WO2010146837A1 - 回転式圧縮機 - Google Patents
回転式圧縮機 Download PDFInfo
- Publication number
- WO2010146837A1 WO2010146837A1 PCT/JP2010/003972 JP2010003972W WO2010146837A1 WO 2010146837 A1 WO2010146837 A1 WO 2010146837A1 JP 2010003972 W JP2010003972 W JP 2010003972W WO 2010146837 A1 WO2010146837 A1 WO 2010146837A1
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- WIPO (PCT)
- Prior art keywords
- oil
- discharge port
- compression mechanism
- discharge
- cylinder chamber
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/068—Silencing the silencing means being arranged inside the pump housing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/061—Silencers using overlapping frequencies, e.g. Helmholtz resonators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/809—Lubricant sump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/023—Lubricant distribution through a hollow driving shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/122—Arrangements for supercharging the working space
Definitions
- the present invention relates to a rotary compressor, and in particular, high-pressure gas remaining in a discharge port of a compression mechanism that compresses gas in a cylinder chamber returns to the cylinder chamber and re-expands during the next compression process.
- the present invention was devised in view of such problems.
- the purpose of the present invention is to make the high-pressure gas remaining in the discharge port of the compression mechanism at the completion of the discharge process become a low pressure at the start of the next compression process. It is to prevent vibration and noise generated by re-expansion in the cylinder chamber, and to prevent oil from entering the cylinder chamber too much.
- the first invention includes a casing (10) and a compression mechanism (20) provided in the casing (10) and compressing gas in the cylinder chamber (25).
- the compression mechanism (20) includes: A discharge port (21b) equipped with a discharge valve (28a) that is opened during the discharge process and closed during the next compression process from the end of the discharge process is provided, the discharge port (21b) A high-pressure dome-type rotary compressor in which high-pressure gas discharged during the discharge process is discharged to the outside of the casing (10) through a space in the casing (10) is assumed.
- the rotary compressor supplies lubricating oil stored in the bottom of the casing (10) to the inside of the discharge port (21b) from the middle of the discharge process to the start of the compression process.
- An oil supply path (40) is provided.
- the compression mechanism (20) is operated to compress the low pressure gas into the high pressure gas.
- the high-pressure gas discharged from the discharge port (21b) of the compression mechanism (20) into the casing (10) of the compressor and filling the space in the casing (10) is transferred to the casing (10).
- the refrigerant is again sucked into the compression mechanism (20) and compressed after undergoing the condensation stroke, the expansion stroke, and the evaporation stroke. .
- the operation of expanding and reducing the volume of the cylinder chamber (25) is repeated. Then, the refrigerant is sucked when the volume of the cylinder chamber (25) increases, and the refrigerant is compressed and discharged when the volume of the cylinder chamber (25) decreases.
- oil is supplied to the discharge port (21b) from the middle of the discharge process during the operation of the compression mechanism (20) to the start of the compression process.
- the discharge port (21b) is closed by the discharge valve (28a), so that oil remains in the discharge port (21b) until the compression process starts. It is in the state.
- the oil supply path (40) supplies oil into the discharge port (21b) between the middle of the discharge process and the end of the discharge process. It is characterized by being composed.
- the oil when the discharge process is completed, the oil enters the discharge port (21b). Therefore, when the compression process is started next, the oil in the discharge port (21b) flows into the cylinder chamber (25). Therefore, even if the cylinder chamber (25) becomes low pressure and the next compression process starts, the occurrence of pulsation can be suppressed.
- the oil supply path (40) supplies oil to the inside of the discharge port (21b) between the end of the discharge process and the start of the compression process. It is characterized by being.
- the oil in the discharge port (21b) flows into the cylinder chamber (25) when the discharge process ends and the compression process starts next. Therefore, even if the cylinder chamber (25) becomes low pressure and the next compression process starts, the oil in the discharge port (21b) flows into the cylinder chamber (25), so that occurrence of pulsation can be suppressed.
- one cycle of the operation of the compression mechanism (20) is performed by a rotation operation of 360 °, and the end position of the discharge process in the compression mechanism (20) If the position between the start positions of the compression process is the reference position of the rotation operation and the rotation angle of the reference position is 0 °, the oil supply path (40) has a rotation angle in the range between 315 ° and 45 °. The oil is supplied to the inside of the discharge port (21b).
- the above rotation angle is an angle corresponding to the period from the middle of the discharge process during the operation of the compression mechanism (20) to the start of the compression process. Therefore, as in the first to third aspects of the invention, when the discharge process ends and the compression process starts next, the oil in the discharge port (21b) flows into the cylinder chamber (25). Therefore, even if the cylinder chamber (25) becomes low pressure and the next compression process starts, the occurrence of pulsation can be suppressed.
- the oil supply path (40) is connected to the discharge port (14) from an oil reservoir (14) provided in the casing (10).
- the oil supply direct passage (40A) communicates with the oil reservoir (14) and the discharge port (21b) so as to supply oil to 21b).
- oil flows from the oil reservoir (14) to the discharge port (21b) of the compression mechanism (20) via the oil supply direct passage (40A). Supplied.
- the oil contained in the discharge port (21b) enters the low-pressure cylinder chamber (25) at the end of the discharge process. Occurrence is suppressed.
- an oil stirring mechanism (50) is provided for stirring the oil stored in the oil reservoir (14) in conjunction with the rotational operation of the compression mechanism (2). It is characterized by.
- the refrigerant dissolved in the oil is foamed and separated from the oil. Therefore, the oil into which the refrigerant is hardly dissolved is supplied to the discharge port (21b).
- the compression mechanism (20) is configured so that the piston (26) is rotated by a rotating operation of a crankshaft (33) having an eccentric part (33b).
- a concave portion (42) into which oil is introduced, and the concave portion (42) is provided with the compression mechanism (42) within an angular range for supplying oil into the discharge port (21b). It is characterized by being configured to communicate with the discharge port (21b) of 20).
- the crankshaft (33) rotates during the operation of the compression mechanism (20), and the piston (26) rotates in the cylinder chamber (25).
- the recess (42) formed in the eccentric part (33b) of the crankshaft (33) also turns around the center of the crankshaft (33), and the recess (42) discharges from the compression mechanism (20). It communicates with the port (21b) in the above angle range. Since oil is introduced into the recess (42), the oil flows from the recess (42) into the discharge port (21b) when the recess (42) communicates with the discharge port (21b). . Accordingly, when the compression process of the compression mechanism (20) starts, the oil that has entered the discharge port (21b) at that time is introduced into the cylinder chamber (25).
- the discharge port (21b) is located at a position where the discharge port (21b) partially overlaps the recess (42) in an angle range in which oil is supplied to the inside of the discharge port (21b). It is characterized by being constituted by a through hole formed in the compression mechanism (20).
- the discharge port (21b) partially overlaps the recess (42) in an angular range in which oil is supplied into the discharge port (21b) during the turning operation of the recess (42).
- the recess (42) and the discharge port (21b) communicate with each other within the above angle range. Since oil is introduced into the recess (42), the oil flows from the recess (42) into the discharge port (21b). Therefore, when the compression mechanism (20) starts the compression process, the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25).
- the discharge port (21b) is formed by a through-hole formed at a position deviating radially outward from the turning track of the recess (42), and the piston (26 ) Is formed with a notch (43) that allows the discharge port (21b) and the recess (42) to communicate with each other within an angular range for supplying oil into the discharge port (21b). It is a feature.
- the discharge port (21b) is formed by a through hole formed at a position deviating radially outward from the turning track of the recess (42), and the end face of the piston (26)
- a notch (43) is formed to communicate the discharge port (21b) and the recess (42) in an angle range for supplying oil to the inside of the discharge port (21b), so that the compression mechanism (20)
- the recess (42) and the discharge port (21b) communicate with each other in a certain angular range while the recess (42) turns around the center of the crankshaft (33). Since oil is introduced into the recess (42), the oil flows from the recess (42) into the discharge port (21b). Therefore, when the compression mechanism (20) starts the compression process, the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25).
- the discharge port (21b) is formed by a through hole formed at a position deviated radially outward from the turning track of the recess (42), and the discharge port ( 21b) is formed with a notch (44) that allows the discharge port (21b) and the recess (42) to communicate with each other within an angle range for supplying oil into the discharge port (21b). It is said.
- the discharge port (21b) is formed by a through-hole formed at a position deviating radially outward from the orbit of the recess (42), and the discharge port (21b) Since a notch (44) is formed to communicate the discharge port (21b) and the recess (42) in an angle range for supplying oil to the inside of the discharge port (21b), a compression mechanism (20 ), The recess (42) and the discharge port (21b) communicate with each other within a certain angle range while the recess (42) turns around the center of the crankshaft (33). Since oil is introduced into the recess (42), the oil flows from the recess (42) into the discharge port (21b). Therefore, at the start of the compression process of the compression mechanism (20), the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25).
- the oil supply path (40) is compressed from an oil reservoir (14) provided in the casing (10). It is characterized by having an oil supply indirect path (40B) that intermittently supplies oil to the discharge port (21b) through the inside of (20) (sliding surface and cylinder chamber (25)) .
