WO2016024409A1

WO2016024409A1 - Centrifugal rotary machine

Info

Publication number: WO2016024409A1
Application number: PCT/JP2015/051049
Authority: WO
Inventors: 信頼八木
Original assignee: 三菱重工業株式会社
Priority date: 2014-08-13
Filing date: 2015-01-16
Publication date: 2016-02-18
Also published as: EP3171037A1; CN106574635A; US20170226896A1; JP2016040461A; EP3171037A4

Abstract

Provided is a centrifugal rotary machine that comprises: a rotor (2) that has a rotary shaft (4) that rotates around an axis (P), and impellers (3) that rotate together with the rotary shaft (4); a casing (7) that surrounds the rotor (2) from an outer peripheral side; diaphragms (6) that are provided such that a plurality thereof are stacked in a direction of the axis (P) between the rotor (2) and the casing (7), and that define a flow channel for a fluid (G) that is pressure fed by the impellers (3); and restraining members (20) that restrain the diaphragms (6) from an outer peripheral side.

Description

Centrifugal rotating machine

The present invention relates to a centrifugal rotating machine having a plurality of impellers.
This application claims priority in Japanese Patent Application No. 2014-164735 for which it applied on August 13, 2014, and uses the content here.

Centrifugal rotating machines such as centrifugal compressors generally have a gap between a rotating body such as a rotating shaft / impeller (impeller) and a stationary body such as a surrounding diaphragm. Therefore, in many cases, a sealing device that suppresses the inflow of the working fluid is provided in the gap between the rotating body and the stationary body. In the case of a centrifugal compressor, the sealing device is provided at a cap portion at the inlet of the impeller, between each stage of the multistage impeller, and a balance piston portion provided at the final stage of the multistage impeller. For example, a damper seal or a labyrinth seal is used in such a sealing device.

In the sealing device, the gap between the sealing member such as a sealing fin and the rotating body is set to a small dimension (for example, 0.1 mm to several mm) in order to suppress the leakage amount. During operation of the centrifugal compressor, internal components such as a diaphragm of the centrifugal compressor, an impeller, and the like are deformed by heat, stress, and centrifugal force. This causes contact between the rotating body and the stationary body depending on the size of the gap of the sealing device, which causes unstable vibration of the rotating shaft.

In recent years, for example, in a centrifugal compressor for a gas field, an increase in discharge pressure has become remarkable. For example, a high pressure compressor having a discharge pressure of 20 MPa or more is required. For this reason, the deformation of the stationary body / rotating body tends to increase.
Further, with the increase in pressure of the centrifugal compressor, for example, the absolute value of the differential pressure of the pressure distribution generated around the inner parts such as a diaphragm also increases. Thereby, there is a possibility of displacing the inner part. If contact is prevented by enlarging the gap of the sealing device in consideration of such deformation / displacement, the performance of the centrifugal compressor will be reduced, so that it is difficult to set the gap of the sealing device.

Patent Document 1 describes a centrifugal compressor including a ring that resists deformation of a sealing device in order to suppress deformation of the sealing device.

JP 2011-32908 A

However, the structure described in Patent Document 1 cannot suppress the deformation and displacement of the diaphragm. This may cause unstable vibration of the rotating shaft due to non-uniform gaps in the sealing device due to deformation or displacement of the diaphragm.

An object of the present invention is to provide a centrifugal rotating machine that can prevent deformation and displacement of the diaphragm and prevent unstable vibration of the rotating shaft of the centrifugal rotating machine.

According to the first aspect of the present invention, the centrifugal rotating machine includes a rotor having a rotating shaft that rotates around an axis and an impeller that rotates together with the rotating shaft, a casing that surrounds the rotor from an outer peripheral side, the rotor, A plurality of layers stacked in the axial direction between the casing and a diaphragm defining a flow path of a fluid pumped by the impeller; and a restraining member for restraining the diaphragm from an outer peripheral side. It is characterized by.

According to such a configuration, the restraining member exhibits the function of suppressing the deformation and displacement of the diaphragm, thereby suppressing the change in the relative position between the stationary body and the rotating body due to the deformation and displacement of the diaphragm. And the rotating body can be prevented from contacting each other.

In the centrifugal rotating machine, the constraining member is an annular ring fitted to the outer peripheral surface of the diaphragm, and the outer peripheral surface of the ring is formed so as to contact the inner peripheral surface of the casing. It is good.

