IPC분류정보
국가/구분 |
United States(US) Patent
등록
|
국제특허분류(IPC7판) |
|
출원번호 |
US-0183443
(2008-07-31)
|
등록번호 |
US-8308420
(2012-11-13)
|
우선권정보 |
JP-2007-202576 (2007-08-03); JP-2007-204000 (2007-08-06); JP-2008-115102 (2008-04-25) |
발명자
/ 주소 |
- Yagi, Manabu
- Kishibe, Tadaharu
- Shibata, Takanori
- Nishida, Hideo
- Kobayashi, Hiromi
- Kuwano, Tetsuya
|
출원인 / 주소 |
- Hitachi Plant Technologies, Ltd.
|
대리인 / 주소 |
|
인용정보 |
피인용 횟수 :
1 인용 특허 :
5 |
초록
▼
A centrifugal compressor is equipped with an impeller having a blade angle distribution that makes it possible to achieve a relatively wide operating range. The blade angle of a shroud side facing a circular plate of a blade is termed a first angle and a blade angle of a hub side disposed at the cir
A centrifugal compressor is equipped with an impeller having a blade angle distribution that makes it possible to achieve a relatively wide operating range. The blade angle of a shroud side facing a circular plate of a blade is termed a first angle and a blade angle of a hub side disposed at the circular plate is a second. The shroud side is formed in a curved shape having an angle distribution from a front area in a shaft direction toward a centrifugal direction in which the first angle is the local maximum point before a substantially middle portion and the local minimum point after the substantially middle point. The hub side is formed in a curved shape having an angle distribution from the front area in the shaft direction toward the centrifugal direction in which the second angle is the maximum local point before the substantially middle portion.
대표청구항
▼
1. A centrifugal compressor comprising a rotary shaft, a circular plate supported by the rotary shaft, and a plurality of blades substantially radially disposed and protruding from the circular plate, and having flow channels of a cross sectional area formed between the blades, in order to suck flui
1. A centrifugal compressor comprising a rotary shaft, a circular plate supported by the rotary shaft, and a plurality of blades substantially radially disposed and protruding from the circular plate, and having flow channels of a cross sectional area formed between the blades, in order to suck fluid from a front area in a shaft direction by rotating the circular plate with the rotary shaft and then discharge the fluid, which increases in pressure while passing through the flow channels, in a centrifugal direction, wherein, assuming that a blade angle of a shroud side of the blade is a first angle and a blade angle of a hub side disposed at the circular plate is a second angle,the shroud side is formed in a curved shape having a first angle distribution from the front area in the shaft direction toward the centrifugal direction in which the first angle distribution has a local maximum point at which the cross sectional area of the flow channel changes from expansion to reduction that is before a substantially middle portion and has a local minimum point after the substantially middle portion at which the cross sectional area of the flow channel changes from reduction to expansion, andthe hub side is formed in a curved shape having a second angle distribution from the front area in the shaft direction toward the centrifugal direction in which the second angle distribution has a local maximum point at which the cross sectional area of the flow channel changes from expansion to reduction before the substantially middle portion. 2. The centrifugal compressor according to claim 1, wherein the flow channel adjacent to the fluid intake is enlarged by tapering the shroud side at a predetermined angle in the shaft direction, and the flow channel adjacent to the fluid outlet of the shroud side or the fluid outlet of the hub side at the circular plate is reduced by tapering the shroud side toward the centrifugal direction at a predetermined angle. 3. The centrifugal compressor according to claim 1, wherein an angle made by a straight line connecting the shroud side of the fluid outlet with the hub side and an edge of the circular plate that is perpendicular to the rotary shaft is in the range of 60° to 90° in a tangential direction of the circular plate. 4. The centrifugal compressor according to claim 1, wherein the shroud side is formed in an S-shape, and the hub side is formed in an S-shape. 5. The centrifugal compressor according to claim 1, wherein a width of the blade is gradually reduced from an end of the fluid discharging side of the flow channel to the downstream. 6. The centrifugal compressor according to claim 5, wherein the end is formed in a cylindrical shape having elliptical surface such that a long axis is arranged in a direction of the flow channel and a short axis is arranged in a width direction of the blade. 7. The centrifugal compressor according to claim 5, wherein the end is formed in a semi-circular cylinder shape. 8. The centrifugal compressor according to claim 5, wherein the end is formed in an edge shape. 