WO2016151689A1

WO2016151689A1 - Centrifugal compressor and supercharger comprising same

Info

Publication number: WO2016151689A1
Application number: PCT/JP2015/058538
Authority: WO
Inventors: 直志神坂
Original assignee: 三菱重工業株式会社
Priority date: 2015-03-20
Filing date: 2015-03-20
Publication date: 2016-09-29
Also published as: US20180073515A1; JP6598388B2; EP3273068A4; CN107407291A; JPWO2016151689A1; EP3273068A1

Abstract

A housing (40) has formed therein an impeller side communicating path (51) extending from an impeller chamber (45) in a direction containing a radial outward (Dro) component, a circulating channel (52) extending from the impeller side communicating path (51) in a direction containing an axial front Daf component, and an intake side communicating path (55) communicating with the circulating channel (52) and an intake channel (41) that guides gas into the impeller chamber (45). The radial measurement (Ri) from an axial line (Ar) to a communication position with the intake side communicating path (55) in the circulating channel (52) is larger than the radial measurement (Ro) from the axial line (Ar) to a communication position with the impeller side communicating path (51) in the circulating channel (52). The channel area (Ao) of the circulating path (52) at the communication position with the intake side communicating path (55) is larger than the channel area (Ai) of the circulating channel (52) in the communication position with the impeller side communicating path (51).

Description

Centrifugal compressor and supercharger equipped with the same

The present invention relates to a centrifugal compressor and a supercharger including the same.

The centrifugal compressor includes a rotating shaft, an impeller attached to the outer periphery of the rotating shaft, and a housing that covers the impeller. The impeller of the centrifugal compressor guides the gas flowing in from the front side in the axial direction to the outside in the radial direction. A suction channel that guides gas to the front side in the axial direction of the impeller, an impeller chamber that communicates with the suction channel, and stores an impeller that communicates with the impeller chamber, and gas that is sent radially outward from the impeller flows into the housing. And a discharge flow path to be formed.

In such a centrifugal compressor, when the flow rate of the gas flowing in the housing is reduced, a phenomenon called surging in which the gas vibrates vigorously in the gas flow direction occurs. For this reason, various methods for suppressing this surging have been studied for centrifugal compressors.

Therefore, for example, the following Patent Document 1 discloses a centrifugal compressor in which the operating range is expanded by moving the surge limit where surging occurs to the smaller flow side. The housing of the centrifugal compressor is formed with a chamber that communicates the impeller chamber of the housing with the suction flow path, and a chamber that communicates the impeller chamber of the housing and the suction pipe connected to the suction flow path side of the housing. ing. By forming the chamber in the housing in this way, even when the flow rate of the gas flowing from the suction flow path to the discharge flow path through the impeller chamber is small, a part of the gas in the impeller chamber passes through the chamber and the suction flow path to the impeller chamber. By returning, the gas flow rate in the upstream portion of the impeller chamber increases, and surging can be suppressed.

Japanese Patent No. 3006215

In the technique described in Patent Document 1, the operating range of the centrifugal compressor can be expanded. However, in the centrifugal compressor, it is desired to expand the operating range.

Therefore, an object of the present invention is to provide a centrifugal compressor capable of expanding an operation region, and a supercharger including the centrifugal compressor.

A centrifugal compressor as one aspect according to the invention for achieving the above object is as follows:
A rotation shaft that rotates about an axis; an impeller that is attached to an outer periphery of the rotation shaft; and a housing that covers the impeller. The impeller includes a hub attached to the rotation shaft and the axis A plurality of the hubs are provided at intervals in the circumferential direction around the center, and by rotating integrally with the hub, the gas flowing in from the axial front side that is one side of the axial direction in which the axis extends extends to the diameter of the axis. A blade that guides outward in the direction, and the housing includes a suction channel that guides gas to the front side in the axial direction of the impeller, an impeller chamber that communicates with the suction channel and stores the impeller, and A discharge passage through which the gas sent to the radially outer side from the impeller communicates with the impeller chamber; and a component on the radially outer side from the impeller chamber that communicates with the impeller chamber. An impeller side communication passage extending in a direction extending in a direction, a circulation passage communicating with the impeller side communication passage and extending in a direction including a component on the front side in the axial direction from the impeller side communication passage, the circulation passage and the suction flow A suction side communication passage that communicates with the passage, and a suction side diameter dimension that is a dimension in a radial direction from the axis to a communication position with the suction side communication passage in the circulation channel is from the axis. The flow path area of the circulation flow path is larger than the impeller side diameter dimension which is a radial dimension to the communication position with the impeller side communication path in the circulation flow path, and the flow path area of the circulation flow path at the communication position with the suction side communication path is It is larger than the flow path area of the circulation flow path at the communication position with the impeller side communication path.

In the centrifugal compressor, when the flow rate of the gas flowing into the suction passage is small, the pressure in the impeller chamber is higher than the pressure in the suction passage. For this reason, when a circulation channel or the like is formed in the compressor housing as in the centrifugal compressor, a part of the gas in the impeller chamber returns to the suction channel via the circulation channel or the like. As a result, the flow rate in the front portion in the axial direction from the impeller side communication path in the impeller chamber is increased. For this reason, surging can be suppressed in the centrifugal compressor. That is, in the centrifugal compressor, the surge limit line can be on the small flow rate side, and the operating range can be expanded.

The flow direction component of the gas flowing into the circulation flow path from the impeller chamber via the impeller side communication path includes a swirl component around the axis and the same direction as the impeller rotation direction. If the gas having this swirl component as a flow component returns to the impeller chamber through the circulation flow path, the suction side communication path, and the suction flow path, the angle of attack of the blade is reduced. For this reason, the discharge pressure is reduced, in other words, the pressure ratio is reduced.

In the centrifugal compressor, the suction side diameter dimension of the circulation flow path is larger than the impeller side diameter dimension of the circulation flow path. Therefore, in the centrifugal compressor, the flow velocity of the swirl component of the gas at the communication position with the suction-side communication passage in the circulation flow path is set to the flow velocity of the swirl component of the gas at the communication position with the impeller-side communication passage in the circulation flow path. It can be made smaller than the flow rate.

Further, in the centrifugal compressor, the flow passage area of the circulation flow path at the communication position with the suction side communication path is larger than the flow passage area of the circulation flow path at the communication position with the impeller communication path. For this reason, in the centrifugal compressor, not only the flow rate of the axial component of the gas but also the flow rate of the swirl component at the communication position with the suction side communication path in the circulation channel can be reduced.

