WO2012124388A1 - 遠心圧縮機のスクロール構造 - Google Patents

遠心圧縮機のスクロール構造 Download PDF

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Publication number
WO2012124388A1
WO2012124388A1 PCT/JP2012/051891 JP2012051891W WO2012124388A1 WO 2012124388 A1 WO2012124388 A1 WO 2012124388A1 JP 2012051891 W JP2012051891 W JP 2012051891W WO 2012124388 A1 WO2012124388 A1 WO 2012124388A1
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WO
WIPO (PCT)
Prior art keywords
scroll
flow
chamber
shape
diffuser
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2012/051891
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English (en)
French (fr)
Japanese (ja)
Inventor
健一郎 岩切
勲 冨田
白石　隆
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to US13/981,042 priority Critical patent/US9562541B2/en
Priority to EP12757491.1A priority patent/EP2687730B1/en
Priority to CN201280012280.7A priority patent/CN103415707B/zh
Publication of WO2012124388A1 publication Critical patent/WO2012124388A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • 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
    • 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
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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 invention relates to a scroll structure (swirl chamber structure) of a centrifugal compressor used for vehicles, marine turbochargers and the like.
  • Centrifugal compressors used in compressors for vehicular and marine turbochargers give kinetic energy to the fluid through rotation of the impeller and discharge the fluid radially outward to obtain a pressure increase due to centrifugal force Is.
  • This centrifugal compressor is required to have a high pressure ratio and high efficiency in a wide operating range, and various devices have been devised for the scroll structure.
  • Patent Document 1 Japanese Patent No. 4492045 discloses a centrifugal compressor including a casing provided with a scroll channel formed in a spiral shape, and the axial direction of the scroll channel is A technique is shown in which the channel width gradually increases from the radially inner side to the outer side and is maximized radially outside the midpoint of the radial channel width. Yes.
  • Patent Document 2 Japanese Patent Publication No. 2010-529358 relates to a centrifugal compressor for a turbocharger, which includes a spiral housing and a diffuser, and the diffuser has a transition region or a position of a tongue portion of the spiral housing. It is shown that the diameter is expanded so that the negative pressure region in the region to be reduced is reduced.
  • FIGS. 12 and 13 Improvements in the cross-sectional shape of the scroll channel as shown in Patent Document 1 and improvements in the diffuser part as shown in Patent Document 2 have been made, but further improvements are necessary to improve the efficiency of the compressor. is there.
  • a diffuser 02 is formed on the outer peripheral side of the compressor impeller 01, and a scroll channel 03 is provided on the outer peripheral side.
  • the cross-sectional shape of the scroll channel 03 is generally The flow path connecting portion 04 at the beginning and end of winding of the scroll flow path 03 is connected at the tongue portion 05 portion. Further, after the end of winding, the liquid is discharged through the outlet channel 06.
  • FIG. 13 shows the scroll cross-sectional shapes at ⁇ 1, ⁇ 2,... Superimposed at predetermined angles ⁇ from the tongue portion 05 in the clockwise direction.
  • the tongue portion 05 has a shape in which the flow path connection portion 04 is connected to the circular portion 09 and the outlet portion 011 of the diffuser 02 so as to contact the circular portion 09 as indicated by the oblique lines in FIG.
  • FIG. 9B is a cross-sectional view taken along the line CC of FIG. 12, and the exit channel 06 having a circular cross section and the scroll channel 03 having a circular cross section intersect each other at the intersection near the tongue 05.
  • a ridge line P is generated.
  • the diffuser outlet flow A has an upward velocity component in the vicinity of the tongue portion 05 and interferes with the swirl flow B in the scroll flow path.
  • the interference causes a flow separation in the vicinity of the tongue portion 05, which causes a flow loss.
  • An object of the present invention is to provide a scroll structure for a centrifugal compressor that improves the loss reduction effect in a wide range of operation during operation.
  • the present invention provides a centrifugal compressor including a diffuser provided on the outer peripheral side of an impeller and a scroll passage formed in a spiral shape connected to the outer periphery of the diffuser.
  • the axial cross-sectional shape of the scroll flow path is a substantially circular shape, and a position where the diffuser outlet connected to the substantially circular shape is closer to the circular center than the tangential position to the circular shape and does not reach the circular center
  • the substantially circular shape is constituted by a scroll chamber that protrudes greatly in the axial direction with respect to the diffuser outlet position, and a shift chamber in which the remaining portion of the substantially circular shape is formed in the opposite direction to the scroll chamber.
