WO2017098911A1 - 遠心圧縮機の吐出部構造 - Google Patents
遠心圧縮機の吐出部構造 Download PDFInfo
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- WO2017098911A1 WO2017098911A1 PCT/JP2016/084491 JP2016084491W WO2017098911A1 WO 2017098911 A1 WO2017098911 A1 WO 2017098911A1 JP 2016084491 W JP2016084491 W JP 2016084491W WO 2017098911 A1 WO2017098911 A1 WO 2017098911A1
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- WIPO (PCT)
- Prior art keywords
- flow path
- discharge
- scroll
- tongue
- flow passage
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/422—Discharge tongues
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/32—Engines with pumps other than of reciprocating-piston type
- F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
- F02B33/40—Engines with pumps other than of reciprocating-piston type with rotary pumps of non-positive-displacement type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/50—Inlet or outlet
- F05D2250/52—Outlet
Definitions
- the present disclosure relates to a discharge unit structure of a centrifugal compressor.
- a spiral scroll is known in a turbocharger compressor housing that starts from a tongue and gradually increases in cross-sectional area clockwise, leading to a discharge pipe. ing.
- the tongue is formed at a branch point between the scroll and the discharge pipe.
- the tongue is defined as the start point and end point of scrolling, the start point is 0 °, the angle is clockwise, and 360 ° is the end point, and the scrolling ends at this position.
- a portion following the end point of the scroll is a discharge pipe.
- the shape of the discharge part is often configured to be straight.
- a loss due to a collision of flows tends to occur on the larger flow rate side than the flow rate showing the peak efficiency. As a result, a decrease in efficiency occurs.
- This disclosure describes a discharge unit structure of a centrifugal compressor that can suppress a decrease in efficiency in the discharge unit.
- the inventor has intensively studied the cause of the loss due to the collision of the flow in the scroll flow path or the discharge flow path and the countermeasures for the cause. As a result, the inventor has found that the above problem can be solved by devising the shape of the discharge flow path and the position of the tongue relative thereto. That is, it has been found that in a conventional straight discharge section, a loss occurs due to, for example, the flow from the diffuser or the like colliding with the tongue.
- One aspect of the present disclosure is a discharge unit structure of a centrifugal compressor provided with a compressed gas flow path including a scroll flow path and a discharge flow path connected to a discharge side of the scroll flow path.
- a tongue provided at a branch portion between the discharge flow path, a first flow path portion having a center of curvature on the origin side of the scroll flow path, and a discharge flow of the first flow path portion;
- a second flow path part having a center of curvature outside the path, wherein the first flow path part includes at least a part of the scroll flow path, and the second flow path part is at least a part of the discharge flow path.
- the tongue portion faces the second flow path portion and is located in the middle of the second flow path portion.
- FIG. 1 is a cross-sectional view of a supercharger including a compressor to which an embodiment of the present disclosure is applied.
- FIG. 2 is a perspective view of the compressor housing in FIG.
- FIG. 3 is a perspective view showing the outer shape of the compressed gas channel.
- FIG. 4 is a view showing the outer shape of the compressed gas flow path, and is a cross-sectional view cut along a plane orthogonal to the central axis passing through the origin.
- FIG. 5A is a view showing the relationship between the winding end portion and the tongue portion
- FIG. 5B is a cross-sectional view of the flow path cut along a plane including the central axis.
- FIG. 6 is a diagram showing a flow channel shape from the winding end portion to the discharge flow channel.
- FIG. 7A is a diagram showing the relationship between the circumferential angle and the distance from the origin to the channel center
- FIG. 7B is a diagram showing the relationship between the circumferential angle and the cross-sectional area of the channel.
- 8A is a view showing the total pressure distribution in the discharge portion structure of the present embodiment shown in FIG. 3
- FIG. 8B is a view showing the total pressure distribution in the discharge portion structure of the comparative example shown in FIG.
- FIG. 9 is a perspective view showing an outer shape of a compressed gas channel according to a comparative example.
- FIG. 10A is a view showing the outer shape of a compressed gas flow path according to a modification
- FIG. 10B is a view showing the outer shape of a compressed gas flow path according to another modification.
