WO2010131328A1 - Two-stage compressor and refrigeration air-conditioner - Google Patents
Two-stage compressor and refrigeration air-conditioner Download PDFInfo
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- WO2010131328A1 WO2010131328A1 PCT/JP2009/058830 JP2009058830W WO2010131328A1 WO 2010131328 A1 WO2010131328 A1 WO 2010131328A1 JP 2009058830 W JP2009058830 W JP 2009058830W WO 2010131328 A1 WO2010131328 A1 WO 2010131328A1
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- pressure
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- refrigerant
- stage compression
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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
- F04C23/001—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 of similar working principle
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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
- F04C18/34—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
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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
- F04C29/028—Means for improving or restricting lubricant flow
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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
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
- F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
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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
Definitions
- the present invention relates to, for example, a two-stage compressor including a compression unit in a sealed container, and a refrigeration air conditioner including the two-stage compressor.
- a rotary compressor is widely used for a refrigerator-freezer, an air conditioner, a heat pump hot water heater, and the like because it can be downsized and has a simple structure.
- a two-stage rotary compressor provided with two compression sections (a low-stage compression section and a high-stage compression section) in the compressor has an advantage that the differential pressure per stage is small and the leakage loss is small.
- the two-stage rotary compressor has an advantage that the performance can be improved by injecting the refrigerant into the intermediate flow path connecting the low-stage compression section and the high-stage compression section.
- hydrocarbon (HC) refrigerant that has excellent refrigerant characteristics.
- Hydrocarbons have refrigerant characteristics equivalent to those of chlorofluorocarbon refrigerants from the viewpoint of sliding portion lubrication performance, leakage seal performance, and theoretical refrigeration cycle COP.
- hydrocarbons when hydrocarbons are used, operation is possible at a pressure equivalent to that of conventional chlorofluorocarbon refrigerants.
- hydrocarbons are flammable.
- Non-Patent Document 1 the amount of hydrocarbon refrigerant that can be charged into a home air conditioner is within about 150 g. For this reason, it is necessary to reduce the amount of refrigerant to be filled.
- the methods for reducing the amount of refrigerant it is effective to use a closed container as a low-pressure shell. By suppressing the pressure during operation between the refrigerant in the sealed container and the stored lubricating oil, it is possible to reduce both the amount of refrigerant dissolved in the lubricating oil and the amount of refrigerant not dissolved.
- the two-stage rotary compressor has a pressure that the pressure in the intermediate flow path (intermediate pressure) becomes higher than the discharge pressure (high pressure) when starting, changing operating conditions, or operating at a low compression ratio.
- a reversal phenomenon may occur.
- the inside of the sealed container is a low-pressure shell
- the difference between the pressure in the high-stage compression section and the pressure in the sealed container becomes large. Therefore, the lubricating oil is liable to leak from the high-stage compression portion, and the probability that a pressure reversal phenomenon occurs is increased.
- the pressure reversal phenomenon occurs, the pressure in the high-stage compression section becomes higher than the pressure that is supplied to the vane back pressure chamber. This makes it impossible to supply oil due to the differential pressure to the high stage compression section.
- the pressure in the high-stage compression section becomes higher than the pressure in the vane back pressure chamber that presses the vanes in the high-stage compression section against the rolling piston.
- the pressure in the high-stage compression section may exceed the force that is the sum of the load that presses the vane against the rolling piston by the spring provided in the vane back pressure chamber and the pressure in the vane back pressure chamber. Then, a vane jump that causes the vane to move away from the rolling piston occurs, and compression in the high-stage compression unit becomes impossible. For this reason, performance deteriorates, and seizure or the like of a portion that slides due to eccentric rotation of the rolling piston occurs, thereby reducing reliability.
- a rolling piston type compressor has been described as an example, but this vane jump also occurs in a sliding vane type compressor or the like.
- Patent Document 1 describes a bypass channel that connects an intermediate channel and a high-pressure part.
- a bypass valve provided in the bypass channel is opened, and the bypass channel is opened.
- Patent Document 2 describes a bypass channel that connects an intermediate channel and a high-pressure part.
- Patent Document 2 in order to relieve pressure from the high pressure portion to the intermediate flow path, a decompression unit is used in the bypass flow path. For this reason, in Patent Document 2, when a pressure reversal phenomenon occurs, the pressure reducing means prevents the differential pressure oil supply from being restored.
- An object of the present invention is to quickly eliminate the pressure reversal phenomenon and return to the normal state when the pressure reversal phenomenon occurs.
- the two-stage compressor according to the present invention is, for example, A low-stage compression section that compresses the refrigerant; A high-stage compression unit that further compresses the refrigerant compressed by the low-stage compression unit using a compression chamber formed by vanes that have come out of the back pressure chamber; An intermediate flow path connecting the low-stage compression section and the high-stage compression section, and allowing the refrigerant discharged from the low-stage compression section to flow into the high-stage compression section; An oil supply section for supplying oil to the back pressure chamber and pressurizing the vane; A bypass circuit connecting the intermediate flow path and the oil supply unit; When the pressure of the refrigerant compressed by the low-stage compression unit is higher than the pressure of the refrigerant compressed by the high-stage compression unit, the oil supply that causes the refrigerant flowing through the intermediate flow path to flow into the oil supply unit via the bypass circuit And a promotion unit.
- the refrigeration air conditioner according to this invention is The two-stage compressor is provided.
- the two-stage compressor according to the present invention can quickly eliminate the pressure reversal phenomenon and return to the normal state when the pressure reversal phenomenon occurs. Moreover, the refrigerating and air-conditioning apparatus according to the present invention has good performance and high reliability.
- FIG. 1 is a longitudinal sectional view of a two-stage rotary compressor according to Embodiment 1.
- FIG. FIG. 3 is a transverse cross-sectional view of a compression portion of the rolling piston type rotary compressor according to the first embodiment. The figure which shows the operation
- FIG. 3 is a transverse cross-sectional view showing a refrigerant leakage path in the compression section of the rolling piston rotary compressor according to the first embodiment. The figure which shows the operation
- FIG. 5 is a cross-sectional view of a compression unit of a sliding vane rotary compressor according to a second embodiment.
- FIG. 6 is a longitudinal sectional view of a two-stage rotary compressor according to a third embodiment.
- the figure which shows the longitudinal cross-sectional view of the oil separation mechanism 9 of FIG. The block diagram which shows an example of the non-return mechanism 11 which concerns on Embodiment 4.
- FIG. The block diagram which shows an example of the non-return mechanism 11 which concerns on Embodiment 4.
- the vertical direction is an axial direction of a drive shaft 41 described later
- the horizontal direction is a vertical direction of the axial direction of the drive shaft 41. Therefore, the longitudinal sectional view is a sectional view in the axial direction of the drive shaft 41, and the transverse sectional view is a sectional view in the vertical direction of the axial direction of the drive shaft 41.
- the same reference numerals denote the same or corresponding parts, and this is common throughout the entire specification.
- FIG. 1 is a longitudinal sectional view of a two-stage rotary compressor according to Embodiment 1.
- the low-stage compression section 1 and the high-stage compression section 2 are accommodated in the sealed container 21 with the intermediate plate 48 interposed therebetween.
- An electric motor 22 is disposed above the low-stage compression unit 1 and the high-stage compression unit 2 in the hermetic container 21.
- the electric motor 22 is connected to the low-stage compression unit 1 and the high-stage compression unit 2 by a drive shaft 41.
- the electric motor 22 is driven, the low-stage compressor 1 and the high-stage compressor 2 are driven, and the low-stage compressor 1 and the high-stage compressor 2 sequentially compress the refrigerant.
- the flow of refrigerant and lubricating oil will be described.
- the low-pressure refrigerant is sucked into the sealed container 21 ((2) in FIG. 1).
- the refrigerant sucked into the sealed container 21 flows into the low-stage compression section 1 via the low-stage suction pipe 6 that connects the sealed container 21 and the low-stage compression section 1 ((3) in FIG. 1). ((4) in FIG. 1).
- the low stage compression unit 1 compresses a low-pressure refrigerant to an intermediate pressure.
- the refrigerant compressed to the intermediate pressure is discharged to the low-stage discharge muffler 3 ((5) in FIG. 1).
- the refrigerant discharged to the low-stage discharge muffler 3 flows into the high-stage compression section 2 ((7) in FIG. 1) via the intermediate connecting section 7 ((6) in FIG. 1).
- the low-stage discharge muffler 3, the intermediate connecting portion 7 and the like that connect the low-stage compression unit 1 and the high-stage compression unit 2 are referred to as an intermediate flow path.
- the high-stage compression unit 2 compresses the intermediate pressure refrigerant to a high pressure.
- the refrigerant compressed to a high pressure is discharged to the high-stage discharge muffler 4 ((8) in FIG. 1).
- the refrigerant discharged to the high-stage discharge muffler 4 flows into the oil separation mechanism 9 ((10) in FIG. 1) via the high-stage discharge pipe 8 ((9) in FIG. 1).
- the refrigerant that has flowed into the oil separation mechanism 9 is separated into lubricating oil by the oil separation mechanism 9 and discharged to the external circuit ((11) in FIG. 1).
- the lubricating oil separated by the oil separation mechanism 9 is stored in the high-pressure oil storage section 51 below the oil separation mechanism 9 ((12) in FIG. 1).
- the lubricating oil stored in the high-pressure oil storage 51 passes through the oil supply circuit 13 ((13) in FIG. 1), and from the low oil supply pipe 14 and the high oil supply pipe 15 ((14) in FIG. 1), Oil is supplied to the vane back pressure chamber 50 of the stage compression section 1 and the high stage compression section 2 ((15) and (16) in FIG. 1). Further, oil is supplied also to the upper and lower end surfaces of the high-stage rolling piston 42 by the high-stage rolling piston oil supply pipe 20 ((17) in FIG. 1). A part of the lubricating oil stored in the high-pressure oil storage unit 51 passes through the oil supply circuit 13 ((13) in FIG. 1) and is stored in the buffer unit 12 (oil supply unit) ((18) in FIG. 1). ).
- the refrigerant discharged to the low-stage discharge muffler 3 flows into the buffer part 12 from the bypass circuit 10 branched from the intermediate connecting part 7 and connected to the buffer part 12 ((19) in FIG. 1).
- the bypass circuit 10 is provided with a check mechanism 11.
- the non-return mechanism 11 is configured so that when the pressure reversal phenomenon occurs in which the pressure in the intermediate flow path (intermediate pressure) becomes higher than the discharge pressure (high pressure) of the high-stage compression section 2, the intermediate coupling section 7 and the buffer section The refrigerant is caused to flow into 12.
- the non-return mechanism 11 allows only the flow from the intermediate connecting portion 7 toward the buffer portion 12.
- a pressure equalizing circuit 16 that branches from between the non-return mechanism 11 of the bypass circuit 10 and the buffer unit 12 and is connected to the oil separation mechanism 9 is provided.
- the pressure equalizing circuit 16 is provided with a pressure equalizing unit 17.
- the pressure in the oil separation mechanism 9 and the pressure in the buffer unit 12 become a uniform pressure through the pressure equalizing unit 17.
- the pressure equalizing unit 17 adjusts the pressure in the oil separation mechanism 9 and the pressure in the buffer unit 12 and the speed at which the pressure is uniform (the time required to reach a uniform pressure).
- FIG. 2 is a cross-sectional view of a compression portion of a rolling piston type rotary compressor.
- the basic configuration is the same for both the low-stage compression unit 1 and the high-stage compression unit 2.
- the compression portion of the rolling piston type rotary compressor includes a cylinder 45, a rolling piston 42, and a vane 43.
- One of the cylinders 45 is closed by a bearing and the other is closed by an intermediate plate 48 to form a compression space.
- the rolling piston 42 is fitted into the eccentric shaft portion of the drive shaft 41 in the cylinder 45.
- the vane 43 abuts on the rolling piston 42 and forms a suction chamber 70 and a compression chamber 71 in a compression space formed by the cylinder 45, the bearing, and the intermediate plate 48.
- the vane 43 is loaded from the vane back pressure chamber 50 side to the rolling piston 42 side by the spring force of the spring 44 and the pressure of the lubricating oil supplied to the vane back pressure chamber 50. Due to this load, the vane 43 is always pressed against the rolling piston 42.
- the rolling piston 42 fitted to the drive shaft 41 rotates eccentrically.
- the volumes of the suction chamber 70 and the compression chamber 71 change. Due to this change in volume, the refrigerant is sucked from the suction port 46, compressed and discharged from the discharge port 47.
- FIG. 3 is a diagram illustrating an operation during normal operation of the two-stage rotary compressor according to the first embodiment.
- a thick line indicates a refrigerant circuit
- a dotted line indicates an oil supply circuit.
- a solid line arrow shows the flow of a refrigerant
- a dotted line arrow shows the flow of lubricating oil.
- the check mechanism 11 blocks the high pressure side (buffer portion 12 side) and the intermediate pressure side (intermediate connection portion 7 side) of the bypass circuit 10. Therefore, the refrigerant does not flow from the intermediate connecting portion 7 to the buffer portion 12 via the bypass circuit 10.
- the buffer unit 12 connected to the oil separation mechanism 9 is at a high pressure because it has a uniform pressure with the oil separation mechanism 9.
- the pressure in the vane back pressure chamber 50 to which the lubricating oil is supplied from the oil separation mechanism 9 is also high.
- the pressure in the cylinder 45 of the high-stage compression unit 2 changes between an intermediate pressure and a high pressure. If an average is taken, the pressure is between the intermediate pressure and the high pressure. That is, during normal operation, the pressure in the vane back pressure chamber 50 is higher than the pressure in the cylinder 45 of the high-stage compression unit 2. Therefore, during normal operation, the vane 43 is pressed from the vane back pressure chamber 50 side to the rolling piston 42 side by the pressure in the vane back pressure chamber 50 and is pressed against the rolling piston 42.
- FIG. 4 is a transverse cross-sectional view showing a refrigerant leakage path in the compression portion of the rolling piston rotary compressor according to the first embodiment.
- refrigerant leakage may occur from the compression chamber 71 side to the suction chamber 70 side. This occurs, for example, when the oil supply is temporarily unstable or when the refrigerant in the lubricating oil is separated from the lubricating oil and foamed.
- the refrigerant leaks from the portion sealed with the lubricating oil. That is, as indicated by dotted arrows in FIG. 4, the clearance between the rolling piston 42 and the cylinder 45 (a in FIG. 4), the clearance between the upper and lower end surfaces of the rolling piston 42 (b in FIG.
- the refrigerant leaks from the compression chamber 71 side to the suction chamber 70 side.
- refrigerant leaks also from the compression chamber 71 to the drive shaft 41 side of the rolling piston 42 (d in FIG. 4).
- the intermediate pressure rises. A pressure reversal phenomenon occurs in which the intermediate pressure is higher than the high pressure.
- the refrigerant is not compressed in the high stage compression unit 2.
- a chattering phenomenon may occur in which the vane 43 is separated from the rolling piston 42 and repeatedly collides with the rolling piston 42.
- the vane 43 and the rolling piston 42 may be damaged, and vibration and noise of the compressor may be caused.
- the refrigerant is not compressed by the high-stage compression unit 2, the refrigerant is compressed only by the low-stage compression unit 1. Therefore, the performance of the compressor is lowered, and the reliability is lowered due to the load applied to the low-stage compression unit 1.
- FIG. 5 is a diagram illustrating an operation when a pressure reversal phenomenon occurs in the two-stage rotary compressor according to the first embodiment.
- a thick line indicates a refrigerant circuit
- a dotted line indicates an oil supply circuit.
- a solid line arrow shows the flow of a refrigerant
- coolant coolant
- a dotted line arrow shows the flow of lubricating oil.
- the vane back pressure chamber 50 of the high stage compression unit 2 is supplied with a differential pressure. That is, when the refrigerant flows from the intermediate connecting portion 7 to the buffer portion 12 via the bypass circuit 10, the fuel supply to the vane back pressure chamber 50 of the high stage compression portion 2 is promoted. As a result, the pressure in the vane back pressure chamber 50 and the pressure in the high-stage compression unit 2 become uniform. That is, the pressure in the cylinder 45 of the high-stage compression unit 2 is high due to the reverse phenomenon of pressure.
- the pressure in the vane back pressure chamber 50 is also high. Therefore, the pressure in the vane back pressure chamber 50 and the pressure in the cylinder 45 of the high-stage compression unit 2 are uniform. Therefore, the vane 43 is pressed from the vane back pressure chamber 50 side to the rolling piston 42 side by the spring force of the spring 44 and is pressed against the rolling piston 42. When the vane 43 is pressed against the rolling piston 42, the suction chamber 70 and the compression chamber 71 are formed, and the refrigerant is compressed in the high-stage compression unit 2. When the refrigerant is compressed by the high-stage compression unit 2, the intermediate pressure decreases and the normal operation state is restored.
- the oil level in the buffer unit 12 is lower than the oil level in the oil separation mechanism 9. This is because the pressure in the buffer unit 12 is higher than the pressure in the oil separation mechanism 9. In this state, even after returning to the normal operation state, the differential pressure is supplied to the vane back pressure chamber 50 and the like of the high-stage compression unit 2 by the high pressure in the buffer unit 12. Further, when the check mechanism 11 is actuated again with the upper body with the oil level in the buffer portion 12 lowered, there is a possibility that the oil in the buffer portion 12 may be lost. Therefore, the pressure in the refrigerant gas space in the oil separation mechanism 9 and the buffer part 12 is made uniform by the pressure equalization part 17 provided in the pressure equalization circuit 16 that connects the oil separation mechanism 9 and the buffer part 12.
- the pressure equalizing unit 17 is, for example, a minute gap or a minute hole that has little influence when the check mechanism 11 is operated.
- the fact that there is little influence when the check mechanism 11 is operated does not prevent the pressure in the vane back pressure chamber 50 and the pressure in the high-stage compression unit 2 from being made uniform when the check mechanism 11 is operated. That's what it means.
- the non-return mechanism 11 is actuated to cause the refrigerant to flow into the buffer portion 12 from the intermediate connecting portion 7 and increase the pressure in the buffer portion 12, thereby increasing the pressure in the vane back pressure chamber 50.
- the pressure in the compression unit 2 is made uniform.
- the pressure equalizing unit 17 causes the pressure in the buffer unit 12 to increase when the refrigerant flows into the buffer unit 12 from the intermediate coupling unit 7 as a minute gap or a minute hole.
- the pressure in the buffer unit 12 is lowered over a predetermined time, and the oil level is restored. That is, when the check mechanism 11 is activated and the refrigerant flows from the intermediate connecting portion 7 to the buffer portion 12 via the bypass circuit 10, the pressure in the buffer portion 12 temporarily changes in the oil separation mechanism 9. Higher than pressure. Then, after a while after the operation of the check mechanism 11 is stopped, the pressure in the buffer unit 12 and the pressure in the oil separation mechanism 9 become a uniform pressure. As a result, the oil level in the buffer unit 12 returns to the original state over a predetermined time.
- the pressure in the buffer unit 12 follows the pressure in the oil separating mechanism 9 even when the pressure in the oil separating mechanism 9 fluctuates.
- the pressure equalizing unit 17 is not limited to a minute gap, a minute hole, or the like, and may be configured by a valve or the like.
- the valve is always opened minutely.
- the valve may be closed normally, and the valve may be slightly opened temporarily after the check mechanism 11 is activated or when the pressure in the oil separation mechanism 9 varies.
- the two-stage rotary compressor according to the first embodiment when the pressure reversal phenomenon occurs, the refrigerant is caused to flow from the intermediate coupling portion 7 to the buffer portion 12 via the bypass circuit 10. Thereby, the oil supply to the vane back pressure chamber 50 of the high stage compression unit 2 is promoted, and the pressure in the vane back pressure chamber 50 of the high stage compression unit 2 and the pressure in the high stage compression unit 2 are made uniform. Can be pressure. As a result, phenomena such as vane jumping are eliminated, and the refrigerant is compressed even in the high-stage compression unit 2, and the normal state can be restored. Therefore, the two-stage rotary compressor according to Embodiment 1 has good performance and high reliability.
- the pressure reversal phenomenon occurs when the refrigerant leaks.
- the pressure reversal phenomenon may occur even under conditions where the discharge pressure is reached only by the low-stage compression unit 1. Even in this case, in the two-stage rotary compressor according to the first embodiment, it is possible to return to the normal state as in the case where the refrigerant leaks.
- Embodiment 2 FIG. In the first embodiment, the rolling piston type two-stage rotary compressor has been described. In the second embodiment, a sliding vane type two-stage rotary compressor will be described.
- FIG. 6 is a cross-sectional view of a compression unit of a sliding vane rotary compressor according to the second embodiment.
- the basic configuration is the same for both the low-stage compression unit 1 and the high-stage compression unit 2.
- the compression unit of the sliding vane type rotary compressor includes a cylinder 85 and a rotor 60. Both ends of the cylinder 85 are closed by side plates.