- the oil supply path (40) causes the oil reservoir (14) provided in the casing (10) to move into the interior of the compression mechanism (20) ( Oil is introduced into the sliding surface and cylinder chamber (25)). Then, the oil is intermittently pushed from the inside of the compression mechanism (20) into the discharge port (21b) during the operation of the compression mechanism (20). Therefore, when the discharge process ends and the next compression process starts, the oil is in the discharge port (21b).
- the oil supply path (40) functions as an indirect path for oil supply (40B).
- the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25).
- the refrigerant dissolved in the oil is foamed and separated from the oil. Therefore, the oil into which the refrigerant is hardly dissolved is supplied to the discharge port (21b).
- the compression mechanism (20) is configured so that the oil supplied to the sliding surface of the compression mechanism (20) is within the predetermined angle range between the compression process and the discharge process.
- the communication groove (45) causes the sliding surface of the compression mechanism (20) and the cylinder chamber (25) to move between the compression process and the discharge process.
- oil is supplied from the sliding surface to the cylinder chamber (25).
- This oil is pushed into the discharge port (21b) as the volume of the cylinder chamber (25) decreases. Therefore, when the discharge process is finished and the next compression process starts, oil is in the discharge port (21b).
- the oil supply path (40) functions as an oil supply indirect path (40B).
- the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25).
- the cylinder chamber (25) is configured such that the compression mechanism (20) temporarily stores oil introduced from the oil reservoir (14) into the cylinder chamber (25). It has the oil storage recessed part (46) formed in the inner wall surface of this.
- the cylinder chamber of the compression mechanism (20) is separated from the oil reservoir (14) provided in the casing (10) by the oil supply path (40). Oil is introduced into (25), and the oil is stored in the oil storage recess (46). The oil in the oil reservoir recess (46) is pushed into the discharge port (21b), which is the only destination, as the volume of the cylinder chamber (25) is reduced. Therefore, when the discharge process is finished and the next compression process starts, oil is in the discharge port (21b). Thus, since oil is introduced into the discharge port (21b) via the cylinder chamber (25), the oil supply path (40) functions as an indirect path for oil supply (40B). At the start of the compression process of the compression mechanism (20), the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25).
- the compression mechanism (20) causes the piston (26) to move within the cylinder (21) by rotating the crankshaft (33) having the eccentric portion (33b).
- the oil storage recess (46) is configured by a revolving compression mechanism (20) having a suction port (21a) and a discharge port (21b).
- the cylinder chamber (25) is formed at a position that is opened and closed by the piston (26) at the axial end face, and is released from the end face of the piston (26) at the timing from the end of the discharge process to the start of the compression process to start the discharge process. It is characterized in that it is covered with the end face of the piston (26) before being communicated, and is in communication with the sliding surface of the crankshaft (33) and the piston (26) during the discharging process.
- the position of the oil storage recess (46) is specified, so that the end face of the piston (26) is covered at the timing when the discharge process is started, while the crankshaft (33) is covered during the discharge process.
- the oil is stored in communication with the sliding surface of the piston (26), and the oil is discharged into the compression chamber at the timing when the suction port (21a) is closed. This oil accumulates in the discharge port (21b) as the compression stroke proceeds. Therefore, when the compression mechanism (20) starts the compression process, the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25).
- the cylinder (21) of the compression mechanism (20) includes an oil reservoir (14) in the casing (10) and a cylinder chamber (25) of the compression mechanism (20).
- An oil introduction hole (47) that communicates with each other is formed.
- oil is introduced into the cylinder chamber (25) of the compression mechanism (20) from the oil reservoir (14) provided in the casing (10) through the oil introduction hole (47).
- the oil introduced into the cylinder chamber (25) is pushed into the discharge port (21b), which is the only destination, as the volume of the cylinder chamber (25) is reduced. Therefore, when the discharge process is finished and the next compression process starts, oil is in the discharge port (21b).
- the oil supply path (40) functions as an indirect path for oil supply (40B).
- the oil that has entered the discharge port (21b) at that time is introduced into the low-pressure cylinder chamber (25).
- the compression mechanism (20) includes a swing piston (26) in which a piston (26) and a blade (26b) are integrally formed.
- the suction port (21a) and the discharge port (21b) are composed of swing compressors arranged on both sides of the blade (26b), and the blade (26b) has the discharge port (21b) side.
- a slit (48) communicating from the back pressure chamber formed on the back surface of the blade (26b) to the cylinder chamber (25) is formed on the side surface of the blade (26b).
- oil is introduced from the back pressure chamber into the discharge port (21b) by the slit (48). Therefore, when the discharge process is finished and the next compression process starts, oil is in the discharge port (21b).
- the oil supply path (40) functions as an indirect path for oil supply (40B).
- the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25).
- the oil in the discharge port (21b) flows into the cylinder chamber (25) of the compression mechanism (20), and at this time, the expansion of the oil Does not happen. Therefore, the occurrence of pulsation due to re-expansion can be suppressed. Further, in the present invention, since oil is supplied to the discharge port (21b), it is possible to prevent an excessive amount of oil from being introduced into the cylinder chamber where the compression process has started. Furthermore, in this invention, in order to introduce oil into the discharge port (21b), it is only necessary to put oil into the discharge port (21b) between the middle of the discharge process and the start of the compression process, and supply it to the compression mechanism. Since the used lubricating oil can be used, the configuration can be simplified and the cost of the compressor can be reduced.
- the oil in the discharge port (21b) flows into the cylinder chamber (25), and the low-pressure cylinder chamber (25) Can suppress the occurrence of pulsation. It is also possible to prevent the amount of oil introduced into the cylinder chamber where the compression process has started from increasing too much. Furthermore, since the lubricating oil supplied to the compression mechanism can be used, the configuration can be simplified and the cost of the compressor can be reduced.
- the oil reservoir (14) to the discharge port (21b) of the compression mechanism (20) via the oil supply direct passage (40A). Since the supplied oil enters the cylinder chamber (25) at the start of the compression process of the compression mechanism (20), occurrence of pulsation due to re-expansion of the high-pressure gas is suppressed. Further, the configuration can be simplified as in the first to fourth inventions, and oil can be prevented from entering the cylinder chamber (25) too much.
- the oil stored in the oil reservoir (14) is agitated so that the refrigerant dissolved in the oil is foamed and separated from the oil, and the oil in which the refrigerant is hardly dissolved is discharged.
- Supply to port (21b) Therefore, the refrigerant flowing out from the discharge port (21b) to the cylinder chamber (25) at the start of the compression process is reduced, and the pulsation reducing effect can be enhanced.
- the concave portion (42) formed in the eccentric portion (33b) of the crankshaft (33) extends around the center of the crankshaft (33).
- the concave portion (42) communicates with the discharge port (21b) of the compression mechanism (20) within a certain angle range therebetween. Since oil is introduced into the recess (42), when the recess (42) and the discharge port (21b) communicate with each other, the oil is transferred from the recess (42) to the discharge port (21b). Inflow. Therefore, at the start of the compression process of the compression mechanism (20), the oil contained in the discharge port (21b) is introduced into the low-pressure cylinder chamber (25).
- the recess (42) into which the oil is introduced may be configured to communicate with the discharge port (21b), so that pulsation due to re-expansion of the high-pressure gas can be suppressed with a simple configuration. It becomes.
- the discharge port (21b) is formed so as to partially overlap the recess (42) in an angular range for supplying oil into the discharge port (21b).
- the concave portion (42) and the discharge port (21b) communicate with each other in the above-described angle range during the operation of the compression mechanism (20). Since oil is introduced into the recess (42), the oil flows from the recess (42) into the discharge port (21b). Therefore, when the compression mechanism (20) starts the compression process, the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25). Therefore, pulsation due to re-expansion of the high-pressure gas can be suppressed with a simple configuration in which the concave portion (42) is formed in the eccentric portion (33b) of the crankshaft (33).
- the discharge port (21b) is formed by a through hole formed at a position deviated radially outward from the turning track of the recess (42), and the end face of the piston (26) Has a notch (43) for communicating the discharge port (21b) and the recess (42) in an angle range for supplying oil to the inside of the discharge port (21b).
- the recess (42) turns around the center of the crankshaft (33) during the operation of 20)
- the recess (42) and the discharge port (21b) communicate with each other in the above-mentioned angular range. Since oil is introduced into the recess (42), the oil flows from the recess (42) into the discharge port (21b).
- the compression mechanism (20) starts the compression process
- the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25). Therefore, the pulsation caused by the re-expansion of the high-pressure gas forms a recess (42) in the eccentric portion (33b) of the crankshaft (33), and also when the oil is supplied into the discharge port (21b), the recess (42 ) And the discharge port (21b) can be suppressed with a simple configuration in which the cutout (43) communicates.
- the discharge port (21b) is formed by a through-hole formed at a position deviating radially outward from the turning track of the recess (42), and the discharge port (21b) Has a notch (44) that connects the discharge port (21b) and the recess (42) in an angle range for supplying oil to the inside of the discharge port (21b).
- the recess (42) turns around the center of the crankshaft (33) during the operation of)
- the recess (42) and the discharge port (21b) communicate with each other in the above-mentioned angle range. Since oil is introduced into the recess (42), the oil flows from the recess (42) into the discharge port (21b).
- the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25). Therefore, the pulsation caused by the re-expansion of the high-pressure gas is formed in the concave portion (42) in the eccentric portion (33b) of the crankshaft (33) and in the angular range in which oil is supplied into the discharge port (21b) 42) and the discharge port (21b) can be suppressed with a simple configuration in which only the notch (44) communicates.
