WO2012124293A1

WO2012124293A1 - Multistage centrifugal compressor and turbo refrigeration machine using same

Info

Publication number: WO2012124293A1
Application number: PCT/JP2012/001552
Authority: WO
Inventors: 直人阪井; 隼人坂本; 正史山内
Original assignee: 川崎重工業株式会社
Priority date: 2011-03-16
Filing date: 2012-03-07
Publication date: 2012-09-20
Also published as: JP5722673B2; JP2012193653A

Abstract

A rotor (9) is formed integrally with a rotary shaft (8) by arranging a front-stage and a rear-stage impeller (4, 6) back to back. A front-stage intake port (52), front-stage discharge flow paths (54, 55) arranged at the outer periphery of the front-stage impeller (4), a rear-stage intake port (72), and rear-stage discharge flow paths (74, 75) arranged at the outer periphery of the rear-stage impeller (6) are provided in housings (5, 7), which house this rotor, and the front-stage discharge flow path (55) and the rear-stage intake port (72) communicate by means of a gas flow channel (57). When the rotor (9) is formed with a metal material, a circular groove (90) opening toward the outer peripheral side can be formed between the front-stage and rear-stage impellers (4, 6).

Description

Multistage centrifugal compressor and turbo refrigerator using the same

The present invention relates to a multi-stage compressor in which at least two centrifugal impellers are provided side by side in the axial direction of a rotary shaft, and the gas compressed by the front stage impeller is further compressed by the rear stage impeller.

As is conventionally known, a centrifugal turbo compressor imparts energy to a gas by a rotating centrifugal impeller (hereinafter simply referred to as an impeller) to increase its pressure. Since there is a certain restriction between the flow rate of the gas flowing through the impeller flow path and the pressure ratio, in order to achieve a higher pressure ratio, multiple impellers are connected in series and compressed in multiple stages. The formula is used.

Here, in general, in a centrifugal compressor, a larger pressure ratio is obtained as the number of revolutions of the impeller increases. Therefore, in the multistage type as described above, the number of stages is reduced by increasing the pressure ratio of each stage. It becomes possible to reduce the size and the number of parts. For this reason, there has been a demand for higher rotation in conventional multistage centrifugal compressors, but there has been a limit to higher rotation due to structural limitations.

That is, in the centrifugal compressor, the impeller and the rotating shaft are usually processed and fitted together in consideration of the manufacturing cost. In this case, the inner diameter of the center hole of the impeller is made smaller than the outer diameter of the rotating shaft, and the rotating shaft is press-fitted here, or the impeller is heated and expanded (so-called shrink fitting). An interference fit is employed.

However, if the impeller rotation speed increases, the centrifugal force increases at an accelerated rate, so the tightening margin is insufficient. In other words, the impeller that rotates at a high speed expands due to centrifugal force, and the inner peripheral surface of the center hole appears to float from the outer peripheral surface of the rotating shaft, so that the center of gravity of the impeller deviates from the center of rotation and unbalance vibration occurs. There was a fear. In addition, since a large tensile stress acts in the circumferential direction on the inner peripheral surface of the central hole of the impeller that rotates at a high speed, there is a possibility that a problem in strength may occur as the rotation speed increases.

In this regard, in the centrifugal compressor disclosed in Patent Document 1, the above-described problem occurs by providing a shaft portion forming a part of the rotating shaft integrally with each of the plurality of impellers arranged in the axial direction of the rotating shaft. I try not to. And the shaft part of the impeller of each stage is arranged on the same axis line, and the end parts of the adjacent shaft parts are connected to each other, so that a plurality of impellers are joined together to constitute a multistage rotor.

Japanese Patent Laid-Open No. 2003-293988

However, in the conventional example, it is necessary to provide a fitting portion for connecting the shaft portion between the adjacent impellers, and a certain amount of space is required in consideration of workability. There is a tendency that the dimension of the rotor increases in the direction of the center (axial direction).

In addition, since the back surface of the impeller has a planar shape perpendicular to the rotation axis, there is a possibility that a problem of stress concentration may occur at the boundary (heel portion) with the shaft portion. That is, generally, in a disk rotating at a high speed, a tensile stress σ _r in the radial direction is generated directly by centrifugal force as shown in FIG. 5, and this also causes a tensile stress σ _{θ in the} circumferential direction. appear. And in the part where there is an impeller with a large outer diameter, the stress becomes large as shown on the right side of the figure, while on the shaft part with a small outer diameter, the stress becomes small as shown on the left side of the figure. If the back surface of the impeller is planar, the stress distribution state changes abruptly at the boundary with the shaft portion, and a problem due to stress concentration is likely to occur.