- the rotor 60 is eccentrically disposed with a minute gap formed between the rotor 60 and the inner wall of the cylinder 85.
- a plurality of vanes 83 are inserted into the rotor 60.
- Each vane 83 protrudes from the rotor 60 and abuts against the inner wall of the cylinder 85 to form a working chamber 73 (compression chamber) in a space formed by the cylinder 85 and the side plate.
- the rotor 60 formed integrally with the drive shaft 81 rotates.
- centrifugal force is applied to the vane 83 inserted into the rotor 60.
- the vane 83 is loaded from the vane back pressure chamber 90 side toward the inner wall side of the cylinder 85 by the centrifugal force generated by the rotation of the rotor 60 and the pressure of the lubricating oil supplied to the vane back pressure chamber 90. .
- the vane 83 Due to this load, the vane 83 is always pressed against the inner wall of the cylinder 85 and slides against the inner wall of the cylinder 85.
- the volume of the working chamber 73 changes. Due to this change in volume, the refrigerant is sucked from the suction port 86, compressed and discharged from the discharge port 87.
- the lubricating oil is supplied to the vane back pressure chamber 90 from the oil storage portion arranged on the high pressure side.
- the pressure (intermediate pressure) in the working chamber 73 becomes higher than the pressure (high pressure) applied to the vane back pressure chamber 90 as in the case of the rolling piston type two-stage rotary compressor.
- a load that pushes the vane 83 from the side wall side of the cylinder 85 to the vane back pressure chamber 50 side presses the vane 83 against the inner wall of the cylinder 85 (pressure in the vane back pressure chamber 90).
- the total centrifugal force applied by the rotor 60 a phenomenon of vane jumping occurs in which the vane 83 is detached from the inner wall of the cylinder 85.
- the vane jump can be eliminated and the normal operation state can be restored by the same circuit configuration as that of the rolling piston type two-stage rotary compressor described in the first embodiment. That is, when a pressure reversal phenomenon occurs, the refrigerant is caused to flow from the intermediate connection portion 7 to the buffer portion 12 via the bypass circuit 10. Thereby, the oil supply to the vane back pressure chamber 90 of the high stage compression unit 2 is promoted, and the pressure in the vane back pressure chamber 90 of the high stage compression unit 2 and the pressure of the working chamber 73 of the high stage compression unit 2 are Can be made a uniform pressure. As a result, phenomena such as vane jumping are eliminated, and the refrigerant is compressed even in the high-stage compression unit 2, and the normal state can be restored.
- Embodiment 3 In the first embodiment, the example in which the check mechanism 11 and the buffer unit 12 are provided outside the sealed container 21 and the oil separation mechanism 9 has been described. In the third embodiment, an example in which the check mechanism 11 and the buffer unit 12 are provided inside the sealed container 21 and the oil separation mechanism 9 will be described.
- FIG. 7 is a longitudinal sectional view of a two-stage rotary compressor according to the third embodiment.
- the buffer unit 12 is built in the oil separation mechanism 9. That is, the buffer unit 12 is provided in a partial region in the oil separation mechanism 9.
- the check mechanism 11 is built in the sealed container 21.
- the check mechanism 11 is provided in the low-stage discharge muffler 3 in the sealed container 21.
- the bypass circuit 10 connects the non-return mechanism 11 provided in the low-stage discharge muffler 3 and the buffer unit 12 formed in the oil separation mechanism 9.
- the operation when the pressure reversal phenomenon occurs is the same as in the first embodiment. That is, when a pressure reversal phenomenon occurs, the refrigerant flows from the intermediate flow path into the buffer unit 12 via the bypass circuit 10. Thereby, the oil supply to the vane back pressure chamber 50 of the high stage compression unit 2 is promoted, and the pressure in the vane back pressure chamber 50 of the high stage compression unit 2 and the pressure in the high stage compression unit 2 are made uniform. Can be pressure. As a result, phenomena such as vane jumping are eliminated, and the refrigerant is compressed even in the high-stage compression unit 2, and the normal state can be restored.
- FIG. 8 is a view showing a longitudinal sectional view of the oil separation mechanism 9 of FIG. 7 according to the third embodiment.
- the enlarged view about a broken-line part is shown collectively.
- This gap “( ⁇ A ⁇ B) / 2” becomes a pressure equalizing portion 17 that communicates the inside of the buffer portion 12 and the inside of the oil separation mechanism 9. That is, the gap “( ⁇ A ⁇ B) / 2” returns the oil level in the buffer portion 12 to the same height as the oil level in the oil separation mechanism 9 after the check mechanism 11 is operated.
- FIG. 8 there is a gap “C” between the oil separation mechanism 9 and the portion where the lubricating oil in the lower portion of the buffer portion 12 is stored.
- This gap “C” is the buffer space oil supply section 18.
- the lubricating oil ((1) in FIG. 8) separated in the oil separation mechanism 9 flows from the buffer space oil supply section 18 into the buffer section 12 ((2) in FIG. 8).
- the lubricating oil stored in the buffer part 12 is supplied to each compression part by the oil supply circuit 13 ((3) of FIG. 8).
- the opening area of the pressure equalizing unit 17 and the opening area of the buffer space oil supply unit 18 shown in FIG. 8 are determined according to the air conditioning capability.
- the pressure equalizing unit 17 has an opening area of about 0.1 to 0.5 mm 2 and the buffer space oil supply unit 18 has an opening area of 10 About 50 mm 2 .
- the pressure equalization part 17 and the buffer space oil supply part 18 are not restricted to the structure mentioned above, For example, you may form in a hole shape and the clearance gap formed by a plane and a plane may be sufficient.
- the buffer unit 12 is built in the oil separation mechanism 9 and the check mechanism 11 is built in the sealed container 21 is shown.
- the present invention is not limited thereto, and the buffer unit 12 may be built in the sealed container 21, and the check mechanism 11 may be built in the oil separation mechanism 9.
- the configuration of the buffer unit 12 shown in FIGS. 7 and 8 is an example, and other configurations may be used as long as the functions are satisfied.
- the buffer unit 12 and the check mechanism 11 are incorporated in the oil separation mechanism 9 and the airtight container 21, respectively. Thereby, a compressor can be reduced in size.
- Embodiment 4 FIG. In the fourth embodiment, the configuration of the check mechanism 11 will be described.
- FIG. 9 is a configuration diagram illustrating an example of the check mechanism 11 according to the fourth embodiment.
- FIG. 9 shows an example of the non-return mechanism 11 used when the non-return mechanism 11 is built in the sealed container 21 or the oil separation mechanism 9, for example.
- the check mechanism 11 shown in FIG. 9 has a structure in which the valve body 91 is pressed against the valve seat 92 by a spring.
- FIG. 9A shows a state in which the valve body 91 is pressed against the valve seat 92 and the valve is closed.
- FIG. 9B shows a state where the valve body 91 is separated from the valve seat 92 and the valve is opened.
- the state where the valves are separated is a state where the check mechanism 11 is activated.
- the valve body 91 since the high pressure is higher than the intermediate pressure during normal operation, the valve body 91 is pressed from the high pressure side to the intermediate pressure side, and the valve body 91 is pressed against the valve seat 92. Therefore, the valve is closed.
- the intermediate pressure becomes higher than the high pressure (when a reverse pressure phenomenon occurs)
- the valve body 91 is pushed from the intermediate pressure side to the high pressure side, and the valve body 91 is separated from the valve seat 92. Therefore, the valve is opened.
- FIG. 10 is a configuration diagram illustrating an example of the check mechanism 11 according to the fourth embodiment.
- FIG. 10 shows an example of the check mechanism 11 used when the check mechanism 11 is provided outside the sealed container 21 or the oil separation mechanism 9.
- the check mechanism 11 shown in FIG. 10 has a structure in which a leaf spring 93 is opened and closed.
- FIG. 10A shows a state in which the leaf spring 93 is pressed against the valve seat 94 and the valve is closed.
- FIG. 10B shows a state in which the leaf spring 93 is separated from the valve seat 94 and the valve is opened.
- the state where the valves are separated is a state where the check mechanism 11 is activated.
- the plate spring 93 is pressed from the high pressure side to the intermediate pressure side, and the plate spring 93 is pressed against the valve seat 94. Therefore, the valve is closed.
- the intermediate pressure becomes higher than the high pressure (when a reverse pressure phenomenon occurs)
- the leaf spring 93 is pushed from the intermediate pressure side to the high pressure side, and the leaf spring 93 moves away from the valve seat 94. Therefore, the valve is opened.
- the structure of the non-return mechanism 11 shown to FIG. 9, 10 is an example, and as long as the function is satisfy
- Embodiment 5 FIG.
- the pressure in the sealed container 21 is the pressure (low pressure) before the low-stage compression unit 1 compresses the refrigerant
- low pressure shell type compressor low pressure shell type compressor
- the inside of the sealed container 21 is at an intermediate pressure (discharge pressure of the low-stage compression unit 1) (intermediate pressure shell type compressor)
- the inside of the sealed container 21 is at a high pressure (of the high-stage compression unit 2).
- discharge pressure high-pressure shell type compressor
- FIG. 11 is a diagram illustrating the operation of the two-stage rotary compressor in which the inside of the sealed container 21 according to the fifth embodiment has an intermediate pressure.
- the thick line indicates the refrigerant circuit
- the dotted line indicates the oil supply circuit.
- a solid line arrow shows the flow of a refrigerant
- a dotted line arrow shows the flow of lubricating oil.
- the refrigerant compressed to the intermediate pressure is discharged to the low-stage discharge muffler 3 ((3) in FIG. 11).
- the refrigerant discharged to the low-stage discharge muffler 3 is discharged into the sealed container 21 ((4) in FIG. 11). That is, the inside of the sealed container 21 is at an intermediate pressure.
- the intermediate-pressure refrigerant discharged into the sealed container 21 is sucked into the high-stage compression section 2 via the intermediate coupling portion 7 connected to the sealed container 21 ((5) in FIG. 11) (FIG. 11 (6)).
- the high-stage compression unit 2 compresses the intermediate pressure refrigerant to a high pressure.
- the refrigerant compressed to a high pressure is discharged to the high-stage discharge muffler 4 ((7) in FIG. 11).
- the refrigerant discharged to the high-stage discharge muffler 4 flows into the oil separation mechanism 9 ((9) in FIG. 11) via the high-stage discharge pipe 8 ((8) in FIG. 11).
- the refrigerant that has flowed into the oil separation mechanism 9 is separated into lubricating oil by the oil separation mechanism 9 and discharged to the external circuit ((10) in FIG. 11).
- the lubricating oil separated by the oil separation mechanism 9 is stored in the high-pressure oil storage section 51 below the oil separation mechanism 9 ((11) in FIG. 11).
- the lubricating oil stored in the high-pressure oil storage 51 is supplied to the vane back pressure chamber 50 of the high-stage compression section 2 from the high-stage oil supply pipe 15 via the oil supply circuit 13 ((12) in FIG. 11). ((13) in FIG. 11).
- a part of the lubricating oil stored in the high-pressure oil storage unit 51 passes through the oil supply circuit 13 ((12) in FIG. 1) and is stored in the buffer unit 12 ((14) in FIG. 11).
- the check mechanism 11 When a reverse pressure phenomenon occurs in which the intermediate pressure is higher than the high pressure, the check mechanism 11 is activated. And the refrigerant
- the oil supply to the vane back pressure chamber 50 or the like of the high stage compression unit 2 is promoted, The pressure in the vane back pressure chamber 50 of the high stage compression unit 2 and the pressure in the cylinder 45 of the high stage compression unit 2 can be made uniform.
- the check mechanism 11 and the buffer unit 12 are provided outside. However, as described in the third embodiment, the check mechanism 11 and the buffer unit 12 may be built in the sealed container 21 or the oil separation mechanism 9.
- FIG. 12 is a diagram illustrating the operation of the two-stage rotary compressor in which the inside of the sealed container 21 according to the fifth embodiment is high pressure.
- the thick line indicates the refrigerant circuit
- the dotted line indicates the oil supply circuit.
- a solid line arrow shows the flow of a refrigerant
- a dotted line arrow shows the flow of lubricating oil.
- the refrigerant compressed to the intermediate pressure is discharged to the low-stage discharge muffler 3 ((3) in FIG. 12).
- the refrigerant discharged to the low-stage discharge muffler 3 is sucked into the high-stage compression section 2 ((5) in FIG. 12) via the intermediate connecting section 7 ((4) in FIG. 12).
- the high-stage compression unit 2 compresses the intermediate pressure refrigerant to a high pressure.
- the refrigerant compressed to a high pressure is discharged to the high-stage discharge muffler 4 ((6) in FIG. 12).
- the refrigerant discharged to the high-stage discharge muffler 4 is discharged into the sealed container 21 ((7) in FIG. 12). That is, the inside of the sealed container 21 is at a high pressure.
- the refrigerant discharged into the sealed container 21 is discharged from the upper part of the sealed container 21 to the external circuit ((8) in FIG. 12).
- the sealed container 21 serves as the oil separation mechanism 9. Since the inside of the sealed container 21 is at a high pressure, the lubricating oil separated from the refrigerant is stored in the lower part of the sealed container 21 ((9) in FIG. 12). That is, the lower part of the sealed container 21 becomes the high-pressure oil storage unit 51.
- the lubricating oil stored in the high-pressure oil storage unit 51 flows from the buffer space oil supply unit 18 into the buffer unit 12 provided inside the sealed container 21 ((10) in FIG. 12).
- the lubricating oil that has flowed into the buffer unit 12 is supplied from the high-stage oil supply pipe 15 to the vane back pressure chamber 50 of the high-stage compression unit 2 ((11) in FIG. 12).
- the check mechanism 11 When a reverse pressure phenomenon occurs in which the intermediate pressure is higher than the high pressure, the check mechanism 11 is activated. And the refrigerant
- the oil supply to the vane back pressure chamber 50 and the like of the high-stage compression unit 2 is promoted,
- the pressure in the vane back pressure chamber 50 of the stage compression unit 2 and the pressure in the cylinder 45 of the high stage compression unit 2 can be made uniform. As a result, phenomena such as vane jumping are eliminated, and the refrigerant is compressed even in the high-stage compression unit 2, and the normal state can be restored.
- the refrigerant gas space in the sealed container 21 and the buffer unit 12 have a uniform pressure by the pressure equalizing unit 17.
- the high-stage oil supply pipe 15 is not necessarily required, and the buffer section 12 may include the vane back pressure chamber 50 of the high-stage compression section 2 and may be formed integrally.
- the buffer unit 12 is built in the sealed container 21, and the check mechanism 11 is provided outside the sealed container 21.
- the buffer unit 12 may be provided outside, and the check mechanism 11 may be built in the sealed container 21.
- Embodiment 6 FIG. In the sixth embodiment, a refrigeration air conditioner including the two-stage rotary compressor described in the above embodiment will be described.
- FIG. 13 is a diagram illustrating an example of a refrigerant circuit of the refrigeration air conditioner 95 including the two-stage rotary compressor described in the first to fifth embodiments.
- the condenser 31 is connected to the oil separation mechanism 9 of the two-stage rotary compressor.
- the internal heat exchanger 36, the expansion valve 32, and the evaporator 33 are sequentially connected from the condenser 31 to the suction pipe 5 of the sealed container 21.
- an injection circuit 34 that branches from between the internal heat exchanger 36 and the expansion valve 32 is connected to the intermediate connecting portion 7 from the internal heat exchanger 36 via the injection expansion valve 35.
- the two-stage rotary compressor according to Embodiments 1 to 5 can return to a normal state even when a pressure reversal phenomenon occurs. Therefore, the two-stage rotary compressor according to Embodiments 1 to 5 has good performance and high reliability. Therefore, the refrigerating and air-conditioning apparatus 95 including the two-stage rotary compressor according to the first to fifth embodiments similarly has good performance and high reliability.
- a low-stage compression unit, a high-stage compression unit, and an electric motor that drives the low-stage compression unit and the high-stage compression unit are housed, and a low-pressure refrigerant is sucked into the low-stage compression unit, After being compressed to an intermediate pressure, after being sucked into the high-stage compression part via an intermediate connecting part and compressed to a high pressure, the lubricating oil in the refrigerant is separated by an oil separation mechanism, and the separated lubricating oil Is stored in the high-pressure oil storage unit and then supplied to the low-stage compression unit and the high-stage compression unit in the sealed container by an oil supply circuit, and the refrigerant after the separation of the lubricating oil is supplied to the external refrigerant circuit.
- a non-return mechanism for allowing only a flow from the intermediate connecting portion to a bypass circuit branched from the intermediate connecting portion and connected to the oil supply circuit, and a buffer for storing a part of lubricating oil in the high pressure oil storage portion And a pressure equalizing section connected to the oil separation mechanism on the downstream side of the check mechanism.
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Abstract
A two-stage compressor is returned to a normal operating condition when an intermediate pressure is higher than a high pressure. The two-stage compressor is provided with a buffer section (12) provided separated from an oil content separating mechanism (9) and containing a part of lubricating oil which the oil content separating mechanism (9) contains; an intermediate flow path (including low-stage discharge muffler (3) and intermediate connecting section (7)) for interconnecting a low-stage compression section (1) and a high-stage compression section (2) and allowing a refrigerant discharged from the low-stage compression section (1) to flow into the high-stage compression section (2); and a bypass circuit (10) for interconnecting the intermediate flow path and the buffer section (12). When the pressure (intermediate pressure) of the refrigerant compressed by the low-stage compression section (1) is higher than the pressure(high pressure) of the refrigerant compressed by the high-stage compression section (2), a non-return mechanism (11) causes the refrigerant flowing in the intermediate flow path to flow into the buffer section (12) via the bypass circuit (10). The construction promotes oil supply from the buffer section (12) to a vane back pressure chamber (50).
Description
本発明は、例えば、密閉容器内に圧縮部を備えた二段圧縮機、及び二段圧縮機を備えた冷凍空調装置に関する。
The present invention relates to, for example, a two-stage compressor including a compression unit in a sealed container, and a refrigeration air conditioner including the two-stage compressor.
蒸気圧縮式冷凍サイクルやヒートポンプサイクルに用いられる冷媒圧縮機の1つにロータリ圧縮機がある。ロータリ圧縮機は、小型化が可能なこと、また、構造が簡単なことから、冷凍冷蔵庫、空調機、ヒートポンプ式給湯機等に広く用いられる。
また、圧縮機内に2つの圧縮部(低段圧縮部と高段圧縮部)を備えた二段ロータリ圧縮機は、一段あたりの差圧が小さく漏れ損失が小さいというメリットがある。また、二段ロータリ圧縮機は、低段圧縮部と高段圧縮部とを繋ぐ中間流路に冷媒をインジェクションすることで性能向上を図れるというメリットもある。 One of refrigerant compressors used in vapor compression refrigeration cycles and heat pump cycles is a rotary compressor. A rotary compressor is widely used for a refrigerator-freezer, an air conditioner, a heat pump hot water heater, and the like because it can be downsized and has a simple structure.
In addition, a two-stage rotary compressor provided with two compression sections (a low-stage compression section and a high-stage compression section) in the compressor has an advantage that the differential pressure per stage is small and the leakage loss is small. Further, the two-stage rotary compressor has an advantage that the performance can be improved by injecting the refrigerant into the intermediate flow path connecting the low-stage compression section and the high-stage compression section.
また、圧縮機内に2つの圧縮部(低段圧縮部と高段圧縮部)を備えた二段ロータリ圧縮機は、一段あたりの差圧が小さく漏れ損失が小さいというメリットがある。また、二段ロータリ圧縮機は、低段圧縮部と高段圧縮部とを繋ぐ中間流路に冷媒をインジェクションすることで性能向上を図れるというメリットもある。 One of refrigerant compressors used in vapor compression refrigeration cycles and heat pump cycles is a rotary compressor. A rotary compressor is widely used for a refrigerator-freezer, an air conditioner, a heat pump hot water heater, and the like because it can be downsized and has a simple structure.
In addition, a two-stage rotary compressor provided with two compression sections (a low-stage compression section and a high-stage compression section) in the compressor has an advantage that the differential pressure per stage is small and the leakage loss is small. Further, the two-stage rotary compressor has an advantage that the performance can be improved by injecting the refrigerant into the intermediate flow path connecting the low-stage compression section and the high-stage compression section.