As described above, in the centrifugal compressor, the flow velocity of the swirling component of the air flowing into the impeller chamber can be reduced. As a result, in the centrifugal compressor, the angle of attack of the blade is increased, and the pressure ratio can be increased. Therefore, in the centrifugal compressor, the surge limit line can be on the high pressure ratio side. For this reason, the operating range can be further expanded in the centrifugal compression region.

Here, in the centrifugal compressor, the housing is formed with a plurality of circulation channels arranged in a circumferential direction around the axis, and between the circulation channels adjacent in the circumferential direction. The partition part which partitions off may be formed.

In the centrifugal compressor, the flow rate of the swirl component of the gas in the circulation flow path can be suppressed due to the presence of the partition portion.

In any one of the above centrifugal compressors, the suction flow path has a rotationally symmetric shape about the axis, and the flow path gradually increases toward the rear side in the axial direction, which is the other side of the axial direction. A reduced diameter portion having a small area may be provided, and a communication port for the suction flow path in the suction side communication path may be formed on a surface defining the flow path in the reduced diameter portion.

In the centrifugal compressor, since the suction flow path has a reduced diameter portion that gradually decreases in the flow path area toward the rear side in the axial direction, air easily flows from the outside into the impeller chamber via the suction flow path. Further, in the centrifugal compressor, since the communication port of the suction side communication path is formed in the surface that defines the flow path in the reduced diameter portion, the gas in the suction side communication path is reduced by the static pressure reducing effect on this surface. Can be efficiently guided into the suction flow path.

As a result, in the centrifugal compressor, the flow rate of the gas flowing into the impeller chamber through the suction channel can be increased. For this reason, in the said centrifugal compressor, a surge limit line can be made into the small flow volume side, and an operation range can be made wider.

Further, in the centrifugal compressor having the reduced diameter portion, the surface defining the flow path in the reduced diameter portion may form a curved surface that protrudes toward the axis.

In the centrifugal compressor, since a part of the surface defining the suction flow path forms a curved surface that protrudes toward the axis, that is, a bell mouth surface, gas from the outside passes through the suction flow path to the impeller chamber It becomes easy to flow into. Furthermore, in the centrifugal compressor, since the communication port of the suction side communication passage is formed in the bell mouth surface, the static pressure reducing effect on the bell mouth surface effectively allows the gas in the suction side communication passage to be efficiently discharged. It can be led into the suction channel.

In any one of the centrifugal compressors having the reduced diameter portion, the radial dimension from the axial line to the axially front edge of the communication port of the suction side communication path is the suction side diameter dimension. It may be smaller and larger than the impeller side diameter dimension.

Further, in any one of the above centrifugal compressors, the suction side communication path is folded back from the boundary between the circulation flow path and the suction side communication path, and then directed radially inward with respect to the axis line, the shaft It extends toward the axial rear side, which is the other side of the direction, and may communicate with the suction flow path.

In the centrifugal compressor, the gas until a part of the gas in the impeller chamber returns to the suction flow path through the impeller side communication path, the circulation flow path, and the suction side communication path without increasing the axial dimension of the housing. The flow path length can be increased. When the axial flow path length is increased, the gas is likely to follow the wall surface of the axially extending flow path, and the gas swirl component is reduced. Therefore, in the centrifugal compressor, the angle of attack of the blade is increased, and the pressure ratio can be increased. For this reason, in the said centrifugal compressor, an operating range can be expanded more.

In any one of the above centrifugal compressors, L is defined as an axial distance from a communication position with the suction-side communication path in the circulation flow path to a communication position with the impeller-side communication path in the circulation flow path. Dimensions, do as the equivalent diameter of the flow path area of the circulation flow path at the communication position with the suction side communication path, and di as the flow path area of the circulation flow path at the communication position with the impeller side communication path In the case of the equivalent diameter, the spread angle 2θ defined by the following formula is less than 20 °.
2θ = 2 × tan ((do-di) / 2L)

The rapid deceleration of the flow velocity in the circulation channel leads to the development of a boundary layer on the wall that defines the circulation channel. For this reason, the pressure loss of the gas passing through the circulation channel increases, and the flow rate of the gas flowing through the circulation channel decreases. Therefore, in the centrifugal compressor, the spread angle 2θ is set to be less than 20 ° to suppress a decrease in the flow rate of the gas flowing through the circulation channel.

In any of the above centrifugal compressors, the axial dimension from the communication position with the suction-side communication path in the circulation channel to the communication position with the impeller-side communication path in the circulation channel is: The impeller outer diameter which is the maximum outer diameter of the impeller may be 0.25 times or more.

When the axial flow path length is long, the gas easily follows the wall surface of the axially extending flow path, and the swirl component of the gas is reduced. Therefore, in the centrifugal compressor, the axial dimension from the communication position with the suction-side communication path in the circulation channel to the communication position with the impeller-side communication path in the circulation channel is lengthened, and the swirl component of the gas is reduced. .

The supercharger as one aspect according to the invention for achieving the above object is as follows:
One of the above centrifugal compressors and a turbine are provided, and the turbine is a turbine rotating shaft that rotates about the axis, a turbine impeller that is attached to an outer periphery of the turbine rotating shaft, and the turbine impeller A turbine housing covering the turbine, and the turbine rotating shaft and the rotating shaft of the centrifugal compressor are connected to each other on the same axis and are connected together to form a supercharger rotating shaft.

In one embodiment of the present invention, the operating range of the centrifugal compressor can be expanded.

It is a typical principal part sectional view of the centrifugal compressor in a first embodiment concerning the present invention. 1 is an overall cross-sectional view of a supercharger in a first embodiment according to the present invention. It is explanatory drawing for demonstrating a divergence angle. 6 is a schematic cross-sectional view of a main part of a centrifugal compressor in Comparative Example 2. FIG. It is a graph which shows the characteristic of each centrifugal compressor. It is a typical principal part sectional view of the centrifugal compressor in a second embodiment concerning the present invention. It is a typical principal part sectional view of the centrifugal compressor in a third embodiment concerning the present invention. It is a typical principal part sectional view of the centrifugal compressor in a fourth embodiment concerning the present invention.

Hereinafter, various embodiments according to the present invention will be described with reference to the drawings.