9. A centrifugal compressor comprising a rotary shaft, a circular plate supported by the rotary shaft, and a plurality of blades substantially radially disposed and protruding from the circular plate, and having flow channels of a cross sectional area formed between the blades, in order to suck fluid from a front area in a shaft direction by rotating the circular plate with the rotary shaft and then discharge the fluid, which increases in pressure while passing through the flow channels, in a centrifugal direction, wherein, assuming that a blade angle of a shroud side of the blade is a first angle and a blade angle of a hub side disposed at the circular plate is a second angle,the shroud side is formed in a curved shape having a first angle distribution from the front area in the shaft direction toward the centrifugal direction in which the first angle distribution alternately has a local maximum point at which the cross sectional area of the flow channel changes from expansion to reduction and a local minimum point at which the cross sectional area of the flow channel changes from reduction to expansion, andthe hub side is formed in a curved shape having a second angle distribution from the front area in the shaft direction toward the centrifugal direction in which the second angle distribution has a local maximum point at which the cross sectional area of the flow channel changes from expansion to reduction that is before a substantially middle portion. 10. The centrifugal compressor according to claim 9, wherein an angle made by a straight line connecting the shroud side of the fluid outlet with the hub side and an edge of the circular plate that is perpendicular to the rotary shaft is in the range of 60° to 90° in a tangential direction of the circular plate. 11. The centrifugal compressor according to claim 9, wherein the shroud side is formed in an S-shape, and the hub side is formed in an S-shape. 12. The centrifugal compressor according to claim 9, wherein a width of the blade is gradually reduced from an end of the fluid discharging side of the flow channel to the downstream. 13. The centrifugal compressor according to claim 12, wherein the end is formed in a cylindrical shape having elliptical surface such that a long axis is arranged in a direction of the flow channel and a short axis is arranged in a width direction of the blade. 14. The centrifugal compressor according to claim 12, wherein the end is formed in a semi-circular cylinder shape. 15. The centrifugal compressor according to claim 12, wherein the end is formed in an edge shape. 16. An impeller of a centrifugal compressor comprising a rotary shaft and an impeller having a plurality of blades substantially radially disposed and protruding from a circular plate supported by the rotary shaft, and having flow channels of a cross sectional area formed between the blades, in order to suck fluid from a front area in a shaft direction by rotating the circular plate with the rotary shaft and then discharge the fluid, which increases in pressure while passing through the flow channels, in a centrifugal direction, wherein, assuming that a blade angle of a shroud side of the blade is a first angle and a blade angle of a hub side disposed at the circular plate is a second angle,the shroud side is formed in a curved shape having a first angle distribution from the front area in the shaft direction toward the centrifugal direction in which the first angle distribution has a local maximum point at which the cross sectional area of the flow channel changes from expansion to reduction that is before a substantially middle portion and has a local minimum point at which the cross sectional area of the flow channel changes from reduction to expansion after the substantially middle portion, andthe hub side is formed in a curved shape having a second angle distribution from the front area in the shaft direction toward the centrifugal direction in which the second angle distribution has a local maximum point at which the cross sectional area of the flow channel changes from expansion to reduction that is before the substantially middle portion. 17. A method of operating a centrifugal compressor including a rotary shaft and an impeller having a plurality of blades substantially radially disposed and protruding from a circular plate supported by the rotary shaft and having flow channels formed between the blades in order to suck fluid from a front area in a shaft direction by rotating the circular plate with the rotary shaft and then discharge the fluid, which increases in pressure while passing through the flow channels, in a centrifugal direction, wherein, assuming that a blade angle of a shroud side facing the circular plate of the blade is a first angle and a blade angle of a hub side disposed at the circular plate is a second angle,deceleration flow is promoted at a front half region of the flow channel and acceleration flow is promoted at a rear half region of the flow channel by the impeller that has the shroud side formed in a curved shape having a first angle distribution from the front area in the shaft direction toward the centrifugal direction in which the first angle distribution has a local maximum point at which the cross sectional area of the flow channel changes from expansion to reduction that is before a substantially middle portion and has a local minimum point at which the cross sectional area of the flow channel changes from reduction to expansion after the substantially middle portion, and the hub side is formed in a curved shape having a second angle distribution from the front area in the shaft direction toward the centrifugal direction in which the second angle distribution has a maximum local point before the substantially middle portion.
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