近年、地球温暖化防止を図る観点から、フロンに代わる新たな冷媒として、オゾン層破壊係数がゼロで地球温暖化係数の小さい自然冷媒が注目されている。自然冷媒の1つとして、冷媒特性に優れた炭化水素(HC)冷媒がある。
炭化水素は、摺動部潤滑性能、漏れシール性能、理論冷凍サイクルCOPの観点からフロン冷媒と同等の冷媒特性を備えている。さらに、炭化水素を用いた場合、従来のフロン冷媒と同等の圧力で運転が可能である。しかし、炭化水素は、可燃性であるという課題がある。
既にイソブタンを用いた冷凍冷蔵庫が量産されている。しかし、可燃性冷媒の危険性から、国際規格で冷媒許容充填量が制限されている(非特許文献1参照)。例えば、IEC規格によると、家庭用エアコンに充填できる炭化水素冷媒量は約150g以内となる。このため、充填する冷媒量を低減する必要がある。冷媒量を低減する方法の1つとしては、密閉容器を低圧シェルにすることが有効である。密閉容器内の冷媒と貯蔵した潤滑油との運転時における圧力を低く抑えることで、潤滑油に溶け込んだ冷媒量と溶け込まない冷媒量とをともに低減することができる。 In recent years, from the viewpoint of preventing global warming, natural refrigerants that have a zero ozone depletion coefficient and a small global warming coefficient have attracted attention as a new refrigerant that can replace Freon. One natural refrigerant is a hydrocarbon (HC) refrigerant that has excellent refrigerant characteristics.
Hydrocarbons have refrigerant characteristics equivalent to those of chlorofluorocarbon refrigerants from the viewpoint of sliding portion lubrication performance, leakage seal performance, and theoretical refrigeration cycle COP. Furthermore, when hydrocarbons are used, operation is possible at a pressure equivalent to that of conventional chlorofluorocarbon refrigerants. However, there is a problem that hydrocarbons are flammable.
Refrigerated refrigerators using isobutane have already been mass-produced. However, due to the danger of flammable refrigerants, international standards limit the refrigerant allowable filling amount (see Non-Patent Document 1). For example, according to the IEC standard, the amount of hydrocarbon refrigerant that can be charged into a home air conditioner is within about 150 g. For this reason, it is necessary to reduce the amount of refrigerant to be filled. As one of the methods for reducing the amount of refrigerant, it is effective to use a closed container as a low-pressure shell. By suppressing the pressure during operation between the refrigerant in the sealed container and the stored lubricating oil, it is possible to reduce both the amount of refrigerant dissolved in the lubricating oil and the amount of refrigerant not dissolved.
炭化水素は、摺動部潤滑性能、漏れシール性能、理論冷凍サイクルCOPの観点からフロン冷媒と同等の冷媒特性を備えている。さらに、炭化水素を用いた場合、従来のフロン冷媒と同等の圧力で運転が可能である。しかし、炭化水素は、可燃性であるという課題がある。
既にイソブタンを用いた冷凍冷蔵庫が量産されている。しかし、可燃性冷媒の危険性から、国際規格で冷媒許容充填量が制限されている(非特許文献1参照)。例えば、IEC規格によると、家庭用エアコンに充填できる炭化水素冷媒量は約150g以内となる。このため、充填する冷媒量を低減する必要がある。冷媒量を低減する方法の1つとしては、密閉容器を低圧シェルにすることが有効である。密閉容器内の冷媒と貯蔵した潤滑油との運転時における圧力を低く抑えることで、潤滑油に溶け込んだ冷媒量と溶け込まない冷媒量とをともに低減することができる。 In recent years, from the viewpoint of preventing global warming, natural refrigerants that have a zero ozone depletion coefficient and a small global warming coefficient have attracted attention as a new refrigerant that can replace Freon. One natural refrigerant is a hydrocarbon (HC) refrigerant that has excellent refrigerant characteristics.
Hydrocarbons have refrigerant characteristics equivalent to those of chlorofluorocarbon refrigerants from the viewpoint of sliding portion lubrication performance, leakage seal performance, and theoretical refrigeration cycle COP. Furthermore, when hydrocarbons are used, operation is possible at a pressure equivalent to that of conventional chlorofluorocarbon refrigerants. However, there is a problem that hydrocarbons are flammable.
Refrigerated refrigerators using isobutane have already been mass-produced. However, due to the danger of flammable refrigerants, international standards limit the refrigerant allowable filling amount (see Non-Patent Document 1). For example, according to the IEC standard, the amount of hydrocarbon refrigerant that can be charged into a home air conditioner is within about 150 g. For this reason, it is necessary to reduce the amount of refrigerant to be filled. As one of the methods for reducing the amount of refrigerant, it is effective to use a closed container as a low-pressure shell. By suppressing the pressure during operation between the refrigerant in the sealed container and the stored lubricating oil, it is possible to reduce both the amount of refrigerant dissolved in the lubricating oil and the amount of refrigerant not dissolved.
二段ロータリ圧縮機は、起動時や運転条件を変更する時、低圧縮比で運転する時等に、中間流路内の圧力(中間圧)が吐出圧力(高圧)よりも高くなるという圧力の逆転現象が起こることがある。特に密閉容器内を低圧シェルにした場合、高段圧縮部の圧力と密閉容器内の圧力との差が大きくなる。そのため、高段圧縮部内から潤滑油が漏れやすくなり、圧力の逆転現象が発生する確率が高くなる。
圧力の逆転現象が起こった場合、高段圧縮部内の圧力がベーン背圧室に給油している圧力よりも高くなってしまう。そのため、高段圧縮部への差圧による給油ができなくなってしまう。
また、圧力の逆転現象が起こった場合、高段圧縮部のベーンをローリングピストンに押し付けるベーン背圧室内の圧力よりも、高段圧縮部内の圧力の方が高くなる。さらに、高段圧縮部内の圧力が、ベーン背圧室に設けられたバネによりベーンをローリングピストンへ押し付ける荷重と、ベーン背圧室内の圧力とを加えた力をも超えてしまうことがある。すると、ベーンがローリングピストンから離れてしまうベーン飛びが発生し、高段圧縮部での圧縮ができなくなる。このため、性能が低下するとともに、ローリングピストンの偏芯回転により摺れる部分の焼きつき等が発生して信頼性が低下してしまう。
なお、ここでは、ローリングピストン型の圧縮機を一例として説明したが、このベーン飛びは、スライディングベーン型の圧縮機等でも起こる。 The two-stage rotary compressor has a pressure that the pressure in the intermediate flow path (intermediate pressure) becomes higher than the discharge pressure (high pressure) when starting, changing operating conditions, or operating at a low compression ratio. A reversal phenomenon may occur. In particular, when the inside of the sealed container is a low-pressure shell, the difference between the pressure in the high-stage compression section and the pressure in the sealed container becomes large. Therefore, the lubricating oil is liable to leak from the high-stage compression portion, and the probability that a pressure reversal phenomenon occurs is increased.
When the pressure reversal phenomenon occurs, the pressure in the high-stage compression section becomes higher than the pressure that is supplied to the vane back pressure chamber. This makes it impossible to supply oil due to the differential pressure to the high stage compression section.
Further, when a pressure reversal phenomenon occurs, the pressure in the high-stage compression section becomes higher than the pressure in the vane back pressure chamber that presses the vanes in the high-stage compression section against the rolling piston. In addition, the pressure in the high-stage compression section may exceed the force that is the sum of the load that presses the vane against the rolling piston by the spring provided in the vane back pressure chamber and the pressure in the vane back pressure chamber. Then, a vane jump that causes the vane to move away from the rolling piston occurs, and compression in the high-stage compression unit becomes impossible. For this reason, performance deteriorates, and seizure or the like of a portion that slides due to eccentric rotation of the rolling piston occurs, thereby reducing reliability.
Here, a rolling piston type compressor has been described as an example, but this vane jump also occurs in a sliding vane type compressor or the like.
圧力の逆転現象が起こった場合、高段圧縮部内の圧力がベーン背圧室に給油している圧力よりも高くなってしまう。そのため、高段圧縮部への差圧による給油ができなくなってしまう。
また、圧力の逆転現象が起こった場合、高段圧縮部のベーンをローリングピストンに押し付けるベーン背圧室内の圧力よりも、高段圧縮部内の圧力の方が高くなる。さらに、高段圧縮部内の圧力が、ベーン背圧室に設けられたバネによりベーンをローリングピストンへ押し付ける荷重と、ベーン背圧室内の圧力とを加えた力をも超えてしまうことがある。すると、ベーンがローリングピストンから離れてしまうベーン飛びが発生し、高段圧縮部での圧縮ができなくなる。このため、性能が低下するとともに、ローリングピストンの偏芯回転により摺れる部分の焼きつき等が発生して信頼性が低下してしまう。
なお、ここでは、ローリングピストン型の圧縮機を一例として説明したが、このベーン飛びは、スライディングベーン型の圧縮機等でも起こる。 The two-stage rotary compressor has a pressure that the pressure in the intermediate flow path (intermediate pressure) becomes higher than the discharge pressure (high pressure) when starting, changing operating conditions, or operating at a low compression ratio. A reversal phenomenon may occur. In particular, when the inside of the sealed container is a low-pressure shell, the difference between the pressure in the high-stage compression section and the pressure in the sealed container becomes large. Therefore, the lubricating oil is liable to leak from the high-stage compression portion, and the probability that a pressure reversal phenomenon occurs is increased.
When the pressure reversal phenomenon occurs, the pressure in the high-stage compression section becomes higher than the pressure that is supplied to the vane back pressure chamber. This makes it impossible to supply oil due to the differential pressure to the high stage compression section.
Further, when a pressure reversal phenomenon occurs, the pressure in the high-stage compression section becomes higher than the pressure in the vane back pressure chamber that presses the vanes in the high-stage compression section against the rolling piston. In addition, the pressure in the high-stage compression section may exceed the force that is the sum of the load that presses the vane against the rolling piston by the spring provided in the vane back pressure chamber and the pressure in the vane back pressure chamber. Then, a vane jump that causes the vane to move away from the rolling piston occurs, and compression in the high-stage compression unit becomes impossible. For this reason, performance deteriorates, and seizure or the like of a portion that slides due to eccentric rotation of the rolling piston occurs, thereby reducing reliability.
Here, a rolling piston type compressor has been described as an example, but this vane jump also occurs in a sliding vane type compressor or the like.
圧力の逆転現象が起こった場合の対策としては、中間流路と高圧部とをバイパスさせる方法がある。
特許文献1には、中間流路と高圧部とをつなぐバイパス流路についての記載がある。特許文献1では、圧力の逆転現象が起こった場合にバイパス流路に設けられたバイパス弁を開け、バイパス流路を開通する。しかし、特許文献1では、密閉容器を含む大きな容積に中間流路の圧力を逃がすため、差圧給油が可能な状態に復帰するまでのレスポンスは遅い。
特許文献2には、中間流路と高圧部とをつなぐバイパス流路についての記載がある。しかし、特許文献2では、高圧部から中間流路へ圧力を逃がすために、バイパス流路に減圧手段を用いている。そのため、特許文献2では、圧力の逆転現象が起こった場合、差圧給油を復帰することを減圧手段が妨げてしまう。 As a countermeasure when the pressure reversal phenomenon occurs, there is a method of bypassing the intermediate flow path and the high pressure section.
Patent Document 1 describes a bypass channel that connects an intermediate channel and a high-pressure part. In Patent Document 1, when a pressure reversal phenomenon occurs, a bypass valve provided in the bypass channel is opened, and the bypass channel is opened. However, in Patent Document 1, since the pressure in the intermediate flow path is released to a large volume including the sealed container, the response until returning to a state where differential pressure oil supply is possible is slow.
Patent Document 2 describes a bypass channel that connects an intermediate channel and a high-pressure part. However, in Patent Document 2, in order to relieve pressure from the high pressure portion to the intermediate flow path, a decompression unit is used in the bypass flow path. For this reason, in Patent Document 2, when a pressure reversal phenomenon occurs, the pressure reducing means prevents the differential pressure oil supply from being restored.
特許文献1には、中間流路と高圧部とをつなぐバイパス流路についての記載がある。特許文献1では、圧力の逆転現象が起こった場合にバイパス流路に設けられたバイパス弁を開け、バイパス流路を開通する。しかし、特許文献1では、密閉容器を含む大きな容積に中間流路の圧力を逃がすため、差圧給油が可能な状態に復帰するまでのレスポンスは遅い。
特許文献2には、中間流路と高圧部とをつなぐバイパス流路についての記載がある。しかし、特許文献2では、高圧部から中間流路へ圧力を逃がすために、バイパス流路に減圧手段を用いている。そのため、特許文献2では、圧力の逆転現象が起こった場合、差圧給油を復帰することを減圧手段が妨げてしまう。 As a countermeasure when the pressure reversal phenomenon occurs, there is a method of bypassing the intermediate flow path and the high pressure section.
上述したように、二段圧縮機において、中間流路内の圧力(中間圧)が吐出圧力(高圧)よりも高くなるという圧力の逆転現象が起こることがある。この場合、高段圧縮部への差圧給油ができなくなるとともに、ベーン飛びが発生する虞がある。そのため、高段圧縮部での圧縮ができなくなり、圧縮機の性能が低下するとともに、圧縮機の信頼性が低下するという課題がある。
この発明は、圧力の逆転現象が起こった場合に、速やかに圧力の逆転現象を解消し、正常状態に戻すことを目的とする。 As described above, in the two-stage compressor, a pressure reversal phenomenon in which the pressure in the intermediate flow path (intermediate pressure) becomes higher than the discharge pressure (high pressure) may occur. In this case, the differential pressure oil supply to the high-stage compression unit cannot be performed, and there is a possibility that vane jumping may occur. For this reason, there is a problem in that compression in the high-stage compression section becomes impossible, the performance of the compressor is lowered, and the reliability of the compressor is lowered.
An object of the present invention is to quickly eliminate the pressure reversal phenomenon and return to the normal state when the pressure reversal phenomenon occurs.
この発明は、圧力の逆転現象が起こった場合に、速やかに圧力の逆転現象を解消し、正常状態に戻すことを目的とする。 As described above, in the two-stage compressor, a pressure reversal phenomenon in which the pressure in the intermediate flow path (intermediate pressure) becomes higher than the discharge pressure (high pressure) may occur. In this case, the differential pressure oil supply to the high-stage compression unit cannot be performed, and there is a possibility that vane jumping may occur. For this reason, there is a problem in that compression in the high-stage compression section becomes impossible, the performance of the compressor is lowered, and the reliability of the compressor is lowered.
An object of the present invention is to quickly eliminate the pressure reversal phenomenon and return to the normal state when the pressure reversal phenomenon occurs.
この発明に係る二段圧縮機は、例えば、
冷媒を圧縮する低段圧縮部と、
背圧室から出たベーンにより形成された圧縮室を用いて、前記低段圧縮部が圧縮した冷媒をさらに圧縮する高段圧縮部と、
前記低段圧縮部と前記高段圧縮部とを繋ぎ、前記低段圧縮部から吐出された冷媒を前記高段圧縮部へ流入させる中間流路と、
油を前記背圧室へ供給して、前記ベーンに加圧する給油部と、
前記中間流路と前記給油部とを繋ぐバイパス回路と、
前記低段圧縮部が圧縮した冷媒の圧力が前記高段圧縮部が圧縮した冷媒の圧力よりも高い場合に、前記バイパス回路を介して前記給油部へ前記中間流路を流れる冷媒を流入させる給油促進部と
を備えることを特徴とする。 The two-stage compressor according to the present invention is, for example,
A low-stage compression section that compresses the refrigerant;
A high-stage compression unit that further compresses the refrigerant compressed by the low-stage compression unit using a compression chamber formed by vanes that have come out of the back pressure chamber;
An intermediate flow path connecting the low-stage compression section and the high-stage compression section, and allowing the refrigerant discharged from the low-stage compression section to flow into the high-stage compression section;
An oil supply section for supplying oil to the back pressure chamber and pressurizing the vane;
A bypass circuit connecting the intermediate flow path and the oil supply unit;
When the pressure of the refrigerant compressed by the low-stage compression unit is higher than the pressure of the refrigerant compressed by the high-stage compression unit, the oil supply that causes the refrigerant flowing through the intermediate flow path to flow into the oil supply unit via the bypass circuit And a promotion unit.
冷媒を圧縮する低段圧縮部と、
背圧室から出たベーンにより形成された圧縮室を用いて、前記低段圧縮部が圧縮した冷媒をさらに圧縮する高段圧縮部と、
前記低段圧縮部と前記高段圧縮部とを繋ぎ、前記低段圧縮部から吐出された冷媒を前記高段圧縮部へ流入させる中間流路と、
油を前記背圧室へ供給して、前記ベーンに加圧する給油部と、
前記中間流路と前記給油部とを繋ぐバイパス回路と、
前記低段圧縮部が圧縮した冷媒の圧力が前記高段圧縮部が圧縮した冷媒の圧力よりも高い場合に、前記バイパス回路を介して前記給油部へ前記中間流路を流れる冷媒を流入させる給油促進部と
を備えることを特徴とする。 The two-stage compressor according to the present invention is, for example,
A low-stage compression section that compresses the refrigerant;
A high-stage compression unit that further compresses the refrigerant compressed by the low-stage compression unit using a compression chamber formed by vanes that have come out of the back pressure chamber;
An intermediate flow path connecting the low-stage compression section and the high-stage compression section, and allowing the refrigerant discharged from the low-stage compression section to flow into the high-stage compression section;
An oil supply section for supplying oil to the back pressure chamber and pressurizing the vane;
A bypass circuit connecting the intermediate flow path and the oil supply unit;
When the pressure of the refrigerant compressed by the low-stage compression unit is higher than the pressure of the refrigerant compressed by the high-stage compression unit, the oil supply that causes the refrigerant flowing through the intermediate flow path to flow into the oil supply unit via the bypass circuit And a promotion unit.
この発明に係る冷凍空調装置は、
前記二段圧縮機を備えることを特徴とする。 The refrigeration air conditioner according to this invention is
The two-stage compressor is provided.
前記二段圧縮機を備えることを特徴とする。 The refrigeration air conditioner according to this invention is
The two-stage compressor is provided.
この発明に係る二段圧縮機は、圧力の逆転現象が起こった場合に、速やかに圧力の逆転現象を解消し、正常状態へ復帰することができる。また、この発明に係る冷凍空調装置は、性能がよく、信頼性が高い。
The two-stage compressor according to the present invention can quickly eliminate the pressure reversal phenomenon and return to the normal state when the pressure reversal phenomenon occurs. Moreover, the refrigerating and air-conditioning apparatus according to the present invention has good performance and high reliability.
以下、図に基づき、この発明の実施の形態を説明する。
なお、以下の実施の形態において、縦方向とは、後述する駆動軸41の軸方向であり、横方向とは、駆動軸41の軸方向の垂直方向である。したがって、縦断面図とは、駆動軸41の軸方向の断面図であり、横断面図とは、駆動軸41の軸方向の垂直方向の断面図である。
また、図において、同一の符号を付したものは、同一またはこれに相当するものであり、このことは、明細書の全文において共通することである。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
In the following embodiments, the vertical direction is an axial direction of adrive shaft 41 described later, and the horizontal direction is a vertical direction of the axial direction of the drive shaft 41. Therefore, the longitudinal sectional view is a sectional view in the axial direction of the drive shaft 41, and the transverse sectional view is a sectional view in the vertical direction of the axial direction of the drive shaft 41.
In the drawings, the same reference numerals denote the same or corresponding parts, and this is common throughout the entire specification.
なお、以下の実施の形態において、縦方向とは、後述する駆動軸41の軸方向であり、横方向とは、駆動軸41の軸方向の垂直方向である。したがって、縦断面図とは、駆動軸41の軸方向の断面図であり、横断面図とは、駆動軸41の軸方向の垂直方向の断面図である。
また、図において、同一の符号を付したものは、同一またはこれに相当するものであり、このことは、明細書の全文において共通することである。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
In the following embodiments, the vertical direction is an axial direction of a
In the drawings, the same reference numerals denote the same or corresponding parts, and this is common throughout the entire specification.
実施の形態1.
図1は、実施の形態1に係る二段ロータリ圧縮機の縦断面図である。
二段ロータリ圧縮機は、密閉容器21内に、中間プレート48を挟んで低段圧縮部1と高段圧縮部2とが収納される。密閉容器21内の低段圧縮部1と高段圧縮部2との上側に電動機22が配置される。電動機22は、低段圧縮部1および高段圧縮部2と駆動軸41で連結されている。電動機22が駆動することにより、低段圧縮部1と高段圧縮部2とが駆動され、低段圧縮部1と高段圧縮部2とで冷媒を順次圧縮する。Embodiment 1 FIG.
1 is a longitudinal sectional view of a two-stage rotary compressor according toEmbodiment 1. FIG.
In the two-stage rotary compressor, the low-stage compression section 1 and the high-stage compression section 2 are accommodated in the sealed container 21 with the intermediate plate 48 interposed therebetween. An electric motor 22 is disposed above the low-stage compression unit 1 and the high-stage compression unit 2 in the hermetic container 21. The electric motor 22 is connected to the low-stage compression unit 1 and the high-stage compression unit 2 by a drive shaft 41. When the electric motor 22 is driven, the low-stage compressor 1 and the high-stage compressor 2 are driven, and the low-stage compressor 1 and the high-stage compressor 2 sequentially compress the refrigerant.
