JP2013204550A - Centrifugal compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a centrifugal compressor in which inconvenience such as shaft vibration caused by swirling stall is suppressed and performance reduction caused by a friction loss or the like is suppressed.SOLUTION: In a centrifugal compressor 10 including a diffuser part 15 circulating a fluid discharged from an impeller 13, a passage width W2 of the diffuser part 15 at an inflow position where the fluid flows into the diffuser part 15, is narrower than a passage width W1 of the impeller 13 at a discharge position where the fluid is discharged from the impeller 13 and at a downstream side of the inflow position of the diffuser part 15, a passage width enlarged part 15c is provided which is wider than the passage width W1 of the diffuser part 15 at the inflow position.

Description

  The present invention relates to a centrifugal compressor.

Conventionally, a centrifugal compressor is known as a compressor used in a plant or the like. And several improvement is proposed in order to enable the miniaturization of a centrifugal compressor and the operation | movement by a small flow volume.
For example, Patent Document 1 discloses a centrifugal compressor that can narrow a flow passage width of a part of a diffuser using a variable throttle mechanism in order to enable operation at a small flow rate.
Further, Patent Document 2 discloses a centrifugal compressor in which the flow passage height of the diffuser flow passage is gradually increased to increase the flow passage width in order to expand the operating range to a large flow rate while achieving downsizing. Yes.

JP 2003-120594 A JP 2010-144698 A

  In a centrifugal compressor, in general, when the flow angle (the angle formed by the discharge direction of the fluid from the impeller and the radial direction of the impeller) increases, the loss increases and the flow in the circumferential direction is not uniform. It is known that a malfunction such as shaft vibration, which is considered to be caused by the turning stall, occurs. In order to prevent problems such as shaft vibration, it is effective to reduce the flow angle, that is, to bring the fluid discharge direction from the impeller closer to the radial direction of the impeller. For example, as described in Patent Document 1 and Patent Document 2, by reducing the flow passage width of the diffuser, the flow velocity of the fluid can be increased and the flow angle can be reduced.

  However, although the diffuser of the centrifugal compressor described in Patent Document 1 and Patent Document 2 has a narrow channel width in a part of the channel, the inflow of the diffuser part into which the fluid discharged from the impeller flows The channel width at the position is not narrowed. Therefore, in the diffusers described in Patent Document 1 and Patent Document 2, the flow velocity of the fluid is not sufficiently increased at the position where the fluid flows into the diffuser, and a rotation stall may occur.

  This invention is made in view of such a situation, and it aims at providing the centrifugal compressor which suppressed the malfunctions, such as a shaft vibration by turning stall, and suppressed the performance fall by friction loss etc. .

In order to achieve the above object, the present invention employs the following means.
A centrifugal compressor according to the present invention is capable of rotating around an axis, and includes an impeller that discharges fluid flowing in an axial direction along the axis in a direction inclined from the axial direction, and the impeller And a diffuser portion for circulating the fluid discharged from the impeller, wherein the impeller is disposed between the hub and the shroud arranged along the axial direction, and between the hub and the shroud. The flow passage width of the diffuser portion at the inflow position where the fluid flows into the diffuser portion is larger than the flow passage width of the impeller at the discharge position where the fluid is discharged from the impeller. Narrow, and a downstream side of the inflow position of the diffuser portion is provided with a channel width expanding portion wider than the channel width of the diffuser portion at the inflow position. And butterflies.

  According to the centrifugal compressor of the present invention, the impeller that discharges the fluid flowing in along the axial direction in a direction inclined from the axial direction, the casing portion that houses the impeller, and the fluid discharged from the impeller are circulated. And an impeller includes a hub and a shroud arranged along the axial direction, and a plurality of blades disposed between the hub and the shroud.

  According to the centrifugal compressor according to the present invention, the flow passage width of the diffuser portion at the inflow position where the fluid flows into the diffuser portion is narrower than the flow passage width of the impeller at the discharge position where the fluid is discharged from the impeller. . By doing in this way, the flow velocity of the fluid in the inflow position where the fluid flows into the diffuser part can be sufficiently increased to suppress the occurrence of turning stall, and problems such as shaft vibration due to turning stall can be suppressed.

  Moreover, according to the centrifugal compressor which concerns on this invention, the flow-path width expansion part wider than the flow-path width of the diffuser part in an inflow position is provided in the downstream from the inflow position of a diffuser part. By doing in this way, compared with the case where it is made the same flow path width from the inflow position of the diffuser part to the downstream side, performance degradation such as friction loss caused by the flow velocity of the fluid flowing through the diffuser part becomes faster. Can be suppressed.

  In the centrifugal compressor according to the first aspect of the present invention, the diffuser portion is defined by a hub side wall provided on the hub side and a shroud side wall provided on the shroud side, and the hub side wall in the flow passage width expanding portion. Is disposed in a direction in which the flow passage width of the diffuser portion is larger than the hub side wall at the inflow position, and the shroud side wall at the flow passage width enlargement portion is more than the shroud side wall at the inflow position. It arrange | positions in the direction which expands the flow path width of a diffuser part, It is characterized by the above-mentioned.