“First Embodiment of Centrifugal Compressor and Supercharger”
A first embodiment of a centrifugal compressor and a supercharger will be described with reference to FIGS.

As shown in FIG. 2, the turbocharger of the present embodiment includes a turbine 10 driven by exhaust gas EX from the engine, a centrifugal compressor 30 that compresses air A and sends it to the engine, a centrifugal compressor 30 and a turbine. 10 is provided.

The turbine 10 includes a cylindrical turbine rotating shaft 11 that rotates about an axis Ar, a turbine impeller 12 that is attached to the outer periphery of the turbine rotating shaft 11, and a turbine housing 19 that covers the turbine impeller 12.

The centrifugal compressor 30 includes a cylindrical compressor rotating shaft 31 that rotates about an axis Ar, a compressor impeller 32 that is attached to the outer periphery of the compressor rotating shaft 31, and a compressor housing that covers the compressor impeller 32. 40.

The connecting portion 20 includes a columnar connecting rotary shaft 21 that rotates about the axis Ar, a center housing 29 that covers the connecting rotary shaft 21, and a bearing 28 that rotatably supports the connecting rotary shaft 21. The bearing 28 is fixed to the inner peripheral side of the center housing 29.

The axis line Ar of the compressor rotating shaft 31, the axis line Ar of the connecting rotating shaft 21, and the axis line Ar of the turbine rotating shaft 11 are located on the same axis line Ar, and are connected to each other in this order so as to rotate together and rotate the turbocharger. Make an axis. The compressor housing 40, the center housing 29, and the turbine housing 19 are connected to each other to form a supercharger housing.

Here, the direction in which the axis Ar extends is the axial direction Da, one side of the axial direction Da is the axial front side Daf, and the other side of the axial direction Da is the axial rear side Dab. In the present embodiment, the centrifugal compressor 30 is provided on the axially front side Daf with respect to the connecting part 20, and the turbine 10 is provided on the axially rear side Dab with respect to the connecting part 20. In addition, the radial direction with respect to the axis Ar is simply referred to as the radial direction Dr, the side farther from the axis Ar in the radial direction Dr is the radially outer Drro, and the side closer to the axis Ar in the radial direction Dr is the radially inner Dri. Further, the circumferential direction around the axis Ar is simply referred to as a circumferential direction Dc.

The compressor impeller 32 is an open impeller. The compressor impeller 32 includes a hub 33 that is mounted on the outer periphery of the compressor rotating shaft 31 and a plurality of blades 35 that are provided on the hub 33 at intervals in the circumferential direction Dc.

The shape of the hub 33 viewed from the axial direction Da is circular with the axis line Ar as the center, and the outer diameter gradually increases from the axial front side Daf to the axial rear side Dab. Further, the hub 33 has a position on the boundary line between the hub surface 34, which is the surface of the radially outer side Dro, and the meridional section, as it moves from the axial front side Daf to the axial rear side Dab. The tangent is shaped so as to gradually face the radial direction Dr from a direction substantially parallel to the axis Ar.

The plurality of blades 35 are all provided on the hub surface 34. The blade 35 projects in a direction including a directional component perpendicular to the hub surface 34, and extends along the hub surface 34 from the axial front side Daf of the hub surface 34 to the edge of the axial rear side Dab of the hub surface 34. Yes. An edge of the blade 35 on the front side Daf in the axial direction forms a leading edge 36, and an edge of the blade 35 on the rear side Dab in the axial direction facing the radially outer side Dro forms a trailing edge 37. Further, the tip of the blade 35 in the protruding direction with respect to the hub surface 34 forms a tip 38. The tip 38 of the blade 35 faces the inner peripheral surface of the compressor housing 40.

The compressor housing 40 includes a suction passage 41 that guides air A to the axially front side Daf of the compressor impeller 32, an impeller chamber 45 that communicates with the suction passage 41 and houses the compressor impeller 32, and an impeller chamber 45. And a discharge passage 46 into which the gas sent from the compressor impeller 32 to the radially outer side Dro flows is formed. The suction flow path 41 has a rotationally symmetric shape about the axis Ar. The air A from the suction passage 41 flows between the leading edges 36 of the plurality of blades 35 in the compressor impeller 32 and between the plurality of blades 35. The discharge flow path 46 includes a diffuser portion 47 extending from the trailing edge 37 of the plurality of blades 35 to the radially outer side Dro, a scroll portion 48 extending in the circumferential direction Dc from the edge of the diffuser portion 47 on the radially outer side Dro, Have The air A from the discharge passage 46 flows into the engine cylinder from the intake manifold of the engine.

The compressor housing 40 further communicates with the impeller chamber 45, communicates with the impeller side communication passage 51 from the impeller chamber 45 in a direction including the radially outer component Dro, and communicates with the impeller side communication passage 51. A plurality of circulation passages 52 extending in a direction including the component of the axial front side Daf from the passage 51, and a suction-side communication passage 55 communicating with the plurality of circulation passages 52 and the suction passage 41 are formed.

The impeller side communication passage 51 opens at an impeller chamber inner surface 45ip that faces the tip 38 of the compressor impeller 32 and faces the radially inner side Dri among the surfaces that define the impeller chamber 45 of the compressor housing 40. ing. The opening is formed on the impeller chamber inner surface 45ip, at a position that is axially rearward Dab from the leading edge 36 of the compressor impeller 32 and axially forward Daf from the trailing edge 37 of the compressor impeller 32. Has been. In the present embodiment, the impeller side communication passage 51 has an annular shape around the axis Ar. In other words, the impeller side communication passage 51 extends from the impeller chamber 45 in a direction including the radially outer component Dro and extends 360 ° in the circumferential direction Dc centered on the axis Ar. For this reason, the opening formed in the impeller inner surface 45ip of the compressor impeller 32 side passage opens 360 ° in the circumferential direction Dc centering on the axis Ar.

The plurality of circulation channels 52 all extend from the radially outer side Dro end of the impeller side communication passage 51 in the direction including the axial front Daf component and spread in the circumferential direction Dc. The plurality of circulation channels 52 are arranged in the circumferential direction Dc around the axis Ar. The circulation channels 52 adjacent in the circumferential direction Dc are partitioned by struts (partitions) 62 of the compressor housing 40.