- One aspect of the present disclosure is a discharge unit structure of a centrifugal compressor provided with a compressed gas flow path including a scroll flow path and a discharge flow path connected to a discharge side of the scroll flow path.
- a tongue provided at a branch portion between the discharge flow path, a first flow path portion having a center of curvature on the origin side of the scroll flow path, and a discharge flow of the first flow path portion;
- a second flow path part having a center of curvature outside the path, wherein the first flow path part includes at least a part of the scroll flow path, and the second flow path part is at least a part of the discharge flow path.
- the tongue portion faces the second flow path portion and is located in the middle of the second flow path portion.
- the second flow path portion including at least a part of the discharge flow path has a center of curvature outside the scroll flow path. That is, the curving direction is opposite to that of the first flow path portion having the center of curvature on the origin side of the scroll flow path.
- a tongue portion facing the second flow path portion is located in the middle of the second flow path portion. Since the tongue portion is provided in the middle of the second flow path portion that curves outward, the tongue portion is positioned on the outer peripheral side of the second flow path portion that draws the curve. Therefore, compared with the case where the discharge flow path is straight, the tongue portion is positioned far from the flow, and the flow hardly collides with the tongue portion. Loss can be reduced by the positional relationship between the curved discharge channel and the tongue. As a result, a decrease in efficiency in the discharge unit is suppressed.
- the tongue may be located at the center of the second flow path portion or downstream from the center. According to this structure, the position of a tongue part becomes farther and the said effect can be exhibited more notably.
- the angle formed by the wall surface on the scroll flow path side of the tongue and the wall surface on the discharge flow path side of the tongue is 50 ° or more. May be.
- the supercharger 1 is applied to, for example, an internal combustion engine of a ship or a vehicle.
- the supercharger 1 includes a turbine 2 and a compressor (centrifugal compressor) 3.
- the turbine 2 includes a turbine housing 4 and a turbine impeller 6 housed in the turbine housing 4.
- the turbine housing 4 has a scroll portion 4a extending in the circumferential direction at the inner peripheral edge.
- the compressor 3 includes a compressor housing 5 and a compressor impeller 7 housed in the compressor housing 5.
- the compressor housing 5 has a scroll portion 5a extending in the circumferential direction at the inner peripheral edge.
- the turbine impeller 6 is provided at one end of the rotating shaft 14, and the compressor impeller 7 is provided at the other end of the rotating shaft 14.
- the compressor wheel 7 is fixed to the rotating shaft 14 by a nut 16 provided at the other end of the rotating shaft 14.
- a bearing housing 13 is provided between the turbine housing 4 and the compressor housing 5.
- the rotating shaft 14 is rotatably supported by the bearing housing 13 via the journal bearing 15, and the rotating shaft 14, the turbine impeller 6 and the compressor impeller 7 rotate around the rotation axis H as an integral rotating body 12. .
- the turbine housing 4 is provided with an exhaust gas inlet (not shown) and an exhaust gas outlet 10.
- Exhaust gas (fluid) discharged from an internal combustion engine (not shown) flows into the turbine housing 4 through the exhaust gas inlet, and flows into the turbine impeller 6 through the scroll passage 19 in the scroll portion 4a. The impeller 6 is rotated. Thereafter, the exhaust gas flows out of the turbine housing 4 through the exhaust gas outlet 10.
- the compressor housing 5 is provided with a suction port 9 and a discharge port 11 (see FIG. 2).
- the compressor impeller 7 rotates via the rotating shaft 14.
- the rotating compressor wheel 7 sucks external air through the suction port 9, compresses it, and discharges it from the discharge port through the scroll flow path 21 in the scroll portion 5a.
- the compressed air discharged from the discharge port 11 is supplied to the internal combustion engine described above.
- the compressor housing 5 to which the discharge part structure of the present embodiment is applied will be described with reference to FIGS.
- the compressor housing 5 is connected to a spiral scroll portion 5a, a cylindrical suction pipe 5b provided at the center of the scroll portion 5a, and the scroll portion 5a, and the discharge port 11 described above. And a discharge pipe 5c.
