WO2013046632A1 - 圧縮機 - Google Patents
圧縮機 Download PDFInfo
- Publication number
- WO2013046632A1 WO2013046632A1 PCT/JP2012/006065 JP2012006065W WO2013046632A1 WO 2013046632 A1 WO2013046632 A1 WO 2013046632A1 JP 2012006065 W JP2012006065 W JP 2012006065W WO 2013046632 A1 WO2013046632 A1 WO 2013046632A1
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- WIPO (PCT)
- Prior art keywords
- groove
- lubricating oil
- oil
- thrust bearing
- drive shaft
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- 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
- F04C18/22—Rotary-piston pumps specially adapted for elastic fluids of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth equivalents than the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/023—Lubricant distribution through a hollow driving shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/56—Bearing bushings or details thereof
-
- 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
-
- 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 a rotary compressor, and particularly relates to measures for cooling a thrust bearing surface.
- a thrust bearing that receives a thrust load is constituted by the lower end surface of the eccentric part and the upper end surface of the lower end plate constituting the lower end plate.
- Lubricating oil is supplied between the lower end surface of the eccentric part constituting the sliding surface of the thrust bearing and the upper end surface of the lower end plate, and the sliding surface of the thrust bearing is cooled by the lubricating oil. The seizure on the sliding surface of the thrust bearing is suppressed.
- the present invention has been made in view of such a point, and an object thereof is to promote cooling of the sliding surface of the thrust bearing with lubricating oil in a rotary compressor.
- the first invention includes a drive mechanism (20) having a drive shaft (23) formed with an eccentric portion (26) and extending vertically, and a cylindrical cylinder (34) covering the outer periphery of the eccentric portion (26).
- a piston (50) disposed in the cylinder (34) and externally fitted to the eccentric part (26), an upper end plate (31) closing the upper end of the cylinder (34), and the cylinder (34)
- a compression mechanism (30) having a lower end plate (35) for closing the lower end of the shaft, and a thrust bearing surface in sliding contact with the upper end surface (35b) of the lower end plate (35) on the lower end surface of the eccentric portion (26) (26a) and an oil passage (70) through which lubricating oil flows in the drive shaft (23), wherein the eccentric portion (26) includes the thrust Opened in the bearing surface (26a) and extending in the circumferential direction, a pressure reducing groove (65) is formed for supplying the lubricating oil in the oil passage (70) to depressurize the lubric
- the lubricating oil flowing through the oil passage (70) in the drive shaft (23) is supplied to the decompression groove (65) formed in the eccentric part (26). Further, the lubricating oil supplied to the pressure reducing groove (65) is supplied between the thrust bearing surface (26a) of the eccentric portion (26) and the upper end surface (35b) of the lower end plate (35), which are in sliding contact with each other. It flows radially outward by force.
- the gas refrigerant is dissolved in the lubricating oil supplied from the oil passage (70) to the decompression groove (65), the lubricant is decompressed in the decompression groove (65).
- the gas refrigerant dissolved in the lubricating oil is separated and foamed. Since the specific gravity of the lubricating oil is larger than that of the gas refrigerant, the centrifugal force received by the lubricating oil is larger than the centrifugal force received by the gas refrigerant. Therefore, when the gas refrigerant is separated from the lubricating oil in the decompression groove (65), the gas refrigerant accumulates in the upper part of the decompression groove (65), while the lubricant having a higher specific gravity than the gas refrigerant receives a large centrifugal force and depressurizes.
- oil that extends in the circumferential direction and is supplied with lubricating oil in the oil passage (70) is provided between the lower end plate (35) and the drive shaft (23).
- a groove (74) is formed, and the decompression groove (65) communicates with the oil groove (74) through a communication portion (65a), and the communication portion (65a) is communicated with the pressure reduction from the oil groove (74). It is comprised so that it may become a throttle part which decompresses the lubricating oil supplied to a groove
- the lubricating oil in the oil passage (70) passes through the oil groove (74) extending in the circumferential direction between the lower end plate (35) and the drive shaft (23) into the decompression groove (65).
- the communicating part (65a) between the oil groove (74) and the pressure reducing groove (65) is a throttle part, the lubricating oil that has flowed into the pressure reducing groove (65) is rapidly decompressed and melted. The generated gas refrigerant is separated and foamed.
