WO2013140819A1 - 遠心圧縮機 - Google Patents
遠心圧縮機 Download PDFInfo
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- WO2013140819A1 WO2013140819A1 PCT/JP2013/001968 JP2013001968W WO2013140819A1 WO 2013140819 A1 WO2013140819 A1 WO 2013140819A1 JP 2013001968 W JP2013001968 W JP 2013001968W WO 2013140819 A1 WO2013140819 A1 WO 2013140819A1
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- WIPO (PCT)
- Prior art keywords
- wing
- centrifugal compressor
- main
- sub
- working fluid
- 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
- F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
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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
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/02—Surge control
- F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
- F04D27/0215—Arrangements therefor, e.g. bleed or by-pass valves
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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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
- F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
- F04D29/682—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid extraction
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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
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/02—Surge control
- F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
- F04D27/023—Details or means for fluid extraction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/072—Intercoolers therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/16—Receivers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
Definitions
- the present invention relates to a centrifugal compressor.
- Patent Document 1 discloses a centrifugal compressor 100 as shown in FIG.
- a cylindrical treatment chamber 130 is provided on the shroud wall 120 surrounding the impeller 110. From one end of the treatment chamber 130, a slit-shaped first flow path 131 opens toward the impeller 110, and from the other end of the treatment chamber 130, a slit-shaped second flow path 132 opens to the suction port 101. is doing.
- the present disclosure aims to improve the performance of the centrifugal compressor.
- a centrifugal compressor for compressing a working fluid An impeller in which main wings and sub-wings shorter than the main wings are alternately arranged; A shroud wall having a shape along the impeller and forming an inlet; An extraction chamber that faces the outer surface of the shroud wall and is connected to a discharge space with a pressure equal to or less than the pressure of the working fluid at the inlet; The shroud wall is provided with an extraction passage for guiding a part of the working fluid flowing between the pressure surface of the sub blade and the main wing to the extraction chamber, In the meridional projection obtained by rotating and projecting the main wing, the sub wing, and the shroud wall on the meridian plane passing through the rotation axis of the impeller, the intersection of the upstream end of the sub wing and the tip of the sub wing Is provided closer to the suction port than an opening edge on the side of the extraction passage near the suction port.
- the performance of the centrifugal compressor can be improved.
- Sectional drawing of the centrifugal compressor concerning one embodiment of this indication Partial cross-sectional perspective view of the centrifugal compressor shown in FIG. The figure explaining the positional relationship of a main wing and a 1st slit in a meridian surface, and the positional relationship of a sub wing and a 2nd slit Partial enlarged view of FIG. Sectional drawing of the centrifugal compressor which concerns on a modification Configuration diagram of a refrigeration cycle apparatus using the centrifugal compressor shown in FIG. 1 or FIG. Cross section of a conventional centrifugal compressor
- An impeller of a centrifugal compressor usually has a configuration in which main wings and sub-wings shorter than the main wings are alternately arranged.
- the working fluid sucked into the centrifugal compressor first flows between the main wings and then is divided by the sub wings.
- the gap between the tip of these blades and the shroud wall is often set to less than 10% with respect to the height of the blade.
- the gap between the blade tip and the shroud wall may be relatively large. In such a configuration, the working fluid leaks through the gap between the blade tip and the shroud wall (in other words, the working fluid gets over the blade tip), so that the working fluid flows between the main blades.
- vortices are also generated in the working fluid flowing between the main wing and the sub wing.
- the present inventors extract both the part of the working fluid that flows between the main wings and the part of the working fluid that flows between the main wings and the sub wings, and thereby the two-stage vortex as described above. It has been found that the occurrence of can be prevented or suppressed. Thereby, the performance of a centrifugal compressor can be improved.