- the compressor housing 5 includes a new compressed gas flow path 20 inside, thereby reducing the flow loss particularly at a large flow rate and improving the efficiency.
- the compressor housing 5 is characterized by an internal flow path shape from the scroll portion 5a to the discharge pipe 5c.
- FIG. 3 is a perspective view showing the outer shape of the compressed gas channel 20.
- FIG. 4 is a view showing the outer shape of the compressed gas channel 20, for example, a cross-sectional view taken along a plane orthogonal to the rotation axis H (center axis) passing through the origin C of the scroll channel 21.
- the compressed gas flow path 20 provided in the compressor housing 5 includes a spiral scroll flow path 21 and a discharge flow path 22 connected to the discharge side of the scroll flow path 21. Contains.
- the outer shape of the compressed gas channel 20 is, for example, a position where the outer wall surface of each channel cross section is the largest in the radial direction (referred to as the outermost peripheral portion) and a position where the inner wall surface is the smallest in the radial direction (the outermost portion). It is a curve connecting the inner circumference).
- the heights of the outermost peripheral part and the innermost peripheral part in the direction of the rotation axis H are not necessarily the same.
- the outermost peripheral portion and the innermost peripheral portion are projected in the rotation axis H direction on the plane orthogonal to the rotation axis H passing through the origin C.
- the projected outer peripheral line and inner peripheral line may be considered as the outer shape of the compressed gas flow path 20.
- the air sent by the compressor impeller 7 is collected in the compressed gas flow path 20 via the diffuser 17 (see FIG. 5B) and discharged from the discharge port 11.
- the annular diffuser 17 is a parallel flow path having a certain height in the rotation axis H direction.
- the diffuser 17 is provided between the space in which the compressor impeller 7 is disposed and the compressed gas flow path 20 to communicate these.
- An annular diffuser outlet 21 c appears on the inner peripheral side of the compressed gas flow path 20.
- the origin C of the scroll channel 21 is, for example, a point that serves as a reference for the radial distance from the rotation axis H of the inner wall 23 or the outer wall 24 of each channel cross section in the scroll channel 21.
- the rotation axis H passes through the origin C.
- the rotation axis H can be determined based on, for example, the structure of the compressor housing 5 or the fitting structure between the compressor housing 5 and the bearing housing 13 (see FIG. 1).
- the rotation axis H may be the axis of the inner peripheral surface of the suction pipe 5b (that is, the suction port 9).
- the rotation axis H may be the tip of the outer peripheral side of the wall 5d of the compressor housing 5 that forms the diffuser 17 (the wall facing the scroll channel 21), that is, the axial center of the outer peripheral edge 17a of the diffuser 17. .
- the rotation axis H may be the axis of the fitting portion 18 between the compressor housing 5 and the bearing housing 13.
- the rotation axis H can be the center (center) thereof.
- the rotation axis H may be the center of their area.
- a tongue portion 30 is provided at a branch portion between the scroll flow path 21 and the discharge flow path 22.
- a range from the winding start portion 21 a corresponding to the tongue portion 30 to the winding end portion 21 b is a scroll flow passage 21 in the compressed gas flow passage 20. More specifically, the circumferential angle from the winding start portion 21a to the winding end portion 21b is, for example, about 300 °. The angle in the circumferential direction from the winding start portion 21a to the winding end portion 21b is not limited to this aspect, and may be less than 300 ° or 300 ° or more.
- the range of the scroll flow path 21 can be changed depending on the shape of the discharge pipe 5c, the position of the discharge port 11, the design method, and the like.
- the scroll flow path 21 may be continuous over one round (that is, 360 °).
- the scroll flow path 21 starts at a position corresponding to the tongue 30, and the scroll flow path 21 ends at the position of the representative cross section A (see FIG. 5A).
- the flow path following the scroll flow path 21 is the discharge flow path 22 described above.