- the oil that extends in the circumferential direction and is supplied with lubricating oil in the oil passage (70) is provided between the lower end plate (35) and the drive shaft (23), the oil that extends in the circumferential direction and is supplied with lubricating oil in the oil passage (70) is provided.
- a groove (74) is formed, and the pressure-reducing groove (65) and the oil groove (74) are formed between the thrust bearing surface (26a) and the upper end surface (35b) of the lower end plate (35) ( 65b), and the gap (65b) serves as a throttle for reducing the pressure of the lubricating oil supplied from the oil groove (74) to the pressure reducing groove (65).
- the lubricating oil in the oil passage (70) passes through the oil groove (74), and then the gap between the thrust bearing surface (26a) and the upper end surface (35b) of the lower end plate (35) ( 65b) is supplied to the decompression groove (65), but since this gap (65b) is a constricted portion, the lubricating oil that has flowed into the decompression groove (65) was suddenly decompressed and dissolved. The gas refrigerant is separated and foamed.
- the peripheral portion of the hole portion through which the drive shaft (23) is inserted in the upper end surface (35b) of the lower end plate (35) extends in the circumferential direction.
- a groove portion (61) for forming an elastic bearing (62) is formed on the inner peripheral edge, and the pressure reducing groove (65) is formed at a position overlapping the elastic bearing (62) in plan view.
- the pressure of the compressed fluid acts on the eccentric part (26) of the drive shaft (23) via the piston (50). Therefore, when the internal pressure of the fluid compression chamber is relatively high during high load operation or the like, the drive shaft (23) may be greatly bent.
- a corner formed by the upper end surface (35b) and the inner peripheral surface of the lower end plate (35) is slidably contacted with the main shaft portion of the drive shaft (23), so-called corner contact occurs. .
- corner contact occurs, the contact surface pressure increases, the sliding loss and wear at the bearing portion of the lower end plate increase, and the operating efficiency and reliability of the rotary compressor are lowered.
- the drive shaft (23) is elastically supported by the elastic bearing (62), thereby suppressing an increase in contact surface pressure due to angular contact.
- the elastic bearing (62) flexibly supports the drive shaft (23) by bending, but when bent, a part of the upper end is caught on the thrust bearing surface (26a) of the eccentric part (26), and the thrust The bearing surface (26a) could be damaged.
- the pressure reducing groove (65) is provided at a position overlapping the elastic bearing (62) in plan view. Thereby, even if the elastic bearing (62) is deformed, the upper end of the elastic bearing (62) does not get caught on the thrust bearing surface (26a) of the eccentric part (26) because it enters the pressure reducing groove (65). Further, since the elastic bearing (62) is formed on the inner peripheral edge of the lower end plate (35), the pressure reducing groove (65) is provided at a position overlapping the elastic bearing (62) in plan view. Is formed at the inner peripheral end of the thrust bearing surface (26a). By forming the pressure reducing groove (65) at the inner peripheral end of the thrust bearing surface (26a) in this way, the lubricating oil flowing out from the pressure reducing groove (65) spreads over the entire thrust bearing surface (26a). Become.
- the decompression groove (65) is formed such that the outer peripheral edge is located on the inner peripheral side with respect to the outer peripheral edge of the groove (61).
- the decompression groove (65) is formed such that the outer peripheral edge is located on the inner peripheral side with respect to the outer peripheral edge of the groove (61). That is, the decompression groove (65) is formed with a smaller diameter than the groove part (61) forming the elastic bearing (62).
- the area of the thrust bearing surface (26a) decreases as the diameter of the decompression groove (65) opened to the thrust bearing surface (26a) increases.
- the decompression groove (65) is formed with a smaller diameter than the groove portion forming the elastic bearing (62), the reduction of the area of the thrust bearing surface (26a) is suppressed to the minimum necessary reduction.
- the eccentric portion (26) communicates with an upper portion of the decompression groove (65) and the oil passage (70). 66) is formed.
- the gas refrigerant separated from the lubricating oil in the decompression groove (65) is discharged to the oil passage (70) through the communication passage (66).
- a side oil groove (72) is formed to guide oil below the eccentric part (26), and the pressure reducing groove (65) is open at the lower end of the side oil groove (72) to the pressure reducing groove (65). It is formed to do.
