressor 1
in this embodiment, the rotor 2 is constituted of the rotary shaft
4, the plurality of impellers 3, and the balance piston 17.
[0048] The process gas G is compressed in the three-stage impeller
group 3A and reaches a position near the central position C of the
rotary shaft 4. After that, the process gas G is introduced into
the three-stage impeller group 3B, is further compressed, and
reaches the position near the central position C again (refer to a
dotted line of FIG. 1). Therefore, a pressure difference occurs at
a position between the three-stage impeller group 3A and the
three-stage impeller group 3B serving as the central position C of
the rotary shaft 4.
[0049] The three types of sealing devices 5 are provided at the
centrifugal compressor 1 in this embodiment.
[0050] A first sealing device 5 is a first sealing device 5a
configured to seal gaps between an outer peripheral surface of the
balance piston 17 and the diaphragms 6. A second sealing device 5
is a second sealing device 5b configured to seal gaps between outer
peripheral surfaces of the shrouds 10 of the impellers 3 and the
diaphragms 6. A third sealing device 5 is a third sealing device 5c
configured to seal gaps between the outer peripheral surface of the
rotary shaft 4 and the diaphragms 6 between the impellers 3.
[0051] Here, the sealing devices 5 in this embodiment will be
described using the first sealing device 5a. The first sealing
device 5a prevents the process gas G from flowing from the
three-stage impeller group 3B to the three-stage impeller group 3A
along the axis P at the central position C using the pressure
difference between the three-stage impeller group 3A and the
three-stage impeller group 3B.
[0052] The sealing devices 5 has a sealing device main body
attached to the diaphragms 6 and a plurality of seal fins extending
from the sealing device main body toward the rotor 2. The plurality
of seal fins are directed toward the rotor 2, extend from the
sealing device main body to an inner peripheral side, and extend in
the peripheral direction. These seal fins form micro-gaps with
respect to the rotor 2 in the radial direction.
[0053] The sealing devices 5 forms a so-called labyrinth seal using
the plurality of seal fins. Note that a sealing structure used for
the sealing devices 5 can also adopt a damper seal (a hole pattern
seal or a honeycomb seal) without being limited to a labyrinth
seal.
[0054] The centrifugal compressor 1 in this embodiment includes
annular deformation restrain rings 20 configured to restrain the
diaphragms 6 from the outer peripheral side. In other words, the
deformation restrain rings 20 are cylindrical restraining members
with a predetermined thickness in the radial direction. In the case
of the deformation restrain rings 20, inner diameters of the
deformation restrain rings 20 are formed to be substantially the
same as or slightly smaller than diameters of the diaphragms 6. In
other words, the deformation restrain rings 20 have inner diameters
such that they are able to be fitted to the outer peripheral
surfaces of the diaphragms 6.
[0055] As shown in FIG. 2, in the case of the deformation restrain
rings 20, outer peripheral surfaces of the deformation restrain
rings 20 are formed to correspond to the inner peripheral surface
of the casing 7. In other words, in the case of the deformation
restrain rings 20, inner peripheral sides thereof are fixed to the
outer peripheral surfaces of the diaphragms 6, and outer peripheral
sides thereof are in contact with the inner peripheral surface of
the casing 7.
[0056] The deformation restrain rings 20 are disposed at the outer
peripheral surfaces of the diaphragms 6 along grooves for rings 21
formed on the outer peripheral surfaces of the diaphragms 6 in the
peripheral direction. Groove widths of the grooves for ring 21
correspond to widths of the deformation restrain rings 20.
[0057] The deformation restrain rings 20 are formed of a resin with
high slidability such as, for example, polytetrafluoroethylene
(PTFE). Materials forming the deformation restrain rings 20 are not
limited thereto, and any materials which have high slidability and
have lower rigidity than a material forming the casing 7 may be
adopted. For example, a polyacetal resin or the like can also be
adopted.
[0058] The deformation restrain rings 20 in this embodiment are
attached to two diaphragms 6 farthest away from the bearings 16
serving as a support point of the rotary shaft 4 among the
plurality of diaphragms 6. That is to say, the deformation restrain
rings 20 are attached to the diaphragms 6 near the discharge ports
15A and 15B. In other words, the deformation restrain rings 20 are
attached to the diaphragms 6A closest to the central position C
side among the plurality of diaphragms 6A corresponding to the
first impeller group 3A and the diaphragms 6B closest to the
central position C side among the plurality of diaphragms 6B
corresponding to the second impeller group 3B.
[0059] According to the above-described embodiment, the deformation
restrain rings 20 serving as the restraining members disposed at
the gaps S serve to suppress deformation or displacement of the
diaphragms 6. Thus, a change in relative position of a stationary
body and a rotating body such as the rotor 2 along with
displacement of the diaphragms 6 is suppressed, and thus contact
between the stationary body and the rotating body can be
prevented.
[0060] The restraining members are the annular deformation restrain
rings 20 fitted to the outer peripheral surfaces of the diaphragms
6, and the outer peripheral surfaces of the deformation restrain
rings 20 are formed to come into contact with the inner peripheral
surface of the casing 7. Thus, the gaps S between the diaphragms 6
and the casing 7 can be kept constant. Also, deformation of the
diaphragms 6 can also be suppressed. In other words, the diaphragms
6 can be prevented from being displaced in the radial direction.