- the recess (42) is formed only at one place in the circumferential direction, and oil is supplied to the inside of the discharge port (21b) of the compression mechanism (20). Since it is sufficient that the discharge port (21b) and the recess (42) communicate with each other within a range of angles, oil can be intermittently supplied to the discharge port (21b).
- the oil supply path (40) causes the compression mechanism (20) to move from the oil reservoir (14) provided in the casing (10). Oil is introduced into the interior (sliding surface and cylinder chamber (25)). This oil is intermittently pushed into the discharge port (21b) as the compression mechanism (20) operates. Therefore, when the discharge process is finished and the next compression process starts, oil is in the discharge port (21b). Thus, since oil is introduced into the discharge port (21b) through the inside of the compression mechanism (20), the oil supply path (40) functions as an indirect path for oil supply (40B).
- the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25). Therefore, pulsation due to re-expansion of the high-pressure gas can be suppressed with a simple configuration in which oil is introduced into the discharge port (21b) via the cylinder chamber (25).
- the oil stored in the oil reservoir (14) is agitated to foam the refrigerant dissolved in the oil and separate it from the oil, and discharge the oil in which the refrigerant is hardly dissolved.
- Supply to port (21b) Therefore, the refrigerant flowing out from the discharge port (21b) to the cylinder chamber (25) at the start of the compression process is reduced, and the pulsation reducing effect can be enhanced.
- the sliding surface of the compression mechanism (20) and the cylinder are defined by the communication groove (45) in a predetermined angle range between the compression process and the discharge process.
- oil is supplied from the sliding surface to the cylinder chamber (25). This oil is pushed into the discharge port (21b) as the volume of the cylinder chamber (25) decreases. Therefore, when the discharge process is finished and the next compression process starts, oil is in the discharge port (21b).
- the oil supply path (40) functions as an oil supply indirect path (40B).
- the oil that has entered the discharge port (21b) at that time is introduced into the low-pressure cylinder chamber (25). Accordingly, pulsation due to re-expansion of the high-pressure gas can be suppressed with a simple configuration in which oil is introduced into the cylinder chamber (25) using the communication groove (45).
- the oil supply path (40) causes the compression mechanism (20) to move from the oil reservoir (14) provided in the casing (10). Oil is introduced into the cylinder chamber (25), and the oil is stored in the oil storage recess (46). The oil in the oil reservoir recess (46) is pushed into the discharge port (21b), which is the only destination, as the volume of the cylinder chamber (25) is reduced. Therefore, when the discharge process is finished and the next compression process starts, oil is in the discharge port (21b). Thus, since oil is introduced into the discharge port (21b) via the cylinder chamber (25), the oil supply path (40) functions as an indirect path for oil supply (40B).
- the oil that has entered the discharge port (21b) at that time is introduced into the low-pressure cylinder chamber (25). Therefore, the pulsation due to re-expansion of the high-pressure gas can be suppressed with a simple configuration in which oil is introduced into the cylinder chamber (25) and the oil is stored in the oil reservoir.
- the oil released into the compression chamber at the timing when the suction port (21a) is closed is accumulated in the discharge port (21b) as the compression stroke proceeds, and the compression process of the compression mechanism (20) At the start, the oil currently contained in the discharge port (21b) is introduced into the low-pressure cylinder chamber (25). Therefore, pulsation due to re-expansion of the high-pressure gas can be suppressed.
- the oil introduction hole (47) causes the compression mechanism (20) from the oil reservoir (14) provided in the casing (10). Oil is introduced into the cylinder chamber (25). The oil introduced into the cylinder chamber (25) is pushed into the discharge port (21b), which is the only destination, as the volume of the cylinder chamber (25) is reduced. Therefore, when the discharge process is finished and the next compression process starts, oil is in the discharge port (21b). Thus, since oil is introduced into the discharge port (21b) via the cylinder chamber (25), the oil supply path (40) functions as an indirect path for oil supply (40B).
- the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25). Therefore, pulsation due to re-expansion of the high-pressure gas can be suppressed with a simple configuration in which oil is introduced into the cylinder chamber (25) through the oil introduction hole (47).
- the slit (48) introduces oil from the back pressure chamber to the discharge port (21b). Therefore, when the discharge process is finished and the next compression process starts, oil is in the discharge port (21b).
- the oil supply path (40) functions as an indirect path for oil supply (40B).
- the oil that has entered the discharge port (21b) at that time is introduced into the low-pressure cylinder chamber (25). Therefore, pulsation due to re-expansion of the high-pressure gas can be suppressed with a simple configuration in which oil is introduced into the discharge port (21b) by the slit (48).
- the oil is not directly introduced from the oil reservoir (14) into the cylinder chamber (25) after the suction is closed, but from the discharge port (21b) to the cylinder chamber ( 25) Since oil is introduced into the cylinder chamber, oil can be prevented from entering the cylinder chamber too much.
- FIG. 1 is a longitudinal sectional view of a rotary compressor according to Embodiment 1 of the present invention.
- 2A is a cross-sectional view of a main part of the rotary compressor of FIG. 1
- FIG. 2B is an internal structure diagram of the compression mechanism.
- FIG. 3 is a graph showing a change in pressure in the compression chamber that increases and decreases as the rotation angle of the piston changes, and a displacement amount of the discharge valve.
- 4A and 4B show a rotary compressor according to Modification 1 of Embodiment 1
- FIG. 4A is a longitudinal sectional view of a main part
- FIG. 4B is an internal structure diagram of a compression mechanism.
- FIG. 5 shows a rotary compressor according to Modification 2 of Embodiment 1
- FIG. 5 (A) is a longitudinal sectional view of an essential part
- FIG. 5 (B) is an internal structural view of a compression mechanism.
- 6A and 6B show a rotary compressor according to the second embodiment.
- FIG. 6A is a longitudinal sectional view of a main part
- FIG. 6B is an internal structure diagram of a compression mechanism.
- FIG. 7 shows a rotary compressor according to a modification of the second embodiment
- FIG. 7 (A) is a longitudinal sectional view of the main part
- FIG. 7 (B) is an internal structure diagram showing a first state of the compression mechanism
- 7 (C) is an internal structure diagram showing a second state of the compression mechanism.
- FIGS. 8A to 8H are cross-sectional views of the compression mechanism showing a state in which the piston is turning.
- FIG. 9A and 9B show a rotary compressor according to the third embodiment.
- FIG. 9A is a longitudinal sectional view of a main part
- FIG. 10A and 10B show a rotary compressor according to the fourth embodiment.
- FIG. 10A is a longitudinal sectional view of a main part
- FIG. 10B is an internal structure diagram of a compression mechanism.
- 11A and 11B show a rotary compressor according to the fifth embodiment, in which FIG. 11A is a vertical sectional view of a main part, and FIG. 11B is a bottom view showing a part of the compression mechanism.
- FIG. 1 is a longitudinal sectional view of a rotary compressor (1) according to a first embodiment.
- the compressor (1) performs a compression process for compressing a refrigerant in a vapor compression refrigeration cycle.
- the compressor (1) includes a vertically long cylindrical casing (10), and a compression mechanism (20) and a drive mechanism (30) disposed in the casing (10).
- the compression mechanism (20) is disposed at a lower position in the casing (10)
- the drive mechanism (30) is disposed at an upper position in the casing (10).
- the drive mechanism (30) is constituted by an electric motor for driving the compression mechanism (20).
- the casing (10) is a vertically long cylindrical body (11) whose upper and lower ends are open, and an upper end plate fixed to the body (11) so as to close the upper opening of the body (11). (12) and a lower end plate (13) fixed to the body (11) so as to close the lower opening of the body (11).
- An oil sump (14) for storing oil (refrigeration machine oil) is formed at the lower end of the casing (10).
- the oil level (15) of the oil sump (14) is set to such a height that the lower part of the compression mechanism (20) is immersed in the oil.
- the body (11) of the casing (10) is provided with a suction pipe (16) at a position corresponding to the compression mechanism (20) at a lower position. Further, the upper end plate (12) of the casing (10) is provided with a discharge pipe (17) at substantially the center position thereof along the axial center line of the casing (10).
- the compressor (1) includes a high-pressure dome type compressor (1) that discharges high-pressure gas discharged from the compression mechanism (20) to the outside of the casing (10) through a space in the casing (10). It is configured as.
- the electric motor (30) has a stator (31) and a rotor (32).
- the stator (31) includes a stator core (31a) formed into a cylindrical shape by laminating electromagnetic steel plates, and a coil (31b) wound around the stator core (31a).
- the outer peripheral surface of the stator core (31a) is welded or shrink-fitted to the body (11) at a position above the compression mechanism (20) in the body (11) of the casing (10). It is fixed.
- the rotor (32) includes a rotor core (32a) formed by laminating electromagnetic steel plates and a permanent magnet (32b) attached to the rotor core (32a).
- the rotor (32) is formed so that a uniform and fine radial gap (in the drawing, the gap is exaggerated) is formed between the outer peripheral surface and the inner peripheral surface of the stator (31). 31) is arranged on the inner circumference side.
- the drive shaft (33) (crankshaft) is fixed to the inner peripheral surface of the rotor (32).