- the first aspect of the present disclosure is: A centrifugal compressor for compressing a working fluid, An impeller in which main wings and sub-wings shorter than the main wings are alternately arranged; A shroud wall having a shape along the impeller and forming an inlet; An extraction chamber that faces the outer surface of the shroud wall and is connected to a discharge space with a pressure equal to or less than the pressure of the working fluid at the inlet; The shroud wall is provided with an extraction passage for guiding a part of the working fluid flowing between the pressure surface of the sub blade and the main wing to the extraction chamber, In the meridional projection obtained by rotating and projecting the main wing, the sub wing, and the shroud wall on the meridian plane passing through the rotation axis of the impeller, the intersection of the upstream end of the sub wing and the tip of the sub wing Is provided closer to the suction port than an opening edge on the side of the extraction passage near the suction port.
- the working fluid leaks through the gap between the tip of the sub wing and the shroud wall by extracting a part of the working fluid flowing between the pressurized surface of the sub wing and the main wing through the extraction passage. It is possible to prevent or suppress the occurrence of vortices caused by the above. Thereby, the performance of a centrifugal compressor can be improved. Further, when the inlet of the extraction passage is at the position as described above, a part of the working fluid flowing between the pressurized surface of the sub blade and the main blade can be efficiently guided to the extraction chamber.
- the shroud wall is further provided with an additional extraction passage for guiding a part of the working fluid flowing between the adjacent main wings to the extraction chamber.
- an additional extraction passage for guiding a part of the working fluid flowing between the adjacent main wings to the extraction chamber.
- the length of the additional extraction passage in the circumferential direction of the shroud wall is such that the additional extraction passage is adjacent to the main wing at a position where the additional extraction passage opens toward the impeller.
- a centrifugal compressor is provided that is shorter than the distance between.
- the inlet of the additional extraction passage is the upstream of the main wing when the projection length of the tip of the main wing is L1.
- a centrifugal compressor is provided that is in the range of 0.02L1 to 0.4L1 from the end. If the inlet of the additional extraction passage is located in such a range, the generation of vortices can be prevented or suppressed very effectively.
- the extraction passage and the additional extraction passage there are a plurality of both of the extraction passage and the additional extraction passage, and the extraction passage and the additional extraction passage are arranged in a circumferential direction of the shroud wall.
- a centrifugal compressor arranged alternately in a staggered pattern. According to such a configuration, it is possible to efficiently extract both part of the working fluid flowing between the main wings and part of the working fluid flowing between the main wing and the sub wing.
- the number of the additional extraction passages is equal to the number of the main wings, and the additional extraction passages are arranged at the same angular pitch as the main wings.
- the length of the extraction passage in the circumferential direction of the shroud wall is the length of the extraction passage at a position where the extraction passage opens toward the impeller.
- a centrifugal compressor is provided that is shorter than a distance between a main wing and the sub wing. If it is this structure, the front-end
- the inlet of the extraction passage may be configured so that the projection length of the tip of the sub wing is L2.
- a centrifugal compressor is provided in the range of 0.02L2 to 0.4L2 from the upstream end of the sub wing. If the inlet of the extraction passage is located in such a range, the generation of vortices can be prevented or suppressed very effectively.
- the ninth aspect is A main circuit in which an evaporator for storing the refrigerant liquid and evaporating the refrigerant liquid therein, a first compressor for compressing the refrigerant vapor, and a condenser for condensing the refrigerant vapor and storing the refrigerant liquid are connected in this order.
- a second circulation path for circulating the refrigerant liquid stored in the condenser or the heat medium heated in the condenser via a heat dissipation heat exchanger
- the refrigeration cycle apparatus wherein the first compressor is a centrifugal compressor according to any one of the first to eighth aspects, and further includes a reflux path for returning refrigerant vapor from the extraction chamber of the centrifugal compressor to the evaporator.
- the refrigerant vapor is returned from the extraction chamber of the centrifugal compressor to the evaporator through the reflux path.
- the tenth aspect provides the refrigeration cycle apparatus in addition to the ninth aspect, wherein the second compressor is a centrifugal type, and the first compressor and the second compressor are connected by a rotating shaft. If the 1st compressor and the 2nd compressor are connected with a rotating shaft, the number of parts of the 1st compressor and the 2nd compressor can be reduced.