- the discharge flow path 22 can have any shape or size as the position or shape of the discharge port 11 is changed depending on the usage pattern of the supercharger 1. The shapes of the scroll flow path 21 and the discharge flow path 22 are determined so that the efficiency increases with respect to the predetermined discharge port 11.
- the compressed gas flow path 20 has a second flow path portion F ⁇ b> 2 that is curved outward in the range of the discharge flow path 22. That is, the compressed gas flow path 20 is provided so as to be continuous with the first flow path portion F1 having the center of curvature on the origin C side (in other words, on the inner side) and the first flow path portion F1. And a second flow path portion F2 having a center of curvature on the outside.
- each flow path portion is, for example, the center of the cross section when the compressed gas flow path 20 is cut along a plane passing through the origin C (refer to the center of gravity or the centroid, the center P in FIG. 5B).
- the curves connecting the centers are not necessarily located on the same plane.
- a curve connecting the centers may be projected in the axial direction passing through the origin C, and the curvature of each flow path portion may be calculated based on the central line L projected on a plane orthogonal to the axial line.
- the curvature is not limited to the case where the curvature is determined by the center of the cross section, and the curvature of each flow path portion is determined based on the portion of the cross section closest to the origin C (see the inner end E of FIG. 5B). Also good. On the contrary, the curvature of each flow path portion may be determined based on the portion farthest from the origin C.
- each channel part can vary depending on the location.
- the first channel portion F1 and the second channel portion F2 are determined depending on whether the center of curvature is inside or outside the scroll channel 21.
- the center line L described above includes a first center line L1 corresponding to the first flow path portion F1 and a second center line L2 corresponding to the second flow path portion F2.
- the center of curvature of the first center line L ⁇ b> 1 is located inside the scroll channel 21, and the center of curvature of the second center line L ⁇ b> 2 is located outside the scroll channel 21. That is, the curvature changes between the first flow path part F1 and the second flow path part F2 (there is an inflection point).
- the first flow path portion F1 includes an inner wall part 23 that generally constitutes the inner peripheral side of the scroll flow path 21 and an outer wall part 24 that generally constitutes the outer peripheral side of the scroll flow path 21.
- the second flow path portion F ⁇ b> 2 includes an outer wall portion 25 that generally configures the outer peripheral side of the discharge flow channel 22 and an inner wall portion 26 that generally configures the inner peripheral side of the discharge flow channel 22.
- the outer wall portion 24 is continuous with the inner wall portion 26.
- a tongue portion 30 is provided between the outer wall portion 24 and the outer wall portion 25.
- the scroll channel 21 and the first channel portion F1 may be in the same range or different ranges. Even if the scroll flow path 21 and the first flow path portion F1 are in different ranges, they partially overlap.
- the discharge flow path 22 and the second flow path portion F2 may be in the same range or different ranges. Even if the discharge flow path 22 and the second flow path portion F2 are in different ranges, they partially overlap each other.
- the first flow path portion F1 includes at least a part of the scroll flow path 21.
- the second flow path portion F2 includes at least a part of the discharge flow path 22.
- one end point (upstream end point) of the scroll flow path 21 and the first flow path portion F1 coincides, and the other end point (downstream end point) coincides. Absent. Regarding the discharge flow path 22 and the second flow path portion F2, neither one end point (upstream end point) nor the other end point (downstream end point) is coincident.
- the tongue 30 is located in the middle of the second flow path portion F2 curved outward.
- the tongue portion 30 faces the second flow path portion F2 (that is, faces the second flow path portion F2).
- the second flow path portion F ⁇ b> 2 includes the position of the tongue portion 30.
- the discharge flow path 22 also includes the position of the tongue 30.
- the tongue portion 30 is located at the center of the second flow path portion F2.
- the outer wall portion 25 constitutes the outer peripheral portion of the curve.
- the inner wall part 23 of the first flow path part F1 and the outer wall part 25 of the second flow path part F2 are not continuous in the region where the tongue part 30 is facing, and the space between them is a space, A virtual surface 27 that smoothly connects the inner wall portion 23 and the outer wall portion 25 can be assumed.