  By doing in this way, the walls on both sides of the diffuser section flow width expanding section are arranged in the direction of expanding the diffuser section flow path width, and the same flow path width from the inflow position of the diffuser section to the downstream side. Compared with the case where it does, performance degradation, such as a friction loss resulting from the increase in the flow velocity of a fluid, can be suppressed.

  In the centrifugal compressor according to the second aspect of the present invention, the diffuser portion is defined by a hub side wall provided on the hub side and a shroud side wall provided on the shroud side, and the hub side wall in the flow passage width expanding portion. However, it is characterized by being arranged in a direction in which the flow passage width of the diffuser portion is larger than the hub side wall at the inflow position.

  By doing in this way, the hub side wall in the channel width expansion part of the diffuser part is arranged in the direction in which the channel width of the diffuser part is expanded, and the same channel width is made from the inflow position of the diffuser part to the downstream side. Compared to the case, it is possible to suppress performance degradation such as friction loss due to the increase in the flow velocity of the fluid. Further, since the hub side wall is arranged in the direction of expanding the flow passage width of the diffuser portion, when the discharge direction of the fluid discharged from the impeller is directed toward the hub side wall from the direction orthogonal to the axial direction, A flow path through which the fluid flows in a stable state can be formed.

  In the centrifugal compressor according to the third aspect of the present invention, the diffuser portion is defined by a hub side wall provided on the hub side and a shroud side wall provided on the shroud side, and the shroud side wall in the flow passage width expanding portion. However, it is arranged in a direction in which the flow passage width of the diffuser portion is larger than the shroud side wall at the inflow position.

  By doing in this way, the shroud side wall in the channel width expansion part of the diffuser part is arranged in the direction in which the channel width of the diffuser part is enlarged, and the same channel width is provided from the inflow position of the diffuser part to the downstream side. Compared to the case, it is possible to suppress performance degradation such as friction loss due to the increase in the flow velocity of the fluid.

In the centrifugal compressor according to the first aspect of the present invention described above, the shape of the hub side wall is along the flow direction of the fluid at an intermediate position between the inflow position of the diffuser portion and the flow path width expanding portion. Even if the shape of the shroud side wall is a tapered shape in which the flow path width gradually increases along the flow direction of the fluid at the intermediate position of the diffuser portion. Good.
By doing in this way, the flow path which distribute | circulates the fluid in the stable state in the flow path of the intermediate position of a diffuser part can be formed.

In the centrifugal compressor according to the second aspect of the present invention described above, the shape of the hub side wall is along the flow direction of the fluid at an intermediate position between the inflow position of the diffuser section and the flow path width expanding section. A tapered shape in which the flow path width gradually increases may be used.
By doing in this way, the flow path which distribute | circulates the fluid in the stable state in the flow path of the intermediate position of a diffuser part can be formed.

In the above-described centrifugal compressor according to the third aspect of the present invention, the shape of the shroud side wall is along the flow direction of the fluid at an intermediate position between the inflow position of the diffuser section and the flow path width expanding section. A tapered shape in which the flow path width gradually increases may be used.
By doing in this way, the flow path which distribute | circulates the fluid in the stable state in the flow path of the intermediate position of a diffuser part can be formed.

In the centrifugal compressor according to the first aspect of the present invention described above, the shape of the hub side wall is along the flow direction of the fluid at an intermediate position between the inflow position of the diffuser portion and the flow path width expanding portion. The shape of the shroud side wall is a step shape in which the channel width is increased stepwise along the fluid flow direction at the intermediate position of the diffuser portion. Also good.
By doing in this way, the flow path which connects an inflow position and a downstream can be formed in the intermediate position of a diffuser part by a comparatively easy processing process.

In the above-described centrifugal compressor of the second aspect of the present invention, the shape of the hub side wall is stepped along the fluid flow direction at an intermediate position between the inflow position of the diffuser portion and the flow passage width widening portion. Alternatively, a step shape in which the channel width is enlarged may be used.
By doing in this way, the flow path which connects an inflow position and a downstream can be formed in the intermediate position of a diffuser part by a comparatively easy processing process.

In the above-described centrifugal compressor according to the third aspect of the present invention, the shape of the shroud side wall is along the flow direction of the fluid at an intermediate position between the inflow position of the diffuser section and the flow path width expanding section. A step shape in which the channel width gradually increases may be used.
By doing in this way, the flow path which connects an inflow position and a downstream can be formed in the intermediate position of a diffuser part by a comparatively easy processing process.

In the centrifugal compressor according to the fourth aspect of the present invention, the ratio of the flow path width of the diffuser portion at the inflow position to the flow path width of the impeller at the discharge position is 0.5 or more and less than 0.8. It is characterized by being.
In this way, the flow path width at the inflow position of the diffuser part is made sufficiently narrow, and the flow velocity of the fluid at the inflow position where the fluid flows into the diffuser part is sufficiently increased to suppress the occurrence of turning stall, Problems such as shaft vibration due to stall can be suppressed.

In the centrifugal compressor according to the fifth aspect of the present invention, the ratio of the flow path width of the diffuser section in the flow path width expanding section to the flow path width of the impeller at the discharge position is 0.8 or more, and 1 0.0 or less.
By doing in this way, compared with the case where the flow path width in the flow-path width expansion part of a diffuser part is made sufficiently wide, and it is made the same flow-path width from the inflow position of a diffuser part to the downstream side, the flow velocity of fluid It is possible to suppress performance degradation such as friction loss due to the increase in speed.