- the eleventh aspect provides a refrigeration cycle apparatus in addition to the ninth or tenth aspect, wherein a flow rate adjusting valve is provided in the reflux path.
- the efficiency of the centrifugal compressor can be optimized by adjusting the flow rate of the refrigerant vapor with the flow rate adjusting valve.
- FIG. 1 and 2 show a centrifugal compressor 1A according to an embodiment of the present invention.
- Centrifugal compressor 1 ⁇ / b> A is connected to an electric motor or is connected to a turbine and a generator by rotating shaft 11.
- the centrifugal compressor 1A is driven by the rotation of the rotary shaft 11 and compresses the working fluid.
- the centrifugal compressor 1 ⁇ / b> A includes an impeller 2 fixed to the rotary shaft 11, a back plate 13 disposed on the back side of the impeller 2, and a housing 15 that houses the impeller 2.
- the front side of the back plate 13 in the axial direction of the rotary shaft 11 may be referred to as the front, and the back side may be referred to as the rear.
- the impeller 2 includes a main body 20 that smoothly expands from the minimum diameter portion to the maximum diameter portion along the axial direction of the rotary shaft 11, and a main wing 21 and a sub wing 22 that protrude from the flared outer peripheral surface of the main body portion 20. including.
- the main wings 21 and the sub wings 22 are alternately arranged in the circumferential direction of the impeller 2.
- the sub wing 22 is shorter than the main wing 21, and as shown in FIG. 3, the downstream end 22 c of the sub wing 22 is located at the same position as the downstream end 21 c of the main wing 21, while the upstream end 22 a of the sub wing 22 is It is located behind the upstream end 21 a of the main wing 21.
- the surface on the rotational direction side of the impeller 2 is a pressure surface, and the surface on the opposite side is a non-pressure surface.
- the housing 15 includes a shroud wall 3 having a shape along the impeller 2, a flange 5 extending radially outward from a front end portion of the shroud wall 3, a peripheral member 17 connected to the rear end portion of the shroud wall 3, and a peripheral member 17 and a front member 18 held between the flanges 5.
- the shroud wall 3 extends forward from the impeller 2 to form a suction port 12, and the peripheral member 17 communicates with a diffuser formed between the back plate 13 and the shroud wall 3 around the impeller 2.
- a spiral chamber 16 is formed.
- the shroud wall 3 is divided into front and rear in the vicinity of the upstream end 21 a of the main wing 21 of the impeller 2, the front portion of the shroud wall 3 and the flange 5 are integrated, and the shroud wall 3 The rear portion and the peripheral member 17 are integrated.
- the outer peripheral edge of the main wing 21 facing the suction port 12 is defined as the upstream end 21 a of the main wing 21.
- the outer peripheral edge of the main wing 21 facing the shroud wall 3 is defined as the tip 21 b of the main wing 21.
- the outer peripheral edge of the sub wing 22 facing the suction port 12 is defined as the upstream end 22 a of the sub wing 22.
- the outer peripheral edge of the sub wing 22 facing the shroud wall 3 is defined as the tip 22 b of the sub wing 22.
- the front member 18 covers the space facing the outer surface of the shroud wall 3 together with the flange 5. That is, the shroud wall 3, the flange 5, and the front member 18 form an annular extraction chamber (bleed chamber) 4 around the suction port 12.
- the front member 18 has a cylindrical surface 18 a that extends forward beyond the flange 5.
- the cylindrical surface 18 a forms a ring-shaped space (corresponding to the discharge space of the present invention) 18 b that faces the front surface of the flange 5 and is continuous with the suction port 12. Since the ring-shaped space 18 b is filled with the working fluid, the ring-shaped space 18 b has a pressure equal to the pressure of the working fluid at the suction port 12.
- “equal” is a concept including not only a state in which the pressure in the ring-shaped space 18b completely matches the pressure of the working fluid in the suction port 12, but also a state in which the former is larger than the latter by the amount of pressure loss. is there.