- the imaginary surface 27 and the outer wall portion 25 form a convex wall portion of the second flow path portion F2. Since the upstream end of the outer wall 25 is the tip 30a of the tongue 30, the virtual surface 27 passes through the tip 30a.
- the tongue 30 is located at the center of the convex wall.
- the tongue part 30 may be located in the upstream of a convex-shaped wall part, and may be located in a downstream.
- At least the tongue portion 30 is on the outer peripheral side of the imaginary line 28 connecting the outer peripheral wall portion Wa at the start point of the second flow path portion F2 and the outer peripheral wall portion Wb at the end point of the second flow path portion F2 (FIG. 4).
- the discharge flow path 22 exists at a position along a curved shape, but exists at a more retracted position when the conventional straight discharge portion shape is considered as a reference.
- the tongue part 30 may be located in the downstream rather than the center part of the 2nd flow-path part F2.
- the characteristics of the tongue portion 30 will be described from another point of view.
- the outer wall portion 24 that is the wall surface of the tongue portion 30 on the scroll channel 21 side
- the angle formed by the outer wall 25 which is the wall surface on the discharge flow path 22 side (they intersect at the tip 30a) is 50 ° or more.
- the angle of the tongue 30 may be 30 ° or more and less than 50 °, or 50 ° or more.
- the compressed gas channel 20 can also be described as follows.
- a plane perpendicular to a straight line connecting the center of the radius of curvature of the scroll channel 21 and the tip 30a of the tongue 30 is assumed.
- this plane may be considered as a perpendicular bisector between the two points.
- the center of the radius of curvature of the discharge channel 22 at the position of the tongue 30 is located on the opposite side of the center of the radius of curvature of the scroll channel 21 across the plane.
- Such a feature means the same technical matter as the second flow path portion F2 described above.
- the representative cross section A is a cross section at a position of 360 °.
- the representative cross section A is a cross section at a position shifted by several tens of degrees (for example, 30 to 60 °) upstream from the tongue portion 30 with respect to the discharge flow path 22.
- the representative cross section A may be a cross section at a position shifted by 50 ° or 60 ° upstream from the tongue 30 with respect to the discharge flow path 22.
- the representative cross section A As shown in FIG. 7A, the distance R (see FIG. 5B) from the origin C to the center P of the compressed gas passage 20 increases with a substantially constant inclination.
- the final region may be the representative cross section A.
- the final region where the cross-sectional area of the compressed gas channel 20 increases with a substantially constant inclination may be the representative cross-section A.
- the representative cross section A may be a cross section at any position in the range of 360 to 390 ° in the circumferential angle.
- the representative cross section A may be a cross section at a position of 360 ° in the circumferential angle.
- the direction connecting the origin C and the representative cross section A is defined as the Y-axis direction
- the direction orthogonal to the plane including the origin C and the representative cross section A is defined as the X-axis direction.
- a straight flow path shape from the winding end part 21b toward the discharge port 11 is often used. That is, the linear shape as shown by the broken line in FIG. 6 is often used.
- the channel 20 of the present embodiment has a downwardly convex shape. This feature means the same technical matter as the second flow path portion F2 described above.
- FIG. 8A is a diagram showing the total pressure distribution in the discharge portion structure of the present embodiment
- FIG. 8B is a diagram showing the total pressure distribution in the discharge portion structure of the comparative example shown in FIG. .
- the total pressure in the flow path is shown in shades. That is, the area displayed lighter has a higher total pressure, and the area displayed darker has a lower total pressure.
- the conventional compressed gas flow path 120 shown in FIG. 9 includes a scroll flow path 121 and a discharge flow path 122, and the discharge flow path 122 has a straight shape.
- the shape of the flow path from the winding start part 121a to the winding end part 121b, the thickness of the diffuser outlet 121c, etc. are not significantly different from the compressed gas flow path 20 of this embodiment, but the position and shape of the tongue 130 are different. Yes. That is, the tongue portion 130 is at a higher position in the Y direction with respect to the winding end portion 121b.
- the second flow path portion F2 is not formed in the compressed gas flow path 120.