The centrifugal compressor according to a sixth aspect of the present invention is characterized in that the impeller discharges the fluid flowing in along the axial direction in a direction orthogonal to the axial direction.
In this way, in the centrifugal compressor that discharges the fluid flowing in along the axial direction in a direction orthogonal to the axial direction, it is possible to suppress problems such as shaft vibration due to turning stall and to reduce performance due to friction loss and the like. Can be suppressed.

The centrifugal compressor according to the seventh aspect of the present invention has a flow coefficient of 0.01 or more and 0.05 or less.
By doing in this way, in a centrifugal compressor with a comparatively small flow coefficient, while being able to suppress malfunctions, such as shaft vibration by turning stall, the performance fall by friction loss etc. can be controlled.

  ADVANTAGE OF THE INVENTION According to this invention, while suppressing malfunctions, such as a shaft vibration by turning stall, the centrifugal compressor which suppressed the performance fall by friction loss etc. can be provided.

It is a longitudinal cross-sectional view of the centrifugal compressor of 1st Embodiment. It is a front view of the centrifugal compressor of a 1st embodiment. It is a longitudinal cross-sectional view of the centrifugal compressor of 2nd Embodiment. It is a longitudinal cross-sectional view of the centrifugal compressor of 3rd Embodiment. It is a longitudinal cross-sectional view of the centrifugal compressor of 4th Embodiment. It is a longitudinal cross-sectional view of the centrifugal compressor of 5th Embodiment.

[First Embodiment]
Hereinafter, the centrifugal compressor 10 of 1st Embodiment is demonstrated using FIG. 1 and FIG. FIG. 1 is a longitudinal sectional view of a centrifugal compressor 10 of the first embodiment. FIG. 2 is a front view of the centrifugal compressor 10 of the first embodiment.
A centrifugal compressor 10 shown in FIG. 1 includes an impeller 13 that can rotate around an axis A, a casing portion 11 that houses the impeller 13, a diffuser portion 15 that circulates fluid discharged from the impeller 13, and a diffuser. And a volute section 16 provided downstream of the section 15.

FIG. 2 is a front view of the position where the fluid flows into the impeller 13 along the axial direction of the axis A. For ease of explanation, the impeller 13, the diffuser portion 15, and the casing portion are illustrated. 11 and a part of the volute unit 16 are omitted.
Moreover, the centrifugal compressor 10 of 1st Embodiment is a comparatively small centrifugal compressor whose flow coefficient is 0.01 or more and 0.05 or less.

  The impeller 13 is connected to a drive device such as a motor or a turbine (not shown) via a rotation axis (not shown) along the axis A, and can rotate around the axis A. The impeller 13 has a hub 1 and a shroud 2 arranged along the axial direction of the axis A, and a plurality of blades 3 arranged between the hub 1 and the shroud 2. In FIG. 1, only one blade 3 is shown, but a plurality of blades 3 are arranged between the hub 1 and the shroud 2 at equal intervals in the circumferential direction around the axis A (see FIG. 1). 2).

  The impeller 13 is provided with a space defined by the inner wall 1 a of the hub 1 and the inner wall 2 a of the shroud 2, and this space is partitioned into a plurality of spaces by a plurality of blades 3. The impeller 13 applies a centrifugal force in the radial direction to the fluid flowing in the axial direction (the direction indicated by the arrow in FIG. 1), and is perpendicular to the axial direction (inclined direction; the radius of the impeller 13). Direction) and flow into the diffuser section 15.

  The diffuser portion 15 is a fluid flow path defined by a hub side wall 15a provided on the hub 1 side and a shroud side wall 15b provided on the shroud 2 side. As shown in FIG. 2, the diffuser portion 15 is provided so as to surround a discharge position provided on the entire circumference of the impeller 13. The diffuser unit 15 converts kinetic energy (dynamic pressure) applied to the fluid into pressure energy (static pressure) by decelerating the flow velocity of the fluid discharged from the discharge position of the impeller 13.

  The fluid whose flow velocity is reduced when passing through the diffuser portion 15 is compressed and flows into a volute portion (vortex chamber) 16 communicating with the diffuser portion 15. The compressed fluid that has flowed into the volute unit 16 is discharged to a discharge pipe (not shown) through a discharge port (not shown).

Here, the operation of the centrifugal compressor 10 will be described.
The centrifugal compressor 10 rotates the impeller 13 around the axis A by a driving device such as a motor or a turbine (not shown). As the impeller 13 rotates, the fluid taken from an intake port (not shown) is introduced into the casing portion 11. The fluid introduced into the casing portion 11 is given a centrifugal force in a direction (radial direction) perpendicular to the axis A through the blade 3 by the rotation of the impeller 13. The fluid to which the centrifugal force is applied is discharged from the impeller 13 and flows into the diffuser portion 15. The fluid that has flowed into the diffuser portion 15 is compressed at a reduced flow rate and is discharged to the volute portion 16. The compressed fluid that has flowed into the volute unit 16 is discharged to a discharge pipe (not shown) through a discharge port (not shown).