According to such a configuration, the gap between the diaphragm and the casing can be kept constant. In other words, the diaphragm can be prevented from being displaced in the radial direction. Moreover, the deformation of the diaphragm can also be suppressed. Thereby, when the sealing apparatus is provided in the diaphragm, the contact in the clearance gap between the sealing apparatuses can be prevented.

In the centrifugal rotating machine, the constraining member may be formed of resin.
According to such a configuration, the slidability between the casing and the restraining member can be improved.

In the centrifugal rotating machine, a concave groove formed at equal intervals in the circumferential direction may be formed on the outer peripheral surface of the restraining member.
According to such a configuration, the slidability between the casing and the restraining member can be improved.

In the centrifugal rotating machine, the constraining member may be a key groove formed continuously with the adjacent diaphragm and a key member fitted into the key groove.

According to such a configuration, it is possible to strengthen the coupling of the diaphragms continuous in the axial direction by using the key member. Thereby, it can suppress that a diaphragm displaces, and when the sealing apparatus is provided in the diaphragm, the contact in the clearance gap between sealing apparatuses can be prevented.

In the centrifugal rotating machine, the impeller is disposed on a first side in the axial direction and circulates the fluid toward a central position in the axial direction of the rotary shaft, and the first impeller in the axial direction. A second impeller group that is disposed on the second side opposite to the first side and circulates the fluid toward a central position in the axial direction of the rotating shaft, and is provided at both ends of the rotating shaft. A bearing that rotatably supports the rotating shaft, and the restraining member may be provided in the vicinity of the center position of the diaphragm.

According to such a configuration, it is possible to effectively suppress the deformation and displacement of the diaphragm located in the vicinity of the central position that is the farthest from the bearing that is the support portion of the rotating shaft.

According to the present invention, the restraining member exhibits the function of suppressing the deformation and displacement of the diaphragm, thereby suppressing the deformation and change of the relative position of the stationary body and the rotating body accompanying the displacement of the diaphragm, and rotating the stationary body and the stationary body. Contact with the body can be prevented.

It is a schematic sectional drawing of the centrifugal compressor of 1st embodiment of this invention. It is a partial enlarged view of the centrifugal compressor of the first embodiment of the present invention. It is the figure seen from the axial direction of the deformation | transformation restraint ring of the modification of 1st embodiment of this invention. It is the figure seen from the axial direction of the spacer of the modification of 1st embodiment of this invention. It is a partially expanded view of the centrifugal compressor of the second embodiment of the present invention.

(First embodiment)
Hereinafter, a centrifugal compressor which is a centrifugal rotating machine according to a first embodiment of the present invention will be described.
As shown in FIG. 1, the centrifugal compressor 1 of the present embodiment is a single-shaft multi-stage centrifugal compressor including a plurality of impellers 3 (impellers).

The centrifugal compressor 1 includes a rotor 2 that rotates about an axis P, a cylindrical casing 7 that surrounds the rotor 2 from the outer peripheral side, and a plurality of layers stacked in the axial direction between the rotor 2 and the casing 7. And a plurality of diaphragms 6 that form a flow path of a process gas G (fluid) to be pumped by the impeller 3.

The rotor 2 includes a rotating shaft 4 and a plurality of impellers 3 that rotate together with the rotating shaft 4. The impeller 3 is an impeller that is attached to the rotating shaft 4 and compresses the process gas G using centrifugal force.
The rotating shaft 4 is connected to a driving machine (not shown) such as a motor, and the rotor 2 is driven to rotate by this driving machine.

The rotary shaft 4 has a columnar shape and extends in the direction of the axis P. The rotating shaft 4 is rotatably supported by bearings 16 at both ends in the direction of the axis P. A sealing device 5 is appropriately provided between the rotating shaft 4 and the plurality of impellers 3 constituting the rotating body and the diaphragm 6.

The plurality of impellers 3 are arranged between the bearings 16 provided at both ends in the direction of the axis P of the rotating shaft 4. The plurality of impellers 3 constitute two sets of three-

stage impeller groups

3A and 3B in which the directions of the blades are opposite to each other in the direction of the axis P of the rotating shaft 4. The first impeller group 3 A and the second impeller group 3 B are attached to the rotating shaft 4 with their rear surfaces facing the center position C in the direction of the axis P.

The first impeller group 3A is disposed on the first side in the axial direction (left side in FIG. 1). The second impeller group 3B is disposed on the second side (the right side in FIG. 1) opposite to the first side in the axial direction. Each

impeller group

3A, 3B has three compressor stages corresponding to each impeller 3 arranged in the axial direction.