In order to avoid such a problem due to stress concentration, for example, the back surface of the impeller is gradually raised on the inner peripheral side, and a curved shape that gently connects to the shaft portion may be considered. Will become longer in the axial direction.

Further, in the multistage rotor of the conventional example, since the plurality of impellers are all arranged in the same direction, the gas flow is directed from the outer peripheral side of the front impeller toward the suction port on the inner peripheral side of the adjacent rear impeller. The return channel must be provided so as to be folded, and if the gas flow is to be smoothly folded, the interval between adjacent impellers will naturally increase.

Focusing on this point, an object of the present invention is to increase the rotation speed of the multistage centrifugal compressor and to reduce the dimension in the rotation axis direction as much as possible.

In order to achieve the above object, the present invention provides a multi-stage centrifugal system in which at least two centrifugal impellers are arranged in the axial direction of the rotary shaft, and the gas compressed by the front impeller is further compressed by the rear impeller. The compressor is the target.

The front stage and rear stage impellers are arranged back to back and formed integrally with the rotary shaft, and a housing that accommodates the front stage and the rear stage impeller includes a front stage suction port facing the axial direction of the front stage impeller, and a front stage impeller. A front-stage discharge flow path disposed on the outer periphery of the impeller, a rear-stage suction port facing the axial direction of the rear-stage impeller, and a rear-stage discharge flow path disposed on the outer periphery of the rear-stage impeller. The discharge passage and the suction port at the latter stage are communicated with each other through a gas guide passage.

In a multistage centrifugal compressor having such a configuration, at least two impellers are back-to-back and integrated with the rotary shaft, so that the center of gravity of the impeller does not deviate from the center of rotation unlike conventional ones and is unbalanced. There is no worry of vibration. A heel portion where stress concentration occurs at the boundary between the impeller and the rotating shaft is not formed, which is advantageous for high rotation.

Further, there is no provision of a joint (fitting portion) on the rotating shaft between the adjacent impellers as in the multistage rotor of the above-described conventional example (Patent Document 1), and the gas flows in from the discharge channel in the previous stage. Since the guide channel is communicated with the rear suction port behind the rear impeller, a space for providing the gas guide channel between the two impellers is unnecessary. Therefore, the axial dimension of the multistage compressor can be shortened as much as possible.

The rotating shaft and the front and rear impellers may be integrally formed of, for example, a metal material. In this case, an annular groove that is open toward the outer peripheral side may be formed between the two impellers. Good. In general, when the impeller is formed of a metal material, heat treatment (for example, quenching is required for iron-based materials and solution treatment is used for aluminum alloys) is required. However, as described above, an annular groove between two impellers is required. If a large diameter impeller is manufactured, heat treatment can be performed up to the center of the rotating shaft.

In this case, the housing is provided with an annular partition wall portion for partitioning the storage chambers of the front and rear impellers so as to be inserted from the outer peripheral side of the annular groove portion. A seal may be provided between a portion on the inner peripheral side and a portion on the inner peripheral side of the annular groove portion. That is, a seal must be provided between the front and rear impeller housing chambers having different pressures in order to reduce gas leakage, but if this seal is provided on the inner peripheral side of the annular groove, its outer periphery Compared with the provision at the side portion, the area of the leakage gap is small, which is advantageous in terms of improving the sealing performance and cost.

From the viewpoints of both the heat treatment and the sealing properties, the inner circumferential diameter of the annular groove is preferably as small as possible, but if the inner diameter is too small, stress concentration tends to be a problem, so the inner diameter of the annular groove is You may set larger than the outer diameter of a rotating shaft. Further, in order to alleviate the stress concentration at the inner circumferential end of the annular groove, the groove width at least at the inner circumferential side of the annular groove may be gradually reduced toward the inner circumferential side.

As described above, according to the multistage centrifugal compressor according to the present invention, at least two front-stage and rear-stage impellers are arranged back to back and integrally formed with the rotating shaft, and the rear-stage impeller is discharged from the discharge channel on the outer periphery of the front-stage impeller. By providing the gas guide flow path to the rear suction port, the axial dimension of the multistage compressor can be shortened as much as possible while increasing the rotation speed of the impeller.