The suction side communication passage 55 extends from the axially front Daf end of each of the plurality of circulation flow paths 52 in a direction having a radially inner Dri component and communicates with the suction flow path 41. Similarly to the impeller side communication path 51, the suction side communication path 55 also has an annular shape around the axis Ar in the present embodiment.

In the compressor housing 40, the portion inside the radial direction Dri of the plurality of circulation channels 52 and the outside diameter Dro of the suction channel 41 forms a treatment cylinder 63. The treatment cylinder 63 has a cylindrical shape around the axis Ar. The edge of the treatment tube 63 on the front side Daf in the axial direction forms the edge of the rear side Dab in the axial direction of the suction side communication passage 55. The edge of the treatment tube 63 in the axial rear side Dab forms the edge of the impeller side communication path 51 in the axial front side Daf. The treatment tube 63 is connected to a housing body 61 that forms a radially outer portion Dro portion of the plurality of circulation channels 52 in the compressor housing 40 by a plurality of struts (partition portions) 62.

Next, the dimensions of each part of the compressor housing 40 in this embodiment will be described with reference to FIG.

Here, the communication position of the circulation flow path 52 with the impeller side communication path 51 is the inlet 53 of the circulation flow path 52, and the communication position of the circulation flow path 52 with respect to the suction side communication path 55 is the outlet 54 of the circulation flow path 52. . In the present embodiment, the suction side diameter dimension Ro (hereinafter referred to as the outlet inner diameter) Ro, which is the dimension from the axis Ar to the edge of the radially inner side Dri of the outlet 54 of the circulation channel 52, is expressed by the following equation (1). As described above, the impeller side diameter dimension (hereinafter referred to as the inlet inner diameter) Ri, which is the dimension from the axis Ar to the edge of the radially inner side Dri of the outlet 54 of the circulation channel 52, is larger.
Ro> Ri (1)

In the present embodiment, as shown in the following formula (2), the flow area (hereinafter referred to as the outlet flow area) Ao at the outlet 54 of the circulation flow path 52 is the inlet 53 of the circulation flow path 52. It is larger than the flow area at Ai (referred to as the inlet flow area).
Ao> Ai (2)

In the present embodiment, the flow path length L of the circulation flow path 52, which is the dimension in the axial direction Da from the inlet 53 to the outlet 54 in the circulation flow path 52, is expressed by the following formula (3). It is at least 0.25 times the outer diameter D2 of the impeller, which is the maximum diameter.
L ≧ 0.25 × D2 (3)

In the present embodiment, the divergence angle 2θ of the circulation channel 52 represented by the following formula (4) is less than 20 °.
2θ = 2 × tan ((do-di) / 2L) <20 ° (4)

In addition, L in Formula (4) is the flow path length of the axial direction Da of the circulation flow path 52 as mentioned above. Further, as shown in FIG. 3, do is an equivalent diameter with respect to the outlet flow passage area Ao, and di is an equivalent diameter with respect to the inlet flow passage area Ai. That is, the divergence angle 2θ is assumed to be a simple diffuser having a conical flow path. In this case, a line segment connecting the edge at the inlet position of the flow path and the edge at the outlet position of the flow path, The angle is twice the angle θ formed with the axis. In addition, the equivalent diameter regarding a flow path area is a diameter of the circle of this flow path area.

Next, Comparative Examples 1 and 2 of the centrifugal compressor will be described in order to explain the operational effects of the present embodiment.

As in the compressor housing 40 in the centrifugal compressor 30 of the present embodiment, a suction passage, an impeller chamber, and a discharge passage are formed in the compressor housing in the centrifugal compressor of Comparative Example 1. However, the compressor housing in the centrifugal compressor of Comparative Example 1 is formed with the impeller side communication path 51, the circulation flow path 52, and the suction side communication path 55 of the compressor housing 40 in the centrifugal compressor 30 of the present embodiment. It has not been.

As shown in FIG. 4, the compressor housing 40x in the centrifugal compressor 30x of Comparative Example 2 includes a suction passage 41 and an impeller chamber 45 as in the compressor housing 40 in the centrifugal compressor 30 of the present embodiment. The discharge flow path 46, the impeller side communication path 51, the circulation flow path 52x, and the suction side communication path 55 are formed.

However, in Comparative Example 2, the outlet inner diameter Ro of the circulation flow path 52x and the impeller side diameter Ri of the circulation flow path 52x are equal. In Comparative Example 2, the outlet channel area Ao of the circulation channel 52x is equal to the inlet channel area Ai of the circulation channel 52x.

In the centrifugal compressor, when the flow rate of the gas flowing into the suction passage is small, the pressure in the suction passage is lower than the pressure in the impeller chamber. For this reason, when the circulation passages 52, 52x and the like are formed in the

compressor housings

40, 40x as in the present embodiment and the comparative example 2, a part of the gas in the impeller chamber 45 is circulated in the circulation passages 52, 52x. It returns to the suction flow path 41 via 52x etc. As a result, in the impeller chamber 45, the flow rate of the portion on the axially front side Daf from the impeller side communication passage 51 increases.

In the present embodiment and Comparative Example 2, when the flow rate of the gas flowing into the suction flow channel 41 is small, the flow rate of the gas flowing through the discharge flow channel 46 is small, but the front side in the axial direction from the impeller side communication passage 51 in the impeller chamber 45. The flow rate of the Daf portion is larger than the flow rate of the gas flowing into the suction flow path 41, and surging can be suppressed. Therefore, as shown in FIG. 5, the surge limit lines S1 to S4 and Sx2 of Examples 1 to 4 and Comparative Example 2 which are various forms of the present embodiment are smaller than the surge limit line Sx1 of Comparative Example 1. become. For this reason, in Examples 1 to 4 and Comparative Example 2 which are various forms of the present embodiment, the operating range of the centrifugal compressor 30 can be expanded as compared with Comparative Example 1. The centrifugal compressors of Examples 1 to 4 are centrifugal compressors that satisfy the above-described formulas (1) to (4). However, the flow path lengths L of the circulation flow paths in the centrifugal compressors of Examples 1 to 4 are different from each other as described later. Further, in FIG. 5, a plurality of curves drawn with solid lines are characteristic curves showing the relationship between the flow rate and the pressure ratio at different rotational speeds.