- the flange 5 is provided with an arc-shaped opening 51 through which the extraction chamber 4 is connected to the ring-shaped space 18b.
- the shroud wall 3 is provided with a plurality of first slits 31 (additional extraction passages) and second slits 32 (extraction passages) extending in the circumferential direction.
- the first slit 31 opens from the extraction chamber 4 in the vicinity of the upstream end 21 a of the main wing 21 of the impeller 2, and the second slit 32 opens from the extraction chamber 4 in the vicinity of the upstream end 22 a of the sub wing 22.
- the first slits 31 and the second slits 32 are arranged in a staggered pattern alternately in the circumferential direction.
- the 1st slit 31 and the 2nd slit 32 do not necessarily need to be completely parallel with the circumferential direction, and may incline slightly with respect to the circumferential direction.
- the first slit 31 guides part of the working fluid flowing between the adjacent main wings 21 to the extraction chamber 4, and the second slit 32 flows between the pressurized surface of the sub wing 22 and the main wing 21. A part of the working fluid is guided to the extraction chamber 4.
- the number of first slits 31 is equal to the number of main wings 21, and the first slits 31 are arranged at the same angular pitch as the main wings 21. If it is this structure, the front-end
- the first slit 31 opens at a position behind the upstream end 21 a of the main wing 21 and ahead of the upstream end 22 a of the sub wing 22 in the axial direction of the rotary shaft 11. ing.
- an intersection 21t between the upstream end 21a of the main wing 21 and the tip 21b of the main wing 21 is an opening on the side close to the inlet 12 of the inlet of the first slit 31. It is located closer to the inlet 12 than the edge 31e.
- the entire entrance of the first slit 31 faces the tip 21b of the main wing. If there is an entrance of the first slit 31 at such a position, a part of the working fluid flowing between the main wings 21 can be efficiently guided to the extraction chamber 4.
- the second slit 32 opens at a position behind the upstream end 22 a of the sub blade 22 in the axial direction of the rotary shaft 11. Specifically, as shown in FIG. 4, in the meridional projection, the intersection 22t of the upstream end 22a of the sub wing 22 and the tip 22b of the sub wing 22 is the side close to the inlet 12 of the inlet of the second slit 32. It is located closer to the suction port 12 than the opening edge 32e. In the present embodiment, the entire entrance of the second slit 32 faces the tip 22 b of the sub wing 22. When the inlet of the second slit 32 is located at such a position, a part of the working fluid flowing between the pressurized surface of the sub blade 22 and the main blade 21 can be efficiently guided to the extraction chamber 4.
- the length of the first slit 31 in the circumferential direction of the shroud wall 3 is preferably shorter than the distance between adjacent main wings 21 at the position where the first slit 31 opens toward the impeller 2. If it is this structure, the front-end
- the inlet of the first slit 31 (opening on the impeller 2 side) is the tip of the tip 21 b of the main wing 21.
- the projection length is L1, it is in the range of, for example, 0.02L1 to 0.4L1 (or 0.05L1 to 0.1L1) from the upstream end 21a of the main wing 21.
- the inlet (opening on the impeller 2 side) of the second slit 32 is, for example, 0.02L2 to 0.4L2 (from 0.02L2 to 0.4L2) from the upstream end 22a of the sub wing 22 when the projection length of the tip 22b of the sub wing 22 is L2. Or in the range of 0.05 L2 to 0.1 L2).
- the width of the first slit 31 is, for example, 3 to 5 times the thickness of the main wing 21 at a position facing the first slit 31.
- the width of the second slit 32 is, for example, 3 to 5 times the thickness of the sub blade 22 at a position facing the second slit 32.
- “Projection length” means the length of an arc drawn by the tips 21b and 22b in the meridional projection of FIG.