- This drive shaft (33) is comprised from the main-shaft part (33a) and the eccentric part (33b) formed in the downward direction of the axial direction intermediate part of this main-shaft part (33a).
- the eccentric portion (33b) has a larger diameter than the main shaft portion (33a), and the center thereof is eccentric from the center of the main shaft portion (33a).
- the compression mechanism (20) is constituted by a swing type compression mechanism (20) which is a kind of a swing type compression mechanism.
- 2A is a longitudinal sectional view of the main part of the compressor (1), mainly showing a longitudinal sectional structure of the compression mechanism (20), and
- FIG. 2B is a plan view of the compression mechanism (20).
- the internal structure is shown.
- the compression mechanism (20) has a cylinder (21) having a cylinder chamber (25) and swivels inside the cylinder chamber (25) along the inner peripheral surface of the cylinder chamber (25). And a rocking piston (26) configured to be able to move.
- the cylinder (21) is fixed to the upper surface of FIG. 2 (A) with respect to the substantially annular cylinder body (22) fixed to the body (11) of the casing (10) and the cylinder body (22). And a rear head (24) fixed to the lower surface of FIG. 2 (A) with respect to the cylinder body (22).
- the front head (23) is fixed to the upper surface of the cylinder body (22) by a fastening member such as a bolt
- the rear head (24) is fixed to the lower surface of the cylinder body (22) by a fastening member such as a bolt.
- a space defined by the cylinder body (22), the front head (23), and the rear head (24) is the cylinder chamber (25).
- the eccentric portion (33b) of the drive shaft (33) is located inside the cylinder chamber (25).
- a swing piston (26) is attached to the eccentric part (33b).
- the swing piston (26) is slidably fitted to the outer periphery of the eccentric part (33b).
- the front head (23) and the rear head (24) are formed with bearing portions (23a, 24a) that rotatably support the main shaft portion (33a) of the drive shaft (33).
- the oscillating piston (26) has an outer peripheral surface of the oscillating piston (26) substantially connected to an inner peripheral surface of the cylinder chamber (25) via an oil film. It is configured to touch.
- the oscillating piston (26) includes an annular oscillating piston main body (26a) that fits in the eccentric portion (33b) of the drive shaft (33), and a radially outer portion from the oscillating piston main body (26a). And a blade (26b) projecting in the same direction.
- the cylinder body (22) is provided with a swinging bush (27) that holds the blade (26b) so as to be swingable.
- the swing bush (27) is a pair of members having a substantially semicircular cross section and a thickness similar to that of the cylinder body (22).
- a blade groove (27a) is formed between the flat surfaces of the pair of swing bushes (27), and the blade (26b) of the swing piston (26) is slidably held in the blade groove (27a).
- a back pressure chamber is formed on the outer side in the radial direction with respect to the bush holding recess (22a).
- the compression mechanism (20) swings the swinging bush (27) and moves the blade in the blade groove (27a) of the swinging bush (27).
- (26b) advances and retreats, and the oscillating piston (26) swivels along the inner peripheral surface of the cylinder chamber (25) in the cylinder chamber (25).
- the compression mechanism (20) is configured such that the swinging piston (26) is moved to the cylinder (21) while the blade (26b) is swung by the rotation of the drive shaft (33) having the eccentric portion (33b). It is comprised by the above-mentioned swing type compression mechanism (20) which carries out a turning motion in the inside.
- the suction port (21a) is formed in the cylinder body (22) of the cylinder (21), and the suction pipe (16) is connected to the suction port (21a). Further, a discharge port (21b) is formed in the front head (23) of the cylinder (21), and the lower surface side of the discharge port (21b) opens into the cylinder chamber (25).
- a discharge valve (28a) that is a reed valve and a valve presser (28b) for regulating the lift amount of the discharge valve are provided on the upper surface of the discharge port (21b).
- a discharge cover (29) discharge muffler
- a discharge recess (29a) is formed between the inner peripheral side end portion and the bearing portion (23a) of the front head (23).
- the oil pump (34) immersed in the oil reservoir (14) is provided at the lower end of the drive shaft (33).
- An oil supply passage (35) extending upward from the oil supply pump (34) along the center of the drive shaft (33) is formed in the drive shaft (33) as shown in FIG. Yes.
- the oil supply passage (35) is connected to the bearing portion (23a, 24a) and the drive shaft via a bearing portion oil supply passage (36) extending in the radial direction of the drive shaft (33) at positions on both the upper and lower sides of the eccentric portion (33b). Oil is supplied to the sliding surface with (33).
- the oil supply passage (35) is formed from the lower end of the drive shaft (33) upward through the center of the drive shaft (33).
- the oil supply passage (35) has a large-diameter oil supply passage (35a) formed in a region from the lower end of the drive shaft (33) to slightly above the eccentric portion (33b), and an upper end of the oil supply passage (35a). It is composed of a small-diameter gas vent passage (35b) formed in a region up to a position slightly above the upper end of the front head (23).
- a gas vent hole (35c) is formed at the upper end of the gas vent passage (35b), and the gas vent hole (35c) penetrates the drive shaft (33) in the radial direction.
- the compressor (1) includes an oil supply path (40) for supplying oil from an oil reservoir (14) provided in the casing (10) to the discharge port (21b).
- the oil supply path (40) is configured as an oil supply direct path (40A) that communicates directly from the oil reservoir (14) to the discharge port (21b).
- the oil supply path (40) is configured using the oil supply passage (35) of the drive shaft (33).
- the oil supply path (40) includes a radial oil supply hole (41a) that opens in the radial direction of the eccentric portion (33b) at a substantially vertical center of the eccentric portion (33b), and an eccentric portion of the drive shaft (33).
- An axial slit (41b) extending in the axial direction on the outer peripheral surface of (33b) is included.
- An annular groove (42) (concave portion) is formed in the eccentric portion (33b) so as to communicate with the axial slit (41b).
- the annular groove (42) is formed at both axial ends of the eccentric portion (33b).
- the annular groove (42) is originally for supplying oil to the sliding surfaces of the eccentric part (33b) and the swing piston (26).
- the discharge port (21b) is overlapped with the annular groove (42) during the turning operation of the annular groove (42) (concave portion) between the middle of the discharge process and the start of the compression process.
- the inner peripheral end is a region in the vicinity where the eccentric portion (33b) is located at the top dead center (region between the middle of the discharge process and the start of the compression process) Thus, it is formed so as to overlap with the annular groove (42) of the eccentric portion (33b).
- the range of the rotation angle at which the annular groove (42) and the discharge port (21b) overlap is 315 in the clockwise direction when the position of FIG.
- this angle range may be set in a range from near 330 ° to 20 °.
- This graph shows the pressure change in the compression chamber that increases and decreases as the rotation angle of the piston changes, and the displacement amount (valve displacement) of the discharge valve.
- the unit of pressure is MPa
- the unit of valve displacement is mm.
- the compression of the refrigerant starts when the suction port (21a) is closed during the rotation of the piston.
- the angle is 0 ° with respect to the position of FIG. 2B where the piston is at the top dead center. Then, the position is about 45 ° in the clockwise direction.
- “Port lubrication” indicates the compressor of this embodiment that supplies oil to the discharge port (21b)
- “Base machine” indicates conventional compression that does not perform port lubrication. Represents the machine.
- the pressure in the compression chamber (25) hardly changes until the rotation angle reaches about 90 °, and gradually gradually increases from about 90 ° to about 225 °.
- the pressure increases rapidly.
- the discharge valve (28a) starts to open at an angle of about 225 °, and immediately opens to the maximum lift amount at that pressure.
- the pressure in the compression chamber (25) decreases once, and the valve maintains a substantially constant lift amount until the rotation angle is just before 270 °.
- valve displacement gradually decreases, and during that period, the pressure in the compression chamber (25) is maintained at a substantially constant value, but eventually the angle at which the discharge valve (28a) is substantially closed (over 315 ° and 330 °). Near), the discharge process is substantially finished. And when a discharge valve (28a) is closed, the pressure of a compression chamber (25) will also fall rapidly.
- the lubricating oil stored in the bottom portion of the casing (10) is passed between the middle of the discharge process and the start of the compression process by the oil supply path (40) (piston of the piston).
- the inside of the discharge port (21b) is supplied at a rotation angle between 315 ° and 45 °.
- the above “middle of discharge process” indicates that the pressure in the compression chamber (25) has dropped from the peak value. Also, since the pressure in the discharge port (21b) is high immediately after the start of discharge, it is practically impossible to supply oil to the port even if an oil supply configuration is adopted, and then the discharge pressure peaks. When it starts to fall, oil begins to enter the discharge port (21b).
- the internal pressure of the discharge port (21b) is reduced to a conventional compressor that gradually decreases after the discharge ends and then rapidly decreases. In comparison, it shows a change that suddenly decreases after rising once.
- the discharge port (21b) is closed by the discharge valve (28a).
- the discharge port (21b) is closed by the discharge valve (28a).
- the piston passes through the discharge port (21b)
- oil is accumulated in the discharge port (21b). Therefore, oil is contained in the discharge port (21b) at the timing of the conventional refrigerant reexpansion that comes immediately after that.
- the refrigerant instead of the refrigerant flowing out into the compression chamber (25) and re-expanding within the angular range where the refrigerant re-expands in the conventional case, the refrigerant is discharged from the discharge port (21b) to the compression chamber (25). Oil spills. Since the oil does not expand, the oil spill does not induce pulsation.