- the second flow path portion F ⁇ b> 2 including at least a part of the discharge flow path 22 has the center of curvature outside the scroll flow path 21. That is, the curving direction is opposite to that of the first flow path portion F1 having the center of curvature on the origin C side of the scroll flow path 21.
- the tongue 30 facing the second flow path part F2 is located in the middle of the second flow path part F2.
- the tongue part 30 is located in the outer peripheral side of the 2nd flow-path part F2 which draws a curve by providing the tongue part 30 in the middle of the 2nd flow-path part F2 curved toward the outer side.
- the tongue portion 30 is positioned far from the flow, and the flow is less likely to collide with the tongue portion 30. Loss is reduced by the positional relationship between the curved discharge channel 22 and the tongue 30. As a result, a decrease in efficiency at the discharge port 11 is suppressed. This effect is particularly effective on the larger flow rate side than the flow rate showing the peak efficiency. In the conventional straight discharge portion shape, the efficiency tends to decrease when the flow rate is large, but in this embodiment, this point is improved.
- the position of the tongue 30 becomes farther than the representative cross section A, and the above-described effect can be exhibited more remarkably.
- the diffuser flow By smoothly connecting the path (scroll flow path) and the discharge flow path, for example, the disturbance of the flow flowing in from the diffuser flow path can be reduced, and the above-described effect can be exhibited more remarkably.
- the present invention is not limited to the above embodiments.
- transformation aspect shown by FIG. 10A even when the position of the discharge port 11 is set low in the Y direction with respect to the representative cross section A, the scroll flow path 41 extending from the winding start portion 41a to the winding end portion 41b A compressed gas flow path 40 having a discharge flow path 42 connected to the scroll flow path 41 may be employed.
- a second channel portion F2 that is gently curved is formed on the downstream side of the representative cross section A, and the tongue portion 30 that faces the second channel portion F2 is located in the middle of the second channel portion F2. ing.
- the scroll flow path from the winding start portion 51a to the winding end portion 51b may be employ
- a second flow path portion F2 is formed on the downstream side of the representative cross section A, and a tongue portion 30 facing the second flow path portion F2 is located in the middle of the second flow path portion F2.
- Such compressed gas passages 40 and 50 also provide the same operations and effects as shown in FIG.
- the first flow path part F1 and the second flow path part F2 are not limited to being continuous.
- a straight channel portion may be provided over a predetermined length between the first channel portion F1 and the second channel portion F2. In this case, there is no inflection point, and the first flow path portion F1 and the second flow path portion F2 are communicated with each other through a straight flow path portion.
- the shape of the discharge port is not limited to the case of extending in the substantially circumferential direction of the scroll flow path.
- a shape curved in the paper surface direction may be provided.
- the scroll flow path from the winding start portion to the winding end portion similar to the above-described embodiment, A scroll flow path including a discharge flow path connected to the scroll flow path may be employed.
- the present invention is not limited to the supercharger 1 and can be applied to any centrifugal compressor.
- the spiral of the scroll flow path is not limited to being formed from the winding start portion to the winding end portion in the clockwise direction.
- the scroll channel may be swirled counterclockwise from the winding start portion to the winding end portion.