- centrifugal compressor 1 ⁇ / b> A described above a part of the working fluid flowing between the main blades 21 is extracted through the first slit 31, so that the working fluid flows through the gap between the tip 21 b of the main blade 21 and the shroud wall 3. The generation of vortices due to leakage can be prevented or suppressed. Further, by extracting a part of the working fluid flowing between the pressurized surface of the sub wing 22 and the main wing 21 through the second slit 32, the working fluid is passed through the gap between the tip 22 b of the sub wing 22 and the shroud wall 3. The generation of vortices due to leakage can be prevented or suppressed. Thereby, the performance of the centrifugal compressor 1A can be improved.
- the vortex caused by the working fluid leaking through the gap between the tip of the blade and the shroud wall often appears immediately downstream of the upstream end of the blade.
- the opening (inlet) of the first slit 31 is positioned within the range of, for example, 0.02L1 to 0.4L1 (or 0.05L1 to 0.1L1) from the upstream end 21a of the main wing 21, generation of a vortex is generated. It can be prevented or suppressed very effectively.
- the opening (inlet) of the second slit 32 is positioned in the range of 0.02L2 to 0.4L2 (or 0.05L2 to 0.1L2) from the upstream end 22a of the sub blade 22, generation of vortices will occur. Can be prevented or suppressed extremely effectively.
- the centrifugal compressor 1B according to the modification is the same as the centrifugal compressor 1A described with reference to FIGS. 1 to 4 except that the first slit 31 is not provided in the shroud wall 3. It has a structure.
- the shroud wall 3 is provided with at least one second slit 32 as an extraction passage for guiding a part of the working fluid to the extraction chamber 4.
- the description of the centrifugal compressor 1A can be applied to other parts of the centrifugal compressor 1B.
- the extraction passage slit 32
- the performance of the centrifugal compressor 1B is improved. It can be improved effectively.
- first slits 31 and the second slits 32 are provided.
- first slits 31 and the second slits 32 may be provided one by one.
- the cross-sectional shape of the extraction passage for guiding a part of the working fluid to the extraction chamber 4 is not particularly limited.
- a through hole having another cross-sectional shape such as a circle, an ellipse, or a rectangle may be provided.
- extraction passages having different cross-sectional shapes may be formed along the circumferential direction of the shroud wall 3. This also applies to the second slit 32.
- the extraction chamber 4 is connected to the ring-shaped space 18 b continuous with the suction port 12 by the opening 51 provided in the flange 5.
- the extraction chamber 4 may be connected to a space smaller than the pressure of the working fluid at the suction port 12.
- the extraction chamber 4 may be connected to a negative pressure source (for example, the suction side of another compressor) installed separately from the centrifugal compressor 1A or 1B by a flow path that penetrates the housing 15.
- centrifugal compressors 1A and 1B are not particularly limited, but may be used in a stationary type or a gas turbine power generation device mounted on a vehicle such as an automobile.
- the centrifugal compressors 1A and 1B can be used in a refrigeration cycle apparatus 10 as shown in FIG. 6, for example.
- the refrigeration cycle apparatus 10 includes a main circuit 6 for circulating a refrigerant, a first circulation path 7 for heat absorption, and a second circulation path 8 for heat dissipation.
- the main circuit 6, the first circulation path 7, and the second circulation path 8 are filled with a liquid refrigerant at room temperature.
- a refrigerant having a negative saturated vapor pressure at room temperature is used as the refrigerant.
- examples of such a refrigerant include a refrigerant mainly composed of water or alcohol.
- the main circuit 6, the first circulation path 7, and the second circulation path 8 are in a negative pressure state lower than the atmospheric pressure.
- the “main component” means a component that is contained most in mass ratio.
- the main circuit 6 includes an evaporator 66, a first compressor 61, an intercooler 62, a second compressor 63, a condenser 64, and an expansion valve 65, and these devices are connected in this order by flow paths.