- the oil supply path (40) is configured to supply the refrigerating machine oil to the inside of the discharge port (21b) between the middle of the discharge process and the start of the compression process.
- the piston is frozen to the discharge port (21b) only in a certain angle range from the middle of the discharge process to the start of the compression process.
- Machine oil is supplied intermittently. This is because the annular groove (42) formed in the eccentric part (33b) of the drive shaft (33) and the discharge port (21b) of the compression mechanism (20) are in the middle of the discharge process. This is because only the area until the start is intermittently communicated.
- the high-pressure refrigerant discharged from the cylinder chamber (25) fills the casing (10).
- the high-pressure refrigerant filled in the casing (10) flows out from the discharge pipe (17), passes through the condensation stroke, the expansion stroke, and the evaporation stroke when circulating through the refrigerant circuit, and is sucked into the compressor (1) again.
- a compression stroke is performed.
- the refrigerant circulates in the refrigerant circuit, whereby the vapor compression refrigeration cycle is performed.
- the refrigerating machine oil sucked up from the oil sump (14) by the oil supply pump (34) is supplied to the bearing portions (23a, 24a), and the drive shaft (33) and the bearing portion (23a , 24a) is suppressed from increasing, and is also supplied between the eccentric portion (33b) and the swing piston (26), and the increase in sliding resistance therebetween is suppressed.
- the oil pumped up by the oil supply pump (34) passes between the middle of the discharge process and the start of the compression process until the radial oil supply hole (41a) and the axial slit (41b) of the oil supply path (40). And is supplied to the discharge port (21b) through the annular groove (42) (concave portion) of the eccentric portion (33b).
- one cycle of operation in the compression mechanism (20) includes an intake process, a compression process, and a discharge process.
- the swing piston (26) is positioned slightly before the position near the top dead center shown in FIG. 2 (A), and at this time, the discharge port (21b) is discharged. Both ends are closed by the valve (28a) and the swing piston (26). Therefore, the discharge port (21b) becomes a sealed space, and the high-pressure refrigerant remains, resulting in a dead volume where the high-pressure refrigerant cannot be discharged. Therefore, as it is, the next time the compression process is started, the high-pressure refrigerant in the discharge port (21b) flows into the low-pressure cylinder chamber (25) and re-expands, resulting in pulsation.
- high-pressure refrigeration oil is supplied into the discharge port (21b) from the middle of the discharge process to the start of the compression process. This reduces the dead volume in the discharge port (21b).
- the refrigeration oil flows from the discharge port (21b) into the low-pressure cylinder chamber (25) when the next compression process starts. At that time, the refrigerating machine oil does not substantially expand unlike the refrigerant gas. Therefore, pulsation due to re-expansion can be suppressed.
- the high-pressure refrigerating machine oil is supplied into the discharge port (21b) from the middle of the discharge process to the start of the compression process.
- the pulsation of the compression mechanism (20) due to re-expansion of the high-pressure refrigerant can be suppressed. Therefore, vibration and noise generated by the re-expansion can be reduced. Further, vibration and noise are generated by re-expansion of the high-pressure gas remaining in the discharge port (21b) with a simple configuration for supplying oil to the discharge port (21b) using the oil supply passage (35). .
- the present embodiment since it is only necessary to shift the position of the discharge port (21b) radially inward, it is possible to suppress an increase in manufacturing cost compared to the conventional structure.
- the refrigeration oil is intermittently supplied to the discharge port (21b), the oil does not accumulate in the discharge port (21b). If the refrigerating machine oil accumulates too much in the discharge port (21b), the refrigerant discharge operation may be hindered. However, in this embodiment, the refrigerant enters the discharge port (21b) only intermittently. Absent. Moreover, since the oil is supplied into the discharge port (21b) from the middle of the discharge process to the start of the compression process, the oil supply amount is stabilized.
- the oil flowing through the oil supply passage (35) is foamed by being stirred in the oil supply passage (35), thereby reducing the solubility of the refrigerant in the oil. That is, since the operation can be performed in a state where the oil and the refrigerant are separated, it is possible to suppress a decrease in efficiency.
- the oil supply path (40) according to the first modification is provided on the upper end surface of the swing piston (26) between the discharge port (21b) and the eccentric portion between the middle of the discharge process and the start of the compression process.
- This is an example in which a notch (43) for communicating with the annular groove (42) of (33b) is formed.
- the discharge port (21b) is a front and rear region including the position where the swing piston (26) is at the top dead center, and the inner peripheral end thereof is an annular groove ( 42) It is formed at a position that does not directly overlap.
- the discharge port (21b) and the annular groove (42) of the eccentric part (33b) are formed when the swing piston (26) is at the top dead center and in the region before and after (at the middle of the discharge process) (Until the start of), the notch (43) communicates.
- the same effect as the example shown in FIG. 2 can be obtained, and the amount of oil supplied to the discharge port (21b) does not change even if the position of the discharge port (21b) is slightly shifted. Can be.
- the swing piston (26) can be formed by integral molding by sintering. Therefore, machining for forming the notch (43) is not necessary. Therefore, it is possible to suppress an increase in the number of machining steps and to suppress an increase in manufacturing cost.
- the oil supply path (40) according to the modified example 2 is connected to the discharge port (21b) between the discharge port (21b) and the eccentric portion (33b) between the middle of the discharge process and the start of the compression process.
- This is an example in which a notch (44) that communicates with the annular groove (42) is formed.
- the discharge port (21b) is a front and rear region including the position where the swing piston (26) is at the top dead center, and the inner peripheral end thereof is an annular groove ( 42) formed in a position that does not overlap.
- the discharge port (21b) and the annular groove (42) of the eccentric part (33b) are formed when the swing piston (26) is at the top dead center and in the region before and after (at the middle of the discharge process) (Until the start of), the notch (43) communicates.
- the oil is supplied into the discharge port (21b) from the middle of the discharge process to the start of the compression process, but the range is narrowed so that the discharge process is started from the middle of the discharge process. Oil may be supplied into the discharge port (21b) until the end. Even in this case, since the oil can be put into the discharge port (21b) after the discharge process is completed, the occurrence of pulsation due to re-expansion of the refrigerant gas when the next compression process starts can be suppressed.
- the oil is supplied into the discharge port (21b) from the middle of the discharge process to the start of the compression process. Oil may be supplied into the discharge port (21b) before the start of the process. Even in this case, since oil can be put into the discharge port (21b) before the compression process starts, the occurrence of pulsation due to re-expansion of the refrigerant gas when the next compression process starts can be suppressed.
- Embodiment 2 of the Invention A second embodiment of the present invention will be described.
- the oil supply path (40) is configured so that the refrigerating machine oil is discharged from the oil reservoir (14) of the casing (10) to the discharge port (21b
- the oil supply path (40) is configured so that the refrigerating machine oil is once accumulated in the cylinder chamber (25) and then supplied to the discharge port (21b). is doing. That is, in the second embodiment, the oil supply path (40) is an oil supply indirect path for indirectly supplying the refrigerating machine oil in the oil reservoir (14) to the discharge port (21b) via the cylinder chamber (25). (40B).
- the oil supply path (40) includes a communication groove (45) formed in the cylinder chamber (25).
- the communication groove (45) is formed on the inner surface side of the cylinder chamber (25) in the rear head (24).
- the communication groove (45) is formed by a radial groove extending in the radial direction of the cylinder chamber (25). This communication groove (45) is used while the rotation angle of the upper swing piston (26) is in an angle range from the start of the compression process to the end of the discharge process (a predetermined angle range between the compression process and the discharge process).
- the thickness of the oscillating piston body (26a) so that a passage can be formed across the cylinder chamber (25) from the sliding surface between the eccentric part (33b) of the drive shaft (33) and the oscillating piston (26). It is formed by a groove slightly longer than the dimension.
- the compression mechanism (20) when the compression mechanism (20) is operated, the refrigerant is sucked into the cylinder chamber (25) from the suction port (21a), and the swing piston (26) is moved along the inner surface of the cylinder chamber (25). It is compressed by the swiveling motion. The compressed high-pressure refrigerant is discharged from the discharge port (21b) to the space in the casing (10). The above suction process, compression process, and discharge process are repeated.
- refrigeration oil is introduced from the oil reservoir (14) of the casing (10) to the sliding surface between the eccentric part (33b) and the swing piston (26).
- the refrigerating machine oil flows out from the sliding surface to the cylinder chamber through the communication groove (45) in an angular range from the start of the compression process to the end of the discharge process.
- the volume on the discharge side of the cylinder chamber (25) decreases, during the period from the middle of the discharge process to the start of the compression process (within the angle range in which oil is supplied into the discharge port (21b)) ), Refrigeration oil flows into the discharge port (21b).
- the refrigeration oil contained in the discharge port (21b) flows out into the compression chamber (25), so that the high-pressure refrigerant hardly re-expands and the pulsation caused by it is reduced. Is done. Therefore, the vibration and noise of the compressor are reduced.
- the degree of freedom in designing the rotation angle when refueling is increased, so that it is possible to easily refuel at the optimum timing.
- the oil supply passage is not always open to the cylinder chamber (25), so that excessive oil can be prevented from entering the cylinder chamber (25) in order to prevent re-expansion.