Next, the flow path width of the impeller 13 and the diffuser part 15 will be described.
As shown in FIG. 1, the flow passage width W2 of the diffuser portion 15 at the inflow position where the fluid flows into the diffuser portion 15 is larger than the flow passage width W1 of the impeller 13 at the discharge position where the fluid is discharged from the impeller 13. narrow. By narrowing in this way, it is possible to sufficiently increase the flow velocity of the fluid at the inflow position where the fluid flows into the diffuser portion 15 to suppress the occurrence of turning stall, and to suppress problems such as shaft vibration due to turning stall.

  In this way, by sufficiently increasing the fluid flow velocity at the inflow position where the fluid flows into the diffuser portion 15, the occurrence of the turning stall is suppressed. On the other hand, when the fluid flow rate increases, loss due to friction between the fluid and the hub side wall 15a and the shroud side wall 15b increases. Therefore, in the first embodiment, a flow path width expanding portion 15c that increases the flow path width of the diffuser portion 15 is provided on the downstream side of the inflow position where the fluid flows into the diffuser portion 15 in order to suppress loss due to friction.

As shown in FIG. 1, the channel width W <b> 1 indicates the length in the direction along the axis A (axial direction). The flow path width W1 is equal to the axial distance between the inner wall 1a of the hub 1 and the inner wall 2a of the shroud 2 at the discharge position where the fluid is discharged from the impeller 13.
Further, as shown in FIG. 1, the flow path width W <b> 2 indicates the length in the direction along the axis A. The flow path width W2 is equal to the axial distance between the hub side wall 15a and the shroud side wall 15b at the inflow position where the fluid flows into the diffuser portion 15.

  The flow path width of the diffuser portion 15 (the distance in the axial direction between the hub side wall 15a and the shroud side wall 15b) is such that the distance from the inflow position where the fluid flows into the diffuser portion 15 in the fluid flow direction (the direction orthogonal to the axial direction) is L1. The flow path width W2 remains constant until it reaches. And in the position (intermediate position) from the inflow position to the distance L1 to L2, the hub side wall 15a which demarcates the diffuser part 15 is a taper shape where a flow path width expands gradually along the flow direction of a fluid. It has become. Further, at a position (intermediate position) where the distance from the inflow position extends from L1 to L2, the shroud side wall 15b that defines the diffuser portion 15 also has a tapered shape in which the channel width gradually increases along the fluid flow direction. It has become.

  Further, the hub side wall 15a is located at a position from the inflow position where the fluid flows into the diffuser section 15 from L2 to L3, and the diffuser section is more than the hub side wall 15a at the inflow position where the fluid flows into the diffuser section 15. It arrange | positions in the direction which expands 15 flow path widths. Similarly, the shroud side wall 15b is also arranged in a direction in which the flow passage width of the diffuser portion 15 is larger than the shroud side wall 15b at the inflow position where the fluid flows into the diffuser portion 15. And in the position where the distance from an inflow position reaches from L2 to L3, the flow path width of the diffuser part 15 is constant with the flow path width W3.

As described above, the channel width expanding portion 15c wider than the channel width of the diffuser portion 15 at the inflow position of the diffuser portion 15 is located downstream of the inflow position where the fluid flows into the diffuser portion 15 in the fluid flow direction. Is provided.
In the flow path width expanding portion 15c, it is desirable that the shape of the hub side wall 15a and the shape of the shroud side wall 15b be symmetric with respect to the central axis of the flow path.

  In the first embodiment, the ratio of the flow path width W2 at the inflow position of the diffuser portion 15 to the flow path width W1 at the discharge position of the impeller 13 is 0.5 or more and less than 0.8. Further, the ratio of the flow path width W3 of the diffuser portion 15 in the flow path width enlarged portion 15c to the flow path width W1 at the discharge position of the impeller 13 is set to 0.8 or more and 1.0 or less. However, as described above, the respective ratios are selected so that the flow path width W3 of the diffuser section 15 in the flow path width expanding section 15c is wider than the flow path width W2 at the inflow position of the diffuser section 15. The

  As described above, the centrifugal compressor 10 of the first embodiment includes the impeller 13 that discharges the fluid flowing in along the axial direction in a direction inclined in the axial direction (radial direction orthogonal to the axial direction), and the impeller A hub 11 and a shroud 2, and a hub 1 and a shroud, each of which includes a casing portion 11 for housing the wheel 13 and a diffuser portion 15 for circulating the fluid discharged from the impeller 13. 2 has a plurality of blades 3 arranged between the two.

  And according to the centrifugal compressor 10 of 1st Embodiment, the flow-path width | variety W2 of the diffuser part 15 in the inflow position where a fluid flows in into the diffuser part 15 is the impeller 13 in the discharge position where a fluid discharges from the impeller 13. It is narrower than the channel width W1. By doing in this way, generation | occurrence | production of a rotation stall can be suppressed by fully increasing the flow velocity of the fluid in the inflow position where the fluid flows in into the diffuser part 15, and problems, such as a shaft vibration by a rotation stall, can be suppressed.

  Moreover, according to the centrifugal compressor 10 of 1st Embodiment, the flow path width W3 wider than the flow path width W2 of the diffuser part 15 in the inflow position of the diffuser part 15 in the downstream from the inflow position of the diffuser part 15. The flow path width enlarged portion 15c is provided. By doing in this way, compared with the case where it is set as the same flow path width W2 from the inflow position of the diffuser part 15 to a downstream side, friction loss etc. resulting from the increase in the flow velocity of the fluid which distribute | circulates the diffuser part 15 etc. Performance degradation can be suppressed.