By the way, the flow of the air A that flows into the circulation flow paths 52 and 52x from the impeller chamber 45 through the impeller side communication passage 51 is a swirl component centered on the axis Ar and is the same as the rotation direction of the compressor impeller 32. Contains a directional component. If the air A having this swirl component as a flow component returns to the impeller chamber 45 via the circulation flow path 52x, the suction side communication path 55, and the suction flow path 41 in Comparative Example 2, the angle of attack of the blade 35 Therefore, the discharge pressure is reduced, in other words, the pressure ratio is reduced.

When no external force is applied to the gas swirling around the axis Ar, the following equation (5) is established.
ci × Ri = co × Ro (5)
In equation (5), ci represents the flow velocity of the swirl component of the air A at the inlet 53 of the circulation flow path, and co represents the flow velocity of the swirl component of the air A at the outlet 54 of the circulation flow path. In Equation (5), Ri represents the inlet inner diameter of the swirl flow path, and Ro represents the outlet inner diameter of the circulation flow path 52.

For this reason, when the outlet inner diameter Ro of the circulation channel 52 is larger than the inlet inner diameter Ri of the circulation channel 52 as in the present embodiment, the flow velocity co of the swirl component of the air A at the outlet 54 of the circulation channel 52 circulates. It becomes smaller than the flow velocity ci of the swirling component of the air A at the inlet 53 of the flow path 52.

In the present embodiment, the outlet channel area Ao of the circulation channel 52 is larger than the inlet channel area Ai of the circulation channel 52. For this reason, in this embodiment, the flow velocity co of the swirl component of the air A at the outlet 54 of the circulation flow path 52 is further smaller than the flow velocity ci of the swirl component of the air A at the inlet 53 of the circulation flow path 52.

Therefore, in the centrifugal compressor 30 of this embodiment, the flow velocity of the swirl component of the air A flowing into the impeller chamber 45 can be made smaller than that of the centrifugal compressor 30x of the comparative example 2.

Among Examples 1 to 4 which are various forms of the present embodiment, Example 1 is a centrifugal compressor 30 in which the flow path length L of the circulation flow path 52 is 0.25 × D. The second embodiment is a centrifugal compressor 30 in which the flow path length L of the circulation flow path 52 is 0.50 × D. The third embodiment is a centrifugal compressor 30 in which the flow path length L of the circulation flow path 52 is 0.64 × D. The fourth embodiment is a centrifugal compressor 30 in which the flow path length L of the circulation flow path 52 is 0.89 × D. That is, in Examples 1 to 4, the channel length L of Example 1 is the shortest, and the channel length L becomes longer as in Example 2, Example 3, and Example 4.

As shown in FIG. 5, in Examples 1 to 4, the surge limit line S1 of Example 1 is on the largest flow rate side, and the surge limit line becomes smaller in accordance with Examples 2, 3, and 4. Move to the flow rate side. That is, as the flow path length L of the circulation flow path 52 becomes longer, the surge limit line becomes a smaller flow rate side, and the operating range of the centrifugal compressor 30 can be expanded. This is because not only the velocity component in the axial direction Da of the flow of the air A but also the flow channel length L of the circulation channel 52 becomes longer due to the influence of friction between the circulation channel 52 and the air A, etc. This is because the swirl component is also reduced. Therefore, in this embodiment, the flow path length L of the circulation flow path 52 is set to 0.25 × D or more.

By the way, in the present embodiment, as described above, the outlet flow passage area Ao of the circulation passage 52 is made larger than the inlet passage area Ai of the circulation passage 52, and the flow rate of the air A in the circulation passage 52 is increased. It is small. However, the rapid deceleration in the circulation channel 52 leads to the development of a boundary layer on the wall surface that defines the circulation channel 52. For this reason, the pressure loss of the gas passing through the circulation flow path 52 increases, and the flow rate of the gas flowing through the circulation flow path 52 decreases. Therefore, in the present embodiment, as described above using Expression (5), the spread angle 2θ is set to be less than 20 ° to suppress a decrease in the flow rate of the air A flowing through the circulation flow path 52. As can be understood from the equation (5), in order to reduce the spread angle 2θ, it is preferable that the flow path length of the circulation flow path 52 is long.

That is, it is preferable that the flow path length L of the circulation flow path 52 is long both in terms of reducing the swirl component and in reducing the spread angle 2θ. From this viewpoint, the flow path length of the circulation flow path 52 is preferably 0.25 × D or more, and preferably 0.50 × D or more if possible. However, when the flow path length L of the circulation flow path 52 is increased, the compressor housing 40 is lengthened in the axial direction Da. For this reason, it is preferable to determine the flow length L of the circulation flow path 52 by comparing and considering the viewpoint of reducing the swivel component while reducing the spread angle and the viewpoint of increasing the length of the compressor housing 40.

“Second Embodiment of Centrifugal Compressor”
A second embodiment of the centrifugal compressor will be described with reference to FIG.

The centrifugal compressor 30a of the present embodiment also has a compressor impeller 32 and a compressor housing 40a, similar to the centrifugal compressor 30 of the first embodiment. The configuration of the compressor impeller 32 is the same as that of the first embodiment.

Similarly to the compressor housing 40 in the centrifugal compressor 30 of the first embodiment, the compressor housing 40a of the present embodiment also has a suction flow path 41a, an impeller chamber 45, a discharge flow path 46, an impeller side communication path 51, and a plurality of A circulation flow path 52 and a suction side communication path 55a are formed. However, the shape of the suction flow path 41a and the suction side communication path 55a in the compressor housing 40a of the present embodiment is different from that of the first embodiment.

The suction flow path 41a of the present embodiment has a rotationally symmetric shape about the axis Ar, and has a reduced diameter portion 42 that gradually decreases in flow path area from the axial front side Daf to the axial rear side Dab. Have. The reduced diameter portion 42 has a bell mouth shape centered on the axis Ar. For this reason, the surface that defines the flow path in the reduced diameter portion 42 forms a smooth convex bell mouth surface 42f toward the radially inner side Dri that is closer to the axis Ar.

The communication port 55o for the suction flow path 41a in the suction side communication path 55a is formed in the bell mouth surface 42f that defines the flow path in the reduced diameter portion 42. In the suction side communication path 55a, a portion of the axial rear side Dab with respect to the suction side communication path 55a is formed of a treatment tube 63a as in the first embodiment. In addition, the suction side communication passage 55 a is formed with a housing body 61 and a bell mouth cap 65 at a portion on the axial front side Daf with reference to the suction side communication passage 55 a.