- the evaporator 66 stores the refrigerant liquid and evaporates the refrigerant liquid inside. Specifically, the refrigerant liquid stored in the evaporator 66 is circulated through the heat absorption heat exchanger 71 by the first circulation path 7. For example, when the refrigeration cycle apparatus 10 is an air conditioner that cools a room, the heat-absorbing heat exchanger 71 is installed in the room and cools the room air supplied by the blower by heat exchange with the refrigerant liquid.
- the first compressor 61 and the second compressor 63 compress the refrigerant vapor in two stages.
- the first compressor 61 the centrifugal compressor 1A or 1B described above is used.
- the second compressor 63 may be a positive displacement compressor independent of the first compressor 61, but in the present embodiment, the second compressor 63 is a centrifugal compressor connected to the first compressor 61 by the rotary shaft 11. .
- the electric motor 67 that rotates the rotating shaft 11 may be disposed between the first compressor 61 and the second compressor 63, or may be disposed outside one of the compression devices. If the 1st compressor 61 and the 2nd compressor 63 are connected by the rotating shaft 11, the number of parts of the 1st compressor 61 and the 2nd compressor 63 can be reduced.
- the intermediate cooler 62 cools the refrigerant vapor discharged from the first compressor 21 before being sucked into the second compressor 22.
- the intermediate cooler 62 may be a direct contact heat exchanger or an indirect heat exchanger.
- the condenser 64 condenses the refrigerant vapor inside and stores the refrigerant liquid. Specifically, the refrigerant liquid stored in the condenser 64 is circulated through the heat dissipation heat exchanger 81 by the second circulation path 8. For example, when the refrigeration cycle apparatus 10 is an air conditioner that cools an indoor room, the heat-dissipating heat exchanger 81 is installed outside and heats the outdoor air supplied by the blower by heat exchange with the refrigerant liquid.
- the refrigeration cycle apparatus 10 does not necessarily need to be an air conditioning apparatus dedicated to cooling. For example, if each of the first heat exchanger installed indoors and the second heat exchanger installed outdoor is connected to the evaporator 66 and the condenser 64 via a four-way valve, the cooling operation and the heating operation are performed. A switchable air conditioner can be obtained. In this case, both the first heat exchanger and the second heat exchanger function as the heat absorption heat exchanger 71 and the heat dissipation heat exchanger 81. Further, the refrigeration cycle apparatus 10 is not necessarily an air conditioner, and may be a chiller, for example. Furthermore, the object to be cooled by the heat exchanger 71 for heat absorption and the object to be heated by the heat exchanger 81 for heat dissipation may be a gas or a liquid other than air.
- the expansion valve 65 is an example of a decompression mechanism that decompresses the condensed refrigerant liquid.
- the pressure reducing mechanism for example, the expansion valve 65 is not provided in the main circuit 6, and the liquid level of the refrigerant liquid in the evaporator 66 is higher than the liquid level of the refrigerant liquid in the condenser 64. It is also possible to adopt a configuration.
- the extraction chamber 4 (see FIGS. 1 to 4) of the centrifugal compressor 1A or 1B is connected to the internal space of the evaporator 66 by the reflux path 9. That is, the internal space of the evaporator 66 corresponds to the discharge space of the present invention. For this reason, the refrigerant vapor is returned to the evaporator 66 from the extraction chamber 4 of the centrifugal compressor 1 ⁇ / b> A or 1 ⁇ / b> B through the reflux path 9. Thereby, the performance of the centrifugal compressor 1A or 1B can be improved, and as a result, the performance of the refrigeration cycle apparatus 10 can be improved. It is desirable that a flow rate adjusting valve 91 is provided in the reflux path 9. By adjusting the flow rate of the refrigerant vapor with the flow rate adjusting valve 91, the efficiency of the centrifugal compressor 1A or 1B can be optimized.
- the evaporator 66 is not necessarily a direct contact heat exchanger, and may be an indirect heat exchanger. In this case, the heat medium cooled in the evaporator 66 circulates through the first circulation path 7.
- the condenser 64 is not necessarily a direct contact heat exchanger, and may be an indirect heat exchanger. In this case, the heat medium heated in the condenser 64 circulates through the second circulation path 8.