It is sectional drawing which shows schematic structure of the multistage centrifugal compressor which concerns on embodiment of this invention. It is a perspective view of the rotor with which the impeller and the rotating shaft were integrated. It is an enlarged view showing the mutual positional relationship of the annular groove of a rotor, and a partition wall. FIG. 6 is a view corresponding to FIG. 1 according to another embodiment in which no annular groove is provided between the impellers. It is explanatory drawing showing the stress distribution state of the rotating disc.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. In the following description, the same or corresponding elements are denoted by the same reference symbols throughout all the drawings, and redundant description thereof is omitted.

As an example, the multistage centrifugal compressor 1 according to the embodiment of the present invention is shown in FIG. 1 in a case of two stages. After compressing the gas R1 sucked in the compressor front stage 1F on the left side of FIG. The compressor is further compressed by the rear stage 1R of the compressor on the right side. The compressor front stage 1F includes a front stage impeller 4 and a front stage housing 5 that accommodates the front stage impeller 4, and the compressor rear stage 1R similarly includes a rear stage impeller 6 and a housing 7. As will be described in detail later, in the present embodiment, two

impellers

4 and 6 at the front stage and the rear stage are integrated back to back, and the rotary shaft 8 is also integrated to form the rotor 9.

Both the front and

rear housings

5 and 7 are formed by casting, for example, using a metal material, and the rear wall of the front housing 5 and the front wall of the rear housing 7 are overlapped and integrated, The rotor 9 is accommodated in the interior. An opening 50 having a circular cross section is formed at substantially the center of the two overlapped walls, and the impeller 4 in the previous stage is accommodated by the annular partition wall 10 fitted in the inner periphery of the opening 50. A front impeller housing chamber 51 and a rear impeller housing chamber 71 for housing the rear impeller 6 are partitioned.

The front housing 5 is provided with a suction port 52 having a circular cross section that communicates with the front impeller housing chamber 51 and opens in front of the impeller 4. The front half of the rotary shaft 8 communicates with the suction port 52. An intake passage portion 53 extends forward so as to surround the. On the other hand, a diffuser 54 is provided concentrically so as to surround the outer periphery of the impeller 4 and communicated with the outer peripheral side of the impeller accommodating chamber 51, and a spiral volute 55 (scroll) is provided so as to surround the periphery. Is also provided. The diffuser 54 and the volute 55 surround the outer periphery of the front impeller 4 and constitute a discharge flow path for the front discharge gas R2.

Similarly, the rear housing 7 is also provided with an impeller accommodating chamber 71, a suction port 72, an intake passage portion 73, a diffuser 74 and a volute 75, and the rear stage impeller 6 surrounds the outer periphery of the rear impeller 6 by the volute 75 and the diffuser 74. A discharge flow path for the discharge gas R3 is configured. Further, an intermediate duct 57 is provided as a gas guiding channel for guiding the upstream discharge gas R2 from the outlet of the upstream volute 55 to the inlet 73a of the downstream intake passage 73. In addition, although the vane is provided in each of the

diffusers

54 and 74 shown in FIG. 1, the vane may not be provided.

-Rotor structure-
The rotor 9 housed in the front and

rear housings

5 and 7 is, as an example, the axis of the rotating shaft 8 that extends in a generally horizontal direction (the left-right direction in FIG. 1, the left side being the front and the right side also being the rear). In the direction of the core 8a (axial direction), the two

impellers

4 and 6 are integrated in a back-to-back arrangement substantially from the center to a little rearward. As shown in FIG. 2, the two

impellers

4 and 6 are provided so as to expand toward the center of the rotating shaft 8, in other words, radially outward as they approach each other.

The front impeller 4 that appears on the left front side in FIG. 2 is a concave curved surface in which the surface of the hub 40 gradually increases in diameter from the front to the rear, and a plurality of blades 41 that extend radially on the inner and outer peripheries are arranged around each other. The hubs 40 are juxtaposed over the entire circumference of the hub 40 with an interval in the direction. When viewed in the axial direction, the blade 41 is curved so that the outer peripheral side of the hub 40 is positioned on the rear side in the rotational direction of the impeller 4. Further, as an example, in the impeller 4 of FIG. 2, the blade 41 is relatively short over the inner and outer periphery of the hub 40, and the inner peripheral end is extended toward the outer peripheral surface of the rotating shaft 8 and is curved forward in the rotational direction of the impeller 4. The relatively long ones are arranged alternately.