  • the shift chamber is formed at least in the scroll flow path at the end of winding in the circumferential direction of the spiral.
  • the axial cross-sectional shape of the scroll channel is substantially circular, and the diffuser outlet connected to the substantially circular shape is circular.
  • the scroll chamber is formed at a position shifted from the tangential position to the center side of the circle, and the substantially circular shape largely protrudes in the axial direction with respect to the diffuser outlet position, and the remaining of the substantially circular shape is opposite to the scroll chamber.
  • the diffuser outlet flow A is directed downward in the compressor rotation axis direction along the scroll channel wall surface (downward in FIG. 9 (a)). With a velocity component of For this reason, as shown in FIG.
  • the direction of the diffuser outlet flow A can be adapted to the flow of the swirl flow B in the scroll flow path, and interference between the diffuser outlet flow A and the swirl flow B in the scroll flow path is prevented.
  • the occurrence of peeling near the tongue caused by the interference is suppressed.
  • the circular cross-sectional shape and the circular cross-sectional shape are shifted to intersect with each other, so that the intersecting portion is raised in a mountain shape and a portion of the ridge line P is generated.
  • the circular shape and the circular shape intersect with each other by shifting the connecting position of the diffuser outlet from the tangential position to the circular shape to the circular center side.
  • it becomes difficult to generate a ridge line at the intersection and the generation of the ridge line P in the vicinity of the tongue can be suppressed, and the distance between the ridge lines can be shortened.
  • interference between the diffuser outlet flow A generated in the ridge line portion and the swirl flow B in the scroll flow path is suppressed, occurrence of separation caused by the interference is suppressed, and flow loss can be reduced.
  • the direction of the diffuser outlet flow A is adapted to the flow of the swirl flow B in the scroll flow path, and the generation of ridge lines in the vicinity of the tongue is suppressed, thereby shortening the ridge line distance.
  • the interference between the diffuser outlet flow A and the in-scroll swirl flow B is prevented, the occurrence of separation near the tongue caused by the interference is suppressed, and the flow loss is suppressed.
  • the shift chamber starts shifting from a position approximately 180 degrees in the circumferential direction from the end portion of winding and increases so as to become a maximum at a position of approximately 360 degrees. It is preferable to increase the shift amount linearly or parabolically with increasing.
  • the shift amount is gradually increased over a range of about 180 degrees in the circumferential direction, thereby smoothly changing the circumferential shape of the shift chamber and suppressing the loss of the scroll flow path with respect to the circumferential flow.
  • the shift chamber is also formed in a scroll flow path at a winding start portion.
  • the interference between the scroll flow swirl flow B flowing in the arrow Y direction (FIG. 11B) with the scroll flow swirl flow B and the diffuser outlet flow A is As described above, the direction of the diffuser outlet flow A is prevented from being adapted to the flow of the swirl flow B in the scroll flow path, and by reducing the ridge line distance by suppressing the generation of ridge lines in the vicinity of the tongue, Occurrence of separation near the tongue caused by interference is suppressed, and flow loss is suppressed.
  • the shape of the connection opening to the winding end portion of the scroll flow path at the winding start portion is formed in a flat shape having the same height as the width of the diffuser outlet, and one of the flat shapes is formed.
  • the shift chamber may be provided in the direction, and the height of the shift chamber may vary along the circumferential direction.
  • forming the shift chamber at the winding start portion is effective in reducing the flow loss that occurs in the flow from the vicinity of the tongue portion toward the outlet flow channel at the time of high flow operation, in addition to this effect,
  • the shape of the connection opening to the winding end portion of the scroll flow path at the winding start portion is formed in a flat shape having the same height as the width of the diffuser outlet, thereby allowing circulation compared to the connecting portion having a circular cross section.
  • the area can be reduced, and the inflow of the recirculation flow (arrow Z in FIG. 11A) from the outlet channel (the end of the scroll channel) to the vicinity of the tongue can be suppressed.
  • the opening of the winding start part is formed in a flat shape having the same height as the width of the diffuser outlet, the outlet channel (the end of winding of the scroll channel) Of the scroll flow in the scroll flow path B is prevented from flowing in as the scroll flow inflow E in the scroll flow path, so that, as shown in FIG. This can reduce the flow loss due to peeling.