- the oil supply path (40) of the compression mechanism (20) is oil formed in the cylinder chamber (25).
- a storage recess (46) is included.
- the oil storage recess (46) is formed on the inner surface side of the cylinder chamber (25) in the rear head (24).
- the oil storage recess (46) is formed in the cylinder (21) of the compression mechanism (20) at a position away from the discharge port (21b).
- the oil storage recess (46) is formed by a circular recess.
- the degree of freedom in designing the rotation angle when refueling is increased, so that it is possible to easily refuel at the optimum timing.
- the oil supply passage is not always open to the cylinder chamber (25), so that excessive oil can be prevented from entering the cylinder chamber (25) in order to prevent re-expansion.
- the amount of oil supply per rotation can be made constant. Therefore, even if the rotation speed changes, the dead volume of the discharge port (21b) can be filled with an appropriate amount of oil supply.
- FIG. 8 shows a state in which the piston is turning in the order of (A) ⁇ (B) ⁇ (C) ⁇ (D) ⁇ (E) ⁇ (F) ⁇ (G) ⁇ (H) ⁇ (A). It is sectional drawing of a compression mechanism (20), and has shown the state which the rocking
- the oil storage recess (46) is formed at a position that is opened and closed by the swing piston (26) on the axial end surface of the cylinder chamber (25). Specifically, the oil reservoir recess (46) is opened from the end face of the swing piston (26) at the timing of FIG. 8B when the suction port (21a) is closed, and immediately before the discharge process is started. The end face of the swing piston (26) is covered at the timing of FIG. 8E, and the sliding surface of the crankshaft (33) and the swing piston (26) at the timing of FIG. 8G during the discharge process. It is formed in a communicating position.
- the oil storage recess (46) When the position of the oil storage recess (46) is specified in this way, the oil storage recess (46) is covered by the end face of the piston (26) at the timing of FIG. 8 (E) immediately before the discharge process is started.
- the storage recess (46) communicates with the sliding surfaces of the crankshaft (33) and the piston (26) during the discharging process of FIG. 8 (G). Then, oil is stored in the oil storage recess (46), and the oil is discharged to the compression chamber (25) at the timing when the suction port (21a) is closed. This oil is accumulated in the discharge port (21b) until the next compression process starts after the compression process and further through the discharge process.
- the oil that has entered the discharge port (21b) at that time is introduced into the low-pressure cylinder chamber (25).
- the oil released into the compression chamber (25) at the timing when the suction port (21a) is closed is accumulated in the discharge port (21b) until the next compression process starts, and at the start of the compression process
- the oil contained in the discharge port (21b) at the end of the discharge process is introduced into the low-pressure cylinder chamber (25). Therefore, pulsation due to re-expansion of the high-pressure gas can be suppressed.
- Embodiment 3 of the Invention >> Embodiment 3 of the present invention will be described.
- Embodiment 3 as shown in FIGS. 9 (A) and 9 (B), the configuration of the oil supply path (40) is different from the examples of FIGS.
- the cylinder (21) is provided with an oil introduction hole (47) for communicating the oil reservoir (14) in the casing (10) and the cylinder chamber (25) of the compression mechanism (20). Yes.
- the oil accumulated in the oil sump (14) enters the cylinder chamber (25) through the oil introduction hole (47), and further in the middle of the discharge process.
- the introduction of oil from the oil introduction hole (47) into the cylinder chamber (25) is performed when the oil introduction hole (47) is intermittently opened during the operation of the swing piston (26). Since the oil enters the discharge port (21b) at the start of the compression process, the discharge port (21b) is dead as compared with the case where no oil is introduced into the discharge port (21b). The volume becomes smaller. Therefore, as in the above embodiments, the occurrence of vibration and noise due to re-expansion of the high-pressure refrigerant can be suppressed.
- the degree of freedom in designing the rotation angle for refueling is high, so that it is possible to refuel at an optimal timing.
- Embodiment 4 of the Invention >> Embodiment 4 of the present invention will be described.
- the compression mechanism (20) is constituted by a swing compressor (1) in which a piston and a blade (26b) are integrally formed.
- the blade (26b) is formed with a slit (48) communicating with the cylinder chamber (25) from the back pressure chamber on the back surface of the blade (26b) on the side surface on the discharge port (21b) side. .
- the slit (48) is formed on the lower end surface of the blade (26b).
- the oil level (15) of the oil sump (14) is set to a height at which the slit (48) is immersed.
- the slit (48) communicates with the cylinder chamber (25) when the swing piston (26) is located near the bottom dead center as shown in FIG. 10 (B). That is, the slit (48) intermittently communicates with the cylinder chamber (25) during the operation of the swing piston (26).
- oil in the oil sump (14) passes through the slit (48) and enters the cylinder chamber (25). Is introduced into the discharge port (21b) until the start of the operation. Since the oil enters the discharge port (21b) when the compression process starts, the dead volume of the discharge port (21b) is smaller than when no oil is introduced into the discharge port (21b). Become. Therefore, as in the above embodiments, the occurrence of vibration and noise due to re-expansion can be suppressed.
- the slit (48) communicates with the cylinder chamber (25) intermittently, it is possible to prevent oil from entering the discharge port (21b) too much.
- the slit (48) is formed along the lower end of the blade (26b), but the slit (48) is at a position that bisects the blade (26b) in the height direction.
- the blade (26) may be formed in parallel with the end face.
- the amount of oil in the oil sump (14) may be set so that the oil level is higher than in the above embodiments.
- the slit (48) should be formed along the lower end of the blade (28b) rather than at the center of the blade (28b) in the height direction. Since oil can be introduced into the discharge port (21b) even when the pressure becomes low, vibration and noise due to re-expansion can be more reliably suppressed.
- Embodiment 5 of the Invention >> Embodiment 5 of the present invention will be described.
- the oil stored in the oil reservoir (14) at the lower end of the crankshaft (33) is rotated by the compression mechanism (20).
- This is an example in which an oil agitation mechanism (50) for agitation in conjunction with is provided.
- an oil stirring member (50) is attached to the lower end of the crankshaft (33), and has a stirring blade (52) at the lower end.
- the stirring member (50) is formed by processing a metal plate having a thickness of about 1.6 mm.
- the stirring member (50) of this embodiment may be applied to any of the above embodiments 1 to 4 and modifications.
- the oil stored in the oil reservoir (14) is stirred by the stirring blade (52), so that the refrigerant dissolved in the oil is foamed and separated from the refrigerating machine oil. Therefore, the oil into which the refrigerant is hardly dissolved is supplied to the discharge port (21b) of the compression mechanism (20). Therefore, the refrigerant flowing out from the discharge port (21b) to the cylinder chamber (25) at the start of the compression process is reduced, and the pulsation reducing effect can be enhanced.
- the centrifugal force acts on the refrigeration oil that rises in the oil supply passage (35a)
- the refrigeration oil is compressed through the radial oil supply hole (41a) and the axial slit (41b) by the action of the centrifugal force. Supplied to the mechanism (20).
- the refrigerant separated from the oil also rises in the oil supply passage (35a).
- the gas refrigerant is light, so it is not affected by centrifugal force and gathers in the center.
- Embodiments 1 to 3 show examples in which the present invention is applied to a compressor (1) provided with a swing type compression mechanism (20), but the oil supply path (40) of Embodiment 1 is a cylinder.
- a rolling piston type compression mechanism (20) is provided in which a cylindrical piston and a plate-like blade (26b) are formed of separate members, and the radially inner end of the blade (26b) is pressed against the outer peripheral surface of the piston. You may apply to a compressor (1).
- the communication groove (45) in FIG. 6 and the oil storage recess (46) in FIG. 7 may be provided in the front head.
- a reed valve is used as the discharge valve (28a).
- the discharge valve (28a) is not limited to the reed valve, and a poppet valve is used instead of the reed valve. It is also possible.
- Embodiments 2 to 5 refrigeration oil is supplied to the discharge port (21b) from the middle of the discharge process to the start of the compression process, and when the next compression process starts, the discharge port (21b) refrigerant flows out to the compression chamber (25), but the refrigerant is supplied to the discharge port (21b) from the middle of the discharge process until the discharge process is completed, or the discharge process. It may be performed between the end of the process and the start of the compression process. Even if it does in this way, since oil is supplied to a discharge port by the time of a compression process, generation
- the present invention allows the high-pressure gas remaining in the discharge port (21b) of the compression mechanism (20) that compresses gas in the cylinder chamber (25) to flow into the cylinder chamber (25 It is useful for a technique for reducing vibration and noise generated by re-expanding the inside.