The rear impeller 6 located in the right back of FIG. 2 is basically the same structure as the front impeller 4 and will not be described. Reference numeral 60 is assigned to the hub of the impeller 6, and reference numeral 61 is assigned to the blade. The rotor 9 composed of the two

impellers

4 and 6 and the rotating shaft 8 is obtained by cutting a workpiece integrally formed by casting using a metal material, for example, when machining the surfaces of the

hubs

40 and 60. Then, the

blades

41 and 61 are cut out. The workpiece is then subjected to heat treatment (quenching for iron-based materials, solution treatment for aluminum alloys, etc.) before, during, or during the machining process.

In the rotor 9, an annular groove 90 is formed between the two

impellers

4 and 6 and is opened toward the outer peripheral side so as to separate them. The bottom surface of the annular groove 90, that is, the innermost peripheral surface thereof is located slightly outward from the outer peripheral surface of the rotary shaft 8 in the radial direction of the rotary shaft 8. If the annular groove 90 is formed in this way, the distance from the bottom surface to the central portion of the rotating shaft 8 is shortened as can be seen from FIG. 1, so that the rotating shaft can be located even between the two

impellers

4 and 6. Heat treatment can be effectively performed up to the center of 8.

This is effective when the

impellers

4 and 6 have a relatively large diameter, for example, 50 cm or more, and when the

impellers

4 and 6 are small, effective heat treatment can be performed without the annular groove 90. . From the viewpoint of heat treatment, it is desirable that the annular groove 90 is deep (inner diameter is small). On the other hand, if the annular groove 90 is deep, a problem of stress concentration occurs at the boundary between the side surface and the bottom surface. There is a fear.

That is, as described above with reference to FIG. 5, tensile stresses σ _r and σ _θ are generated in both the radial direction and the circumferential direction by the centrifugal force on the disk that rotates at high speed. On the other hand, the tensile stresses σ _r and σ _θ also increase at a portion having a large outer diameter, while the tensile stresses σ _r and σ _θ also decrease at a portion having a small outer diameter such as the bottom of the annular groove 90. This stress difference increases as the annular groove 90 becomes deeper, and the stress distribution state may change suddenly at the bottom of the annular groove 90 to cause stress concentration.

In this regard, in the present embodiment, the depth of the annular groove 90, that is, the inner peripheral diameter thereof is made larger than the outer diameter of the rotary shaft 8, and the change in stress at the bottom portion is alleviated as a U-shaped cross section as a whole. is doing. That is, as shown in an enlarged view in FIG. 3, the annular groove 90 inclines the side surface 90 a so that the groove width gradually decreases from the outer periphery toward the inner periphery, and the inner peripheral end portion (in FIG. 3). A curved portion 90c that is curved so as to be smoothly connected to the bottom surface 90b is formed at the lower end portion, and the centrifugal stress can be gradually changed in the curved portion 90c.

An annular partition wall 10 is inserted into the annular groove 90 from the outer peripheral side (upper side in FIG. 3) to partition the front impeller housing chamber 51 and the rear impeller housing chamber 71. Yes. That is, in the opening 50 of the double wall at the center of the

housings

5 and 7, a ring groove is formed over the entire circumference of the inner peripheral surface, and the ridge 10 a on the outer peripheral surface of the partition wall 10 is fitted therein. ing. Although illustration is omitted, the partition wall 10 is composed of two halved members, which are inserted into the annular grooves 90 of the rotor 9 and accommodated in the

housings

5 and 7 in a state of being fitted to each other.

Further, the side surface of the partition wall 10 is inclined in the same manner as the side surface 90a of the adjacent annular groove 90, and the thickness of the partition wall 10 gradually decreases from the outer peripheral end toward the inner peripheral side. A labyrinth seal 11 is provided between the inner peripheral end face 10 b of the partition wall 10 and the bottom face 90 b of the annular groove 90, and the higher-pressure impeller housing chamber 71 leads to the front-stage impeller housing chamber 51. Gas leakage is suppressed.

The labyrinth seal 11 has an annular fin formed of an elastic material such as metal or resin as is well known in the art in the axial direction on the inner peripheral end face 10b of the partition wall 10 on the fixed side in the example of FIG. A plurality of them are mounted and fixed side by side. Thus, if the labyrinth seal 11 is provided between the inner peripheral end face 10b of the partition wall 10 and the bottom face 90b of the annular groove 90, the diameter thereof is small and the seal area can be reduced. This is also advantageous in terms of cost.