  • the shift chamber is formed in the scroll channel over the entire circumferential direction. Since the shift chamber is formed over the entire circumference in this way, the shift chamber is made part of the circumferential direction while obtaining the effects obtained by forming the shift chamber at the winding start portion and the winding end portion. Manufacturing is facilitated rather than forming, and moreover, loss of the scroll flow path in the circumferential direction can be suppressed as compared to forming the shift chamber in a part in the circumferential direction.
  • the axial cross-sectional shape of the scroll flow path is formed in a substantially circular shape, and the diffuser outlet connected to the substantially circular shape is formed at a position shifted from the tangential position to the circular shape toward the circular center side,
  • the substantially circular shape is constituted by a scroll chamber that protrudes greatly in the axial direction with respect to the diffuser outlet position, and a shift chamber in which the remaining portion of the substantially circular shape is formed in a direction opposite to the scroll chamber.
  • the outlet flow A has an axially downward velocity component along the scroll channel wall surface. For this reason, as shown in FIG.
  • the direction of the diffuser outlet flow A can be adapted to the flow of the swirl flow B in the scroll flow path, and interference between the diffuser outlet flow A and the swirl flow B in the scroll flow path is prevented. Further, the occurrence of separation near the tongue caused by the interference is suppressed, and the loss reduction effect can be improved.
  • the circular cross-sectional shape and the circular cross-sectional shape are shifted to intersect with each other, so that the intersecting portion is raised in a mountain shape and a portion of the ridge line P is generated.
  • the circular shape and the circular shape intersect with each other by shifting the connecting position of the diffuser outlet from the tangential position to the circular shape to the circular center side.
  • it becomes difficult to generate a ridge line at the intersection and the generation of the ridge line P in the vicinity of the tongue can be suppressed, and the distance between the ridge lines can be shortened.
  • interference between the diffuser outlet flow A generated in the ridge line portion and the swirl flow B in the scroll flow path is suppressed, occurrence of separation caused by the interference is suppressed, and flow loss can be reduced.
  • FIG. 1 is explanatory drawing which shows 1st Embodiment of scroll cross-sectional shape.
  • B is the example which provided the inclination-angle (alpha) in the compressor housing.
  • C is an example in which an inclination angle ⁇ is provided on the bearing housing side. It is explanatory drawing which shows 2nd Embodiment of scroll cross-sectional shape. It is explanatory drawing which shows 3rd Embodiment of scroll cross-sectional shape. It is explanatory drawing which shows 4th Embodiment of scroll cross-sectional shape.
  • FIG. 2B shows the prior art and shows a sectional view taken along the line CC of FIG.
  • FIG. 3 is a cross-sectional view taken along the line DD of FIG. 2, in which (a) shows the first to third embodiments, and (b) shows the fourth embodiment.
  • It is explanatory drawing of the flow field in the vicinity of a tongue part (a) shows the flow near the tongue part at the time of a low flow rate, (b) shows the flow at the time of a high flow rate. It is explanatory drawing of a prior art. It is explanatory drawing of a prior art.
  • FIG. 1 shows a schematic diagram of an axial cross section of a centrifugal compressor 1 of the present invention.
  • the present embodiment shows a centrifugal compressor 1 applied to a turbocharger, and a plurality of compressor blades 7 are erected on the surface of a hub 5 fixed to a rotary shaft 3 driven by a turbine (not shown).
  • a compressor housing 9 covers the outside of the compressor blade 7.
  • a diffuser 11 is formed on the outer peripheral side of the compressor blade 7, and a scroll flow path 13 is formed and connected around the diffuser 11.
  • the compressor housing 9 includes a scroll flow path 13 and a linear outlet flow path 15 communicating with the scroll flow path 13, and the scroll flow path 13 is clockwise from the winding start portion 17 as shown in FIG.
  • the cross-sectional shape of the scroll channel 13 will be described.
  • the cross-sectional shape of the flow path connecting portion 23 where the winding start portion 17 and the winding end portion 19 intersect in the scroll flow path 13 is connected to a substantially circular shape at the winding start portion 17.
  • the cross-sectional shape of the scroll flow path 13 is the same as the outlet portion 11a of the diffuser 11.
  • the tangential position of the circular shape shifts to a position that is on the circular center side and does not reach the circular center, and the substantially circular shape is in the axial direction (upward in FIG. 3) with respect to the position of the outlet portion 11a of the diffuser 11.