  Moreover, in 1st Embodiment, the diffuser part 15 is demarcated by the hub side wall 15a provided in the hub 1 side, and the shroud side wall 15b provided in the shroud 2 side. And the hub side wall 15a in the flow path width expansion part 15c is arrange | positioned in the direction which expands the flow path width of the diffuser part 15 rather than the hub side wall 15a in an inflow position. Further, the shroud side wall 15b in the flow path width expanding portion 15c is arranged in a direction in which the flow path width of the diffuser portion 15 is larger than the shroud side wall 15b at the inflow position.

  By doing in this way, the wall of the both sides in the flow-path width expansion part 15c of the diffuser part 15 is arrange | positioned in the direction which expands the flow-path width of the diffuser part 15, and it is the same from the inflow position of the diffuser part 15 to a downstream side. Compared with the case where the flow path width W2 is set, it is possible to suppress performance degradation such as friction loss due to an increase in the flow velocity of the fluid.

  In the first embodiment, the shape of the hub side wall 15a is such that the channel width gradually increases along the fluid flow direction at an intermediate position between the inflow position of the diffuser portion 15 and the channel width expanding portion 15c. It is a taper shape, and the shape of the shroud side wall 15 b is a taper shape in which the flow path width gradually increases along the fluid flow direction at the intermediate position of the diffuser portion 15. By doing in this way, the flow path which distribute | circulates the fluid in the stable state in the flow path of the intermediate position of the diffuser part 15 can be formed.

  Moreover, in 1st Embodiment, the ratio of the flow path width W2 of the diffuser part 15 in the inflow position with respect to the flow path width W1 of the impeller 13 in a discharge position is 0.5 or more and less than 0.8. By doing so, the flow path width W2 with respect to the flow path width W1 is made sufficiently narrow, and the flow velocity of the fluid at the inflow position where the fluid flows into the diffuser portion 15 is sufficiently increased to suppress the occurrence of turning stall, Problems such as shaft vibration due to turning stall can be suppressed.

  In the first embodiment, the ratio of the channel width W3 of the diffuser portion 15 in the channel width expanding portion 15c to the channel width W1 of the impeller 13 at the discharge position is 0.8 or more and 1.0. It is as follows. By doing in this way, compared with the case where the flow path width W3 with respect to the flow path width W1 is made sufficiently wide, and the flow path width W2 is the same from the inflow position of the diffuser portion 15 to the downstream side, the fluid flow velocity is higher. It is possible to suppress performance degradation such as friction loss due to speeding up.

[Second Embodiment]
Next, the centrifugal compressor 10 of 2nd Embodiment is demonstrated using FIG. FIG. 3 is a longitudinal sectional view of the centrifugal compressor 10 of the second embodiment.
In the first embodiment, the walls (hub side wall 15 a and shroud side wall 15 b) on both sides of the flow passage width expanding portion 15 c of the diffuser portion 15 are arranged in the direction in which the flow passage width of the diffuser portion 15 is increased. On the other hand, in the second embodiment, one side wall (hub side wall 15a) of the flow passage width expanding portion 15c of the diffuser portion 15 is arranged in the direction in which the flow passage width of the diffuser portion 15 is increased.
The second embodiment is a modification of the first embodiment, and other configurations are the same as those of the first embodiment except for the shape of the hub side wall 15a that defines the diffuser portion 15. Therefore, the following description will be given. Is omitted.

  In the second embodiment, as shown in FIG. 3, the hub side wall 15a in the flow path width expanding portion 15c is arranged in a direction in which the flow path width of the diffuser portion 15 is larger than the hub side wall 15a at the inflow position. Yes. On the other hand, the shroud side wall 15b in the flow path width enlarged portion 15c and the shroud side wall 15b at the inflow position are arranged so that the positions in the axial direction are the same.

  The centrifugal compressor 10 shown in FIG. 3 discharges the fluid flowing into the impeller 13 in a direction orthogonal to the axial direction, but is inclined to the hub side wall 15a from the direction orthogonal to the axial direction. A modification of discharging in the direction is also applicable. In this case, the fluid that has flowed into the diffuser portion 15 includes a velocity component in a direction that hits the hub side wall 15a perpendicularly. Therefore, since loss due to friction is more likely to occur in the hub side wall 15a than in the shroud side wall 15b, it is desirable to suppress the friction loss generated in the hub side wall 15a.

  In the modification of the second embodiment, the hub side wall 15a is disposed in the direction in which the flow passage width of the diffuser portion 15 is increased, so that the discharge direction of the fluid discharged from the impeller 13 is greater than the direction perpendicular to the axial direction. When facing (inclined) toward the side wall 15a, it is possible to form a flow path in which the fluid flows in a stable state and the friction loss generated at the hub side wall 15a is suppressed.

  A compressor that discharges in a direction inclined to the hub side wall 15a rather than a direction orthogonal to the axial direction of the impeller 13 as in the modification of the second embodiment may be referred to as a mixed flow compressor. . In the second embodiment, the fluid flowing in the axial direction is converted into a fluid containing a velocity component in the direction orthogonal to the axis A (centrifugal direction), and is called a centrifugal compressor instead of a mixed flow compressor. Shall.