The inner peripheral surface of the treatment cylinder 63a of this embodiment forms a portion of the axial rear side Dab of the bell mouth surface 42f. For this reason, the flow path area defined by the inner peripheral surface of the treatment tube 63a gradually decreases in size from the axial front side Daf to the axial rear side Dab.

The bell mouth cap 65 has a rotationally symmetric shape about the axis Ar. The bell mouth cap 65 is fixed to the axially front side Daf of the housing body 61 and to the radially inner side Dri. The bell mouth cap 65 is fixed to the housing main body 61 with a space from the treatment tube 63a to the axially front side Daf. A space between the treatment tube 63a and the bell mouth cap 65 serves as a suction side communication passage 55a. The inner peripheral surface of the treatment tube 63a forms a portion on the axially front side Daf of the bell mouth surface 42f. For this reason, the flow path defined by the inner peripheral surface of the bell mouth cap 65 gradually decreases in the flow path area from the axial front side Daf to the axial rear side Dab.

Similarly to the compressor housing 40 of the first embodiment, the compressor housing 40a of the present embodiment also satisfies the relationships expressed by the equations (1) to (4). Furthermore, in this embodiment, the dimension from the axis Ar to the edge of the axial front side Daf at the communication port 55o of the suction side communication passage 55a, in other words, the radial inner side Dri of the bell mouth cap 65 from the axis Ar to the axial direction. The dimension Rc to the edge of the front Daf is smaller than the outlet inner diameter Ro and larger than the inlet inner diameter Ri as shown in the following formula (6).
Ro>Rc> Ri (6)

For this reason, in this embodiment, in order to satisfy this formula (6), the flow path defined by the bell mouth surface 42f around the communication port 55o of the suction side communication passage 55a is directed toward the axial rear side Dab. The diameter is smoothly reduced.

Similarly to the compressor housing 40 of the first embodiment, the compressor housing 40a of the present embodiment also satisfies the relations expressed by the equations (1) to (4), so that the swirl component of the air A flowing into the impeller chamber 45 is reduced. The flow rate can be reduced, and the operating range of the centrifugal compressor 30a can be expanded.

In addition, since a part of the surface defining the suction channel 41a of the present embodiment forms the bell mouth surface 42f, the air A easily flows into the impeller chamber 45 from the outside through the suction channel 41a. Furthermore, in this embodiment, since the communication port 55o with respect to the suction flow path 41a in the suction side communication path 55a is formed in the bell mouth surface 42f, the suction side communication is achieved by the static pressure reducing effect on the bell mouth surface 42f. The air A in the passage 55a can be efficiently guided into the suction flow path 41a.

As a result, in this embodiment, the flow rate of the air A flowing into the impeller chamber 45 through the suction flow passage 41a can be increased as compared with the first embodiment. For this reason, in this embodiment, a surge limit line can be made into the smaller flow volume side than 1st embodiment, and the operating range of the centrifugal compressor 30a can be made wider.

"Third embodiment of centrifugal compressor"
A third embodiment of the centrifugal compressor will be described with reference to FIG.

The centrifugal compressor 30b of this embodiment also has a compressor impeller 32 and a compressor housing 40b, similar to the

centrifugal compressors

30 and 30a of the first and second embodiments. The configuration of the compressor impeller 32 is the same as in the first and second embodiments.

Similarly to the

compressor housings

40 and 40a in the

centrifugal compressors

30 and 30a of the first and second embodiments, the compressor housing 40b of the present embodiment also has a suction passage 41b, an impeller chamber 45, a discharge passage 46, and an impeller. A side communication path 51, a plurality of circulation channels 52, and a suction side communication path 55b are formed. However, the shape of the suction flow path 41b and the suction side communication path 55b in the compressor housing 40b of the present embodiment is different from that of the first embodiment.

The suction flow path 41b of the present embodiment includes a reduced diameter portion 42b and a straight body portion 43b that are rotationally symmetric about the axis Ar. As for the diameter-reduced part 42b, a flow path area becomes small gradually as it goes to the axial direction rear side Dab from the axial direction front side Daf. The reduced diameter portion 42b has a bell mouth shape centered on the axis Ar. For this reason, the surface that defines the flow path in the reduced diameter portion 42b forms a smooth convex bell mouth surface 42bf toward the radially inner side Dri that is closer to the axis Ar. The straight body portion 43b has the same flow path area at each position in the axial direction Da. For this reason, the surface that defines the flow path in the straight body portion 43b forms a cylindrical inner peripheral surface 43bg centered on the axis Ar.

The communication port 55o for the suction flow path 41b in the suction side communication path 55b is formed in a cylindrical inner peripheral surface 43bg that defines the flow path in the straight body portion 43b. In the suction side communication path 55b, a portion of the axial rear side Dab with respect to the suction side communication path 55b is formed of a treatment cylinder 63b as in the first and second embodiments. Further, the suction side communication passage 55b is formed by a housing main body 61 and a bell mouth cap 65b at a portion on the axial front side Daf with reference to the suction side communication passage 55b. As in the second embodiment, the bell mouth cap 65b is fixed to the axially front Daf of the housing main body 61 and to the radially inner Dri thereof. The bell mouth cap 65b is also fixed to the housing body 61 with a space from the treatment tube 63b to the axially front side Daf. The space between the treatment tube 63b and the bell mouth cap 65b is a suction side communication passage 55b.

The suction side communication path 55b is folded back from the boundary between the circulation flow path 52 and the suction side communication path 55b, and then extends toward the axial rear side Dab while facing the radial inner side Dri with respect to the axis Ar. It communicates with 41b.

The treatment tube 63b of the present embodiment has a reduced inner diameter surface 63bf whose inner diameter is gradually reduced toward the axial rear side Dab, and a cylindrical inner peripheral surface 63bg whose inner diameter is constant in the axial direction Da. Is formed. The cylindrical inner peripheral surface 63bg is formed from the edge of the axially rear side Dab of the reduced diameter inner peripheral surface 63bf. The bell mouth cap 65b is formed with a bell mouth surface 65bf whose inner diameter is gradually reduced toward the axial rear side Dab, and a cylindrical inner peripheral surface 65bg whose inner diameter is constant in the axial direction Da. The cylindrical inner peripheral surface 65bg is formed from an edge of the axial rear side Dab of the bell mouth surface 65bf. Further, the bell mouth cap 65b is formed with a reduced-diameter outer peripheral surface 65bh whose outer diameter is gradually reduced toward the axial rear side Dab.