  • the scroll chamber 30 is formed so as to extend greatly, and the shift chamber 32 is formed with a remaining portion having a substantially circular shape in a direction opposite to the scroll chamber 30 (downward in FIG. 3).
  • the scroll channel cross-sectional shape of the scroll chamber 30 and the shift chamber 32 is a substantially circular shape as a whole, but also includes an oval shape or an elliptical shape that is close to a circle.
  • the cross-sectional shape of the scroll flow path 13 at the winding end portion 19 is the shift amount ⁇ from the bottom surface 11b of the outlet portion 11a of the diffuser 11, as illustrated by the shape at the positions of ⁇ n and ⁇ n ⁇ 1 in FIG. It is shifted downward.
  • the lower surface of the shift chamber 32 may be formed with an inclined surface with an inclination angle ⁇ from the end of the bottom surface 11 b of the diffuser 11 instead of the arc surface.
  • the arc surface or the inclined surface provided on the lower surface of the shift chamber 32 may be provided on the bearing housing 50 as shown in FIG. 3C instead of being provided on the compressor housing 9 as shown in FIG. .
  • the diffuser outlet flow does not flow along the inclined surface and may cause separation.
  • the preferable range of the inclination angle ⁇ is about 3 to 25 degrees.
  • a more preferable range is 3 to 15 degrees, and an optimal range is 3 to 8 degrees.
  • the optimum range of the shift amount ⁇ is also the case where the inclination angle ⁇ is included in the above range.
  • the inclined surface does not need to be a straight line, and in this case, the angle formed by connecting the lower surface of the diffuser outlet to the lower surface of the shift chamber may be considered as the inclined angle ⁇ .
  • the diffuser outlet flow is diverted along the wall surface into the axially downward velocity component as shown in FIG. 10 (a). .
  • the directions of the diffuser outlet flow A and the swirl flow B in the scroll flow path coincide with each other, the collision between the swirl flow B in the scroll flow path and the diffuser outlet flow A is avoided, and loss occurs.
  • the occurrence of peeling near the tongue is suppressed.
  • the diffuser outlet is brought to the circular center position.
  • the diffuser outlet flow A is in a state of being divided equally in the vertical direction in the scroll flow path 13, so that the swirl direction of the swirl flow B in the scroll flow path is not fixed, and these flows The flow loss is caused by the interference.
  • the exit part 11a of the diffuser 11 is shifted to the position which does not reach this circular center side from the tangent position to circular shape on the circular center side.
  • the shift chamber 32 is formed in the scroll flow path 13 of the winding end portion 19 in the circumferential direction of the spiral, the tongue that is a connection portion between the winding end portion 19 and the winding start portion 17 is used.
  • the portion 25 In the vicinity of the portion 25, interference between the diffuser outlet flow A and the swirl flow B in the scroll flow path is prevented, and the occurrence of separation in the vicinity of the tongue caused by the interference is suppressed, thereby suppressing the generation of flow loss. it can.
  • the axial cross-sectional shape of the scroll passage 13 is substantially circular, and the outlet portion 11a of the diffuser 11 connected to the substantially circular shape is provided.
  • the scroll chamber 30 is formed at a position shifted from the tangential position to the circular shape toward the center of the circle, and the substantially circular shape protrudes greatly in the axial direction with respect to the position of the outlet portion 11a of the diffuser 11, and the scroll chamber 30 Is formed by the shift chamber 32 in which the remaining part of the substantially circular shape is formed in the opposite direction, so that the diffuser outlet flow A is directed downward in the axial direction along the scroll channel wall surface as shown in FIG.
  • the direction of the diffuser outlet flow A can be adapted to the flow of the swirl flow B in the scroll flow path, and interference between the diffuser outlet flow A and the swirl flow B in the scroll flow path is prevented.
  • the occurrence of peeling near the tongue caused by the interference is suppressed.
  • the circular cross-sectional shape and the circular cross-sectional shape are shifted to intersect with each other so that the intersecting portion is raised in a mountain shape, and a portion of the ridge line P is generated.