Thus, the sealing devices 5 can be prevented from coming into
contact with the rotating body at the gaps.
[0061] The deformation restrain rings 20 are formed of a resin so
that slidability between the casing 7 and the deformation restrain
rings 20 can be improved.
[0062] The deformation restrain rings 20 are disposed near the
central position C so that displacement of the diaphragms 6 near
the central position C farthest away from the bearings 16 serving
as supporting portions of the rotary shaft 4 can be effectively
suppressed.
[0063] The deformation restrain rings 20 are disposed along the
grooves for ring 21 formed in the outer peripheral surfaces of the
diaphragms 6 so that the deformation restrain rings 20 can be
prevented from being shifted in the axial direction.
[0064] Note that it is assumed that the deformation restrain rings
20 in the above-described embodiment have the same cross-sectional
shape in the peripheral direction, but the present invention is not
limited thereto. For example, as in a modified example shown in
FIG. 3, concave grooves 24 formed at regular intervals in the
peripheral direction may be formed in outer peripheral surfaces of
deformation restrain rings 20B.
[0065] As in a modified example shown in FIG. 4, a plurality of
spacers 20C may be intermittently disposed in the peripheral
direction. For example, the spacers 20C may be adhered to the
diaphragms 6 such that the spacers 20C can be disposed at the gaps
between the diaphragms 6 and the casing 7.
[0066] According to the above-described modified examples,
slidability between the casing 7 and the restraining members 20B
and 20C can be improved.
Second Embodiment
[0067] Hereinafter, restraining members of a second embodiment of
the present invention will be described on the basis of the
drawings. Note that this embodiment will be described focusing on
differences from the above-described first embodiment and
descriptions of portions which are the same as those of the first
embodiment will be omitted.
[0068] As shown in FIG. 5, the restraining members in this
embodiment are key grooves 22 formed to continue to neighboring
diaphragms 6A and 6B disposed closest to a central position C and
key members 20D fitted into the key grooves 22. The two key grooves
22 and key members 20D are provided at both ends of diaphragms
6.
[0069] The key grooves 22 are grooves which extend in the axial
direction and of which cross-sectional shapes are rectangular
shapes.
[0070] The key members 20D are fitted into the key grooves 22
formed to continue to the diaphragms 6A and 6B. The key members 20D
may be fixed to the diaphragms 6 using fastening members such as
screws. Furthermore, the key members 20D are not limited to key
members in which both ends thereof have square shapes shown in FIG.
5. Key members in which at least one of both ends thereof has a
rounded shape may be adopted as the key members 20D. Shapes of the
key grooves 22 need not coincide with those of the key members 20D,
and lengths thereof in a longitudinal direction may be longer than
those of the key members 20D.
[0071] The two key grooves 22 and key members 20D are provided at
both ends of the diaphragms 6, but the present invention is not
limited thereto. In addition, they may be further provided at an
upper portion. Only one key groove 22 and one key member 20D may be
provided.
[0072] According to the above-described embodiments, the diaphragms
6 joined in the axial direction can be firmly coupled using the key
members 20D. Thus, displacement of the diaphragms 6 can be
suppressed. In addition, when sealing devices 5 are provided at the
diaphragms 6, the sealing devices 5 can be prevented from coming
into contact with the rotating body at the gaps.
[0073] Note that the technical scope of the present invention is
not limited to the above-described embodiments, and various
modifications are possible without departing from the gist of the
present invention.
[0074] For example, although the restraining members are applied to
the centrifugal compressor in the above-described embodiments, any
centrifugal rotary machines which have a rotor having impellers, a
casing surrounding the rotor from an outer peripheral side, and
diaphragms configured to define a flow channel of a fluid fed under
pressure using the impellers may be adopted. For example, the
restraining members in the above-described embodiments may be
applied to a centrifugal pump.
INDUSTRIAL APPLICABILITY
[0075] According to this centrifugal rotary machine, a change in
relative position of a stationary body and a rotating body along
with deformation or displacement of diaphragms is suppressed, and
thus contact between the stationary body and the rotating body can
be prevented.
REFERENCE SIGNS LIST
[0076] 1 Centrifugal compressor [0077] 2 Rotor [0078] 3 Impeller
[0079] 4 Rotary shaft [0080] 5 Sealing device [0081] 6, 6A, 6B
Diaphragm [0082] 7 Casing [0083] 8 Disk [0084] 9 Blade [0085] 10
Shroud [0086] 11A, 11B Suction port [0087] 12A, 12B, 14A, 14B
Connection flow channel (flow channel) [0088] 13A, 13B Casing flow
channel (flow channel) [0089] 15A, 15B Discharge port [0090] 16
Bearing [0091] 17 Balance piston [0092] 20, 20B Deformation
restrain ring (restraining member) [0093] 20C Spacer (restraining
member) [0094] 20D Key member [0095] 21 Grooves for ring [0096] 22
Key groove [0097] 24 Concave groove [0098] G Process gas (fluid)
[0099] P Axis [0100] S Gap
* * * * *