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Abstract
Description
図1は、実施形態1に係る回転式圧縮機(1)の縦断面図である。この圧縮機(1)は、蒸気圧縮式冷凍サイクルにおいて冷媒を圧縮する圧縮行程を行うものである。図示するように、この圧縮機(1)は、縦長円筒状のケーシング(10)と、このケーシング(10)内に配置された圧縮機構(20)と駆動機構(30)とを備えている。上記圧縮機構(20)は、ケーシング(10)内の下方の位置に配置され、上記駆動機構(30)はケーシング(10)内の上方の位置に配置されている。上記駆動機構(30)は、圧縮機構(20)を駆動するための電動機により構成されている。
次に、この回転式圧縮機(1)の運転動作について説明する。
以上説明したように、この実施形態1によれば、上記吐出過程の途中から上記圧縮過程の開始までの間に、吐出ポート(21b)内に高圧の冷凍機油を供給するようにしているので、高圧冷媒の再膨張による圧縮機構(20)の脈動を抑えることができる。したがって、上記再膨張により発生する振動や騒音を低減することができる。そして、吐出ポート(21b)内に残る高圧ガスの再膨張によって振動や騒音が発生するのを、給油通路(35)を利用して吐出ポート(21b)に油を供給する簡単な構成で実現できる。しかも、本実施形態では、吐出ポート(21b)の位置を径方向内側へずらすだけでよいので、従来構造のものと比べて製造コストが高くなるのも抑えられる。
(変形例1)
実施形態1の第1の変形例は、図4(A),図4(B)に示すように、油供給経路(40)の構成を図1,図2の例とは異なるようにしたものである。
実施形態1の第2の変形例は、図5(A),図5(B)に示すように、油供給経路(400)の構成を図1~図4の例とは異なるようにしたものである。
上記実施形態では、吐出過程の途中から上記圧縮過程の開始までの間に吐出ポート(21b)内へ油を供給するようにしているが、その範囲を狭めて、吐出過程の途中から吐出過程の終了までの間に吐出ポート(21b)内へ油を供給するようにしてもよい。このようにしても、吐出過程が終わった状態で吐出ポート(21b)に油を入れておけるので、次の圧縮過程が開始するときの冷媒ガスの再膨張による脈動の発生を抑えることができる。
また、上記実施形態では、吐出過程の途中から上記圧縮過程の開始までの間に吐出ポート(21b)内へ油を供給するようにしているが、その範囲を狭めて、吐出過程の終了から圧縮過程の開始までの間に吐出ポート(21b)内へ油を供給するようにしてもよい。このようにしても、圧縮過程が始まるまでには吐出ポート(21b)に油を入れておけるので、次の圧縮過程が開始するときの冷媒ガスの再膨張による脈動の発生を抑えることができる。
本発明の実施形態2について説明する。
実施形態2の変形例は、油供給経路(40)を図6の例とは異なるようにしたものである。
このように、吸入ポート(21a)が閉じ切られるタイミングで圧縮室(25)に放出される油が、次の圧縮過程が始まるまでの間に吐出ポート(21b)に溜まり、その圧縮過程開始時には、吐出過程終了時点で吐出ポート(21b)内に入っている油が低圧のシリンダ室(25)へ導入される。したがって、高圧ガスの再膨張による脈動を抑えることが可能となる。
凹部径<(ピストン外径-ピストン内径)/2
半径位置=(ピストン外径+ピストン内径)/4
角度範囲=190°~310°
の条件を満たす位置に形成される。
本発明の実施形態3について説明する。
本発明の実施形態4について説明する。
本発明の実施形態5について説明する。
上記実施形態については、以下のような構成としてもよい。
油が供給されるので、冷媒ガスの再膨張による脈動の発生を抑えることができる。
10 ケーシング
14 油溜まり
20 圧縮機構
21 シリンダ
21b 吐出ポート
25 シリンダ室
26 ピストン
33 クランク軸
33b 偏心部
40 油供給経路
40A 油供給用直通経路
40B 油供給用間接経路
42 凹部
43 切り欠き
44 切り欠き
45 連通溝
46 油貯留凹部
47 貫通孔
48 スリット
Claims (17)
- ケーシング(10)と、該ケーシング(10)内に設けられてシリンダ室(25)でガスを圧縮する圧縮機構(20)とを備え、該圧縮機構(20)には、吐出過程中に開放される一方で該吐出過程の終了時から次の圧縮過程の間に閉鎖される吐出弁(28a)が装着された吐出ポート(21b)が設けられ、該吐出ポート(21b)から吐出過程中に吐出された高圧ガスがケーシング(10)内の空間を介して該ケーシング(10)の外部へ吐出される高圧ドーム式の回転式圧縮機であって、
上記ケーシング(10)の底部に貯留する潤滑油を、上記吐出過程の途中から上記圧縮過程の開始の間に、上記吐出ポート(21b)の内部へを供給する油供給経路(40)を備えていることを特徴とする回転式圧縮機。 - 請求項1において、
上記油供給経路(40)は、上記吐出過程の途中から吐出過程の終了までの間に上記吐出ポート(21b)の内部へ油を供給するように構成されていることを特徴とする回転式圧縮機。 - 請求項1において、
上記油供給経路(40)は、上記吐出過程の終了から圧縮過程の開始の間に上記吐出ポート(21b)の内部へ油を供給するように構成されていることを特徴とする回転式圧縮機。 - 請求項1において、
上記圧縮機構(20)の動作の1サイクルが360°の回転動作により行われるように構成され、
上記圧縮機構(20)における吐出過程の終了位置と圧縮過程の開始位置の間の位置を回転動作の基準位置とし、その基準位置の回転角度を0°とすると、
上記油供給経路(40)は、回転角度が315°と45°の間の範囲で上記吐出ポート(21b)の内部へ油を供給するように構成されていることを特徴とする回転式圧縮機。 - 請求項1から4の何れか1つにおいて、
上記油供給経路(40)は、上記ケーシング(10)内に設けられている油溜まり(14)から上記吐出ポート(21b)へ油を供給するように該油溜まり(14)と吐出ポート(21b)に連通する油供給用直通経路(40A)を備えていることを特徴とする回転式圧縮機。 - 請求項5において、
上記油溜まりに貯留した油を上記圧縮機構の回転動作に連動して撹拌する油撹拌機構(50)が設けられていることを特徴とする回転式圧縮機。 - 請求項1において、
上記圧縮機構(20)は、偏心部(33b)を有するクランク軸(33)の回転動作によりピストン(26)がシリンダ(21)内で上記シリンダ室(25)の内周面に沿って旋回運動をする旋回式圧縮機構(20)により構成され、
上記油供給経路(40)は、上記クランク軸(33)の偏心部(33b)に形成されるとともに油が導入される凹部(42)を備え、上記吐出ポート(21b)の内部へ油を供給する角度範囲で、該凹部(42)が上記圧縮機構(20)の吐出ポート(21b)と連通するように構成されていることを特徴とする回転式圧縮機。 - 請求項7において、
上記吐出ポート(21b)は、上記吐出ポート(21b)の内部へ油を供給する角度範囲で上記凹部(42)と一部分が重なる位置に上記圧縮機構(20)に形成された貫通孔により構成されていることを特徴とする回転式圧縮機。 - 請求項7において、
上記吐出ポート(21b)は、上記凹部(42)の旋回軌道から径方向外側へ外れた位置に形成された貫通孔により形成され、
上記ピストン(26)の端面には、上記吐出ポート(21b)と上記凹部(42)とを上記吐出ポート(21b)の内部へ油を供給する角度範囲で連通させる切り欠き(43)が形成されていることを特徴とする回転式圧縮機。 - 請求項7において、
上記吐出ポート(21b)は、上記凹部(42)の旋回軌道から径方向外側へ外れた位置に形成された貫通孔により形成され、
上記吐出ポート(21b)には、該吐出ポート(21b)と上記凹部(42)とを上記吐出ポート(21b)の内部へ油を供給する角度範囲で連通させる切り欠き(44)が形成されていることを特徴とする回転式圧縮機。 - 請求項1から4の何れか1つにおいて、
上記油供給経路(40)は、上記ケーシング(10)内に設けられている油溜まり(14)から圧縮機構(20)の内部を介して上記吐出ポート(21b)へ油を供給する油供給用間接経路(40B)を備えていることを特徴とする回転式圧縮機。 - 請求項11において、
上記油溜まり(14)に貯留した油を、上記圧縮機構(20)の回転動作に連動して撹拌する油撹拌機構(50)が設けられていることを特徴とする回転式圧縮機。 - 請求項11において、
上記圧縮機構(20)は、該圧縮機構(20)の摺動面に供給される油を、圧縮過程から吐出過程の間の所定の角度範囲で上記シリンダ室(25)に導入するように、該角度範囲で一端が上記摺動面側に開口するとともに他端がシリンダ室(25)に開口する連通溝(45)を備えていることを特徴とする回転式圧縮機。 - 請求項11において、
上記圧縮機構(20)は、上記油溜まり(14)からシリンダ室(25)へ導入された油を一時的に貯留するようにシリンダ室(25)の内壁面に形成された油貯留凹部(46)を備えていることを特徴とする回転式圧縮機。 - 請求項14において、
上記圧縮機構(20)は、偏心部(33b)を有するクランク軸(33)の回転動作によりピストン(26)がシリンダ(21)内で上記シリンダ室(25)の内周面に沿って旋回運動をするとともに、吸入ポート(21a)と吐出ポート(21b)を有する旋回式圧縮機構(20)により構成され、
上記油貯留凹部(46)は、上記シリンダ室(25)の軸方向端面においてピストン(26)で開閉される位置に形成されるとともに、吐出過程終了から圧縮過程開始のタイミングでピストン(26)の端面から開放され、吐出過程が開始される前にピストン(26)の端面に覆われ、吐出過程中に上記クランク軸(33)とピストン(26)の摺動面と連通するように構成されていることを特徴とする回転式圧縮機。 - 請求項11において、
上記圧縮機構(20)のシリンダ(21)には、ケーシング(10)内の油溜まり(14)と圧縮機構(20)のシリンダ室(25)とを連通する油導入孔(47)が形成されていることを特徴とする回転式圧縮機。 - 請求項11において、
上記圧縮機構(20)は、ピストン(26)とブレード(26b)とが一体的に形成された揺動ピストン(26)を有し、圧縮機構(20)の吸入ポート(21a)と吐出ポート(21b)が該ブレード(26b)を挟んで両側に配置されたスイング圧縮機により構成され、
上記ブレード(26b)には、上記吐出ポート(21b)側の側面に、該ブレード(26b)の背面に形成される背圧室からシリンダ室(25)へ連通するスリット(48)が形成されていることを特徴とする回転式圧縮機。
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
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KR1020117026225A KR101320196B1 (ko) | 2009-06-16 | 2010-06-15 | 회전식 압축기 |
EP10789218.4A EP2444672B1 (en) | 2009-06-16 | 2010-06-15 | Rotary compressor |
ES10789218T ES2725791T3 (es) | 2009-06-16 | 2010-06-15 | Compresor rotativo |
US13/378,579 US9512842B2 (en) | 2009-06-16 | 2010-06-15 | Rotary compressor |
CN201080026468.8A CN102459910B (zh) | 2009-06-16 | 2010-06-15 | 回转式压缩机 |