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Abstract
Description
作動流体を圧縮する遠心圧縮機であって、
主翼と前記主翼よりも短い副翼とが交互に配置された羽根車と、
前記羽根車に沿う形状を有し、吸入口を形成するシュラウド壁と、
前記シュラウド壁の外側面に面する、前記吸入口での作動流体の圧力と等しいまたはそれよりも小さな圧力の排出空間に接続される抽出室と、を備え、
前記シュラウド壁には、前記副翼の加圧面と前記主翼との間に流入した作動流体の一部を前記抽出室に導く抽出通路が設けられており、
前記羽根車の回転軸を通る子午面に前記主翼、前記副翼および前記シュラウド壁を回転投影することによって得られる子午面投影図において、前記副翼の上流端と前記副翼の先端との交点が、前記抽出通路の入口の前記吸入口に近い側の開口縁よりも前記吸入口の近くに位置している、遠心圧縮機を提供する。
作動流体を圧縮する遠心圧縮機であって、
主翼と前記主翼よりも短い副翼とが交互に配置された羽根車と、
前記羽根車に沿う形状を有し、吸入口を形成するシュラウド壁と、
前記シュラウド壁の外側面に面する、前記吸入口での作動流体の圧力と等しいまたはそれよりも小さな圧力の排出空間に接続される抽出室と、を備え、
前記シュラウド壁には、前記副翼の加圧面と前記主翼との間に流入した作動流体の一部を前記抽出室に導く抽出通路が設けられており、
前記羽根車の回転軸を通る子午面に前記主翼、前記副翼および前記シュラウド壁を回転投影することによって得られる子午面投影図において、前記副翼の上流端と前記副翼の先端との交点が、前記抽出通路の入口の前記吸入口に近い側の開口縁よりも前記吸入口の近くに位置している、遠心圧縮機を提供する。
冷媒液を貯留するとともに内部で冷媒液を蒸発させる蒸発器、冷媒蒸気を圧縮する第1圧縮機、および内部で冷媒蒸気を凝縮させるとともに冷媒液を貯留する凝縮器がこの順に接続された主回路と、
前記蒸発器に貯留された冷媒液または前記蒸発器内で冷却された熱媒体を吸熱用熱交換器を経由して循環させる第1循環路と、
前記凝縮器に貯留された冷媒液または前記凝縮器内で加熱された熱媒体を放熱用熱交換器を経由して循環させる第2循環路と、を備え、
前記第1圧縮機が第1~第8態様のいずれか1つの遠心圧縮機であり、前記遠心圧縮機の前記抽出室から前記蒸発器に冷媒蒸気を戻す還流路をさらに備える、冷凍サイクル装置を提供する。
図1および図2に、本発明の一実施形態に係る遠心圧縮機1Aを示す。遠心圧縮機1Aは、回転シャフト11により、電動機と連結されたり、タービンおよび発電機と連結されたりする。遠心圧縮機1Aは、回転軸11の回転により駆動され、作動流体を圧縮する。
図5に示すように、変形例に係る遠心圧縮機1Bは、シュラウド壁3に第1スリット31が設けられていない点を除き、図1~4を参照して説明した遠心圧縮機1Aと同じ構造を有する。シュラウド壁3には、作動流体の一部を抽出室4に導く抽出通路として、少なくとも1つの第2スリット32が設けられている。遠心圧縮機1Bのその他の部分には、遠心圧縮機1Aの説明が適用され得る。
前記実施形態では、第1スリット31および第2スリット32が共に複数設けられていたが、第1スリット31および第2スリット32は1つずつ設けられていてもよい。
上述した遠心圧縮機1Aおよび1Bは、特にその用途が限定されるものではないが、定置式や例えば自動車などの車両に搭載されるガスタービン発電装置に用いられてもよい。あるいは、遠心圧縮機1Aおよび1Bは、例えば図6に示すような冷凍サイクル装置10に用いることができる。
Claims (11)
- 作動流体を圧縮する遠心圧縮機であって、