Abstract
Description
3 コンプレッサ(遠心圧縮機)
20 圧縮気体流路
21 スクロール流路
22 吐出流路
23 内側壁部
24 外側壁部
25 外側壁部
26 内側壁部
30 舌部
40 圧縮気体流路
41 スクロール流路
42 吐出流路
50 圧縮気体流路
51 スクロール流路
52 吐出流路
C 原点
F1 第1流路部分
F2 第2流路部分
L 中心線
Claims (4)
- スクロール流路と前記スクロール流路の吐出側に接続された吐出流路とを含む圧縮気体流路が設けられた遠心圧縮機の吐出部構造であって、
前記スクロール流路と前記吐出流路との間の分岐部に設けられた舌部と、
前記スクロール流路の原点側に曲率の中心を有する第1流路部分と、
前記第1流路部分の吐出側に連通し、前記スクロール流路の外側に曲率の中心を有する第2流路部分と、を備え、
前記第1流路部分は、少なくとも前記スクロール流路の一部を含み、
前記第2流路部分は、少なくとも前記吐出流路の一部を含み、
前記舌部は、前記第2流路部分に面すると共に、前記第2流路部分の途中に位置している、遠心圧縮機の吐出部構造。 - 前記舌部は、前記第2流路部分の中央部または前記中央部よりも下流側に位置する、請求項1に記載の遠心圧縮機の吐出部構造。
- 前記スクロール流路の前記原点を通る中心軸線に直交する断面において、前記舌部の前記スクロール流路側の壁面と、前記舌部の前記吐出流路側の壁面とのなす角は、50°以上である、請求項1に記載の遠心圧縮機の吐出部構造。
- 前記スクロール流路の前記原点を通る中心軸線に直交する断面において、前記舌部の前記スクロール流路側の壁面と、前記舌部の前記吐出流路側の壁面とのなす角は、50°以上である、請求項2に記載の遠心圧縮機の吐出部構造。
Priority Applications (4)
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JP2017555005A JP6551541B2 (ja) | 2015-12-10 | 2016-11-21 | 遠心圧縮機の吐出部構造 |
US16/060,070 US10788045B2 (en) | 2015-12-10 | 2016-11-21 | Discharge section structure for centrifugal compressor |
CN201680071745.4A CN108368856B (zh) | 2015-12-10 | 2016-11-21 | 离心压缩机的排出部构造 |
DE112016005630.3T DE112016005630T5 (de) | 2015-12-10 | 2016-11-21 | Ausstosspartie für einen radialverdichter |
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JP (1) | JP6551541B2 (ja) |
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JP2020020340A (ja) * | 2018-07-23 | 2020-02-06 | ミネベアミツミ株式会社 | 遠心送風機 |
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JP6638159B2 (ja) * | 2016-03-30 | 2020-01-29 | 三菱重工エンジン&ターボチャージャ株式会社 | 圧縮機スクロール、および、遠心圧縮機 |
CN110573748B (zh) * | 2017-11-06 | 2021-06-01 | 三菱重工发动机和增压器株式会社 | 离心压缩机以及具备该离心压缩机的涡轮增压器 |
CN113785111A (zh) * | 2019-06-05 | 2021-12-10 | 三菱重工发动机和增压器株式会社 | 离心压缩机的涡旋构造和离心压缩机 |
JP7452708B2 (ja) * | 2020-12-09 | 2024-03-19 | 株式会社Ihi | 遠心圧縮機および過給機 |
US11391296B1 (en) * | 2021-07-07 | 2022-07-19 | Pratt & Whitney Canada Corp. | Diffuser pipe with curved cross-sectional shapes |
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- 2016-11-21 US US16/060,070 patent/US10788045B2/en active Active
- 2016-11-21 WO PCT/JP2016/084491 patent/WO2017098911A1/ja active Application Filing
- 2016-11-21 CN CN201680071745.4A patent/CN108368856B/zh active Active
- 2016-11-21 JP JP2017555005A patent/JP6551541B2/ja active Active
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US6146092A (en) * | 1998-07-13 | 2000-11-14 | Ford Motor Company | Centrifugal blower assembly with a diffuser |
JP2005207337A (ja) * | 2004-01-23 | 2005-08-04 | Toyota Central Res & Dev Lab Inc | ターボ過給機およびそのスラスト気体軸受 |
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JP2020020340A (ja) * | 2018-07-23 | 2020-02-06 | ミネベアミツミ株式会社 | 遠心送風機 |
JP7254648B2 (ja) | 2018-07-23 | 2023-04-10 | ミネベアミツミ株式会社 | 遠心送風機 |
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US20180355886A1 (en) | 2018-12-13 |
DE112016005630T5 (de) | 2018-08-30 |
CN108368856A (zh) | 2018-08-03 |
JPWO2017098911A1 (ja) | 2018-06-14 |
CN108368856B (zh) | 2020-01-31 |
JP6551541B2 (ja) | 2019-07-31 |
US10788045B2 (en) | 2020-09-29 |
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