  As described above, according to the centrifugal compressor 10 of the second embodiment, the flow path width W2 of the diffuser portion 15 at the inflow position where the fluid flows into the diffuser portion 15 is the discharge position where the fluid is discharged from the impeller 13. Is narrower than the flow path width W1 of the impeller 13. By doing in this way, generation | occurrence | production of a rotation stall can be suppressed by fully increasing the flow velocity of the fluid in the inflow position where the fluid flows in into the diffuser part 15, and problems, such as a shaft vibration by a rotation stall, can be suppressed.

  Moreover, in 2nd Embodiment, the hub side wall 15a in the flow path width expansion part 15c is arrange | positioned in the direction which expands the flow path width of the diffuser part 15 rather than the hub side wall 15a in an inflow position. By doing in this way, the hub side wall 15a in the flow-path width expansion part 15c of the diffuser part 15 is arrange | positioned in the direction which expands the flow-path width of the diffuser part 15, and is the same from the inflow position of the diffuser part 15 to a downstream side. Compared with the case where the flow path width W2 is set, it is possible to suppress performance degradation such as friction loss due to an increase in the flow velocity of the fluid.

  In the second embodiment, the shape of the hub side wall 15a is such that the channel width gradually increases along the fluid flow direction at an intermediate position between the inflow position of the diffuser portion 15 and the channel width expanding portion 15c. Tapered shape. By doing in this way, the flow path which distribute | circulates the fluid in the stable state in the flow path of the intermediate position of the diffuser part 15 can be formed.

[Third Embodiment]
Next, the centrifugal compressor 10 of 3rd Embodiment is demonstrated using FIG. FIG. 4 is a longitudinal sectional view of the centrifugal compressor 10 of the third embodiment.
In the first embodiment, the walls (hub side wall 15 a and shroud side wall 15 b) on both sides of the flow passage width expanding portion 15 c of the diffuser portion 15 are arranged in the direction in which the flow passage width of the diffuser portion 15 is increased. On the other hand, in the third embodiment, one side wall (the shroud side wall 15b) of the flow passage width expanding portion 15c of the diffuser portion 15 is arranged in the direction in which the flow passage width of the diffuser portion 15 is increased.
The third embodiment is a modification of the first embodiment, and other configurations are the same as those of the first embodiment except for the shape of the shroud side wall 15b that defines the diffuser portion 15. Therefore, the following description will be given. Is omitted.

  In 3rd Embodiment, as FIG. 4 shows, the shroud side wall 15b in the flow-path width expansion part 15c is arrange | positioned in the direction which expands the flow-path width of the diffuser part 15 rather than the shroud side wall 15b in an inflow position. Yes. On the other hand, the hub side wall 15a in the flow path width enlarged portion 15c and the hub side wall 15a at the inflow position are arranged so that the positions in the axial direction are the same.

  As described above, according to the centrifugal compressor 10 of the third embodiment, the flow path width W2 of the diffuser portion 15 at the inflow position where the fluid flows into the diffuser portion 15 is the discharge position where the fluid is discharged from the impeller 13. Is narrower than the flow path width W1 of the impeller 13. By doing in this way, generation | occurrence | production of a rotation stall can be suppressed by fully increasing the flow velocity of the fluid in the inflow position where the fluid flows in into the diffuser part 15, and problems, such as a shaft vibration by a rotation stall, can be suppressed.

  Moreover, in 3rd Embodiment, the shroud side wall 15b in the flow-path width expansion part 15c is arrange | positioned in the direction which expands the flow-path width of the diffuser part 15 rather than the shroud side wall 15b in an inflow position. By doing in this way, the hub side wall 15a in the flow-path width expansion part 15c of the diffuser part 15 is arrange | positioned in the direction which expands the flow-path width of the diffuser part 15, and is the same from the inflow position of the diffuser part 15 to a downstream side. Compared with the case where the flow path width W2 is set, it is possible to suppress performance degradation such as friction loss due to an increase in the flow velocity of the fluid.

  In the third embodiment, the shape of the shroud side wall 15b is a tapered shape in which the flow path width gradually increases along the fluid flow direction at an intermediate position of the diffuser portion 15. By doing in this way, the flow path which distribute | circulates the fluid in the stable state in the flow path of the intermediate position of the diffuser part 15 can be formed.

[Fourth Embodiment]
Next, the centrifugal compressor 10 of 4th Embodiment is demonstrated using FIG. FIG. 5 is a longitudinal sectional view of the centrifugal compressor 10 of the fourth embodiment.
In the first embodiment, between the flow path width W2 provided at the inflow position of the diffuser portion 15 and the flow path width enlarged portion 15c of the flow path width W3 provided downstream of the diffuser portion 15 (intermediate position). Both the hub side wall 15a and the shroud side wall 15b are tapered so that the flow path width gradually increases along the fluid flow direction.
On the other hand, in 4th Embodiment, it replaces with a taper shape and employ | adopts the step shape which a flow path width expands in steps along the flow direction of a fluid.