The impeller 3 has a substantially disk-shaped disk 8 that gradually expands radially outward of the axis P in the direction of the axis P of the rotary shaft 4 and a circumferential direction of the axis P on the disk 8. A plurality of blades 9 provided radially at intervals, and a shroud 10 provided to face the disk 8 and cover the plurality of blades 9 are provided.
The process gas G is compressed by flowing through each of the first impeller group 3A and the second impeller group 3B toward the center position C in the direction of the axis P.

The bearings 16 are provided one by one at both ends of the rotating shaft 4, and support the rotating shaft 4 so as to be rotatable. As the bearing 16, for example, a journal bearing having a plurality of bearing pads can be employed.

The casing 7 is formed in a cylindrical shape, and its central axis coincides with the axis P. The casing 7 accommodates a plurality of diaphragms 6 therein. The plurality of diaphragms 6 are provided so as to be stacked in the axial direction.

The plurality of diaphragms 6 are provided corresponding to the respective compressor stages of the centrifugal compressor 1. Specifically, the plurality of diaphragms 6 includes 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 a stepped portion. A plurality of diaphragms 6B corresponding to the second impeller group 3B are also connected via a stepped portion. In addition, the diaphragm 6A and the diaphragm 6B which are adjacent in the vicinity of the center position C are in contact with each other, but are not connected via a stepped portion.

A predetermined gap S is formed between the cylindrical casing 7 and the plurality of diaphragms 6. That is, the inner peripheral surface of the casing 7 and the outer peripheral surfaces of the plurality of diaphragms 6 are separated from each other via a predetermined gap S. The gap S is uniformly provided in the axial direction and the circumferential direction.

In the laminated diaphragm 6, an annular suction port 11 A is formed at a position on the radially outer side of the end portion on the first side in the axial direction. Further, a connection flow path 12A is formed between the suction port 11A and the flow path of the impeller 3 located on one side of the three-stage impeller group 3A, and the flow path of the impeller 3 and the suction port 11A. And connected. Thereby, the process gas G can be introduced into the three-stage impeller group 3A from the outside.

Inside the diaphragm 6, there is formed a connection flow path 14A that is connected to the flow path of the impeller 3 located on the second side of the three-stage impeller group 3A and extends outward in the radial direction. Inside the diaphragm 6, an annular discharge port 15 A is formed at a position that is connected to the connection flow path 14 A and is radially outside at the central position C in the axial direction.

Even at the position where the three-stage impeller group 3B is attached, a casing flow path 13B, a suction port 11B,

connection flow paths

12B and 14B, and a discharge port 15B are formed inside the diaphragm 6. And these are arrange | positioned in the position symmetrical with respect to the axial direction with respect to the casing flow path 13A, the suction inlet 11A, the

connection flow paths

12A and 14A, and the discharge outlet 15A with the central position C in the axial direction as a boundary.

Further, a balance piston 17 for adjusting the thrust of the impeller 3 is provided on the outer peripheral surface of the rotating shaft 4 and between the three-stage impeller group 3A and the three-stage impeller group 3B. In the centrifugal compressor 1 of the present embodiment, the rotor 2 is constituted by the rotating shaft 4, the plurality of impellers 3, and the balance piston 17.

The process gas G that has been compressed in the three-stage impeller group 3A and reaches the vicinity of the central position C of the rotating shaft 4 is then introduced into the three-stage impeller group 3B and further compressed, and again near the central position C. (See dotted line in FIG. 1). Therefore, a pressure difference is generated between the three-stage impeller group 3A and the three-stage impeller group 3B, which are the central position C of the rotating shaft 4.

The centrifugal compressor 1 of the present embodiment is provided with three types of sealing devices 5.
The first sealing device 5 is a first sealing device 5 a that seals the gap between the outer peripheral surface of the balance piston 17 and the diaphragm 6. The second sealing device 5 is a second sealing device 5 b that seals the gap between the outer peripheral surface of the shroud 10 of the impeller 3 and the diaphragm 6. The third sealing device 5 is a third sealing device 5 c that seals the gap between the outer peripheral surface of the rotating shaft 4 and the diaphragm 6 during the break of the impeller 3.

Here, the sealing device 5 of the present embodiment will be described using the first sealing device 5a. In the first sealing device 5a, the process gas G moves from the three-stage impeller group 3B to the three-stage impeller group 3A at the central position C due to the pressure difference between the three-stage impeller group 3A and the three-stage impeller group 3B. , So as to prevent circulation along the axis P.

The seal device 5 has a seal device body attached to the diaphragm 6 and a plurality of seal fins extending from the seal device body toward the rotor 2. The plurality of seal fins extend toward the rotor 2 from the seal device main body to the inner peripheral side, and extend in the circumferential direction. These seal fins form a minute gap with the rotor 2 in the radial direction.