図1は、実施の形態1に係る二段ロータリ圧縮機の縦断面図である。
二段ロータリ圧縮機は、密閉容器21内に、中間プレート48を挟んで低段圧縮部1と高段圧縮部2とが収納される。密閉容器21内の低段圧縮部1と高段圧縮部2との上側に電動機22が配置される。電動機22は、低段圧縮部1および高段圧縮部2と駆動軸41で連結されている。電動機22が駆動することにより、低段圧縮部1と高段圧縮部2とが駆動され、低段圧縮部1と高段圧縮部2とで冷媒を順次圧縮する。
1 is a longitudinal sectional view of a two-stage rotary compressor according to
In the two-stage rotary compressor, the low-
冷媒と潤滑油との流れについて説明する。
外部回路と接続された吸入配管5を経由して(図1の(1))、低圧の冷媒が密閉容器21内へ吸入される(図1の(2))。密閉容器21内に吸入された冷媒は、密閉容器21と低段圧縮部1とを接続する低段吸入配管6を経由して(図1の(3))、低段圧縮部1へ流入する(図1の(4))。
低段圧縮部1は、低圧の冷媒を中間圧まで圧縮する。中間圧まで圧縮された冷媒は、低段吐出マフラ3へ吐出される(図1の(5))。低段吐出マフラ3へ吐出された冷媒は、中間連結部7を経由して(図1の(6))、高段圧縮部2へ流入する(図1の(7))。ここで、低段圧縮部1と高段圧縮部2とをつなぐ、低段吐出マフラ3と中間連結部7等を中間流路と呼ぶ。
高段圧縮部2では、中間圧の冷媒を高圧まで圧縮する。高圧まで圧縮された冷媒は、高段吐出マフラ4へ吐出される(図1の(8))。高段吐出マフラ4へ吐出された冷媒は、高段吐出配管8を経由して(図1の(9))、油分離機構9へ流入する(図1の(10))。油分離機構9へ流入した冷媒は、油分離機構9で潤滑油が分離されて外部回路へ吐出される(図1の(11))。 The flow of refrigerant and lubricating oil will be described.
Via thesuction pipe 5 connected to the external circuit ((1) in FIG. 1), the low-pressure refrigerant is sucked into the sealed container 21 ((2) in FIG. 1). The refrigerant sucked into the sealed container 21 flows into the low-stage compression section 1 via the low-stage suction pipe 6 that connects the sealed container 21 and the low-stage compression section 1 ((3) in FIG. 1). ((4) in FIG. 1).
The lowstage compression unit 1 compresses a low-pressure refrigerant to an intermediate pressure. The refrigerant compressed to the intermediate pressure is discharged to the low-stage discharge muffler 3 ((5) in FIG. 1). The refrigerant discharged to the low-stage discharge muffler 3 flows into the high-stage compression section 2 ((7) in FIG. 1) via the intermediate connecting section 7 ((6) in FIG. 1). Here, the low-stage discharge muffler 3, the intermediate connecting portion 7 and the like that connect the low-stage compression unit 1 and the high-stage compression unit 2 are referred to as an intermediate flow path.
The high-stage compression unit 2 compresses the intermediate pressure refrigerant to a high pressure. The refrigerant compressed to a high pressure is discharged to the high-stage discharge muffler 4 ((8) in FIG. 1). The refrigerant discharged to the high-stage discharge muffler 4 flows into the oil separation mechanism 9 ((10) in FIG. 1) via the high-stage discharge pipe 8 ((9) in FIG. 1). The refrigerant that has flowed into the oil separation mechanism 9 is separated into lubricating oil by the oil separation mechanism 9 and discharged to the external circuit ((11) in FIG. 1).
外部回路と接続された吸入配管5を経由して(図1の(1))、低圧の冷媒が密閉容器21内へ吸入される(図1の(2))。密閉容器21内に吸入された冷媒は、密閉容器21と低段圧縮部1とを接続する低段吸入配管6を経由して(図1の(3))、低段圧縮部1へ流入する(図1の(4))。
低段圧縮部1は、低圧の冷媒を中間圧まで圧縮する。中間圧まで圧縮された冷媒は、低段吐出マフラ3へ吐出される(図1の(5))。低段吐出マフラ3へ吐出された冷媒は、中間連結部7を経由して(図1の(6))、高段圧縮部2へ流入する(図1の(7))。ここで、低段圧縮部1と高段圧縮部2とをつなぐ、低段吐出マフラ3と中間連結部7等を中間流路と呼ぶ。
高段圧縮部2では、中間圧の冷媒を高圧まで圧縮する。高圧まで圧縮された冷媒は、高段吐出マフラ4へ吐出される(図1の(8))。高段吐出マフラ4へ吐出された冷媒は、高段吐出配管8を経由して(図1の(9))、油分離機構9へ流入する(図1の(10))。油分離機構9へ流入した冷媒は、油分離機構9で潤滑油が分離されて外部回路へ吐出される(図1の(11))。 The flow of refrigerant and lubricating oil will be described.
Via the
The low
The high-
油分離機構9で分離された潤滑油は、油分離機構9下部の高圧油貯蔵部51に貯えられる(図1の(12))。高圧油貯蔵部51に貯えられた潤滑油は、給油回路13を通って(図1の(13))、低段給油配管14、高段給油配管15から(図1の(14))、低段圧縮部1、高段圧縮部2のベーン背圧室50へ給油される(図1の(15),(16))。さらに、高段ローリングピストン給油配管20により、高段側のローリングピストン42の上下端面へも給油される(図1の(17))。
また、高圧油貯蔵部51に貯えられた潤滑油の一部は、給油回路13を通って(図1の(13))、バッファ部12(給油部)に貯えられる(図1の(18))。 The lubricating oil separated by theoil separation mechanism 9 is stored in the high-pressure oil storage section 51 below the oil separation mechanism 9 ((12) in FIG. 1). The lubricating oil stored in the high-pressure oil storage 51 passes through the oil supply circuit 13 ((13) in FIG. 1), and from the low oil supply pipe 14 and the high oil supply pipe 15 ((14) in FIG. 1), Oil is supplied to the vane back pressure chamber 50 of the stage compression section 1 and the high stage compression section 2 ((15) and (16) in FIG. 1). Further, oil is supplied also to the upper and lower end surfaces of the high-stage rolling piston 42 by the high-stage rolling piston oil supply pipe 20 ((17) in FIG. 1).
A part of the lubricating oil stored in the high-pressureoil storage unit 51 passes through the oil supply circuit 13 ((13) in FIG. 1) and is stored in the buffer unit 12 (oil supply unit) ((18) in FIG. 1). ).
また、高圧油貯蔵部51に貯えられた潤滑油の一部は、給油回路13を通って(図1の(13))、バッファ部12(給油部)に貯えられる(図1の(18))。 The lubricating oil separated by the
A part of the lubricating oil stored in the high-pressure
また、中間連結部7から分岐してバッファ部12へ繋がるバイパス回路10から、低段吐出マフラ3へ吐出された冷媒がバッファ部12内へ流入する(図1の(19))。バイパス回路10には、逆止め機構11が設けられている。逆止め機構11は、中間流路内の圧力(中間圧)が高段圧縮部2の吐出圧力(高圧)よりも高くなるという圧力の逆転現象が起こった場合に、中間連結部7からバッファ部12へ冷媒を流入させる。なお、逆止め機構11は、中間連結部7からバッファ部12へ向かう流れのみ許容する。
また、バイパス回路10の逆止め機構11とバッファ部12との間から分岐して、油分離機構9へ繋がる均圧回路16が設けられる。均圧回路16には、均圧部17が設けられる。油分離機構9内の圧力とバッファ部12内の圧力とは、均圧部17を介して均一の圧力となる。特に、均圧部17は、後述するように、油分離機構9内の圧力とバッファ部12内の圧力と均一の圧力とする速さ(均一の圧力になるまでにかかる時間)を調整する。 Further, the refrigerant discharged to the low-stage discharge muffler 3 flows into the buffer part 12 from the bypass circuit 10 branched from the intermediate connecting part 7 and connected to the buffer part 12 ((19) in FIG. 1). The bypass circuit 10 is provided with a check mechanism 11. The non-return mechanism 11 is configured so that when the pressure reversal phenomenon occurs in which the pressure in the intermediate flow path (intermediate pressure) becomes higher than the discharge pressure (high pressure) of the high-stage compression section 2, the intermediate coupling section 7 and the buffer section The refrigerant is caused to flow into 12. The non-return mechanism 11 allows only the flow from the intermediate connecting portion 7 toward the buffer portion 12.
Further, apressure equalizing circuit 16 that branches from between the non-return mechanism 11 of the bypass circuit 10 and the buffer unit 12 and is connected to the oil separation mechanism 9 is provided. The pressure equalizing circuit 16 is provided with a pressure equalizing unit 17. The pressure in the oil separation mechanism 9 and the pressure in the buffer unit 12 become a uniform pressure through the pressure equalizing unit 17. In particular, as will be described later, the pressure equalizing unit 17 adjusts the pressure in the oil separation mechanism 9 and the pressure in the buffer unit 12 and the speed at which the pressure is uniform (the time required to reach a uniform pressure).
また、バイパス回路10の逆止め機構11とバッファ部12との間から分岐して、油分離機構9へ繋がる均圧回路16が設けられる。均圧回路16には、均圧部17が設けられる。油分離機構9内の圧力とバッファ部12内の圧力とは、均圧部17を介して均一の圧力となる。特に、均圧部17は、後述するように、油分離機構9内の圧力とバッファ部12内の圧力と均一の圧力とする速さ(均一の圧力になるまでにかかる時間)を調整する。 Further, the refrigerant discharged to the low-
Further, a
図2は、ローリングピストン型のロータリ圧縮機の圧縮部の横断面図である。なお、基本的な構成は低段圧縮部1、高段圧縮部2ともに同一である。
ローリングピストン型のロータリ圧縮機の圧縮部は、図2に示すように、シリンダ45、ローリングピストン42、ベーン43を備える。
シリンダ45は、一方が軸受けにより閉塞され、他方が中間プレート48により閉塞され圧縮空間を形成する。ローリングピストン42は、シリンダ45内に駆動軸41の偏芯軸部分に嵌合される。ベーン43は、ローリングピストン42に当接して、シリンダ45、軸受け、中間プレート48により形成された圧縮空間に、吸入室70と圧縮室71とを形成する。特に、ベーン43は、バネ44のバネ力と、ベーン背圧室50に給油された潤滑油の圧力とにより、ベーン背圧室50側からローリングピストン42側へ向けて荷重をかけられる。この荷重により、ベーン43は、常にローリングピストン42に押し付けられている。
電動機22が駆動して、電動機22に連結された駆動軸41が回転することにより、駆動軸41に嵌合されたローリングピストン42が偏芯回転する。ローリングピストン42が偏芯回転することにより、吸入室70と圧縮室71との容積が変化する。この容積の変化により、冷媒が吸入口46から吸入され、圧縮されて吐出口47から吐出される。 FIG. 2 is a cross-sectional view of a compression portion of a rolling piston type rotary compressor. The basic configuration is the same for both the low-stage compression unit 1 and the high-stage compression unit 2.
As shown in FIG. 2, the compression portion of the rolling piston type rotary compressor includes acylinder 45, a rolling piston 42, and a vane 43.
One of thecylinders 45 is closed by a bearing and the other is closed by an intermediate plate 48 to form a compression space. The rolling piston 42 is fitted into the eccentric shaft portion of the drive shaft 41 in the cylinder 45. The vane 43 abuts on the rolling piston 42 and forms a suction chamber 70 and a compression chamber 71 in a compression space formed by the cylinder 45, the bearing, and the intermediate plate 48. In particular, the vane 43 is loaded from the vane back pressure chamber 50 side to the rolling piston 42 side by the spring force of the spring 44 and the pressure of the lubricating oil supplied to the vane back pressure chamber 50. Due to this load, the vane 43 is always pressed against the rolling piston 42.
When theelectric motor 22 is driven and the drive shaft 41 connected to the electric motor 22 rotates, the rolling piston 42 fitted to the drive shaft 41 rotates eccentrically. As the rolling piston 42 rotates eccentrically, the volumes of the suction chamber 70 and the compression chamber 71 change. Due to this change in volume, the refrigerant is sucked from the suction port 46, compressed and discharged from the discharge port 47.
ローリングピストン型のロータリ圧縮機の圧縮部は、図2に示すように、シリンダ45、ローリングピストン42、ベーン43を備える。
シリンダ45は、一方が軸受けにより閉塞され、他方が中間プレート48により閉塞され圧縮空間を形成する。ローリングピストン42は、シリンダ45内に駆動軸41の偏芯軸部分に嵌合される。ベーン43は、ローリングピストン42に当接して、シリンダ45、軸受け、中間プレート48により形成された圧縮空間に、吸入室70と圧縮室71とを形成する。特に、ベーン43は、バネ44のバネ力と、ベーン背圧室50に給油された潤滑油の圧力とにより、ベーン背圧室50側からローリングピストン42側へ向けて荷重をかけられる。この荷重により、ベーン43は、常にローリングピストン42に押し付けられている。
電動機22が駆動して、電動機22に連結された駆動軸41が回転することにより、駆動軸41に嵌合されたローリングピストン42が偏芯回転する。ローリングピストン42が偏芯回転することにより、吸入室70と圧縮室71との容積が変化する。この容積の変化により、冷媒が吸入口46から吸入され、圧縮されて吐出口47から吐出される。 FIG. 2 is a cross-sectional view of a compression portion of a rolling piston type rotary compressor. The basic configuration is the same for both the low-
As shown in FIG. 2, the compression portion of the rolling piston type rotary compressor includes a
One of the
When the
図3は、実施の形態1に係る二段ロータリ圧縮機の正常運転時における動作を示す図である。なお、図3において、太線は冷媒回路を示し、点線は給油回路を示す。また、実線矢印は、冷媒の流れを示し、点線矢印は潤滑油の流れを示す。
正常運転時は、逆止め機構11によりバイパス回路10の高圧側(バッファ部12側)と中間圧側(中間連結部7側)は遮断されている。したがって、バイパス回路10を経由して、中間連結部7からバッファ部12へ冷媒は流入しない。そのため、油分離機構9と繋がるバッファ部12は、油分離機構9と均一の圧力であるため、高圧である。また、油分離機構9から潤滑油が給油されるベーン背圧室50の圧力も高圧である。
高段圧縮部2のシリンダ45内の圧力は、中間圧から高圧の間で変化しており、平均を取れば中間圧と高圧との間の圧力となる。つまり、正常運転時は、ベーン背圧室50内の圧力は、高段圧縮部2のシリンダ45内の圧力よりも高い。そのため、正常運転時には、ベーン背圧室50内の圧力により、ベーン43は、ベーン背圧室50側からローリングピストン42側へ押圧され、ローリングピストン42に押し付けられる。 FIG. 3 is a diagram illustrating an operation during normal operation of the two-stage rotary compressor according to the first embodiment. In FIG. 3, a thick line indicates a refrigerant circuit, and a dotted line indicates an oil supply circuit. Moreover, a solid line arrow shows the flow of a refrigerant | coolant, and a dotted line arrow shows the flow of lubricating oil.
During normal operation, thecheck mechanism 11 blocks the high pressure side (buffer portion 12 side) and the intermediate pressure side (intermediate connection portion 7 side) of the bypass circuit 10. Therefore, the refrigerant does not flow from the intermediate connecting portion 7 to the buffer portion 12 via the bypass circuit 10. Therefore, the buffer unit 12 connected to the oil separation mechanism 9 is at a high pressure because it has a uniform pressure with the oil separation mechanism 9. The pressure in the vane back pressure chamber 50 to which the lubricating oil is supplied from the oil separation mechanism 9 is also high.
The pressure in thecylinder 45 of the high-stage compression unit 2 changes between an intermediate pressure and a high pressure. If an average is taken, the pressure is between the intermediate pressure and the high pressure. That is, during normal operation, the pressure in the vane back pressure chamber 50 is higher than the pressure in the cylinder 45 of the high-stage compression unit 2. Therefore, during normal operation, the vane 43 is pressed from the vane back pressure chamber 50 side to the rolling piston 42 side by the pressure in the vane back pressure chamber 50 and is pressed against the rolling piston 42.
正常運転時は、逆止め機構11によりバイパス回路10の高圧側(バッファ部12側)と中間圧側(中間連結部7側)は遮断されている。したがって、バイパス回路10を経由して、中間連結部7からバッファ部12へ冷媒は流入しない。そのため、油分離機構9と繋がるバッファ部12は、油分離機構9と均一の圧力であるため、高圧である。また、油分離機構9から潤滑油が給油されるベーン背圧室50の圧力も高圧である。
高段圧縮部2のシリンダ45内の圧力は、中間圧から高圧の間で変化しており、平均を取れば中間圧と高圧との間の圧力となる。つまり、正常運転時は、ベーン背圧室50内の圧力は、高段圧縮部2のシリンダ45内の圧力よりも高い。そのため、正常運転時には、ベーン背圧室50内の圧力により、ベーン43は、ベーン背圧室50側からローリングピストン42側へ押圧され、ローリングピストン42に押し付けられる。 FIG. 3 is a diagram illustrating an operation during normal operation of the two-stage rotary compressor according to the first embodiment. In FIG. 3, a thick line indicates a refrigerant circuit, and a dotted line indicates an oil supply circuit. Moreover, a solid line arrow shows the flow of a refrigerant | coolant, and a dotted line arrow shows the flow of lubricating oil.
During normal operation, the
The pressure in the
図4は、実施の形態1に係るローリングピストン型ロータリ圧縮機の圧縮部における冷媒の漏れ経路を示す横断面図である。
圧縮機の起動時や運転条件の変更時において、圧縮室71側から吸入室70側へ冷媒の漏れが発生する場合がある。これは、例えば、一時的に給油が安定しない場合や、潤滑油中の冷媒が潤滑油と分離して発泡した場合等に発生する。特に、潤滑油によりシールされている箇所から冷媒の漏れが発生する。
つまり、図4に点線矢印で示すように、ローリングピストン42とシリンダ45の隙間(図4のa)、ローリングピストン42上下端面の隙間(図4のb)、ベーン43の上下側端面隙間(図4のc)等から、圧縮室71側から吸入室70側へ冷媒の漏れが発生する。なお、圧縮室71からローリングピストン42の駆動軸41側へも冷媒の漏れが発生する(図4のd)。
高段圧縮部2において圧縮室71側から吸入室70側に冷媒が漏れることで、中間圧が上昇する。そして、高圧よりも中間圧の方が高くなる圧力の逆転現象が発生する。 FIG. 4 is a transverse cross-sectional view showing a refrigerant leakage path in the compression portion of the rolling piston rotary compressor according to the first embodiment.
When starting up the compressor or changing operating conditions, refrigerant leakage may occur from thecompression chamber 71 side to the suction chamber 70 side. This occurs, for example, when the oil supply is temporarily unstable or when the refrigerant in the lubricating oil is separated from the lubricating oil and foamed. In particular, the refrigerant leaks from the portion sealed with the lubricating oil.
That is, as indicated by dotted arrows in FIG. 4, the clearance between the rollingpiston 42 and the cylinder 45 (a in FIG. 4), the clearance between the upper and lower end surfaces of the rolling piston 42 (b in FIG. 4), and the upper and lower end surface clearances of the vane 43 (see FIG. 4). 4 c) and the like, the refrigerant leaks from the compression chamber 71 side to the suction chamber 70 side. Note that refrigerant leaks also from the compression chamber 71 to the drive shaft 41 side of the rolling piston 42 (d in FIG. 4).
As the refrigerant leaks from thecompression chamber 71 side to the suction chamber 70 side in the high-stage compression unit 2, the intermediate pressure rises. A pressure reversal phenomenon occurs in which the intermediate pressure is higher than the high pressure.
圧縮機の起動時や運転条件の変更時において、圧縮室71側から吸入室70側へ冷媒の漏れが発生する場合がある。これは、例えば、一時的に給油が安定しない場合や、潤滑油中の冷媒が潤滑油と分離して発泡した場合等に発生する。特に、潤滑油によりシールされている箇所から冷媒の漏れが発生する。
つまり、図4に点線矢印で示すように、ローリングピストン42とシリンダ45の隙間(図4のa)、ローリングピストン42上下端面の隙間(図4のb)、ベーン43の上下側端面隙間(図4のc)等から、圧縮室71側から吸入室70側へ冷媒の漏れが発生する。なお、圧縮室71からローリングピストン42の駆動軸41側へも冷媒の漏れが発生する(図4のd)。
高段圧縮部2において圧縮室71側から吸入室70側に冷媒が漏れることで、中間圧が上昇する。そして、高圧よりも中間圧の方が高くなる圧力の逆転現象が発生する。 FIG. 4 is a transverse cross-sectional view showing a refrigerant leakage path in the compression portion of the rolling piston rotary compressor according to the first embodiment.