  • FIG. 9 (a) by shifting the connection position of the outlet portion 11a of the diffuser to a position that is closer to the circular center side than the tangential position to the circular shape and does not reach the circular center, the circular shape and the circular shape are changed. Even if the shape deviates and intersects, a ridge line is hardly generated at the intersection, and the generation of the ridge line P in the vicinity of the tongue can be suppressed, and the distance between the ridge lines can be shortened. As a result, interference between the diffuser outlet flow A generated in the ridge line portion and the swirl flow B in the scroll flow path is suppressed, occurrence of separation caused by the interference is suppressed, and flow loss can be reduced.
  • the direction of the diffuser outlet flow A is adapted to the flow of the swirl flow B in the scroll flow path, and the generation of the ridge line P in the vicinity of the tongue portion 25 is suppressed, and the ridge line distance is reduced.
  • interference between the diffuser outlet flow A and the scroll flow B swirl flow B is prevented, and the occurrence of separation in the vicinity of the tongue caused by the interference is suppressed. Loss is suppressed.
  • the shift chamber 32 starts shifting from a position approximately 180 degrees in the circumferential direction from the winding end portion 19 and increases so as to become a maximum at a position of approximately 360 degrees.
  • the shift amount ⁇ is gradually increased over a range of 180 degrees substantially in the circumferential direction, so that the circumferential shape of the shift chamber 32 is changed smoothly and the loss of the scroll flow passage 13 with respect to the circumferential flow is reduced. Can be suppressed.
  • a shift chamber 34 is further formed in the scroll flow path 13 of the winding start portion 17.
  • a shift chamber 34 similar to the shift chamber 32 described in the first embodiment is formed in the winding start portion 17 where the winding angle ⁇ is in the range of ⁇ 1 , ⁇ 2 , and ⁇ 3 .
  • the lower surface of the shift chamber 34 may be formed with an inclined surface with an inclination angle ⁇ from the end of the bottom surface 11 b of the diffuser 11 instead of the arc surface.
  • the pressure increases from the vicinity of the tongue portion 25 of the scroll flow path 13 toward the outlet flow path 15, so that the outlet flow path 15 (the winding end portion 19) is near the tongue portion 25.
  • From the high pressure side toward the low pressure side (winding start portion 17) (arrow Z in FIG. 11A) is generated. It flows in the direction of arrow Z while swirling with the swirl flow B in the scroll channel.
  • the pressure decreases from the vicinity of the tongue portion 25 of the scroll flow path 13 toward the outlet flow path 15.
  • a flow toward the direction (arrow Z in FIG. 11A) is generated. It flows in the arrow Y direction while swirling with the swirl flow B in the scroll flow path.
  • the scroll flowing in the arrow Y direction (FIG. 11 (b)) with the swirl flow B in the scroll flow path during high flow rate operation.
  • the interference between the swirl flow B in the flow path and the diffuser outlet flow A is adapted to adapt the direction of the diffuser outlet flow A to the flow of the swirl flow B in the scroll flow path, and the vicinity of the tongue, as in the first embodiment. Is prevented by shortening the ridge line distance by suppressing the generation of the ridge line, and the occurrence of separation in the vicinity of the tongue caused by the interference is suppressed, so that the flow loss can be reduced.
  • the shift chamber 32 is formed at the winding end portion 19, but in the configuration in which the shift chamber 32 is provided only at the winding end portion 19, at the time of high flow rate operation. Interference between the swirl flow B in the scroll passage and the diffuser outlet flow A in the scroll passage 13 (winding end portion 19) from the winding start portion 17 toward the outlet passage 15 (winding end portion 19) (in the arrow Y direction). It was difficult to prevent.
  • the shift chamber 34 is formed in the scroll passage 13 of the winding start portion 17 to reduce the loss in the scroll passage 13 caused by the flow from the vicinity of the tongue portion 25 toward the outlet passage 15. In addition, it is possible to reduce the flow loss caused by the flow from the vicinity of the tongue portion 25 toward the outlet channel 15 during the high flow rate operation.
  • the third embodiment is characterized in that, in addition to the first and second embodiments, the shift chamber 36 is formed in the scroll channel 13 over the entire circumferential direction.
  • the shift chamber 36 is formed in the entire circumferential range where the winding angle ⁇ is ⁇ 1 to ⁇ n .
  • the shift amount ⁇ of the shift chamber 36 is kept constant as indicated by the one-dot chain line L3 in FIG. 8, but the shift amount ⁇ of the shift chamber 36 does not necessarily have to be constant over the entire circumference in the circumferential direction.
  • the shift end ⁇ may be set differently at the winding end portion 19, the winding start portion 17, and other portions, and may be set optimally.