The sealing device 5 constitutes a so-called labyrinth seal by a plurality of seal fins. The seal structure used in the seal device 5 is not limited to the labyrinth seal, and a damper seal (hole pattern seal, honeycomb seal) can also be used.

The centrifugal compressor 1 of this embodiment includes an annular deformation restraining ring 20 that restrains the diaphragm 6 from the outer peripheral side. In other words, the deformation restraining ring 20 is a restraining member having a cylindrical shape having a predetermined thickness in the radial direction. The deformation restraining ring 20 is formed so that the inner diameter of the deformation restraining ring 20 is substantially the same as or slightly smaller than the diameter of the diaphragm 6. That is, the deformation restraining ring 20 has an inner diameter that can be fitted to the outer peripheral surface of the diaphragm 6.

As shown in FIG. 2, the deformation restriction ring 20 is formed so that the outer peripheral surface of the deformation restriction ring 20 abuts on the inner peripheral surface of the casing 7. That is, the deformation restraining ring 20 has an inner peripheral side fixed to the outer peripheral surface of the diaphragm 6 and an outer peripheral side in contact with the inner peripheral surface of the casing 7.
Moreover, the deformation | transformation restraint ring 20 is arrange | positioned so that the groove | channel 21 for rings formed in the outer peripheral surface of the diaphragm 6 over the circumferential direction may be followed. The groove width of the ring groove 21 corresponds to the width of the deformation restraining ring 20.

The deformation restraining ring 20 is made of, for example, a resin having high slidability such as polytetrafluoroethylene (PTFE). The material forming the deformation restraining ring 20 is not limited to this, and any material may be used as long as it has high slidability and lower rigidity than the material forming the casing 7. For example, a polyacetal resin can be used.

The deformation restraining ring 20 of the present embodiment is attached to two diaphragms 6 that are the farthest from the bearing 16 that is the support point of the rotating shaft 4 among the plurality of diaphragms 6. That is, the deformation restraining ring 20 is attached to the diaphragm 6 in the vicinity of the

discharge ports

15A and 15B. In other words, the deformation restraining ring 20 has the diaphragm A on the most central position C side among the plurality of diaphragms 6A corresponding to the first impeller group 3A and the centermost among the plurality of diaphragms 6B corresponding to the second impeller group 3B. It is attached to the diaphragm 6B on the position C side.

According to the above embodiment, the deformation restraining ring 20 which is a restraining member disposed in the gap S exhibits a function of suppressing deformation and displacement of the diaphragm 6. Thereby, the change of the relative position of the stationary body and the rotating body such as the rotor 2 accompanying the displacement of the diaphragm 6 can be suppressed, and the contact between the stationary body and the rotating body can be prevented.

Further, the restraining member is an annular deformation restraining ring 20 fitted to the outer peripheral surface of the diaphragm 6, and the outer peripheral surface of the deformation restraining ring 20 is formed so as to contact the inner peripheral surface of the casing 7. Thereby, the gap S between the diaphragm 6 and the casing 7 can be kept constant. Further, the deformation of the diaphragm 6 can be suppressed. In other words, the diaphragm 6 can be prevented from being displaced in the radial direction. Thereby, the contact in the clearance gap between the sealing devices 5 can be prevented.

Further, since the deformation restraining ring 20 is formed of resin, the slidability between the casing 7 and the deformation restraining ring 20 can be improved.
In addition, by disposing the deformation restraining ring 20 in the vicinity of the center position C, it is possible to effectively suppress the displacement of the diaphragm 6 located in the vicinity of the center position C that is the farthest from the bearing 16 that is the support portion of the rotating shaft 4. it can.
Further, by disposing the deformation restricting ring 20 along the ring groove 21 formed on the outer peripheral surface of the diaphragm 6, it is possible to prevent the deformation restricting ring 20 from being displaced in the axial direction.

In addition, although the deformation | transformation restraint ring 20 of the said embodiment shall have the same cross-sectional shape over the circumferential direction, it is not restricted to this. For example, as in the modification shown in FIG. 3, the grooves 24 formed at equal intervals in the circumferential direction may be formed on the outer peripheral surface of the deformation restraining ring 20B.
Moreover, it is good also as a structure which arrange | positions the some spacer 20C intermittently in the circumferential direction like the modification shown in FIG. The spacer 20 C can be disposed in the gap between the diaphragm 6 and the casing 7, for example, by adhering to the diaphragm 6.
According to the modified example, the slidability between the casing 7 and the restraining members 20B and 20C can be improved.