  The flow path width of the diffuser part 15 (the distance in the axial direction between the hub side wall 15a and the shroud side wall 15b) is the distance in the fluid flow direction (the direction perpendicular to the axial direction) from the inflow position where the fluid flows into the diffuser part 15. The flow path width W2 remains constant until reaching L4. And in the position where the distance from an inflow position reaches from L4 to L3, the flow path width of the diffuser part 15 is constant with the flow path width W3.

  In the fourth embodiment shown in FIG. 5, the diffuser unit 15 provided with only one stage is shown, but a plurality of stages may be provided instead of only one stage. For example, instead of the taper-shaped portion (intermediate position of the diffuser portion 15) shown in FIG. 1 of the first embodiment, a multi-stage shape having two, three, or more stages is formed, and the flow path width gradually increases. You may make it expand to.

  In the fourth embodiment shown in FIG. 5, the step shape is provided on both the hub side wall 15a and the shroud side wall 15b, but the step shape is provided on either the hub side wall 15a or the shroud side wall 15b. The other one may not be provided with a step shape. For example, in the case where the hub side wall 15a is not provided with a step shape, the hub side wall 15a in the flow passage width expanding portion 15c and the hub side wall 15a at the inflow position are arranged so that the positions in the axial direction are the same. Further, for example, when the shroud side wall 15b is not provided with a step shape, the shroud side wall 15b in the flow path width expanding portion 15c and the shroud side wall 15b at the inflow position are arranged so that the positions in the axial direction are the same.

  As described above, according to the centrifugal compressor 10 of the fourth embodiment, the flow path width W2 of the diffuser portion 15 at the inflow position where the fluid flows into the diffuser portion 15 is the discharge position where the fluid is discharged from the impeller 13. Is narrower than the flow path width W1 of the impeller 13. By doing in this way, generation | occurrence | production of a rotation stall can be suppressed by fully increasing the flow velocity of the fluid in the inflow position where the fluid flows in into the diffuser part 15, and problems, such as a shaft vibration by a rotation stall, can be suppressed.

  Moreover, according to the centrifugal compressor 10 of 4th Embodiment, the flow path width W3 wider than the flow path width W2 of the diffuser part 15 in the inflow position of the diffuser part 15 in the downstream from the inflow position of the diffuser part 15. The flow path width enlarged portion 15c is provided. By doing in this way, compared with the case where it is set as the same flow path width W2 from the inflow position of the diffuser part 15 to a downstream side, friction loss etc. resulting from the increase in the flow velocity of the fluid which distribute | circulates the diffuser part 15 etc. Performance degradation can be suppressed.

  Further, in the fourth embodiment, the shape of the hub side wall 15a is such that the flow path width gradually increases along the fluid flow direction at an intermediate position between the inflow position of the diffuser portion 15 and the flow path width expanding portion 15c. The shape of the shroud side wall 15b is a step shape in which the flow path width gradually increases along the fluid flow direction at an intermediate position of the diffuser portion 15. By doing in this way, the flow path which connects an inflow position and a downstream can be formed in the intermediate position of the diffuser part 15 by a comparatively easy processing process.

[Fifth Embodiment]
Next, the centrifugal compressor 10 of 5th Embodiment is demonstrated using FIG. FIG. 6 is a longitudinal sectional view of the centrifugal compressor 10 of the fifth embodiment.
In the first to fourth embodiments, the single-stage centrifugal compressor in which the volute unit 16 is provided downstream of the diffuser unit 15 has been described. However, the centrifugal compressor 10 of the fifth embodiment is the first-stage centrifugal compressor. It is a multistage centrifugal compressor of the form which flows the fluid compressed by the impeller 13 and the diffuser part 15 into the next stage impeller 13 and the diffuser part 15.
The fifth embodiment is a modification of the first embodiment, and the other configuration is the same as that of the first embodiment except that a return bend 17 and a return vane 18 are provided instead of the volute unit 16. Therefore, the description below is omitted.

  In the first embodiment, the compressed fluid that has flowed into the flow path width expanding portion 15c of the diffuser section 15 flows into the volute section 16 provided downstream of the flow path width expanding portion 15c. On the other hand, in the fifth embodiment, the compressed fluid that has flowed into the flow path width expanding portion 15c of the diffuser section 15 flows into the return bend 17 provided downstream of the flow path width expanding portion 15c. The compressed fluid flowing into the return bend 17 is guided to the next stage (second stage) impeller 13 via the return vane 18.

  When a two-stage centrifugal compressor is employed as the centrifugal compressor 10 of the fifth embodiment, the fluid guided to the second-stage impeller 13 is discharged to the second-stage diffuser unit 15. The fluid further compressed by the second-stage diffuser unit 15 is guided to a volute unit 16 similar to that shown in FIG. 1 of the first embodiment.

  Further, when a three-stage centrifugal compressor is employed as the centrifugal compressor 10 of the fifth embodiment, the fluid guided to the second-stage impeller 13 is discharged to the second-stage diffuser unit 15. The fluid further compressed by the second-stage diffuser section 15 flows into the second-stage return bend 17. The compressed fluid that has flowed into the second-stage return bend 17 is guided to the next-stage (third-stage) impeller 13 via the return vane 18. The fluid guided to the third stage impeller 13 is discharged to the third stage diffuser section 15. The fluid further compressed by the third-stage diffuser unit 15 is guided to the volute unit 16 similar to that shown in FIG. 1 of the first embodiment.