  • the lower surface of the shift chamber 36 may be formed with an inclined surface having an inclination angle ⁇ from the end of the bottom surface of the diffuser 11 at the outlet of the diffuser 11 instead of the arc surface. This is the same as in the first and second embodiments.
  • the shift chamber 36 is formed over the entire circumference, the shift chamber is further obtained while obtaining the effect of the shift chamber in the winding start portion 17 and the winding end portion 19 according to the first embodiment and the second embodiment. Manufacturing is facilitated compared to the case where the shift chamber is formed in a part in the circumferential direction, and the loss of the scroll passage 13 with respect to the flow in the circumferential direction can be suppressed as compared with the case where the shift chamber is formed in a part in the circumferential direction. Further, as shown in FIG. 3C, when the inclined surface is formed by the bearing housing 50, the bearing housing 50 can be uniformly cut in the circumferential direction, and there is an advantage that the manufacturing becomes particularly easy.
  • the core installation error at the time of casting manufacture can be absorbed. That is, when the scroll is manufactured by casting, the core is installed in the portion corresponding to the scroll flow path. However, since the core is only placed in the mold, its posture is very unstable. For this reason, in the casting scroll, a sudden expansion of the flow path or a step may occur due to a mismatch with the lower surface of the diffuser.
  • the scroll lower surface is positioned below the lower surface of the diffuser by a shift amount ⁇ over the entire scroll cross section, so even if the core shifts during casting, As long as the shift amount is equal to or less than the shift amount ⁇ of the scroll cross section, stable production can be achieved against the shift of the core during casting without causing any inconvenience.
  • the opening 39 where the winding start portion 17 is connected to the winding end portion 19 of the scroll flow path 13 is formed in a flat shape having the same height as the width of the outlet portion 11a of the diffuser 11.
  • a shift chamber is provided on one surface of the flat shape, and the height of the shift chamber changes along the circumferential direction.
  • the opening 39 is formed in a flat shape in which the cross-sectional shape of the scroll flow path 13 is the same height as the width W of the outlet portion 11 a of the diffuser 11.
  • a shift chamber 38a is provided on the bottom surface 11b). This shift chamber 38a is provided in the scroll flow path 13 at the winding end portion 19 as in the first embodiment.
  • the cross-sectional shape is shifted downward by a shift amount ⁇ from the bottom surface 11b of the outlet portion 11a of the diffuser 11, as illustrated by the shape at the positions of ⁇ n and ⁇ n ⁇ 1 in FIG.
  • the lower surface of the shift chamber 38a may be formed with an inclined surface with an inclination angle ⁇ from the end of the bottom surface 11b of the diffuser 11 instead of an arc surface.
  • the shift amount ⁇ and the shift position are the same as those described in the first embodiment.
  • the effect of providing the shift chamber 38a in the scroll flow path 13 at the winding end portion 19 is the same as in the first embodiment, and the direction of the diffuser outlet flow A can be adapted to the flow of the swirl flow B in the scroll flow path.
  • the interference between the diffuser outlet flow A and the scroll flow swirl flow B is prevented, and the occurrence of separation in the vicinity of the tongue 25 caused by the interference is suppressed.
  • the shape of the opening 39 is formed in a flat shape having the same height as the width of the outlet portion 11a of the diffuser 11, so that the connection portion having a circular cross section is formed.
  • the flow area can be reduced, and the recirculation flow (arrow Z in FIG. 11 (a)) from the outlet flow path (winding end portion 19 of the scroll flow path 13) generated in the low flow rate operation toward the vicinity of the tongue 25. ) Can be suppressed.
  • the opening 39 of the winding start portion 17 is formed in a flat shape having the same height as the width of the outlet portion 11a of the diffuser 11.
  • the swirl flow B in the scroll flow path at the winding end portion 19) of the flow path is prevented from flowing in as the inflow flow E into the scroll flow path 13 of the winding start portion 17, thereby FIG. 10 (a).
  • the opening 39 is formed in a flat shape in which the cross-sectional shape of the scroll channel 13 has the same height as the width W of the outlet portion 11a of the diffuser 11, and
  • a shift chamber 38b is also provided at the winding start portion 17.
  • the opening 39 is formed in a flat shape in which the cross-sectional shape of the scroll channel 13 has the same height as the width W of the outlet portion 11a of the diffuser 11, and A shift chamber 38c is provided over the entire direction.