When starting up the compressor or changing operating conditions, refrigerant leakage may occur from the
That is, as indicated by dotted arrows in FIG. 4, the clearance between the rolling
As the refrigerant leaks from the
圧力の逆転現象が発生した場合、高段圧縮部2のベーン背圧室50にかかっている圧力(高圧)よりも、高段圧縮部2内の圧力(中間圧)の方が高くなってしまう。そして、ベーン43をローリングピストン42側からベーン背圧室50側へ押す荷重(高段圧縮部2内の圧力)が、ベーン43をベーン背圧室50側からローリングピストン42側へ押す荷重(ベーン背圧室50内の圧力と、バネ44のバネ力との合計)を超えると、ベーン43がローリングピストン42から離脱するベーン飛びという現象が発生する。ベーン飛びが発生すると、吸入室70と圧縮室71とが完全に連通する。そのため、高段圧縮部2では冷媒が圧縮されなくなる。
また、この場合、ベーン43が、ローリングピストン42と離脱して、ローリングピストン42へ衝突することを繰り返すチャタリング現象が発生することもある。そのため、ベーン43やローリングピストン42が破損することや、圧縮機の振動、騒音に繋がることもある。
さらに、高段圧縮部2で冷媒が圧縮されないため、低段圧縮部1のみで冷媒を圧縮することになってしまう。そのため、圧縮機の性能が低下するとともに、低段圧縮部1に負荷がかかることによる信頼性の低下にも繋がる。 When the pressure reversal phenomenon occurs, the pressure (intermediate pressure) in the high-stage compression section 2 becomes higher than the pressure (high pressure) applied to the vane back pressure chamber 50 of the high-stage compression section 2. . A load that pushes the vane 43 from the rolling piston 42 side to the vane back pressure chamber 50 side (pressure in the high-stage compression unit 2) pushes the vane 43 from the vane back pressure chamber 50 side to the rolling piston 42 side (vane). When the pressure in the back pressure chamber 50 and the total spring force of the spring 44 are exceeded, a phenomenon of vane jumping in which the vane 43 is detached from the rolling piston 42 occurs. When the vane jump occurs, the suction chamber 70 and the compression chamber 71 are completely communicated with each other. Therefore, the refrigerant is not compressed in the high stage compression unit 2.
In this case, a chattering phenomenon may occur in which thevane 43 is separated from the rolling piston 42 and repeatedly collides with the rolling piston 42. For this reason, the vane 43 and the rolling piston 42 may be damaged, and vibration and noise of the compressor may be caused.
Furthermore, since the refrigerant is not compressed by the high-stage compression unit 2, the refrigerant is compressed only by the low-stage compression unit 1. Therefore, the performance of the compressor is lowered, and the reliability is lowered due to the load applied to the low-stage compression unit 1.
また、この場合、ベーン43が、ローリングピストン42と離脱して、ローリングピストン42へ衝突することを繰り返すチャタリング現象が発生することもある。そのため、ベーン43やローリングピストン42が破損することや、圧縮機の振動、騒音に繋がることもある。
さらに、高段圧縮部2で冷媒が圧縮されないため、低段圧縮部1のみで冷媒を圧縮することになってしまう。そのため、圧縮機の性能が低下するとともに、低段圧縮部1に負荷がかかることによる信頼性の低下にも繋がる。 When the pressure reversal phenomenon occurs, the pressure (intermediate pressure) in the high-
In this case, a chattering phenomenon may occur in which the
Furthermore, since the refrigerant is not compressed by the high-
図5は、実施の形態1に係る二段ロータリ圧縮機において圧力の逆転現象が起こった場合における動作を示す図である。なお、図5において、太線は冷媒回路を示し、点線は給油回路を示す。また、実線矢印は、冷媒の流れを示し、点線矢印は潤滑油の流れを示す。
圧力の逆転現象が発生した場合、逆止め機構11(給油促進部)が作動する。そして、バイパス回路10を経由して、中間連結部7からバッファ部12へ高圧の冷媒よりも圧力の高くなった中間圧の冷媒を流入させる。高圧の冷媒よりも圧力の高くなった中間圧の冷媒をバッファ部12へ流入させることにより、バッファ部12に貯えられた潤滑油に加圧する。これにより、高段圧縮部2のベーン背圧室50へ差圧により給油される。つまり、バイパス回路10を経由して中間連結部7からバッファ部12へ冷媒が流入することにより、高段圧縮部2のベーン背圧室50への給油が促進される。
その結果、ベーン背圧室50の圧力と高段圧縮部2内の圧力とが均一の圧力になる。
つまり、高段圧縮部2のシリンダ45内の圧力は、圧力の逆転現象により高圧である。一方、バッファ部12へ高圧の冷媒を流入させてベーン背圧室50へ差圧給油したため、ベーン背圧室50内の圧力も高圧である。したがって、ベーン背圧室50内の圧力と、高段圧縮部2のシリンダ45内の圧力とは、均一である。そのため、バネ44のバネ力により、ベーン43は、ベーン背圧室50側からローリングピストン42側へ押圧され、ローリングピストン42に押し付けられる。
ベーン43がローリングピストン42に押し付けられることにより、吸入室70と圧縮室71とが形成され、高段圧縮部2で冷媒が圧縮されるようになる。高段圧縮部2で冷媒が圧縮されると中間圧が下がっていき、正常な運転状態に復帰する。 FIG. 5 is a diagram illustrating an operation when a pressure reversal phenomenon occurs in the two-stage rotary compressor according to the first embodiment. In FIG. 5, a thick line indicates a refrigerant circuit, and a dotted line indicates an oil supply circuit. Moreover, a solid line arrow shows the flow of a refrigerant | coolant, and a dotted line arrow shows the flow of lubricating oil.
When the pressure reverse phenomenon occurs, the check mechanism 11 (oil supply promoting portion) operates. Then, an intermediate-pressure refrigerant having a pressure higher than that of the high-pressure refrigerant is caused to flow from theintermediate connection portion 7 to the buffer portion 12 via the bypass circuit 10. By causing the intermediate pressure refrigerant whose pressure is higher than that of the high pressure refrigerant to flow into the buffer unit 12, the lubricating oil stored in the buffer unit 12 is pressurized. Thereby, the vane back pressure chamber 50 of the high stage compression unit 2 is supplied with a differential pressure. That is, when the refrigerant flows from the intermediate connecting portion 7 to the buffer portion 12 via the bypass circuit 10, the fuel supply to the vane back pressure chamber 50 of the high stage compression portion 2 is promoted.
As a result, the pressure in the vane backpressure chamber 50 and the pressure in the high-stage compression unit 2 become uniform.
That is, the pressure in thecylinder 45 of the high-stage compression unit 2 is high due to the reverse phenomenon of pressure. On the other hand, since the high pressure refrigerant is introduced into the buffer unit 12 and the differential pressure oil is supplied to the vane back pressure chamber 50, the pressure in the vane back pressure chamber 50 is also high. Therefore, the pressure in the vane back pressure chamber 50 and the pressure in the cylinder 45 of the high-stage compression unit 2 are uniform. Therefore, the vane 43 is pressed from the vane back pressure chamber 50 side to the rolling piston 42 side by the spring force of the spring 44 and is pressed against the rolling piston 42.
When thevane 43 is pressed against the rolling piston 42, the suction chamber 70 and the compression chamber 71 are formed, and the refrigerant is compressed in the high-stage compression unit 2. When the refrigerant is compressed by the high-stage compression unit 2, the intermediate pressure decreases and the normal operation state is restored.
圧力の逆転現象が発生した場合、逆止め機構11(給油促進部)が作動する。そして、バイパス回路10を経由して、中間連結部7からバッファ部12へ高圧の冷媒よりも圧力の高くなった中間圧の冷媒を流入させる。高圧の冷媒よりも圧力の高くなった中間圧の冷媒をバッファ部12へ流入させることにより、バッファ部12に貯えられた潤滑油に加圧する。これにより、高段圧縮部2のベーン背圧室50へ差圧により給油される。つまり、バイパス回路10を経由して中間連結部7からバッファ部12へ冷媒が流入することにより、高段圧縮部2のベーン背圧室50への給油が促進される。
その結果、ベーン背圧室50の圧力と高段圧縮部2内の圧力とが均一の圧力になる。
つまり、高段圧縮部2のシリンダ45内の圧力は、圧力の逆転現象により高圧である。一方、バッファ部12へ高圧の冷媒を流入させてベーン背圧室50へ差圧給油したため、ベーン背圧室50内の圧力も高圧である。したがって、ベーン背圧室50内の圧力と、高段圧縮部2のシリンダ45内の圧力とは、均一である。そのため、バネ44のバネ力により、ベーン43は、ベーン背圧室50側からローリングピストン42側へ押圧され、ローリングピストン42に押し付けられる。
ベーン43がローリングピストン42に押し付けられることにより、吸入室70と圧縮室71とが形成され、高段圧縮部2で冷媒が圧縮されるようになる。高段圧縮部2で冷媒が圧縮されると中間圧が下がっていき、正常な運転状態に復帰する。 FIG. 5 is a diagram illustrating an operation when a pressure reversal phenomenon occurs in the two-stage rotary compressor according to the first embodiment. In FIG. 5, a thick line indicates a refrigerant circuit, and a dotted line indicates an oil supply circuit. Moreover, a solid line arrow shows the flow of a refrigerant | coolant, and a dotted line arrow shows the flow of lubricating oil.
When the pressure reverse phenomenon occurs, the check mechanism 11 (oil supply promoting portion) operates. Then, an intermediate-pressure refrigerant having a pressure higher than that of the high-pressure refrigerant is caused to flow from the
As a result, the pressure in the vane back
That is, the pressure in the
When the
逆止め機構11が作動した場合、バッファ部12内の油面高さが、油分離機構9内の油面高さよりも下がった状態になる。これは、バッファ部12内の圧力が油分離機構9内の圧力よりも高くなったためである。この状態では、正常な運転状態に復帰した後も、バッファ部12内の高い圧力により、高段圧縮部2のベーン背圧室50等へ差圧給油される。また、バッファ部12内の油面高さが下がったままの上体で再度逆止め機構11が作動した場合、バッファ部12内の油がなくなってしまう虞がある。
そこで、油分離機構9とバッファ部12とを繋ぐ均圧回路16に設けられた均圧部17により、油分離機構9内とバッファ部12内の冷媒ガス空間を均一の圧力にする。 When thecheck mechanism 11 is activated, the oil level in the buffer unit 12 is lower than the oil level in the oil separation mechanism 9. This is because the pressure in the buffer unit 12 is higher than the pressure in the oil separation mechanism 9. In this state, even after returning to the normal operation state, the differential pressure is supplied to the vane back pressure chamber 50 and the like of the high-stage compression unit 2 by the high pressure in the buffer unit 12. Further, when the check mechanism 11 is actuated again with the upper body with the oil level in the buffer portion 12 lowered, there is a possibility that the oil in the buffer portion 12 may be lost.
Therefore, the pressure in the refrigerant gas space in theoil separation mechanism 9 and the buffer part 12 is made uniform by the pressure equalization part 17 provided in the pressure equalization circuit 16 that connects the oil separation mechanism 9 and the buffer part 12.
そこで、油分離機構9とバッファ部12とを繋ぐ均圧回路16に設けられた均圧部17により、油分離機構9内とバッファ部12内の冷媒ガス空間を均一の圧力にする。 When the
Therefore, the pressure in the refrigerant gas space in the
均圧部17は、例えば、逆止め機構11の作動時に影響が少ない微小な隙間、もしくは微小な孔等である。
逆止め機構11の作動時に影響が少ないとは、逆止め機構11が作動した場合に、ベーン背圧室50の圧力と高段圧縮部2内の圧力とを均一の圧力にすることを妨げないということである。
上述したように、逆止め機構11が作動して、中間連結部7からバッファ部12へ冷媒を流入させ、バッファ部12内の圧力を高くすることで、ベーン背圧室50の圧力と高段圧縮部2内の圧力とを均一の圧力にする。ここで、油分離機構9とバッファ部12とが太い冷媒管で繋がっていた場合、中間連結部7からバッファ部12へ流入する冷媒は油分離機構9側へ流れるため、バッファ部12内の圧力は高くならない。
そこで、均圧部17は、微小な隙間、もしくは微小な孔等として、中間連結部7からバッファ部12へ冷媒が流入した場合に、バッファ部12内の圧力が高くなるようにする。 Thepressure equalizing unit 17 is, for example, a minute gap or a minute hole that has little influence when the check mechanism 11 is operated.
The fact that there is little influence when thecheck mechanism 11 is operated does not prevent the pressure in the vane back pressure chamber 50 and the pressure in the high-stage compression unit 2 from being made uniform when the check mechanism 11 is operated. That's what it means.
As described above, thenon-return mechanism 11 is actuated to cause the refrigerant to flow into the buffer portion 12 from the intermediate connecting portion 7 and increase the pressure in the buffer portion 12, thereby increasing the pressure in the vane back pressure chamber 50. The pressure in the compression unit 2 is made uniform. Here, when the oil separation mechanism 9 and the buffer part 12 are connected by a thick refrigerant pipe, the refrigerant flowing from the intermediate connection part 7 to the buffer part 12 flows to the oil separation mechanism 9 side, so the pressure in the buffer part 12 Will not be high.
Therefore, thepressure equalizing unit 17 causes the pressure in the buffer unit 12 to increase when the refrigerant flows into the buffer unit 12 from the intermediate coupling unit 7 as a minute gap or a minute hole.
逆止め機構11の作動時に影響が少ないとは、逆止め機構11が作動した場合に、ベーン背圧室50の圧力と高段圧縮部2内の圧力とを均一の圧力にすることを妨げないということである。
上述したように、逆止め機構11が作動して、中間連結部7からバッファ部12へ冷媒を流入させ、バッファ部12内の圧力を高くすることで、ベーン背圧室50の圧力と高段圧縮部2内の圧力とを均一の圧力にする。ここで、油分離機構9とバッファ部12とが太い冷媒管で繋がっていた場合、中間連結部7からバッファ部12へ流入する冷媒は油分離機構9側へ流れるため、バッファ部12内の圧力は高くならない。
そこで、均圧部17は、微小な隙間、もしくは微小な孔等として、中間連結部7からバッファ部12へ冷媒が流入した場合に、バッファ部12内の圧力が高くなるようにする。 The
The fact that there is little influence when the
As described above, the
Therefore, the
この微小な隙間や微小な孔等により、逆止め機構11の作動が停止した後、所定の時間をかけて、バッファ部12内の圧力が下がり、油面高さが元に戻る。
つまり、逆止め機構11が作動して、バイパス回路10を経由して中間連結部7からバッファ部12へ冷媒が流入した場合に、一時的にバッファ部12内の圧力が油分離機構9内の圧力よりも高くなる。そして、逆止め機構11の作動が停止してしばらく経つと、バッファ部12内の圧力と油分離機構9内の圧力とが均一の圧力となる。その結果、所定の時間をかけて、バッファ部12内の油面高さが元に戻る。 After the operation of thenon-return mechanism 11 is stopped by the minute gap, minute hole, or the like, the pressure in the buffer unit 12 is lowered over a predetermined time, and the oil level is restored.
That is, when thecheck mechanism 11 is activated and the refrigerant flows from the intermediate connecting portion 7 to the buffer portion 12 via the bypass circuit 10, the pressure in the buffer portion 12 temporarily changes in the oil separation mechanism 9. Higher than pressure. Then, after a while after the operation of the check mechanism 11 is stopped, the pressure in the buffer unit 12 and the pressure in the oil separation mechanism 9 become a uniform pressure. As a result, the oil level in the buffer unit 12 returns to the original state over a predetermined time.
つまり、逆止め機構11が作動して、バイパス回路10を経由して中間連結部7からバッファ部12へ冷媒が流入した場合に、一時的にバッファ部12内の圧力が油分離機構9内の圧力よりも高くなる。そして、逆止め機構11の作動が停止してしばらく経つと、バッファ部12内の圧力と油分離機構9内の圧力とが均一の圧力となる。その結果、所定の時間をかけて、バッファ部12内の油面高さが元に戻る。 After the operation of the
That is, when the
また、均圧部17を設けることにより、油分離機構9内の圧力が変動した場合にも、バッファ部12内の圧力が油分離機構9内の圧力に追従する。
Further, by providing the pressure equalizing unit 17, the pressure in the buffer unit 12 follows the pressure in the oil separating mechanism 9 even when the pressure in the oil separating mechanism 9 fluctuates.
なお、均圧部17は、微小な隙間や微小な孔等に限らず、バルブ等で構成してもよい。
均圧部17をバルブで構成した場合、バルブを常に微小に開けておく。あるいは、通常時にはバルブを閉じておき、逆止め機構11の作動後、又は油分離機構9内の圧力変動時に一時的にバルブを微小に開いてもよい。 Thepressure equalizing unit 17 is not limited to a minute gap, a minute hole, or the like, and may be configured by a valve or the like.
When thepressure equalizing unit 17 is configured by a valve, the valve is always opened minutely. Alternatively, the valve may be closed normally, and the valve may be slightly opened temporarily after the check mechanism 11 is activated or when the pressure in the oil separation mechanism 9 varies.
均圧部17をバルブで構成した場合、バルブを常に微小に開けておく。あるいは、通常時にはバルブを閉じておき、逆止め機構11の作動後、又は油分離機構9内の圧力変動時に一時的にバルブを微小に開いてもよい。 The
When the
以上のように、実施の形態1に係る二段ロータリ圧縮機では、圧力の逆転現象が起きた場合に、バイパス回路10を経由して中間連結部7からバッファ部12へ冷媒を流入させる。これにより、高段圧縮部2のベーン背圧室50等への給油を促進して、高段圧縮部2のベーン背圧室50内の圧力と高段圧縮部2内の圧力とを均一の圧力にすることができる。その結果、ベーン飛び等の現象が解消して、高段圧縮部2でも冷媒が圧縮されるようになり、正常状態へ復帰することができる。したがって、実施の形態1に係る二段ロータリ圧縮機は、性能がよく、信頼性が高い。
As described above, in the two-stage rotary compressor according to the first embodiment, when the pressure reversal phenomenon occurs, the refrigerant is caused to flow from the intermediate coupling portion 7 to the buffer portion 12 via the bypass circuit 10. Thereby, the oil supply to the vane back pressure chamber 50 of the high stage compression unit 2 is promoted, and the pressure in the vane back pressure chamber 50 of the high stage compression unit 2 and the pressure in the high stage compression unit 2 are made uniform. Can be pressure. As a result, phenomena such as vane jumping are eliminated, and the refrigerant is compressed even in the high-stage compression unit 2, and the normal state can be restored. Therefore, the two-stage rotary compressor according to Embodiment 1 has good performance and high reliability.
なお、上記説明では、冷媒の漏れが発生した場合に、圧力の逆転現象が起こると説明した。しかし、冷媒の漏れが発生した場合だけでなく、低圧縮比で運転する場合に低段圧縮部1だけで吐出圧力に達してしまうような条件においても、圧力の逆転現象が起こる場合がある。
この場合においても、実施の形態1に係る二段ロータリ圧縮機では、冷媒の漏れが発生した場合と同様に、正常状態に復帰することが可能である。 In the above description, it has been described that the pressure reversal phenomenon occurs when the refrigerant leaks. However, not only when the refrigerant leaks, but also when the operation is performed at a low compression ratio, the pressure reversal phenomenon may occur even under conditions where the discharge pressure is reached only by the low-stage compression unit 1.
Even in this case, in the two-stage rotary compressor according to the first embodiment, it is possible to return to the normal state as in the case where the refrigerant leaks.
この場合においても、実施の形態1に係る二段ロータリ圧縮機では、冷媒の漏れが発生した場合と同様に、正常状態に復帰することが可能である。 In the above description, it has been described that the pressure reversal phenomenon occurs when the refrigerant leaks. However, not only when the refrigerant leaks, but also when the operation is performed at a low compression ratio, the pressure reversal phenomenon may occur even under conditions where the discharge pressure is reached only by the low-
Even in this case, in the two-stage rotary compressor according to the first embodiment, it is possible to return to the normal state as in the case where the refrigerant leaks.
実施の形態2.
実施の形態1では、ローリングピストン型の二段ロータリ圧縮機について説明した。実施の形態2では、スライディングベーン型の二段ロータリ圧縮機について説明する。Embodiment 2. FIG.
In the first embodiment, the rolling piston type two-stage rotary compressor has been described. In the second embodiment, a sliding vane type two-stage rotary compressor will be described.
実施の形態1では、ローリングピストン型の二段ロータリ圧縮機について説明した。実施の形態2では、スライディングベーン型の二段ロータリ圧縮機について説明する。
In the first embodiment, the rolling piston type two-stage rotary compressor has been described. In the second embodiment, a sliding vane type two-stage rotary compressor will be described.