As described above, the rotor 9 in which the two

impellers

4 and 6 are integrated is connected to a drive source which is an electric motor 12 as an example by the rotating shaft 8. The front half of the rotary shaft 8 extends along the intake passage 53 of the front housing 5 and is rotatably supported by the bearing 13. The bearing 13 is supported by a plurality of stays 14 extending from the inner wall of the front intake passage portion 53 toward the inner peripheral side.

On the other hand, the rear half of the rotating shaft 8 extends along the intake passage 73 of the rear housing 7 and is rotatably supported by the bearing 15. The bearing 15 is also supported by a plurality of stays 14 extending from the inner wall of the intake passage portion 73 at the rear stage toward the inner peripheral side. Further, the bearing 15 can receive a thrust force acting in the axial direction of the rotary shaft 8 as the

impellers

4 and 6 rotate. In the present embodiment, since the front and

rear impellers

4 and 6 are back to back, the thrust force of both is reduced, and the bearing 15 is not loaded with a large thrust force.

The front end portion of the rotary shaft 8 extending forward from the front stage bearing 13 is connected to the tip portion of the output shaft 120 (hereinafter referred to as a motor shaft) of the electric motor 12. As an example, flanges are formed at the front end portion of the rotating shaft 8 and the rear end portion of the motor shaft 120, and are overlapped and fastened. In other words, the electric motor 12 is disposed on the upstream side of a relatively low pressure and a low temperature, which is advantageous for ensuring durability. In addition, when durability does not become a problem, you may arrange | position the electric motor 12 in a back | latter stage side.

-Compressor operation-
When the electric motor 12 operates in the multistage centrifugal compressor 1 having such a configuration, the rotor 9, that is, the rotating shaft 8 and the front and

rear impellers

4 and 6 rotate at high speed. Since the two

impellers

4 and 6 are integral with the rotating shaft 8, the center of gravity of the

impellers

4 and 6 does not deviate from the center of rotation even when the rotational speed is high, and this deviation does not cause unbalanced vibration. . Further, since the two

impellers

4 and 6 are back to back and a heel portion is not formed at the boundary with the rotating shaft 8, there is little fear of problems due to stress concentration.

Thus, when the front impeller 4 rotates at a high speed, the pressure in the front intake passage portion 53 is reduced, and gas is sucked. This suction gas R1 flows from the left side of FIG. 1 toward the right side of the intake passage portion 53 in the front stage, and is sucked into the front stage impeller housing chamber 51 from the suction port 52. Then, the gas impelled radially outward by the rotation of the impeller 4 at the front stage and given kinetic energy flows into the diffuser 54 at the front stage, and the flow velocity is converted into pressure. Thus, the gas whose temperature and pressure have increased, that is, the front-stage discharge gas R2 flows in the circumferential direction through the front-stage volute 55 and is discharged from the outlet to the intermediate duct 57.

The upstream discharge gas R2 flowing through the intermediate duct 57 is greatly bent along the intermediate duct 57 and flows into the intake passage 73 at the rear stage from the inlet 73a. 1 flows from the right side to the left side in FIG. 1 and is sucked from the suction port 72 into the rear impeller accommodating chamber 71 and then pushed outward in the radial direction by the rotation of the rear impeller 6. In this way, kinetic energy is applied to flow into the rear diffuser 74, and the gas having an increased temperature and pressure, that is, the rear discharge gas R3 flows through the rear volute 75 and is discharged from its outlet to a discharge duct (not shown). The

As described above, in the multistage centrifugal compressor 1 of the present embodiment, the two

impellers

4 and 6 at the front stage and the rear stage are arranged back to back and formed as the integral rotor 9 together with the rotary shaft 8. As a result, unbalanced vibration caused by the shift of the center of gravity of the heel portion does not occur, and the problem of stress concentration at the heel portion is avoided, and an unprecedented high rotation speed can be realized.

By increasing the rotation speed of the front and

rear impellers

4 and 6 in this way, the pressure ratio can be increased in each of the compressor front stage 1F and the compressor rear stage 1R. Thus, until now, a three-stage or four-stage paragraph has been required. In addition, it is possible to realize a high compression pressure in two stages, and by reducing the number of stages, the dimensions of the compressor 1 are significantly shortened in the axial direction.

Further, an intermediate duct 57 that guides the upstream discharge gas R2 from the compressor front stage 1F to the compressor rear stage 1R passes from the volute 55 on the outer periphery of the front stage impeller 4 to the rear of the rear stage impeller 6, and the two

impellers

4, 6 has only an annular groove 90 into which the partition wall 10 is inserted, so that the distance between the two

impellers

4 and 6 can be minimized, thereby further reducing the axial dimension of the compressor 1. it can.