AU2010261248A AU2010261248B2 (en) | 2009-06-16 | 2010-06-15 | Rotary compressor |
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US (1) | US9512842B2 (ja) |
EP (1) | EP2444672B1 (ja) |
JP (2) | JP4683158B2 (ja) |
KR (1) | KR101320196B1 (ja) |
CN (1) | CN102459910B (ja) |
AU (1) | AU2010261248B2 (ja) |
ES (1) | ES2725791T3 (ja) |
TR (1) | TR201905911T4 (ja) |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012220874A (ja) * | 2011-04-13 | 2012-11-12 | Nikon Corp | 撮像装置およびプログラム |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2014055534A (ja) * | 2012-09-11 | 2014-03-27 | Daikin Ind Ltd | 回転式圧縮機 |
JP2015068303A (ja) * | 2013-09-30 | 2015-04-13 | ダイキン工業株式会社 | 回転式圧縮機 |
CN103867450B (zh) * | 2014-03-26 | 2017-03-29 | 安徽美芝精密制造有限公司 | 旋转式压缩机 |
KR20160001467A (ko) * | 2014-06-27 | 2016-01-06 | 엘지전자 주식회사 | 압축기 |
CN105156154B (zh) * | 2014-09-29 | 2018-12-04 | 摩尔动力(北京)技术股份有限公司 | 摆动滑动机构 |
CN106050662B (zh) * | 2016-07-08 | 2019-04-26 | 珠海格力电器股份有限公司 | 泵体组件及具有其的压缩机 |
JP6489173B2 (ja) * | 2017-08-09 | 2019-03-27 | ダイキン工業株式会社 | ロータリ圧縮機 |
Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5862193U (ja) * | 1981-10-20 | 1983-04-26 | 松下冷機株式会社 | 回転式圧縮機 |
JPS6397895A (ja) * | 1986-10-09 | 1988-04-28 | Daikin Ind Ltd | ヘリウム圧縮機 |
JPH01124092U (ja) * | 1988-02-15 | 1989-08-23 | ||
JPH0250087U (ja) * | 1988-09-27 | 1990-04-06 | ||
JPH06167287A (ja) * | 1992-12-01 | 1994-06-14 | Hitachi Ltd | ロータリ圧縮機 |
JPH06346878A (ja) * | 1993-06-04 | 1994-12-20 | Hitachi Ltd | ロータリ圧縮機 |
JPH08219051A (ja) | 1995-02-17 | 1996-08-27 | Daikin Ind Ltd | 回転式圧縮機 |
JPH08219070A (ja) * | 1995-02-09 | 1996-08-27 | Daikin Ind Ltd | 冷媒圧縮機 |
JPH08219069A (ja) * | 1995-02-20 | 1996-08-27 | Daikin Ind Ltd | 密閉形圧縮機 |
JP2005113766A (ja) * | 2003-10-07 | 2005-04-28 | Matsushita Electric Ind Co Ltd | 回転式電動圧縮機 |
JP2005139973A (ja) * | 2003-11-05 | 2005-06-02 | Sanyo Electric Co Ltd | 多段圧縮式ロータリ圧縮機 |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5854274B2 (ja) * | 1978-10-24 | 1983-12-03 | 株式会社東芝 | 密閉形回転圧縮機 |
JPS55104591A (en) * | 1979-02-06 | 1980-08-11 | Toshiba Corp | Rotary compressor |
JPS55176496U (ja) * | 1979-06-04 | 1980-12-18 | ||
JPS6361589U (ja) * | 1986-10-09 | 1988-04-23 | ||
JP2604835B2 (ja) * | 1988-11-11 | 1997-04-30 | 松下冷機株式会社 | 回転式圧縮機 |
JPH0674170A (ja) * | 1992-08-26 | 1994-03-15 | Matsushita Refrig Co Ltd | ローリングピストン型ロータリー圧縮機 |
SA94140669B1 (ar) * | 1993-04-27 | 2006-03-01 | كارير كوربوريشن | ضاغط دوار مع حقن للزيت |
US6826926B2 (en) * | 2002-01-07 | 2004-12-07 | Carrier Corporation | Liquid injection for reduced discharge pressure pulsation in compressors |
JP4385565B2 (ja) * | 2002-03-18 | 2009-12-16 | ダイキン工業株式会社 | 回転式圧縮機 |
EP1520990B1 (en) | 2003-09-30 | 2010-06-23 | SANYO ELECTRIC Co., Ltd. | Rotary compressor |
KR20070074300A (ko) * | 2006-01-09 | 2007-07-12 | 삼성전자주식회사 | 회전압축기 |
-
2010
- 2010-06-15 TR TR2019/05911T patent/TR201905911T4/tr unknown
- 2010-06-15 ES ES10789218T patent/ES2725791T3/es active Active
- 2010-06-15 CN CN201080026468.8A patent/CN102459910B/zh active Active
- 2010-06-15 AU AU2010261248A patent/AU2010261248B2/en active Active
- 2010-06-15 JP JP2010135745A patent/JP4683158B2/ja active Active
- 2010-06-15 KR KR1020117026225A patent/KR101320196B1/ko active IP Right Grant
- 2010-06-15 WO PCT/JP2010/003972 patent/WO2010146837A1/ja active Application Filing
- 2010-06-15 US US13/378,579 patent/US9512842B2/en active Active
- 2010-06-15 EP EP10789218.4A patent/EP2444672B1/en active Active
- 2010-09-21 JP JP2010210888A patent/JP5370322B2/ja active Active
Patent Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5862193U (ja) * | 1981-10-20 | 1983-04-26 | 松下冷機株式会社 | 回転式圧縮機 |
JPS6397895A (ja) * | 1986-10-09 | 1988-04-28 | Daikin Ind Ltd | ヘリウム圧縮機 |
JPH01124092U (ja) * | 1988-02-15 | 1989-08-23 | ||
JPH0250087U (ja) * | 1988-09-27 | 1990-04-06 | ||
JPH06167287A (ja) * | 1992-12-01 | 1994-06-14 | Hitachi Ltd | ロータリ圧縮機 |
JPH06346878A (ja) * | 1993-06-04 | 1994-12-20 | Hitachi Ltd | ロータリ圧縮機 |
JPH08219070A (ja) * | 1995-02-09 | 1996-08-27 | Daikin Ind Ltd | 冷媒圧縮機 |
JPH08219051A (ja) | 1995-02-17 | 1996-08-27 | Daikin Ind Ltd | 回転式圧縮機 |
JPH08219069A (ja) * | 1995-02-20 | 1996-08-27 | Daikin Ind Ltd | 密閉形圧縮機 |
JP2005113766A (ja) * | 2003-10-07 | 2005-04-28 | Matsushita Electric Ind Co Ltd | 回転式電動圧縮機 |
JP2005139973A (ja) * | 2003-11-05 | 2005-06-02 | Sanyo Electric Co Ltd | 多段圧縮式ロータリ圧縮機 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012220874A (ja) * | 2011-04-13 | 2012-11-12 | Nikon Corp | 撮像装置およびプログラム |
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CN102459910B (zh) | 2015-03-11 |
ES2725791T3 (es) | 2019-09-27 |
JP2011021598A (ja) | 2011-02-03 |
TR201905911T4 (tr) | 2019-05-21 |
CN102459910A (zh) | 2012-05-16 |
EP2444672A1 (en) | 2012-04-25 |
AU2010261248B2 (en) | 2014-03-06 |
US20120087819A1 (en) | 2012-04-12 |
EP2444672A4 (en) | 2015-04-29 |
JP2011021608A (ja) | 2011-02-03 |
US9512842B2 (en) | 2016-12-06 |
AU2010261248A1 (en) | 2012-01-12 |
JP4683158B2 (ja) | 2011-05-11 |
KR20120011028A (ko) | 2012-02-06 |
KR101320196B1 (ko) | 2013-10-23 |
EP2444672B1 (en) | 2019-02-13 |
JP5370322B2 (ja) | 2013-12-18 |
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