図6は、実施の形態2に係るスライディングベーン型のロータリ圧縮機の圧縮部の横断面図である。なお、基本的な構成は低段圧縮部1、高段圧縮部2ともに同一である。
スライディングベーン型のロータリ圧縮機の圧縮部は、図6に示すように、シリンダ85、ロータ60を備える。
シリンダ85は、両端面が側板により閉塞される。ロータ60は、シリンダ85の内壁との間に微小隙間を形成して偏芯配置される。ロータ60には、複数のベーン83が挿入される。各ベーン83は、ロータ60から突き出て、シリンダ85の内壁に当接して、シリンダ85と側板とにより形成された空間に、作動室73(圧縮室)を形成する。
電動機が駆動して、電動機に連結された駆動軸81が回転することにより、駆動軸81と一体に形成されたロータ60が回転する。ロータ60が回転することにより、ロータ60に挿入されたベーン83に遠心力を与える。
ベーン83は、ロータ60が回転することによる遠心力と、ベーン背圧室90に給油された潤滑油の圧力とにより、ベーン背圧室90側からシリンダ85の内壁側へ向けて荷重をかけられる。この荷重により、ベーン83は、常にシリンダ85の内壁に押し付けられ、シリンダ85の内壁と摺動する。
ベーン83がシリンダ85の内壁と摺動しながらロータ60が回転することにより、作動室73の容積が変化する。この容積の変化により、冷媒が吸入口86から吸入され、圧縮されて吐出口87から吐出される。 FIG. 6 is a cross-sectional view of a compression unit of a sliding vane rotary compressor according to the second embodiment. The basic configuration is the same for both the low-stage compression unit 1 and the high-stage compression unit 2.
As shown in FIG. 6, the compression unit of the sliding vane type rotary compressor includes acylinder 85 and a rotor 60.
Both ends of thecylinder 85 are closed by side plates. The rotor 60 is eccentrically disposed with a minute gap formed between the rotor 60 and the inner wall of the cylinder 85. A plurality of vanes 83 are inserted into the rotor 60. Each vane 83 protrudes from the rotor 60 and abuts against the inner wall of the cylinder 85 to form a working chamber 73 (compression chamber) in a space formed by the cylinder 85 and the side plate.
When the electric motor is driven and thedrive shaft 81 connected to the electric motor rotates, the rotor 60 formed integrally with the drive shaft 81 rotates. As the rotor 60 rotates, centrifugal force is applied to the vane 83 inserted into the rotor 60.
Thevane 83 is loaded from the vane back pressure chamber 90 side toward the inner wall side of the cylinder 85 by the centrifugal force generated by the rotation of the rotor 60 and the pressure of the lubricating oil supplied to the vane back pressure chamber 90. . Due to this load, the vane 83 is always pressed against the inner wall of the cylinder 85 and slides against the inner wall of the cylinder 85.
When therotor 60 rotates while the vane 83 slides on the inner wall of the cylinder 85, the volume of the working chamber 73 changes. Due to this change in volume, the refrigerant is sucked from the suction port 86, compressed and discharged from the discharge port 87.
スライディングベーン型のロータリ圧縮機の圧縮部は、図6に示すように、シリンダ85、ロータ60を備える。
シリンダ85は、両端面が側板により閉塞される。ロータ60は、シリンダ85の内壁との間に微小隙間を形成して偏芯配置される。ロータ60には、複数のベーン83が挿入される。各ベーン83は、ロータ60から突き出て、シリンダ85の内壁に当接して、シリンダ85と側板とにより形成された空間に、作動室73(圧縮室)を形成する。
電動機が駆動して、電動機に連結された駆動軸81が回転することにより、駆動軸81と一体に形成されたロータ60が回転する。ロータ60が回転することにより、ロータ60に挿入されたベーン83に遠心力を与える。
ベーン83は、ロータ60が回転することによる遠心力と、ベーン背圧室90に給油された潤滑油の圧力とにより、ベーン背圧室90側からシリンダ85の内壁側へ向けて荷重をかけられる。この荷重により、ベーン83は、常にシリンダ85の内壁に押し付けられ、シリンダ85の内壁と摺動する。
ベーン83がシリンダ85の内壁と摺動しながらロータ60が回転することにより、作動室73の容積が変化する。この容積の変化により、冷媒が吸入口86から吸入され、圧縮されて吐出口87から吐出される。 FIG. 6 is a cross-sectional view of a compression unit of a sliding vane rotary compressor according to the second embodiment. The basic configuration is the same for both the low-
As shown in FIG. 6, the compression unit of the sliding vane type rotary compressor includes a
Both ends of the
When the electric motor is driven and the
The
When the
図2に示すベーン背圧室50へ油分離機構9から差圧給油されたのと同様に、ベーン背圧室90へ高圧側に配置された油貯蔵部から潤滑油が差圧給油される。
圧力の逆転現象が起こった場合、ローリングピストン型の二段ロータリ圧縮機の場合と同様に、ベーン背圧室90にかかる圧力(高圧)よりも作動室73の圧力(中間圧)が高くなる。そして、ベーン83をシリンダ85の側壁側からベーン背圧室50側へ押す荷重(作動室73の圧力)が、ベーン83をシリンダ85の内壁に押し付けている荷重(ベーン背圧室90内の圧力と、ロータ60により与えられた遠心力との合計)を超えると、ベーン83がシリンダ85の内壁から離脱するベーン飛びという現象が発生する。 In the same manner that the differential pressure oil is supplied from theoil separation mechanism 9 to the vane back pressure chamber 50 shown in FIG. 2, the lubricating oil is supplied to the vane back pressure chamber 90 from the oil storage portion arranged on the high pressure side.
When the pressure reversal phenomenon occurs, the pressure (intermediate pressure) in the workingchamber 73 becomes higher than the pressure (high pressure) applied to the vane back pressure chamber 90 as in the case of the rolling piston type two-stage rotary compressor. A load that pushes the vane 83 from the side wall side of the cylinder 85 to the vane back pressure chamber 50 side (pressure in the working chamber 73) presses the vane 83 against the inner wall of the cylinder 85 (pressure in the vane back pressure chamber 90). And the total centrifugal force applied by the rotor 60), a phenomenon of vane jumping occurs in which the vane 83 is detached from the inner wall of the cylinder 85.
圧力の逆転現象が起こった場合、ローリングピストン型の二段ロータリ圧縮機の場合と同様に、ベーン背圧室90にかかる圧力(高圧)よりも作動室73の圧力(中間圧)が高くなる。そして、ベーン83をシリンダ85の側壁側からベーン背圧室50側へ押す荷重(作動室73の圧力)が、ベーン83をシリンダ85の内壁に押し付けている荷重(ベーン背圧室90内の圧力と、ロータ60により与えられた遠心力との合計)を超えると、ベーン83がシリンダ85の内壁から離脱するベーン飛びという現象が発生する。 In the same manner that the differential pressure oil is supplied from the
When the pressure reversal phenomenon occurs, the pressure (intermediate pressure) in the working
この場合にも、実施の形態1で説明したローリングピストン型の二段ロータリ圧縮機と同様の回路構成により、ベーン飛びを解消し、正常な運転状態に復帰することが可能である。
つまり、圧力の逆転現象が起きた場合に、バイパス回路10を経由して中間連結部7からバッファ部12へ冷媒を流入させる。これにより、高段圧縮部2のベーン背圧室90等への給油を促進して、高段圧縮部2のベーン背圧室90内の圧力と高段圧縮部2の作動室73の圧力とを均一の圧力にすることができる。その結果、ベーン飛び等の現象が解消して、高段圧縮部2でも冷媒が圧縮されるようになり、正常状態へ復帰することができる。 Also in this case, the vane jump can be eliminated and the normal operation state can be restored by the same circuit configuration as that of the rolling piston type two-stage rotary compressor described in the first embodiment.
That is, when a pressure reversal phenomenon occurs, the refrigerant is caused to flow from theintermediate connection portion 7 to the buffer portion 12 via the bypass circuit 10. Thereby, the oil supply to the vane back pressure chamber 90 of the high stage compression unit 2 is promoted, and the pressure in the vane back pressure chamber 90 of the high stage compression unit 2 and the pressure of the working chamber 73 of the high stage compression unit 2 are Can be made a uniform pressure. As a result, phenomena such as vane jumping are eliminated, and the refrigerant is compressed even in the high-stage compression unit 2, and the normal state can be restored.
つまり、圧力の逆転現象が起きた場合に、バイパス回路10を経由して中間連結部7からバッファ部12へ冷媒を流入させる。これにより、高段圧縮部2のベーン背圧室90等への給油を促進して、高段圧縮部2のベーン背圧室90内の圧力と高段圧縮部2の作動室73の圧力とを均一の圧力にすることができる。その結果、ベーン飛び等の現象が解消して、高段圧縮部2でも冷媒が圧縮されるようになり、正常状態へ復帰することができる。 Also in this case, the vane jump can be eliminated and the normal operation state can be restored by the same circuit configuration as that of the rolling piston type two-stage rotary compressor described in the first embodiment.
That is, when a pressure reversal phenomenon occurs, the refrigerant is caused to flow from the
実施の形態3.
実施の形態1では、逆止め機構11やバッファ部12が、密閉容器21や油分離機構9の外部に設けられる例を説明した。実施の形態3では、逆止め機構11やバッファ部12が、密閉容器21や油分離機構9の内部に設けられる例を説明する。Embodiment 3 FIG.
In the first embodiment, the example in which thecheck mechanism 11 and the buffer unit 12 are provided outside the sealed container 21 and the oil separation mechanism 9 has been described. In the third embodiment, an example in which the check mechanism 11 and the buffer unit 12 are provided inside the sealed container 21 and the oil separation mechanism 9 will be described.
実施の形態1では、逆止め機構11やバッファ部12が、密閉容器21や油分離機構9の外部に設けられる例を説明した。実施の形態3では、逆止め機構11やバッファ部12が、密閉容器21や油分離機構9の内部に設けられる例を説明する。
In the first embodiment, the example in which the
図7は、実施の形態3に係る二段ロータリ圧縮機の縦断面図である。
図7に示すように、実施の形態3に係る二段ロータリ圧縮機では、バッファ部12が油分離機構9に内蔵される。つまり、油分離機構9内の一部の領域にバッファ部12が設けられる。
また、図7に示すように、実施の形態3に係る二段ロータリ圧縮機では、逆止め機構11が密閉容器21に内蔵される。ここでは、密閉容器21内の低段吐出マフラ3に逆止め機構11を設けた。
そして、低段吐出マフラ3に設けられた逆止め機構11と、油分離機構9内に形成されたバッファ部12とをバイパス回路10が繋ぐ。 FIG. 7 is a longitudinal sectional view of a two-stage rotary compressor according to the third embodiment.
As shown in FIG. 7, in the two-stage rotary compressor according to the third embodiment, thebuffer unit 12 is built in the oil separation mechanism 9. That is, the buffer unit 12 is provided in a partial region in the oil separation mechanism 9.
As shown in FIG. 7, in the two-stage rotary compressor according to the third embodiment, thecheck mechanism 11 is built in the sealed container 21. Here, the check mechanism 11 is provided in the low-stage discharge muffler 3 in the sealed container 21.
Thebypass circuit 10 connects the non-return mechanism 11 provided in the low-stage discharge muffler 3 and the buffer unit 12 formed in the oil separation mechanism 9.
図7に示すように、実施の形態3に係る二段ロータリ圧縮機では、バッファ部12が油分離機構9に内蔵される。つまり、油分離機構9内の一部の領域にバッファ部12が設けられる。
また、図7に示すように、実施の形態3に係る二段ロータリ圧縮機では、逆止め機構11が密閉容器21に内蔵される。ここでは、密閉容器21内の低段吐出マフラ3に逆止め機構11を設けた。
そして、低段吐出マフラ3に設けられた逆止め機構11と、油分離機構9内に形成されたバッファ部12とをバイパス回路10が繋ぐ。 FIG. 7 is a longitudinal sectional view of a two-stage rotary compressor according to the third embodiment.
As shown in FIG. 7, in the two-stage rotary compressor according to the third embodiment, the
As shown in FIG. 7, in the two-stage rotary compressor according to the third embodiment, the
The
なお、圧力の逆転現象が起きた場合の動作は、実施の形態1と同様である。つまり、圧力の逆転現象が起きた場合に、バイパス回路10を経由して中間流路からバッファ部12へ冷媒を流入させる。これにより、高段圧縮部2のベーン背圧室50等への給油を促進して、高段圧縮部2のベーン背圧室50内の圧力と高段圧縮部2内の圧力とを均一の圧力にすることができる。その結果、ベーン飛び等の現象が解消して、高段圧縮部2でも冷媒が圧縮されるようになり、正常状態へ復帰することができる。
The operation when the pressure reversal phenomenon occurs is the same as in the first embodiment. That is, when a pressure reversal phenomenon occurs, the refrigerant flows from the intermediate flow path into the buffer unit 12 via the bypass circuit 10. Thereby, the oil supply to the vane back pressure chamber 50 of the high stage compression unit 2 is promoted, and the pressure in the vane back pressure chamber 50 of the high stage compression unit 2 and the pressure in the high stage compression unit 2 are made uniform. Can be pressure. As a result, phenomena such as vane jumping are eliminated, and the refrigerant is compressed even in the high-stage compression unit 2, and the normal state can be restored.
図8は、実施の形態3に係る図7の油分離機構9の縦断面図を示す図である。なお、図8では、破線部分についての拡大図を併せて示す。
図8に示すように、バイパス回路10とバッファ部12との間には、バイパス回路10の外径φBの配管とバッファ部12に形成された径φAの孔との隙間「(φA-φB)/2」がある。
この隙間「(φA-φB)/2」が、バッファ部12内と油分離機構9内を連通する均圧部17となる。つまり、この隙間「(φA-φB)/2」により、逆止め機構11の作動後にバッファ部12内の油面の高さを油分離機構9内の油面高さと同じ高さに戻す。 FIG. 8 is a view showing a longitudinal sectional view of theoil separation mechanism 9 of FIG. 7 according to the third embodiment. In addition, in FIG. 8, the enlarged view about a broken-line part is shown collectively.
As shown in FIG. 8, between thebypass circuit 10 and the buffer portion 12, a gap “(φA−φB) between a pipe having an outer diameter φB of the bypass circuit 10 and a hole with a diameter φA formed in the buffer portion 12”. / 2 ".
This gap “(φA−φB) / 2” becomes apressure equalizing portion 17 that communicates the inside of the buffer portion 12 and the inside of the oil separation mechanism 9. That is, the gap “(φA−φB) / 2” returns the oil level in the buffer portion 12 to the same height as the oil level in the oil separation mechanism 9 after the check mechanism 11 is operated.
図8に示すように、バイパス回路10とバッファ部12との間には、バイパス回路10の外径φBの配管とバッファ部12に形成された径φAの孔との隙間「(φA-φB)/2」がある。
この隙間「(φA-φB)/2」が、バッファ部12内と油分離機構9内を連通する均圧部17となる。つまり、この隙間「(φA-φB)/2」により、逆止め機構11の作動後にバッファ部12内の油面の高さを油分離機構9内の油面高さと同じ高さに戻す。 FIG. 8 is a view showing a longitudinal sectional view of the
As shown in FIG. 8, between the
This gap “(φA−φB) / 2” becomes a
また、図8に示すように、バッファ部12の下部の潤滑油が貯えられる部分には、油分離機構9との間に隙間「C」がある。
この隙間「C」は、バッファ空間給油部18である。油分離機構9内で分離された潤滑油(図8の(1))は、バッファ空間給油部18からバッファ部12へ流入する(図8の(2))。そして、バッファ部12に貯えられた潤滑油は、給油回路13により各圧縮部に給油される(図8の(3))。 Further, as shown in FIG. 8, there is a gap “C” between theoil separation mechanism 9 and the portion where the lubricating oil in the lower portion of the buffer portion 12 is stored.
This gap “C” is the buffer spaceoil supply section 18. The lubricating oil ((1) in FIG. 8) separated in the oil separation mechanism 9 flows from the buffer space oil supply section 18 into the buffer section 12 ((2) in FIG. 8). And the lubricating oil stored in the buffer part 12 is supplied to each compression part by the oil supply circuit 13 ((3) of FIG. 8).
この隙間「C」は、バッファ空間給油部18である。油分離機構9内で分離された潤滑油(図8の(1))は、バッファ空間給油部18からバッファ部12へ流入する(図8の(2))。そして、バッファ部12に貯えられた潤滑油は、給油回路13により各圧縮部に給油される(図8の(3))。 Further, as shown in FIG. 8, there is a gap “C” between the
This gap “C” is the buffer space
図8に示す均圧部17の開口面積とバッファ空間給油部18の開口面積とは、空調能力に応じて決定される。空調能力が高いほど均圧部17とバッファ空間給油部18との開口面積を広くする必要があり、空調能力が低いほど均圧部17とバッファ空間給油部18との開口面積を狭くする必要がある。
例えば、空調能力2.8kW相当の空気調和機に使用する圧縮機においては、均圧部17の開口面積が0.1~0.5mm2程度であり、バッファ空間給油部18の開口面積が10~50mm2程度である。 The opening area of thepressure equalizing unit 17 and the opening area of the buffer space oil supply unit 18 shown in FIG. 8 are determined according to the air conditioning capability. The higher the air conditioning capacity, the wider the opening area of the pressure equalizing section 17 and the buffer space oil supply section 18, and the lower the air conditioning capacity, the smaller the opening area of the pressure equalization section 17 and the buffer space oil supply section 18. is there.
For example, in a compressor used for an air conditioner having an air conditioning capacity of 2.8 kW, thepressure equalizing unit 17 has an opening area of about 0.1 to 0.5 mm 2 and the buffer space oil supply unit 18 has an opening area of 10 About 50 mm 2 .
例えば、空調能力2.8kW相当の空気調和機に使用する圧縮機においては、均圧部17の開口面積が0.1~0.5mm2程度であり、バッファ空間給油部18の開口面積が10~50mm2程度である。 The opening area of the
For example, in a compressor used for an air conditioner having an air conditioning capacity of 2.8 kW, the
なお、均圧部17とバッファ空間給油部18とは上述した構成に限らず、例えば、孔状に形成されてもよいし、平面と平面とで形成される隙間であってもよい。
In addition, the pressure equalization part 17 and the buffer space oil supply part 18 are not restricted to the structure mentioned above, For example, you may form in a hole shape and the clearance gap formed by a plane and a plane may be sufficient.
また、ここでは、バッファ部12が油分離機構9に内蔵され、逆止め機構11が密閉容器21に内蔵される例を示した。しかし、これに限らず、バッファ部12が密閉容器21に内蔵されてもよいし、逆止め機構11は油分離機構9に内蔵されてもよい。
また、図7,8に示すバッファ部12の構成は一例であり、機能さえ満たしていれば、他の構成であってもよい。 Here, an example in which thebuffer unit 12 is built in the oil separation mechanism 9 and the check mechanism 11 is built in the sealed container 21 is shown. However, the present invention is not limited thereto, and the buffer unit 12 may be built in the sealed container 21, and the check mechanism 11 may be built in the oil separation mechanism 9.
The configuration of thebuffer unit 12 shown in FIGS. 7 and 8 is an example, and other configurations may be used as long as the functions are satisfied.
また、図7,8に示すバッファ部12の構成は一例であり、機能さえ満たしていれば、他の構成であってもよい。 Here, an example in which the
The configuration of the
実施の形態3に係る二段ロータリ圧縮機では、バッファ部12と逆止め機構11とをそれぞれ油分離機構9と密閉容器21とに内蔵した。これにより、圧縮機を小型化することができる。
In the two-stage rotary compressor according to the third embodiment, the buffer unit 12 and the check mechanism 11 are incorporated in the oil separation mechanism 9 and the airtight container 21, respectively. Thereby, a compressor can be reduced in size.
実施の形態4.
実施の形態4では、逆止め機構11の構成について説明する。Embodiment 4 FIG.
In the fourth embodiment, the configuration of thecheck mechanism 11 will be described.
実施の形態4では、逆止め機構11の構成について説明する。
In the fourth embodiment, the configuration of the
図9は、実施の形態4に係る逆止め機構11の一例を示す構成図である。
図9は、例えば、逆止め機構11を密閉容器21や油分離機構9に内蔵する場合に用いられる逆止め機構11の例である。図9に示す逆止め機構11は、バネによって弁体91を弁座92に押し付ける構造である。
図9(a)は、弁体91が弁座92に押し付けられ、弁が閉じた状態を示す。図9(b)は、弁体91が弁座92から離れ、弁が開いた状態を示す。弁が離れている状態とは、逆止め機構11が作動した状態である。
つまり、正常運転時は、高圧が中間圧よりも高いため、高圧側から中間圧側へ弁体91が押され、弁体91が弁座92に押し付けられる。したがって、弁が閉じた状態になる。一方、中間圧が高圧よりも高くなった場合(圧力の逆転現象が起きた場合)、中間圧側から高圧側へ弁体91が押され、弁体91が弁座92から離れる。したがって、弁が開いた状態になる。 FIG. 9 is a configuration diagram illustrating an example of thecheck mechanism 11 according to the fourth embodiment.
FIG. 9 shows an example of thenon-return mechanism 11 used when the non-return mechanism 11 is built in the sealed container 21 or the oil separation mechanism 9, for example. The check mechanism 11 shown in FIG. 9 has a structure in which the valve body 91 is pressed against the valve seat 92 by a spring.