-Other embodiments-
The description of the above-described embodiment is merely an example, and does not limit the present invention, its application, or its use. For example, in the above-described embodiment, as shown in FIGS. 1 and 2, a relatively deep annular groove 90 is formed between the front and

rear impellers

4 and 6. The depth of the annular groove 90 is as follows. May be made shallower, or the annular groove 90 may not be provided as shown in FIG.

Thus, by not providing the annular groove 90, there is a possibility that the dimension of the rotor 9 can be further reduced in the axial direction. In this case, as shown in FIG. The labyrinth seal 11 is provided between the two

impellers

4 and 6. Since a certain width or more is required to ensure sufficient sealing performance, the effect of shortening the dimensions is limited. In addition, it is not limited to the labyrinth seal 11, You may use seals other than this.

Although not shown in the drawing, it is not necessary to provide the

diffusers

54 and 55 and the

volutes

74 and 75 so as to surround the entire outer periphery of the front and

rear impellers

4 and 6, for example, a part of the outer periphery of the

impellers

4 and 6. A volute may be provided only on the pipe, or a gas may be directly discharged to the duct without providing a volute.

Further, although not shown in the drawing, the electric motor 12 may be configured with the front end portion of the rotary shaft 8 of the compressor 1 inserted into the electric motor 12, that is, the motor shaft of the electric motor 12. It is also possible to integrate 120 and the rotating shaft 8. In this case, there is a possibility that the axial dimension can be further reduced as compared with the case where the front end portion of the rotating shaft 8 is fastened to the front end portion of the motor shaft 120 as in the above-described embodiment.

Also, the use of the multistage centrifugal compressor according to the present invention may be applied to various devices such as a refrigerator, a liquefaction device, and a compressor for a gas turbine.

As described above, the multistage centrifugal compressor according to the present invention has a high pressure ratio and an axial dimension that can be shortened as much as possible by increasing the rotation speed, and thus has high industrial applicability.

DESCRIPTION OF SYMBOLS 1 Multistage centrifugal compressor 4 Front stage impeller 5 Front stage housing 52 Front stage inlet 54 Front stage diffuser (front stage discharge flow path)
55 Pre-volute (pre-discharge channel)
57 Intermediate duct (gas channel)
6 Rear stage impeller 7 Rear stage housing 72 Rear stage suction port 74 Rear stage diffuser (rear stage discharge flow path)
75 Second-stage volute (second-stage discharge flow path)
8 Rotating shaft 8a Axis 9 Rotor 90 Toroidal groove (annular groove)
10 partition wall (circular partition wall)
11 Labyrinth seal 12 Electric motor 120 Output shaft (motor shaft)

Claims

A multistage centrifugal compressor provided with at least two centrifugal impellers arranged in the axial direction of the rotating shaft, and configured to further compress the gas compressed by the front impeller by the rear impeller;
The front and rear impellers are arranged back to back and formed integrally with the rotating shaft;
The housing includes a front suction port facing the front impeller in the axial direction, a front discharge passage disposed on the outer periphery of the front impeller, and a rear suction facing the axial direction of the rear impeller. A mouth, and a subsequent discharge channel disposed on the outer periphery of the latter impeller,
The multistage centrifugal compressor, wherein the upstream discharge channel and the downstream suction port are communicated with each other by a gas guiding channel.
2. The rotary shaft and the front and rear impellers are integrally formed of a metal material, and an annular groove that is open toward the outer peripheral side is formed between the front and rear impellers. Multistage centrifugal compressor.
The housing is provided with an annular partition wall portion that is inserted from the outer peripheral side with respect to the annular groove portion and divides each storage chamber of the front and rear impellers, and is provided on the inner peripheral side of the partition wall portion. The multistage centrifugal compressor according to claim 2, wherein a seal is provided between the portion and a portion on the inner peripheral side of the annular groove portion.
The multistage centrifugal compressor according to any one of claims 2 and 3, wherein an inner peripheral diameter of the annular groove is larger than an outer diameter of the rotary shaft.
The multi-stage centrifugal compressor according to any one of claims 2 to 4, wherein the annular groove portion has a shape in which a groove width in at least an inner peripheral side portion gradually decreases toward an inner peripheral side.
A turbo refrigerator using the multistage centrifugal compressor according to any one of claims 1 to 5.