The suction side communication passage 55b is formed between the reduced diameter inner peripheral surface 63bf of the treatment tube 63b and the reduced diameter outer peripheral surface 65bh of the bell mouth cap 65b. The cylindrical inner peripheral surface 43bg that defines the flow path in the straight body portion 43b is formed by the cylindrical inner peripheral surface 63bg of the treatment tube 63b and the cylindrical inner peripheral surface 65bg of the bell mouth cap 65b.

The compressor housing 40b of the present embodiment also satisfies the relationships shown in the equations (1) to (4), like the

compressor housings

40 and 40a of the above embodiments. For this reason, similarly to the compressor housing 40 of the first embodiment, the compressor housing 40b of the present embodiment can reduce the flow velocity of the swirling component of the air A flowing into the impeller chamber 45, and the centrifugal compressor 30b The operating range can be expanded.

In the present embodiment, the suction side communication passage 55b extends from the boundary between the circulation flow path 52 and the suction side communication path 55b and then extends toward the axial rear side Dab to communicate with the suction flow path 41b. Therefore, the flow path length until a part of the air A in the impeller chamber 45 returns to the suction flow path 41b becomes longer. For this reason, similarly to the case where the flow path length L of the circulation flow path 52 is increased, the flow velocity of the swirl component of the air A flowing into the impeller chamber 45 can be reduced. Moreover, in this embodiment, the suction side communication passage 55b extends from the boundary between the circulation flow path 52 and the suction side communication passage 55b and then extends toward the axial rear side Dab, so that the axial direction of the compressor housing 40b It is possible to increase the flow path length until a part of the air A in the impeller chamber 45 returns to the suction flow path 41b while suppressing an increase in length to Da.

"Fourth embodiment of centrifugal compressor"
A fourth embodiment of the centrifugal compressor will be described with reference to FIG.

The centrifugal compressor 30c of the present embodiment is a combination of the structure of the centrifugal compressor 30a of the second embodiment and the structure of the centrifugal compressor 30b of the third embodiment. That is, this embodiment adopts the configuration of the suction side communication path in the third embodiment, and the communication port for the suction flow path in this suction side communication is the bell mouth surface of the suction side flow path as in the second embodiment. Is formed.

The suction flow path 41c of the present embodiment also has a reduced diameter portion 42c and a straight body portion 43c that are rotationally symmetric about the axis Ar as in the third embodiment. As for the diameter-reduced part 42c, a flow path area becomes small gradually as it goes to the axial direction rear side Dab from the axial direction front side Daf. The reduced diameter portion 42c has a bell mouth shape centered on the axis Ar. For this reason, the surface defining the flow path in the reduced diameter portion 42c forms a smooth convex bell mouth surface 42cf toward the radially inner side Dri. The straight body portion 43c has the same flow path area at each position in the axial direction Da. For this reason, the surface that defines the flow path in the straight body portion 43c forms a cylindrical inner peripheral surface 43cg with the axis line Ar as the center.

The communication port 55o with respect to the suction flow path 41c in the suction side communication path 55c is formed in the bell mouth surface 42cf in the reduced diameter portion 42c. In the suction side communication path 55c, a portion of the axial rear side Dab with respect to the suction side communication path 55c is formed by the treatment cylinder 63c as in the above embodiments. Further, the suction side communication passage 55c is formed with a housing main body 61 and a bell mouth cap 65c at the axially front side Daf with reference to the suction side communication passage 55c. As in the second and third embodiments, the bell mouth cap 65c is fixed to the axially front Daf of the housing body 61 and to the radially inner Dri thereof. The bell mouth cap 65c is also fixed to the housing main body 61 with a space from the treatment tube 63c to the axially front side Daf. A suction side communication passage 55c is formed between the treatment tube 63c and the bell mouth cap 65c.

As in the third embodiment, the suction side communication passage 55c is turned from the boundary between the circulation flow path 52 and the suction side communication passage 55c, and then toward the radially inner side Dri with respect to the axis Ar, toward the axial rear side Dab. And communicates with the suction channel 41c.

The treatment tube 63c of the present embodiment has a reduced inner diameter surface 63cf whose inner diameter is gradually reduced toward the axial rear side Dab, and a cylindrical inner peripheral surface 63cg whose inner diameter is constant in the axial direction Da. Is formed. The cylindrical inner peripheral surface 63cg is formed from the edge of the axially rear side Dab of the reduced diameter inner peripheral surface 63cf. The bell mouth cap 65c is formed with a bell mouth surface 65cf whose inner diameter is gradually reduced toward the rear side Dab in the axial direction. Further, the bell mouth cap 65c is formed with a reduced-diameter outer peripheral surface 65ch whose outer diameter is gradually reduced toward the rear side Dab in the axial direction. A portion of the axial rear side Dab in the reduced diameter inner peripheral surface 63cf of the treatment tube 63c forms a bell mouth surface 63cf. The bell mouth surface 63cff of the treatment tube 63c is located on a virtual bell mouth surface obtained by extending the bell mouth surface 65cf of the bell mouth cap 65c to the rear side Dab in the axial direction.

The suction side communication passage 55c is formed between a portion of the reduced diameter inner peripheral surface 63cf of the treatment tube 63c excluding the bell mouth surface 63cf and a reduced diameter outer peripheral surface 65ch of the bell mouth cap 65c. The bell mouth surface 42cf in the reduced diameter portion 42c of the suction channel 41c is formed by the bell mouth surface 65cf of the bell mouth cap 65c and the bell mouth surface 63cf of the treatment tube 63c.

The compressor housing 40c of the present embodiment also satisfies the relationships expressed by the equations (1) to (4), like the

compressor housings

40, 40a, and 40b of the above embodiments. Further, in the present embodiment, as in the second embodiment, the dimension Rc from the axis Ar to the edge of the bell mouth cap 65c on the radially inner side Dri and the axially front side Daf is smaller than the outlet inner diameter Ro and the inlet inner diameter. Greater than Ri.

As in the third embodiment, the suction side communication path 55c of the present embodiment is folded back from the boundary between the circulation flow path 52 and the suction side communication path 55c and then extends toward the axial rear side Dab, and the suction flow path 41c. Communicated with. For this reason, in the present embodiment, as in the third embodiment, while the length of the compressor housing 40c in the axial direction Da is suppressed, a part of the air A in the impeller chamber 45 returns to the suction flow path 41c. The channel length can be increased.