FIG. 9A shows a state in which thevalve body 91 is pressed against the valve seat 92 and the valve is closed. FIG. 9B shows a state where the valve body 91 is separated from the valve seat 92 and the valve is opened. The state where the valves are separated is a state where the check mechanism 11 is activated.
That is, since the high pressure is higher than the intermediate pressure during normal operation, thevalve body 91 is pressed from the high pressure side to the intermediate pressure side, and the valve body 91 is pressed against the valve seat 92. Therefore, the valve is closed. On the other hand, when the intermediate pressure becomes higher than the high pressure (when a reverse pressure phenomenon occurs), the valve body 91 is pushed from the intermediate pressure side to the high pressure side, and the valve body 91 is separated from the valve seat 92. Therefore, the valve is opened.
図9は、例えば、逆止め機構11を密閉容器21や油分離機構9に内蔵する場合に用いられる逆止め機構11の例である。図9に示す逆止め機構11は、バネによって弁体91を弁座92に押し付ける構造である。
図9(a)は、弁体91が弁座92に押し付けられ、弁が閉じた状態を示す。図9(b)は、弁体91が弁座92から離れ、弁が開いた状態を示す。弁が離れている状態とは、逆止め機構11が作動した状態である。
つまり、正常運転時は、高圧が中間圧よりも高いため、高圧側から中間圧側へ弁体91が押され、弁体91が弁座92に押し付けられる。したがって、弁が閉じた状態になる。一方、中間圧が高圧よりも高くなった場合(圧力の逆転現象が起きた場合)、中間圧側から高圧側へ弁体91が押され、弁体91が弁座92から離れる。したがって、弁が開いた状態になる。 FIG. 9 is a configuration diagram illustrating an example of the
FIG. 9 shows an example of the
FIG. 9A shows a state in which the
That is, since the high pressure is higher than the intermediate pressure during normal operation, the
図10は、実施の形態4に係る逆止め機構11の一例を示す構成図である。
図10は、例えば、逆止め機構11を密閉容器21や油分離機構9の外部に設ける場合に用いられる逆止め機構11の例である。図10に示す逆止め機構11は、板バネ93が開閉する構造である。
図10(a)は、板バネ93が弁座94に押し付けられ、弁が閉じた状態を示す。図10(b)は、板バネ93が弁座94から離れ、弁が開いた状態を示す。弁が離れている状態とは、逆止め機構11が作動した状態である。
つまり、正常運転時は、高圧が中間圧よりも高いため、高圧側から中間圧側へ板バネ93が押され、板バネ93が弁座94に押し付けられる。したがって、弁が閉じた状態になる。一方、中間圧が高圧よりも高くなった場合(圧力の逆転現象が起きた場合)、中間圧側から高圧側へ板バネ93が押され、板バネ93が弁座94から離れる。したがって、弁が開いた状態になる。 FIG. 10 is a configuration diagram illustrating an example of thecheck mechanism 11 according to the fourth embodiment.
FIG. 10 shows an example of thecheck mechanism 11 used when the check mechanism 11 is provided outside the sealed container 21 or the oil separation mechanism 9. The check mechanism 11 shown in FIG. 10 has a structure in which a leaf spring 93 is opened and closed.
FIG. 10A shows a state in which theleaf spring 93 is pressed against the valve seat 94 and the valve is closed. FIG. 10B shows a state in which the leaf spring 93 is separated from the valve seat 94 and the valve is opened. The state where the valves are separated is a state where the check mechanism 11 is activated.
That is, during normal operation, since the high pressure is higher than the intermediate pressure, theplate spring 93 is pressed from the high pressure side to the intermediate pressure side, and the plate spring 93 is pressed against the valve seat 94. Therefore, the valve is closed. On the other hand, when the intermediate pressure becomes higher than the high pressure (when a reverse pressure phenomenon occurs), the leaf spring 93 is pushed from the intermediate pressure side to the high pressure side, and the leaf spring 93 moves away from the valve seat 94. Therefore, the valve is opened.
図10は、例えば、逆止め機構11を密閉容器21や油分離機構9の外部に設ける場合に用いられる逆止め機構11の例である。図10に示す逆止め機構11は、板バネ93が開閉する構造である。
図10(a)は、板バネ93が弁座94に押し付けられ、弁が閉じた状態を示す。図10(b)は、板バネ93が弁座94から離れ、弁が開いた状態を示す。弁が離れている状態とは、逆止め機構11が作動した状態である。
つまり、正常運転時は、高圧が中間圧よりも高いため、高圧側から中間圧側へ板バネ93が押され、板バネ93が弁座94に押し付けられる。したがって、弁が閉じた状態になる。一方、中間圧が高圧よりも高くなった場合(圧力の逆転現象が起きた場合)、中間圧側から高圧側へ板バネ93が押され、板バネ93が弁座94から離れる。したがって、弁が開いた状態になる。 FIG. 10 is a configuration diagram illustrating an example of the
FIG. 10 shows an example of the
FIG. 10A shows a state in which the
That is, during normal operation, since the high pressure is higher than the intermediate pressure, the
なお、図9,10に示す逆止め機構11の構成は一例であり、機能さえ満たしていれば、他の構成であってもよい。
In addition, the structure of the non-return mechanism 11 shown to FIG. 9, 10 is an example, and as long as the function is satisfy | filled, another structure may be sufficient.
実施の形態5.
実施の形態1では、密閉容器21内の圧力が低段圧縮部1が冷媒を圧縮する前の圧力(低圧)である場合(低圧シェル型の圧縮機)について説明した。実施の形態5では、密閉容器21内が中間圧(低段圧縮部1の吐出圧)である場合(中間圧シェル型の圧縮機)と、密閉容器21内が高圧(高段圧縮部2の吐出圧)である場合(高圧シェル型の圧縮機)とについて説明する。Embodiment 5 FIG.
In the first embodiment, the case where the pressure in the sealedcontainer 21 is the pressure (low pressure) before the low-stage compression unit 1 compresses the refrigerant has been described (low pressure shell type compressor). In the fifth embodiment, when the inside of the sealed container 21 is at an intermediate pressure (discharge pressure of the low-stage compression unit 1) (intermediate pressure shell type compressor), the inside of the sealed container 21 is at a high pressure (of the high-stage compression unit 2). (Discharge pressure) (high-pressure shell type compressor) will be described.
実施の形態1では、密閉容器21内の圧力が低段圧縮部1が冷媒を圧縮する前の圧力(低圧)である場合(低圧シェル型の圧縮機)について説明した。実施の形態5では、密閉容器21内が中間圧(低段圧縮部1の吐出圧)である場合(中間圧シェル型の圧縮機)と、密閉容器21内が高圧(高段圧縮部2の吐出圧)である場合(高圧シェル型の圧縮機)とについて説明する。
In the first embodiment, the case where the pressure in the sealed
図11は、実施の形態5に係る密閉容器21内が中間圧である二段ロータリ圧縮機の動作を示す図である。なお、図11において、太線は冷媒回路を示し、点線は給油回路を示す。また、実線矢印は、冷媒の流れを示し、点線矢印は潤滑油の流れを示す。
低段吸入配管6を経由して(図11の(1))、低段圧縮部1へ冷媒が吸入される(図11の(2))。
低段圧縮部1では、低圧の冷媒を中間圧まで圧縮する。中間圧まで圧縮された冷媒は、低段吐出マフラ3へ吐出される(図11の(3))。低段吐出マフラ3へ吐出された冷媒は、密閉容器21内に吐出される(図11の(4))。つまり、密閉容器21内は、中間圧となる。密閉容器21内に吐出された中間圧の冷媒は、密閉容器21内に接続された中間連結部7を経由して(図11の(5))、高段圧縮部2に吸入される(図11の(6))。
高段圧縮部2では、中間圧の冷媒を高圧まで圧縮する。高圧まで圧縮された冷媒は、高段吐出マフラ4へ吐出される(図11の(7))。高段吐出マフラ4へ吐出された冷媒は、高段吐出配管8を経由して(図11の(8))、油分離機構9へ流入する(図11の(9))。油分離機構9へ流入した冷媒は、油分離機構9で潤滑油を分離されて外部回路に吐出される(図11の(10))。 FIG. 11 is a diagram illustrating the operation of the two-stage rotary compressor in which the inside of the sealedcontainer 21 according to the fifth embodiment has an intermediate pressure. In FIG. 11, the thick line indicates the refrigerant circuit, and the dotted line indicates the oil supply circuit. Moreover, a solid line arrow shows the flow of a refrigerant | coolant, and a dotted line arrow shows the flow of lubricating oil.
The refrigerant is sucked into the low stage compression section 1 ((2) in FIG. 11) via the low stage suction pipe 6 ((1) in FIG. 11).
The lowstage compression unit 1 compresses the low-pressure refrigerant to an intermediate pressure. The refrigerant compressed to the intermediate pressure is discharged to the low-stage discharge muffler 3 ((3) in FIG. 11). The refrigerant discharged to the low-stage discharge muffler 3 is discharged into the sealed container 21 ((4) in FIG. 11). That is, the inside of the sealed container 21 is at an intermediate pressure. The intermediate-pressure refrigerant discharged into the sealed container 21 is sucked into the high-stage compression section 2 via the intermediate coupling portion 7 connected to the sealed container 21 ((5) in FIG. 11) (FIG. 11 (6)).
The high-stage compression unit 2 compresses the intermediate pressure refrigerant to a high pressure. The refrigerant compressed to a high pressure is discharged to the high-stage discharge muffler 4 ((7) in FIG. 11). The refrigerant discharged to the high-stage discharge muffler 4 flows into the oil separation mechanism 9 ((9) in FIG. 11) via the high-stage discharge pipe 8 ((8) in FIG. 11). The refrigerant that has flowed into the oil separation mechanism 9 is separated into lubricating oil by the oil separation mechanism 9 and discharged to the external circuit ((10) in FIG. 11).
低段吸入配管6を経由して(図11の(1))、低段圧縮部1へ冷媒が吸入される(図11の(2))。
低段圧縮部1では、低圧の冷媒を中間圧まで圧縮する。中間圧まで圧縮された冷媒は、低段吐出マフラ3へ吐出される(図11の(3))。低段吐出マフラ3へ吐出された冷媒は、密閉容器21内に吐出される(図11の(4))。つまり、密閉容器21内は、中間圧となる。密閉容器21内に吐出された中間圧の冷媒は、密閉容器21内に接続された中間連結部7を経由して(図11の(5))、高段圧縮部2に吸入される(図11の(6))。
高段圧縮部2では、中間圧の冷媒を高圧まで圧縮する。高圧まで圧縮された冷媒は、高段吐出マフラ4へ吐出される(図11の(7))。高段吐出マフラ4へ吐出された冷媒は、高段吐出配管8を経由して(図11の(8))、油分離機構9へ流入する(図11の(9))。油分離機構9へ流入した冷媒は、油分離機構9で潤滑油を分離されて外部回路に吐出される(図11の(10))。 FIG. 11 is a diagram illustrating the operation of the two-stage rotary compressor in which the inside of the sealed
The refrigerant is sucked into the low stage compression section 1 ((2) in FIG. 11) via the low stage suction pipe 6 ((1) in FIG. 11).
The low
The high-
油分離機構9で分離された潤滑油は、油分離機構9下部の高圧油貯蔵部51に貯えられる(図11の(11))。高圧油貯蔵部51に貯えられた潤滑油は、給油回路13を経由して(図11の(12))、高段給油配管15から高段圧縮部2のベーン背圧室50等へ給油される(図11の(13))。
また、高圧油貯蔵部51に貯えられた潤滑油の一部は、給油回路13を通って(図1の(12))、バッファ部12に貯えられる(図11の(14))。 The lubricating oil separated by theoil separation mechanism 9 is stored in the high-pressure oil storage section 51 below the oil separation mechanism 9 ((11) in FIG. 11). The lubricating oil stored in the high-pressure oil storage 51 is supplied to the vane back pressure chamber 50 of the high-stage compression section 2 from the high-stage oil supply pipe 15 via the oil supply circuit 13 ((12) in FIG. 11). ((13) in FIG. 11).
A part of the lubricating oil stored in the high-pressureoil storage unit 51 passes through the oil supply circuit 13 ((12) in FIG. 1) and is stored in the buffer unit 12 ((14) in FIG. 11).
また、高圧油貯蔵部51に貯えられた潤滑油の一部は、給油回路13を通って(図1の(12))、バッファ部12に貯えられる(図11の(14))。 The lubricating oil separated by the
A part of the lubricating oil stored in the high-pressure
中間圧が高圧よりも高くなる圧力の逆転現象が起きた場合には、逆止め機構11が作動する。そして、中間連結部7から分岐してバッファ部12へ繋がるバイパス回路10から、中間連結部7を流れる冷媒がバッファ部12内へ流入する(図11の(15))。
これにより、実施の形態1の低圧シェル型の圧縮機の場合と同様に、中間圧シェル型の圧縮機においても、高段圧縮部2のベーン背圧室50等への給油を促進して、高段圧縮部2のベーン背圧室50内の圧力と高段圧縮部2のシリンダ45内の圧力とを均一の圧力にすることができる。その結果、ベーン飛び等の現象が解消して、高段圧縮部2でも冷媒が圧縮されるようになり、正常状態へ復帰することができる。
また、実施の形態1の低圧シェル型の圧縮機の場合と同様に、中間圧シェル型の圧縮機においても、逆止め機構11が作動した後、均圧部17によりバッファ部12内の圧力と油分離機構9内の圧力とを均一の圧力にする。 When a reverse pressure phenomenon occurs in which the intermediate pressure is higher than the high pressure, thecheck mechanism 11 is activated. And the refrigerant | coolant which flows through the intermediate | middle connection part 7 flows in into the buffer part 12 from the bypass circuit 10 branched from the intermediate | middle connection part 7 and connected to the buffer part 12 ((15) of FIG. 11).
Thereby, as in the case of the low pressure shell type compressor of the first embodiment, also in the intermediate pressure shell type compressor, the oil supply to the vane backpressure chamber 50 or the like of the high stage compression unit 2 is promoted, The pressure in the vane back pressure chamber 50 of the high stage compression unit 2 and the pressure in the cylinder 45 of the high stage compression unit 2 can be made uniform. As a result, phenomena such as vane jumping are eliminated, and the refrigerant is compressed even in the high-stage compression unit 2, and the normal state can be restored.
Similarly to the case of the low pressure shell type compressor of the first embodiment, in the intermediate pressure shell type compressor, after thecheck mechanism 11 is operated, The pressure in the oil separation mechanism 9 is made uniform.
これにより、実施の形態1の低圧シェル型の圧縮機の場合と同様に、中間圧シェル型の圧縮機においても、高段圧縮部2のベーン背圧室50等への給油を促進して、高段圧縮部2のベーン背圧室50内の圧力と高段圧縮部2のシリンダ45内の圧力とを均一の圧力にすることができる。その結果、ベーン飛び等の現象が解消して、高段圧縮部2でも冷媒が圧縮されるようになり、正常状態へ復帰することができる。
また、実施の形態1の低圧シェル型の圧縮機の場合と同様に、中間圧シェル型の圧縮機においても、逆止め機構11が作動した後、均圧部17によりバッファ部12内の圧力と油分離機構9内の圧力とを均一の圧力にする。 When a reverse pressure phenomenon occurs in which the intermediate pressure is higher than the high pressure, the
Thereby, as in the case of the low pressure shell type compressor of the first embodiment, also in the intermediate pressure shell type compressor, the oil supply to the vane back
Similarly to the case of the low pressure shell type compressor of the first embodiment, in the intermediate pressure shell type compressor, after the
なお、図11では、逆止め機構11、バッファ部12は外部に設けている。しかし、実施の形態3で説明したように、逆止め機構11、バッファ部12を密閉容器21や油分離機構9に内蔵してもよい。
In FIG. 11, the check mechanism 11 and the buffer unit 12 are provided outside. However, as described in the third embodiment, the check mechanism 11 and the buffer unit 12 may be built in the sealed container 21 or the oil separation mechanism 9.
図12は、実施の形態5に係る密閉容器21内が高圧である二段ロータリ圧縮機の動作を示す図である。なお、図12において、太線は冷媒回路を示し、点線は給油回路を示す。また、実線矢印は、冷媒の流れを示し、点線矢印は潤滑油の流れを示す。
低段吸入配管6を経由して(図12の(1))、低段圧縮部1へ冷媒が吸入される(図12の(2))。
低段圧縮部1では、低圧の冷媒を中間圧まで圧縮する。中間圧まで圧縮された冷媒は、低段吐出マフラ3へ吐出される(図12の(3))。低段吐出マフラ3へ吐出された冷媒は、中間連結部7を経由して(図12の(4))、高段圧縮部2に吸入される(図12の(5))。
高段圧縮部2では、中間圧の冷媒を高圧まで圧縮する。高圧まで圧縮された冷媒は、高段吐出マフラ4へ吐出される(図12の(6))。高段吐出マフラ4へ吐出された冷媒は、密閉容器21内へ吐出される(図12の(7))。つまり、密閉容器21内は、高圧となる。密閉容器21内へ吐出された冷媒は、密閉容器21の上部から外部回路に吐出される(図12の(8))。 FIG. 12 is a diagram illustrating the operation of the two-stage rotary compressor in which the inside of the sealedcontainer 21 according to the fifth embodiment is high pressure. In FIG. 12, the thick line indicates the refrigerant circuit, and the dotted line indicates the oil supply circuit. Moreover, a solid line arrow shows the flow of a refrigerant | coolant, and a dotted line arrow shows the flow of lubricating oil.
The refrigerant is sucked into the low-stage compression section 1 via the low-stage suction pipe 6 ((1) in FIG. 12) ((2) in FIG. 12).
The lowstage compression unit 1 compresses the low-pressure refrigerant to an intermediate pressure. The refrigerant compressed to the intermediate pressure is discharged to the low-stage discharge muffler 3 ((3) in FIG. 12). The refrigerant discharged to the low-stage discharge muffler 3 is sucked into the high-stage compression section 2 ((5) in FIG. 12) via the intermediate connecting section 7 ((4) in FIG. 12).
The high-stage compression unit 2 compresses the intermediate pressure refrigerant to a high pressure. The refrigerant compressed to a high pressure is discharged to the high-stage discharge muffler 4 ((6) in FIG. 12). The refrigerant discharged to the high-stage discharge muffler 4 is discharged into the sealed container 21 ((7) in FIG. 12). That is, the inside of the sealed container 21 is at a high pressure. The refrigerant discharged into the sealed container 21 is discharged from the upper part of the sealed container 21 to the external circuit ((8) in FIG. 12).
低段吸入配管6を経由して(図12の(1))、低段圧縮部1へ冷媒が吸入される(図12の(2))。
低段圧縮部1では、低圧の冷媒を中間圧まで圧縮する。中間圧まで圧縮された冷媒は、低段吐出マフラ3へ吐出される(図12の(3))。低段吐出マフラ3へ吐出された冷媒は、中間連結部7を経由して(図12の(4))、高段圧縮部2に吸入される(図12の(5))。
高段圧縮部2では、中間圧の冷媒を高圧まで圧縮する。高圧まで圧縮された冷媒は、高段吐出マフラ4へ吐出される(図12の(6))。高段吐出マフラ4へ吐出された冷媒は、密閉容器21内へ吐出される(図12の(7))。つまり、密閉容器21内は、高圧となる。密閉容器21内へ吐出された冷媒は、密閉容器21の上部から外部回路に吐出される(図12の(8))。 FIG. 12 is a diagram illustrating the operation of the two-stage rotary compressor in which the inside of the sealed
The refrigerant is sucked into the low-
The low
The high-
なお、密閉容器21内が高圧である場合は、高段吐出マフラ4から吐出された冷媒が密閉容器21上部から外部回路に吐出されるまでにある程度潤滑油が分離される。そのため、一般的に油分離機構9を別途備えないことが多い。つまり、密閉容器21が油分離機構9の役割を果たす。密閉容器21内が高圧であるため、冷媒から分離された潤滑油は、密閉容器21下部に貯えられる(図12の(9))。つまり、密閉容器21の下部が高圧油貯蔵部51となる。
高圧油貯蔵部51に貯えられた潤滑油は、密閉容器21の内部に設けられたバッファ部12へバッファ空間給油部18から流入する(図12の(10))。バッファ部12へ流入した潤滑油は、高段給油配管15から高段圧縮部2のベーン背圧室50等へ給油される(図12の(11))。 When the inside of the sealedcontainer 21 is at a high pressure, the lubricant is separated to some extent before the refrigerant discharged from the high-stage discharge muffler 4 is discharged from the upper part of the sealed container 21 to the external circuit. Therefore, in general, the oil separation mechanism 9 is often not separately provided. That is, the sealed container 21 serves as the oil separation mechanism 9. Since the inside of the sealed container 21 is at a high pressure, the lubricating oil separated from the refrigerant is stored in the lower part of the sealed container 21 ((9) in FIG. 12). That is, the lower part of the sealed container 21 becomes the high-pressure oil storage unit 51.