As described above, when the centrifugal compressor 10 is a two-stage or three-stage centrifugal compressor 10, the compressibility of the fluid can be further increased. Moreover, the same effect as 1st Embodiment can be show | played by the shape of the impeller 13 and the diffuser part 15 of each step | level.
In addition, as the shape of the diffuser portion 15 in each stage, not only the shape shown in the first embodiment but also any shape shown in the second to fourth embodiments can be adopted. .
Further, in the fifth embodiment, the two-stage and three-stage centrifugal compressors 10 have been described. However, a modification example in which four or more stages of the centrifugal compressors 10 are used may be employed.

DESCRIPTION OF SYMBOLS 1 Hub 2 Shroud 3 Blade 10 Centrifugal compressor 11 Casing part 13 Impeller 15 Diffuser part 15a Hub side wall 15b Shroud side wall 15c Channel width expansion part 16 Volute part A Axis line W1 Channel width W2 at the discharge position of the impeller Channel width W3 at the inflow position Channel width at the channel width expansion part of the diffuser

Claims (14)

An impeller that is rotatable about an axis and discharges fluid flowing in the axial direction along the axis in a direction inclined from the axial direction;
A casing portion for housing the impeller;
A diffuser part for circulating the fluid discharged from the impeller, and
The impeller has a hub and a shroud arranged along the axial direction, and a plurality of blades disposed between the hub and the shroud;
The flow passage width of the diffuser portion at the inflow position where the fluid flows into the diffuser portion is narrower than the flow passage width of the impeller at the discharge position where the fluid is discharged from the impeller,
A centrifugal compressor characterized in that, on the downstream side of the inflow position of the diffuser part, a flow path width expanding part wider than the flow path width of the diffuser part at the inflow position is provided. The diffuser portion is defined by a hub side wall provided on the hub side and a shroud side wall provided on the shroud side;
The hub side wall in the flow path width enlarged portion is disposed in a direction in which the flow path width of the diffuser portion is larger than the hub side wall in the inflow position,
2. The centrifugal compression according to claim 1, wherein the shroud side wall in the flow path width enlarged portion is arranged in a direction in which the flow path width of the diffuser portion is larger than the shroud side wall at the inflow position. Machine. The diffuser portion is defined by a hub side wall provided on the hub side and a shroud side wall provided on the shroud side;
2. The centrifugal compression according to claim 1, wherein the hub side wall in the flow path width expanding portion is arranged in a direction in which the flow path width of the diffuser portion is expanded as compared with the hub side wall at the inflow position. Machine. The diffuser portion is defined by a hub side wall provided on the hub side and a shroud side wall provided on the shroud side;
2. The centrifugal compression according to claim 1, wherein the shroud side wall in the flow path width enlarged portion is arranged in a direction in which the flow path width of the diffuser portion is larger than the shroud side wall at the inflow position. Machine. The shape of the hub side wall is a tapered shape in which the flow path width gradually increases along the flow direction of the fluid at an intermediate position between the inflow position of the diffuser part and the flow path width expansion part,
3. The centrifugal compressor according to claim 2, wherein the shroud side wall has a tapered shape in which a flow path width gradually increases along a flow direction of the fluid at the intermediate position of the diffuser portion.   The shape of the hub side wall is a tapered shape in which the channel width gradually increases along the fluid flow direction at an intermediate position between the inflow position of the diffuser portion and the channel width expanding portion. The centrifugal compressor according to claim 3.   The shape of the shroud side wall is a tapered shape in which the flow passage width gradually increases along the fluid flow direction at an intermediate position between the inflow position of the diffuser portion and the flow passage width enlargement portion. The centrifugal compressor according to claim 4. The shape of the hub side wall is a step shape in which the flow path width is gradually increased along the flow direction of the fluid at an intermediate position between the inflow position of the diffuser part and the flow path width expansion part,
The centrifugal compressor according to claim 2, wherein the shape of the shroud side wall is a step shape in which the flow path width is gradually increased along the flow direction of the fluid at the intermediate position of the diffuser portion. .   The shape of the hub side wall is a step shape in which the channel width gradually increases along the fluid flow direction at an intermediate position between the inflow position of the diffuser portion and the channel width expanding portion. The centrifugal compressor according to claim 3, wherein   The shape of the shroud side wall is a step shape in which the channel width gradually increases along the fluid flow direction at an intermediate position between the inflow position of the diffuser portion and the channel width expanding portion. The centrifugal compressor according to claim 4, characterized in that:   The ratio of the flow path width of the diffuser portion at the inflow position to the flow path width of the impeller at the discharge position is 0.5 or more and less than 0.8. Item 11. The centrifugal compressor according to any one of Items 10.   The ratio of the flow path width of the diffuser part in the flow path width enlarged part to the flow path width of the impeller at the discharge position is 0.8 or more and 1.0 or less. The centrifugal compressor according to any one of claims 1 to 11.   The centrifugal compressor according to any one of claims 1 to 12, wherein the impeller discharges the fluid flowing in along the axial direction in a direction orthogonal to the axial direction.   The flow rate coefficient is 0.01 or more and 0.05 or less, The centrifugal compressor given in any 1 paragraph of Claims 1-13 characterized by things.

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