主翼と前記主翼よりも短い副翼とが交互に配置された羽根車と、
前記羽根車に沿う形状を有し、吸入口を形成するシュラウド壁と、
前記シュラウド壁の外側面に面する、前記吸入口での作動流体の圧力と等しいまたはそれよりも小さな圧力の排出空間に接続される抽出室と、を備え、
前記シュラウド壁には、前記副翼の加圧面と前記主翼との間に流入した作動流体の一部を前記抽出室に導く抽出通路が設けられており、
前記羽根車の回転軸を通る子午面に前記主翼、前記副翼および前記シュラウド壁を回転投影することによって得られる子午面投影図において、前記副翼の上流端と前記副翼の先端との交点が、前記抽出通路の入口の前記吸入口に近い側の開口縁よりも前記吸入口の近くに位置している、遠心圧縮機。 - 前記シュラウド壁には、隣り合う前記主翼の間に流入した作動流体の一部を前記抽出室に導く追加の抽出通路がさらに設けられており、
前記子午面投影図において、前記主翼の上流端と前記主翼の先端との交点は、前記追加の抽出通路の入口の前記吸入口に近い側の開口縁よりも前記吸入口の近くに位置している、請求項1に記載の遠心圧縮機。 - 前記シュラウド壁の周方向における前記追加の抽出通路の長さは、当該追加の抽出通路が前記羽根車に向かって開口する位置での隣り合う前記主翼の間の距離よりも短い、請求項2に記載の遠心圧縮機。
- 前記子午面投影図において、前記追加の抽出通路の前記入口は、前記主翼の前記先端の投影長をL1としたときに前記主翼の前記上流端から0.02L1~0.4L1の範囲にある、請求項2に記載の遠心圧縮機。
- 前記抽出通路および前記追加の抽出通路は共に複数あり、前記抽出通路と前記追加の抽出通路が前記シュラウド壁の周方向に交互に千鳥状に並んでいる、請求項2に記載の遠心圧縮機。
- 前記追加の抽出通路の数は前記主翼の数と等しく、前記追加の抽出通路は前記主翼と同一角度ピッチで配置されている、請求項2に記載の遠心圧縮機。
- 前記シュラウド壁の周方向における前記抽出通路の長さは、当該抽出通路が前記羽根車に向かって開口する位置での前記主翼と前記副翼との間の距離よりも短い、請求項1に記載の遠心圧縮機。
- 前記子午面投影図において、前記抽出通路の前記入口は、前記副翼の前記先端の投影長をL2としたときに前記副翼の前記上流端から0.02L2~0.4L2の範囲にある、請求項1に記載の遠心圧縮機。
- 冷媒液を貯留するとともに内部で冷媒液を蒸発させる蒸発器、冷媒蒸気を圧縮する第1圧縮機、および内部で冷媒蒸気を凝縮させるとともに冷媒液を貯留する凝縮器がこの順に接続された主回路と、
前記蒸発器に貯留された冷媒液または前記蒸発器内で冷却された熱媒体を吸熱用熱交換器を経由して循環させる第1循環路と、
前記凝縮器に貯留された冷媒液または前記凝縮器内で加熱された熱媒体を放熱用熱交換器を経由して循環させる第2循環路と、を備え、
前記第1圧縮機が請求項1に記載の遠心圧縮機であり、前記遠心圧縮機の前記抽出室から前記蒸発器に冷媒蒸気を戻す還流路をさらに備える、冷凍サイクル装置。 - 前記第2圧縮機は遠心型であり、
前記第1圧縮機と前記第2圧縮機は、回転シャフトによって連結されている、請求項9に記載の冷凍サイクル装置。 - 前記還流路には流量調整弁が設けられている、請求項9に記載の冷凍サイクル装置。
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CN201380001726.0A CN103620225B (zh) | 2012-03-22 | 2013-03-22 | 制冷循环装置 |
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