  • the fifth embodiment is a modification of the fourth embodiment, and the shape of the opening 39 where the winding start portion 17 is connected to the winding end portion 19 of the scroll flow path 13 is different from the width of the outlet portion 11a of the diffuser 11.
  • the fourth embodiment is the same as the fourth embodiment in that it is formed in a flat shape having the same height, the shift chamber 40 is provided on one surface of the flat shape, and the height of the shift chamber 40 changes along the circumferential direction. It is the same.
  • one flat surface of the opening 39 having the same height as the height of the diffuser 11 is defined as one surface in the height direction of the diffuser 11. While matching, the surface of the diffuser 11 facing the outlet portion 11a is formed in an arc shape, and the arc-shaped surface gradually changes so as to return to a circular shape.
  • the shift chamber 40 is formed on one surface of the opening 39, and the arc center of the arc shape is located at the end T of the outlet portion 11a of the height surface of the diffuser 11, and the arc shape of the radius R1 Further, when ⁇ 2 changes by a constant angle ⁇ , the arc shape has a radius R2, and when ⁇ 3 changes by a certain angle ⁇ , the arc shape changes by a radius R3.
  • the flow discharged from the diffuser 11 is swirling while the deviation toward the scroll outer periphery proceeds, so that the arc shape is sequentially enlarged to a circular shape so as to match the flow.
  • the flow in the scroll channel 13 can be smoothed by an efficient cross-sectional shape, and the cross-sectional shape is made compact and compact because there is no extra shape for the swirling flow. This contributes to reducing the overall size and weight of the compressor.
  • the combination of the flat opening 39 and the shift chambers 38 and 40 makes it possible to reduce flow loss in a wide operation region from low flow to high flow, and centrifugal compression.
  • the machine performance can be expected to improve.
  • the cross-sectional shape of the scroll including the connecting portion with the diffuser outlet is reviewed, and a wide range of operations during high flow operation and low flow operation are performed. Therefore, it is suitable for use in scrolling of a centrifugal compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2012/051891 2011-03-17 2012-01-27 遠心圧縮機のスクロール構造 Ceased WO2012124388A1 (ja)

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US13/981,042 US9562541B2 (en) 2011-03-17 2012-01-27 Scroll structure of centrifugal compressor
EP12757491.1A EP2687730B1 (en) 2011-03-17 2012-01-27 Centrifugal compressor comprising a scroll structure
CN201280012280.7A CN103415707B (zh) 2011-03-17 2012-01-27 离心压缩机的涡旋结构

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JP2011059935A JP5517981B2 (ja) 2011-03-17 2011-03-17 遠心圧縮機のスクロール構造
JP2011-059935 2011-03-17

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KR102126865B1 (ko) * 2013-09-04 2020-06-25 한화파워시스템 주식회사 스크롤 텅 및 이를 구비한 회전 기계
EP3406913B1 (en) * 2016-03-30 2020-04-22 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Compressor scroll and centrifugal compressor
JP6294391B2 (ja) * 2016-06-28 2018-03-14 本田技研工業株式会社 コンプレッサ及び内燃機関の過給システム
CN109072941B (zh) 2016-07-01 2020-08-18 株式会社Ihi 离心压缩机
EP3561311B1 (en) * 2017-03-28 2022-05-04 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Compressor scroll shape and supercharger
US11073164B2 (en) 2017-11-06 2021-07-27 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Centrifugal compressor and turbocharger including the same
JP7013316B2 (ja) * 2018-04-26 2022-01-31 三菱重工コンプレッサ株式会社 遠心圧縮機
CN111120405B (zh) * 2019-12-12 2021-05-25 中国科学院工程热物理研究所 一种轴向偏置的非对称蜗壳及其设计方法
CN115135884B (zh) * 2020-04-17 2025-07-15 三菱重工发动机和增压器株式会社 涡旋壳体以及离心压缩机
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US9562541B2 (en) 2017-02-07
EP2687730B1 (en) 2018-11-07
CN103415707B (zh) 2016-08-10
JP2012193716A (ja) 2012-10-11
JP5517981B2 (ja) 2014-06-11
EP2687730A4 (en) 2014-12-17
CN103415707A (zh) 2013-11-27
US20130343885A1 (en) 2013-12-26
EP2687730A1 (en) 2014-01-22

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