(Second embodiment)
Hereinafter, the restraining member of the second embodiment of the present invention will be described with reference to the drawings. In the present embodiment, differences from the first embodiment described above will be mainly described, and description of similar parts will be omitted.
As shown in FIG. 5, the constraining member of the present embodiment is fitted in the key groove 22 and the key groove 22 formed continuously from the adjacent diaphragms 6 A and 6 B arranged closest to the center position C. This is a key member 20D. The key groove 22 and the key member 20 D of the present embodiment are provided at two locations on both sides of the diaphragm 6.

The key groove 22 is a groove having a rectangular cross-sectional shape extending in the axial direction.
The key member 20D is fitted into a key groove 22 formed continuously with the

diaphragms

6A and 6B. The key member 20D may be fixed to the diaphragm 6 using a fastening member such as a screw. Further, the key member 20D may employ not only a rectangular shape at both ends as shown in FIG. 5 but also a circular shape at least one of both ends. The key groove 22 does not need to have the same shape as the key member 20D, and the length in the longitudinal direction may be longer than that of the key member 20D.
The key groove 22 and the key member 20D are provided at two locations on both sides of the diaphragm 6. However, the present invention is not limited to this and may be provided further upward. Moreover, it is good also as a structure which provides the key groove 22 and the key member 20D only in one place.

According to the above embodiment, the coupling of the diaphragms 6 that are continuous in the axial direction can be strengthened by using the key member 20D. Thereby, it can suppress that the diaphragm 6 displaces, and when the sealing apparatus 5 is provided in the diaphragm 6, the contact in the clearance gap between the sealing apparatuses 5 can be prevented.

The technical scope of the present invention is not limited to the above embodiment, and various modifications can be made without departing from the spirit of the present invention.
For example, in each of the above embodiments, the constraining member is applied to a centrifugal compressor, but a rotor having an impeller, a casing that surrounds the rotor from the outer peripheral side, and a diaphragm that defines a flow path of fluid that is pumped by the impeller, Any centrifugal rotating machine may be used. For example, you may apply the constraining member of said each embodiment to a centrifugal pump.

According to this centrifugal rotating machine, it is possible to suppress a change in the relative position between the stationary body and the rotating body due to the deformation and displacement of the diaphragm, and to prevent contact between the stationary body and the rotating body.

DESCRIPTION OF SYMBOLS 1 Centrifugal compressor 2 Rotor 3 Impeller 4 Rotating shaft 5

Sealing device

6, 6A, 6B Diaphragm 7 Casing 8 Disc 9 Blade 10

Shroud

11A,

11B Suction port

12A, 12B, 14A, 14B Connection flow path (flow path)
13A, 13B Casing channel (channel)
15A, 15B Discharge port 16 Bearing 17

Balance piston

20, 20B Deformation restraint ring (restraint member)
20C spacer (restraint member)
20D Key member 21 Ring groove 22 Key groove 24 Concave groove G Process gas (fluid)
P axis S S clearance

Claims

A rotor having a rotating shaft that rotates around an axis and an impeller that rotates together with the rotating shaft;
A casing surrounding the rotor from the outer peripheral side;
A diaphragm that is provided so as to be stacked in the axial direction between the rotor and the casing, and forms a flow path of fluid to be pumped by the impeller;
And a constraining member for constraining the diaphragm from the outer peripheral side.
The centrifugal restraint according to claim 1, wherein the restraining member is an annular ring fitted to the outer peripheral surface of the diaphragm, and the outer peripheral surface of the ring is formed so as to abut on the inner peripheral surface of the casing. Rotating machine.
The centrifugal rotating machine according to claim 2, wherein the restraining member is made of resin.
The centrifugal rotating machine according to claim 2 or 3, wherein concave grooves formed at equal intervals in the circumferential direction are formed on the outer peripheral surface of the restraining member.
The centrifugal rotating machine according to claim 1, wherein the restraining member is a key groove formed continuously with the adjacent diaphragm and a key member fitted into the key groove.
The impeller is
A first impeller group arranged on the first side in the axial direction to circulate the fluid toward a central position in the axial direction of the rotating shaft;
A second impeller group disposed on the second side opposite to the first side in the axial direction and configured to circulate the fluid toward a central position in the axial direction of the rotating shaft, and
Provided at both ends of the rotating shaft, bearings that rotatably support the rotating shaft,
The centrifugal rotating machine according to any one of claims 1 to 5, wherein the restraining member is provided in the vicinity of the center position of the diaphragm.