Moreover, the communication port 55o with respect to the suction flow path 41c in the suction side communication path 55c of this embodiment is formed in the bell mouth surface 42cf in the reduced diameter part 42c similarly to 2nd embodiment. For this reason, in the present embodiment, as in the second embodiment, air A easily flows from the outside into the impeller chamber 45 through the suction flow path 41c, and the static pressure reduction effect on the bell mouth surface 42cf allows the suction side The air A in the communication path 55c can be efficiently guided into the suction flow path 41c.

Note that the

compressor housings

40b and 40c of the third embodiment and the present embodiment both satisfy the relationship represented by the formula (3). However, the

compressor housings

40b and 40c of the third embodiment and the present embodiment do not have to satisfy the relationship represented by the expression (3).

Further, the centrifugal compressor of each of the above embodiments is a centrifugal compressor provided in the supercharger, but the centrifugal compressor according to the present invention may not be provided in the supercharger.

10: turbine, 11: turbine rotating shaft, 12: turbine impeller, 19: turbine housing, 20: connecting portion, 21: connecting rotating shaft, 29: center housing, 30, 30a, 30b, 30c, 30x: centrifugal compressor, 31: Compressor rotating shaft, 32: Compressor impeller, 33: Hub, 35: Blade, 40, 40a, 40b, 40c, 40x: Compressor housing, 41, 41a, 41b, 41c: Suction flow path, 42, 42b 42c: reduced diameter portion, 42f, 42bf, 42cf: bell mouth surface, 43b, 43c: straight body portion, 43bg: cylindrical inner peripheral surface, 45: impeller chamber, 46: discharge flow path, 51: impeller side communication passage, 52: circulation flow path, 55, 55a, 55b, 55c: suction side communication path, 55o: communication port, 61: housing body, 62: strut (partition part), 63, 63a, 63b, 63c: treatment tube, 65, 65b, 65c: bell mouth cap, Ar: axial line, Da: axial direction, Dab: axial rear side, Daf: axial front side, Dc: circumferential direction, Dr: radial direction , Dri: radially inner side, Dro: radially outer side

Claims

A rotation axis that rotates about an axis;
An impeller attached to the outer periphery of the rotating shaft;
A housing covering the impeller;
With
The impeller includes a hub mounted on the rotating shaft, and a plurality of the impellers are provided in the hub at intervals in a circumferential direction around the axis, and the shaft extends in an axial direction by rotating integrally with the hub. A blade that guides the gas flowing in from the axial front side that is one side of
The housing includes a suction flow path that guides gas to the front side in the axial direction of the impeller, an impeller chamber that communicates with the suction flow path, and stores the impeller, and communicates with the impeller chamber from the impeller in the radial direction. A discharge passage through which gas sent to the outside flows, an impeller side communication passage that communicates with the impeller chamber and extends from the impeller chamber in a direction including the radially outer component, and communicates with the impeller side communication passage A circulation flow path extending in a direction including the component on the front side in the axial direction from the impeller side communication path, and a suction side communication path communicating with the circulation flow path and the suction flow path are formed,
The suction-side diameter dimension, which is a dimension in the radial direction from the axis to the communication position with the suction-side communication path in the circulation flow path, is from the axis to the communication position with the impeller-side communication path in the circulation flow path. It is larger than the impeller side diameter dimension that is a radial dimension, and the flow passage area of the circulation flow path at the communication position with the suction side communication path is the flow of the circulation flow path at the communication position with the impeller side communication path. Larger than the road area,
Centrifugal compressor.
The centrifugal compressor according to claim 1,
The housing is formed with a plurality of circulation channels arranged in the circumferential direction with the axis as the center, and a partition for partitioning the circulation channels adjacent in the circumferential direction is formed. ,
Centrifugal compressor.
The centrifugal compressor according to claim 1 or 2,
The suction flow path has a shape that is rotationally symmetric about the axis, and has a reduced diameter portion that gradually decreases in flow path area toward the rear side in the axial direction, which is the other side of the axial direction.
The communication port for the suction flow path in the suction side communication path is formed on a surface that defines the flow path in the reduced diameter portion,
Centrifugal compressor.
The centrifugal compressor according to claim 3,
The surface that defines the flow path in the reduced diameter portion forms a curved surface that is convex toward the axis.
Centrifugal compressor.
The centrifugal compressor according to any one of claims 3 and 4,
The dimension in the radial direction from the axial line to the front edge in the axial direction at the communication port of the suction side communication path is smaller than the suction side diameter dimension and larger than the impeller side diameter dimension,
Centrifugal compressor.
The centrifugal compressor according to any one of claims 1 to 5,
The suction side communication path is folded back from the boundary between the circulation channel and the suction side communication path, and then toward the radially inner side with respect to the axis, toward the axial rear side that is the other side of the axial direction. Extends and communicates with the suction flow path,
Centrifugal compressor.
The centrifugal compressor according to any one of claims 1 to 6,
L is an axial dimension from a communication position with the suction-side communication path in the circulation flow path to a communication position with the impeller-side communication path in the circulation flow path,
do is defined as an equivalent diameter related to the flow area of the circulation flow path at the communication position with the suction side communication path,
When di is an equivalent diameter related to the flow area of the circulation flow path at the communication position with the impeller side communication path,
The divergence angle 2θ defined by the following equation is less than 20 °.
2θ = 2 × tan ((do-di) / 2L)
Centrifugal compressor.
The centrifugal compressor according to any one of claims 1 to 7,
The axial dimension from the communication position with the suction-side communication path in the circulation flow path to the communication position with the impeller-side communication path in the circulation flow path is 0 of the outer diameter of the impeller, which is the maximum outer diameter of the impeller. .25 times or more,
Centrifugal compressor.
The centrifugal compressor according to any one of claims 1 to 8,
A turbine,
The turbine is
A turbine rotating shaft that rotates about the axis;
A turbine impeller attached to the outer periphery of the turbine rotating shaft;
A turbine housing covering the turbine impeller;
Have
The turbine rotating shaft and the rotating shaft of the centrifugal compressor are located on the same axis and are connected to each other to rotate integrally to form a turbocharger rotating shaft.
Turbocharger.