The lubricating oil stored in the high-pressureoil storage unit 51 flows from the buffer space oil supply unit 18 into the buffer unit 12 provided inside the sealed container 21 ((10) in FIG. 12). The lubricating oil that has flowed into the buffer unit 12 is supplied from the high-stage oil supply pipe 15 to the vane back pressure chamber 50 of the high-stage compression unit 2 ((11) in FIG. 12).
高圧油貯蔵部51に貯えられた潤滑油は、密閉容器21の内部に設けられたバッファ部12へバッファ空間給油部18から流入する(図12の(10))。バッファ部12へ流入した潤滑油は、高段給油配管15から高段圧縮部2のベーン背圧室50等へ給油される(図12の(11))。 When the inside of the sealed
The lubricating oil stored in the high-pressure
中間圧が高圧よりも高くなる圧力の逆転現象が起きた場合には、逆止め機構11が作動する。そして、中間連結部7から分岐してバッファ部12へ繋がるバイパス回路10から、中間連結部7を流れる冷媒がバッファ部12内へ流入する(図12の(11))。
これにより、実施の形態1の低圧シェル型の圧縮機の場合と同様に、高圧シェル型の圧縮機においても、高段圧縮部2のベーン背圧室50等への給油を促進して、高段圧縮部2のベーン背圧室50内の圧力と高段圧縮部2のシリンダ45内の圧力とを均一の圧力にすることができる。その結果、ベーン飛び等の現象が解消して、高段圧縮部2でも冷媒が圧縮されるようになり、正常状態へ復帰することができる。 When a reverse pressure phenomenon occurs in which the intermediate pressure is higher than the high pressure, thecheck mechanism 11 is activated. And the refrigerant | coolant which flows through the intermediate connection part 7 flows in into the buffer part 12 from the bypass circuit 10 branched from the intermediate connection part 7 and connected to the buffer part 12 ((11) of FIG. 12).
As a result, as in the case of the low pressure shell type compressor of the first embodiment, in the high pressure shell type compressor, the oil supply to the vane backpressure chamber 50 and the like of the high-stage compression unit 2 is promoted, The pressure in the vane back pressure chamber 50 of the stage compression unit 2 and the pressure in the cylinder 45 of the high stage compression unit 2 can be made uniform. As a result, phenomena such as vane jumping are eliminated, and the refrigerant is compressed even in the high-stage compression unit 2, and the normal state can be restored.
これにより、実施の形態1の低圧シェル型の圧縮機の場合と同様に、高圧シェル型の圧縮機においても、高段圧縮部2のベーン背圧室50等への給油を促進して、高段圧縮部2のベーン背圧室50内の圧力と高段圧縮部2のシリンダ45内の圧力とを均一の圧力にすることができる。その結果、ベーン飛び等の現象が解消して、高段圧縮部2でも冷媒が圧縮されるようになり、正常状態へ復帰することができる。 When a reverse pressure phenomenon occurs in which the intermediate pressure is higher than the high pressure, the
As a result, as in the case of the low pressure shell type compressor of the first embodiment, in the high pressure shell type compressor, the oil supply to the vane back
なお、密閉容器21内の冷媒ガス空間とバッファ部12とは均圧部17により均一の圧力となる。
また、高段給油配管15は必ずしも必要ではなく、バッファ部12に高段圧縮部2のベーン背圧室50を含ませ、一体に形成してもよい。
また、ここでは、バッファ部12を密閉容器21に内蔵し、逆止め機構11を密閉容器21の外部に設けている。しかし、バッファ部12を外部に設けてもよく、逆止め機構11を密閉容器21に内蔵してもよい。 In addition, the refrigerant gas space in the sealedcontainer 21 and the buffer unit 12 have a uniform pressure by the pressure equalizing unit 17.
The high-stageoil supply pipe 15 is not necessarily required, and the buffer section 12 may include the vane back pressure chamber 50 of the high-stage compression section 2 and may be formed integrally.
Here, thebuffer unit 12 is built in the sealed container 21, and the check mechanism 11 is provided outside the sealed container 21. However, the buffer unit 12 may be provided outside, and the check mechanism 11 may be built in the sealed container 21.
また、高段給油配管15は必ずしも必要ではなく、バッファ部12に高段圧縮部2のベーン背圧室50を含ませ、一体に形成してもよい。
また、ここでは、バッファ部12を密閉容器21に内蔵し、逆止め機構11を密閉容器21の外部に設けている。しかし、バッファ部12を外部に設けてもよく、逆止め機構11を密閉容器21に内蔵してもよい。 In addition, the refrigerant gas space in the sealed
The high-stage
Here, the
実施の形態6.
実施の形態6では、以上の実施の形態で説明した二段ロータリ圧縮機を備える冷凍空調装置について説明する。Embodiment 6 FIG.
In the sixth embodiment, a refrigeration air conditioner including the two-stage rotary compressor described in the above embodiment will be described.
実施の形態6では、以上の実施の形態で説明した二段ロータリ圧縮機を備える冷凍空調装置について説明する。
In the sixth embodiment, a refrigeration air conditioner including the two-stage rotary compressor described in the above embodiment will be described.
図13は、実施の形態1から5で説明した二段ロータリ圧縮機を備える冷凍空調装置95の冷媒回路の一例を示す図である。
冷凍空調装置95では、二段ロータリ圧縮機の油分離機構9に凝縮器31が接続される。そして、凝縮器31から内部熱交換器36、膨張弁32、蒸発器33が順次接続されて、密閉容器21の吸入配管5へと繋がる。
また、内部熱交換器36と膨張弁32の間から分岐するインジェクション回路34が、インジェクション膨張弁35を介して内部熱交換器36から中間連結部7へと繋がる。 FIG. 13 is a diagram illustrating an example of a refrigerant circuit of the refrigeration air conditioner 95 including the two-stage rotary compressor described in the first to fifth embodiments.
In the refrigeration air conditioner 95, thecondenser 31 is connected to the oil separation mechanism 9 of the two-stage rotary compressor. Then, the internal heat exchanger 36, the expansion valve 32, and the evaporator 33 are sequentially connected from the condenser 31 to the suction pipe 5 of the sealed container 21.
In addition, aninjection circuit 34 that branches from between the internal heat exchanger 36 and the expansion valve 32 is connected to the intermediate connecting portion 7 from the internal heat exchanger 36 via the injection expansion valve 35.
冷凍空調装置95では、二段ロータリ圧縮機の油分離機構9に凝縮器31が接続される。そして、凝縮器31から内部熱交換器36、膨張弁32、蒸発器33が順次接続されて、密閉容器21の吸入配管5へと繋がる。
また、内部熱交換器36と膨張弁32の間から分岐するインジェクション回路34が、インジェクション膨張弁35を介して内部熱交換器36から中間連結部7へと繋がる。 FIG. 13 is a diagram illustrating an example of a refrigerant circuit of the refrigeration air conditioner 95 including the two-stage rotary compressor described in the first to fifth embodiments.
In the refrigeration air conditioner 95, the
In addition, an
実施の形態1から5に係る二段ロータリ圧縮機は、圧力の逆転現象が起こった場合であっても、正常状態へ復帰することができる。そのため、実施の形態1から5に係る二段ロータリ圧縮機は、性能がよく、信頼性が高い。したがって、実施の形態1から5に係る二段ロータリ圧縮機を備える冷凍空調装置95も同様に、性能がよく、信頼性が高い。
The two-stage rotary compressor according to Embodiments 1 to 5 can return to a normal state even when a pressure reversal phenomenon occurs. Therefore, the two-stage rotary compressor according to Embodiments 1 to 5 has good performance and high reliability. Therefore, the refrigerating and air-conditioning apparatus 95 including the two-stage rotary compressor according to the first to fifth embodiments similarly has good performance and high reliability.
つまり、以上をまとめると次のようになる。
密閉容器内に、低段圧縮部と、高段圧縮部と、前記低段圧縮部及び前記高段圧縮部を駆動する電動機とが収納され、低圧の冷媒が前記低段圧縮部に吸入され、中間圧まで圧縮された後、中間連結部を経由して、前記高段圧縮部に吸入され、高圧まで圧縮された後、油分離機構によって冷媒中の潤滑油を分離し、分離された潤滑油は、高圧油貯蔵部に貯えられた後、給油回路により前記密閉容器内の、前記低段圧縮部及び前記高段圧縮部に給油され、潤滑油分離後の冷媒は外部冷媒回路に供給される二段ロータリ圧縮機において、
前記中間連結部より分岐して、前記給油回路に接続されるバイパス回路に、前記中間連結部からの流れのみを許容する逆止め機構と、前記高圧油貯蔵部の一部の潤滑油を貯えるバッファ空間とを備え、前記逆止め機構より下流側で前記油分離機構に繋がる均圧部を備えたことを特徴とする。 In other words, the above is summarized as follows.
In a sealed container, a low-stage compression unit, a high-stage compression unit, and an electric motor that drives the low-stage compression unit and the high-stage compression unit are housed, and a low-pressure refrigerant is sucked into the low-stage compression unit, After being compressed to an intermediate pressure, after being sucked into the high-stage compression part via an intermediate connecting part and compressed to a high pressure, the lubricating oil in the refrigerant is separated by an oil separation mechanism, and the separated lubricating oil Is stored in the high-pressure oil storage unit and then supplied to the low-stage compression unit and the high-stage compression unit in the sealed container by an oil supply circuit, and the refrigerant after the separation of the lubricating oil is supplied to the external refrigerant circuit. In a two-stage rotary compressor,
A non-return mechanism for allowing only a flow from the intermediate connecting portion to a bypass circuit branched from the intermediate connecting portion and connected to the oil supply circuit, and a buffer for storing a part of lubricating oil in the high pressure oil storage portion And a pressure equalizing section connected to the oil separation mechanism on the downstream side of the check mechanism.
密閉容器内に、低段圧縮部と、高段圧縮部と、前記低段圧縮部及び前記高段圧縮部を駆動する電動機とが収納され、低圧の冷媒が前記低段圧縮部に吸入され、中間圧まで圧縮された後、中間連結部を経由して、前記高段圧縮部に吸入され、高圧まで圧縮された後、油分離機構によって冷媒中の潤滑油を分離し、分離された潤滑油は、高圧油貯蔵部に貯えられた後、給油回路により前記密閉容器内の、前記低段圧縮部及び前記高段圧縮部に給油され、潤滑油分離後の冷媒は外部冷媒回路に供給される二段ロータリ圧縮機において、
前記中間連結部より分岐して、前記給油回路に接続されるバイパス回路に、前記中間連結部からの流れのみを許容する逆止め機構と、前記高圧油貯蔵部の一部の潤滑油を貯えるバッファ空間とを備え、前記逆止め機構より下流側で前記油分離機構に繋がる均圧部を備えたことを特徴とする。 In other words, the above is summarized as follows.
In a sealed container, a low-stage compression unit, a high-stage compression unit, and an electric motor that drives the low-stage compression unit and the high-stage compression unit are housed, and a low-pressure refrigerant is sucked into the low-stage compression unit, After being compressed to an intermediate pressure, after being sucked into the high-stage compression part via an intermediate connecting part and compressed to a high pressure, the lubricating oil in the refrigerant is separated by an oil separation mechanism, and the separated lubricating oil Is stored in the high-pressure oil storage unit and then supplied to the low-stage compression unit and the high-stage compression unit in the sealed container by an oil supply circuit, and the refrigerant after the separation of the lubricating oil is supplied to the external refrigerant circuit. In a two-stage rotary compressor,
A non-return mechanism for allowing only a flow from the intermediate connecting portion to a bypass circuit branched from the intermediate connecting portion and connected to the oil supply circuit, and a buffer for storing a part of lubricating oil in the high pressure oil storage portion And a pressure equalizing section connected to the oil separation mechanism on the downstream side of the check mechanism.
1 低段圧縮部、2 高段圧縮部、3 低段吐出マフラ、4 高段吐出マフラ、5 吸入配管、6 低段吸入配管、7 中間連結部、8 高段吐出配管、9 油分離機構、10 バイパス回路、11 逆止め機構、12 バッファ部、13 給油回路、14 低段給油配管、15 高段給油配管、16 均圧回路、17 均圧部、18 バッファ空間給油部、20 高段ローリングピストン給油配管、21 密閉容器、22 電動機、31 凝縮器、32 膨張弁、33 蒸発器、34 インジェクション回路、35 インジェクション膨張弁、36 内部熱交換器、41,81 駆動軸、42 ローリングピストン、43,83 ベーン、44 バネ、45,85 シリンダ、46,86 吸入口、47,87 吐出口、48 中間プレート、49,89 吐出弁、50,90 ベーン背圧室、51 高圧油貯蔵部、60 ロータ、70 吸入室、71 圧縮室、73 作動室、91 弁体、92,94 弁座、93 板バネ。
1 Low-stage compression section, 2 High-stage compression section, 3 Low-stage discharge muffler, 4 High-stage discharge muffler, 5 Suction pipe, 6 Low-stage suction pipe, 7 Intermediate connection section, 8 High-stage discharge pipe, 9 Oil separation mechanism, 10 bypass circuit, 11 check mechanism, 12 buffer part, 13 oil supply circuit, 14 low stage oil supply pipe, 15 high stage oil supply pipe, 16 pressure equalization circuit, 17 pressure equalization part, 18 buffer space oil supply part, 20 high stage rolling piston Refueling piping, 21 sealed container, 22 electric motor, 31 condenser, 32 expansion valve, 33 evaporator, 34 injection circuit, 35 injection expansion valve, 36 internal heat exchanger, 41, 81 drive shaft, 42 rolling piston, 43, 83 Vane, 44 spring, 45, 85 cylinder, 46, 86 suction port, 47, 87 discharge port, 48 intermediate pre 49, 89 Discharge valve, 50, 90 vane back pressure chamber, 51 high pressure oil reservoir, 60 rotor, 70 suction chamber, 71 compression chamber, 73 working chamber, 91 valve body, 92, 94 valve seat, 93 leaf spring .
Claims (7)
- 低段側のシリンダ内に形成された圧縮空間であって、低段側の背圧室から出た低段側のベーンにより吸入室と圧縮室とが仕切られた圧縮空間を用いて、冷媒を圧縮する低段圧縮部と、
高段側のシリンダ内に形成された圧縮空間であって、高段側の背圧室から出た高段側のベーンにより吸入室と圧縮室とが仕切られた圧縮空間を用いて、前記低段圧縮部が圧縮した冷媒をさらに圧縮する高段圧縮部と、
前記低段圧縮部と前記高段圧縮部とを内部に収納する密閉容器と、
前記低段圧縮部と前記高段圧縮部とを繋ぎ、前記低段圧縮部から吐出された冷媒を前記高段圧縮部へ流入させる中間流路と、
油を前記高段側の背圧室へ供給して、前記高段側のベーンに加圧する給油部と、
前記中間流路と前記給油部とを繋ぐバイパス回路と、
前記低段圧縮部から吐出された冷媒の圧力が前記高段圧縮部から吐出された冷媒の圧力よりも高い場合に、前記バイパス回路を介して前記給油部へ前記中間流路を流れる冷媒を流入させる給油促進部と
を備えることを特徴とする二段圧縮機。 A compression space formed in a low-stage side cylinder, wherein the suction chamber and the compression chamber are partitioned by a low-stage vane coming out of the low-stage side back pressure chamber, A low-stage compression section to compress,
A compression space formed in a high-stage cylinder, wherein the suction chamber and the compression chamber are separated from each other by a high-stage vane coming out of the high-pressure side back pressure chamber. A high-stage compression section that further compresses the refrigerant compressed by the stage compression section;
A sealed container that houses the low-stage compression section and the high-stage compression section;
An intermediate flow path connecting the low-stage compression section and the high-stage compression section, and allowing the refrigerant discharged from the low-stage compression section to flow into the high-stage compression section;
An oil supply section that supplies oil to the high pressure side back pressure chamber and pressurizes the high pressure vane;
A bypass circuit connecting the intermediate flow path and the oil supply unit;
When the pressure of the refrigerant discharged from the low-stage compression unit is higher than the pressure of the refrigerant discharged from the high-stage compression unit, the refrigerant flowing through the intermediate flow path flows into the oil supply unit via the bypass circuit A two-stage compressor comprising: an oil supply facilitating part. - 前記二段圧縮機は、さらに、
前記高段圧縮部が圧縮した冷媒が吐出され、吐出された冷媒から油を分離して、分離した油を前記高段側の背圧室へ供給する油分離部を備え、
前記給油部と前記油分離部との間には、前記給油部の圧力と前記油分離部の圧力とを均一にする均圧部が設けられた
ことを特徴とする請求項1に記載の二段圧縮機。 The two-stage compressor further includes:
The refrigerant compressed by the high-stage compression unit is discharged, oil is separated from the discharged refrigerant, and an oil separation unit that supplies the separated oil to the back pressure chamber on the high-stage side is provided.
2. The pressure equalizing unit is provided between the oil supply unit and the oil separation unit, and a pressure equalizing unit that equalizes the pressure of the oil supply unit and the pressure of the oil separation unit is provided. Stage compressor. - 前記給油部は、前記油分離部の内部に設けられた
ことを特徴とする請求項2に記載の二段圧縮機。 The two-stage compressor according to claim 2, wherein the oil supply unit is provided inside the oil separation unit. - 前記給油促進部は、前記油分離部の内部に設けられた
ことを特徴とする請求項2に記載の二段圧縮機。 The two-stage compressor according to claim 2, wherein the oil supply promoting unit is provided inside the oil separation unit. - 前記給油部は、前記密閉容器の内部に設けられた
ことを特徴とする請求項1に記載の二段圧縮機。 The two-stage compressor according to claim 1, wherein the oil supply unit is provided inside the sealed container. - 前記給油促進部は、前記密閉容器の内部に設けられた
ことを特徴とする請求項1に記載の二段圧縮機。 The two-stage compressor according to claim 1, wherein the oil supply promoting unit is provided inside the sealed container. - 請求項1から6までのいずれか1項に記載の二段圧縮機
を備えることを特徴とする冷凍空調装置。 A refrigerating and air-conditioning apparatus comprising the two-stage compressor according to any one of claims 1 to 6.
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Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012202357A (en) * | 2011-03-28 | 2012-10-22 | Toshiba Carrier Corp | Rotary compressor and refrigeration cycle device |
CN103291624A (en) * | 2012-02-22 | 2013-09-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Single two-stage totally sealed refrigeration compressor with external mixing chamber |
CN103375405A (en) * | 2012-04-26 | 2013-10-30 | 珠海格力电器股份有限公司 | Compressor and air conditioning system and heat pump water heater with same |
CN110219803A (en) * | 2019-07-18 | 2019-09-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, air conditioner |
CN111486609A (en) * | 2020-04-02 | 2020-08-04 | 珠海格力节能环保制冷技术研究中心有限公司 | Air conditioning system and control method |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104500405A (en) * | 2014-12-09 | 2015-04-08 | 广东美芝制冷设备有限公司 | Low-backpressure rotation type compressor |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002276578A (en) * | 2001-03-14 | 2002-09-25 | Matsushita Electric Ind Co Ltd | Rotary type multi-stage compressor |
JP2006214445A (en) * | 2006-03-31 | 2006-08-17 | Sanyo Electric Co Ltd | Rotary compressor |
WO2009028261A1 (en) * | 2007-08-28 | 2009-03-05 | Mitsubishi Electric Corporation | Rotary compressor |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3895976B2 (en) * | 2001-11-30 | 2007-03-22 | 三洋電機株式会社 | Multistage rotary compressor |
-
2009
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Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002276578A (en) * | 2001-03-14 | 2002-09-25 | Matsushita Electric Ind Co Ltd | Rotary type multi-stage compressor |
JP2006214445A (en) * | 2006-03-31 | 2006-08-17 | Sanyo Electric Co Ltd | Rotary compressor |
WO2009028261A1 (en) * | 2007-08-28 | 2009-03-05 | Mitsubishi Electric Corporation | Rotary compressor |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012202357A (en) * | 2011-03-28 | 2012-10-22 | Toshiba Carrier Corp | Rotary compressor and refrigeration cycle device |
CN103291624A (en) * | 2012-02-22 | 2013-09-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Single two-stage totally sealed refrigeration compressor with external mixing chamber |
CN103375405A (en) * | 2012-04-26 | 2013-10-30 | 珠海格力电器股份有限公司 | Compressor and air conditioning system and heat pump water heater with same |
CN110219803A (en) * | 2019-07-18 | 2019-09-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, air conditioner |
CN111486609A (en) * | 2020-04-02 | 2020-08-04 | 珠海格力节能环保制冷技术研究中心有限公司 | Air conditioning system and control method |
CN111486609B (en) * | 2020-04-02 | 2021-10-08 | 珠海格力节能环保制冷技术研究中心有限公司 | Air conditioning system and control method |
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