- side oil supply grooves (72) for guiding lubricating oil from the upper side to the lower side of the eccentric part (26) are formed on the side surface of the eccentric part (26). That is, the side oil supply groove (72) extends from the upper end to the lower end on the side surface of the eccentric portion (26).
- the side oil supply groove (72) is formed so as to open in the thrust bearing surface (26a)
- a corner portion is formed between the wall surface forming the side oil supply groove (72) and the thrust bearing surface (26a).
- the thrust bearing surface (26a) slides with respect to the upper end surface (35b) of the lower end plate (35)
- the upper end surface (35b) of the lower end plate (35) may be scraped off.
- the pressure reducing groove (65) is formed so that the lower end of the side oil supply groove (72) opens in the pressure reducing groove (65). Therefore, even if a corner portion is formed between the wall surface that forms the side oil supply groove (72) and the wall surface that forms the upper end of the decompression groove (65), the corner portion causes the upper end surface (35b) of the lower end plate (35). ) Is not cut.
- a part of the lubricating oil flowing through the oil passage (70) in the drive shaft (23) is supplied to the decompression groove (65) opened in the thrust bearing surface (26a) and decompressed. It was.
- the gas refrigerant dissolved in the lubricating oil is separated in the decompression groove (65), and only the lubricating oil that receives a centrifugal force larger than that of the gas refrigerant flows out of the decompression groove (65) to the outside in the radial direction. It can be supplied between the thrust bearing surface (26a) constituting the sliding surface and the upper end surface (35b) of the lower end plate (35). Therefore, since generation
- the oil groove (74) for guiding the lubricating oil in the oil passage (70) to the pressure reducing groove (65) and the pressure reducing groove (65) are communicated via the communicating portion (65a).
- the communicating portion (65a) is configured to be a throttle portion that depressurizes the lubricating oil supplied from the oil groove (74) to the pressure reducing groove (65). Therefore, with a simple configuration, the lubricating oil in which the gas refrigerant has melted in the decompression groove (65) can be rapidly depressurized, and the gas refrigerant can be reliably separated from the lubricating oil.
- the oil groove (74) for guiding the lubricating oil in the oil passage (70) to the pressure reducing groove (65) and the pressure reducing groove (65) are connected to the thrust bearing surface (26a) and the lower end plate (35). ) Through the gap (65b) between the upper end surface (35b) and the throttle part for reducing the pressure of the lubricating oil supplied from the oil groove (74) to the pressure reduction groove (65).
- the oil groove (74) and the decompression groove (65) were configured so that Therefore, with a simple configuration, the lubricating oil in which the gas refrigerant has melted in the decompression groove (65) can be rapidly depressurized, and the gas refrigerant can be reliably separated from the lubricating oil.
- the pressure reducing groove (65) is provided at a position overlapping the elastic bearing (62) in plan view, the elastic bearing (62) of the elastic bearing (62) is deformed. It is possible to prevent the eccentric portion (26) at the upper end from being caught on the thrust bearing surface (26a). Therefore, damage to the thrust bearing surface (26a) can be prevented. Further, since the pressure reducing groove (65) is formed at the inner peripheral end of the thrust bearing surface (26a), the lubricating oil flowing out from the pressure reducing groove (65) spreads over the entire thrust bearing surface (26a), and the thrust bearing surface (26a) The entire area can be cooled by lubricating oil.
- the pressure reducing groove (65) since the pressure reducing groove (65) has a smaller diameter than the groove portion (61) that forms the elastic bearing (62), the pressure reducing groove (65) opening in the thrust bearing surface (26a). It is possible to suppress the reduction in the area of the thrust bearing surface (26a) due to the formation to the minimum necessary.
- the gas refrigerant separated from the lubricating oil in the decompression groove (65) can be discharged. Therefore, even when the engine is operated for a long time at a high rotational speed, only the lubricating oil from which the gas refrigerant has been separated can be supplied between the sliding surfaces of the thrust bearing. Therefore, the thrust bearing surface (26a) of the eccentric portion (26) that becomes the sliding surface of the thrust bearing and the upper end surface (35b) of the lower end plate (35) can be reliably cooled.
- the side oil supply groove (72) is provided on the side surface of the eccentric portion (26), and the lower end of the side oil supply groove (72) is opened in the pressure reducing groove (65).
- the reduced pressure groove (65) was formed. Therefore, it is possible to prevent the upper end surface (35b) of the lower end plate (35) in sliding contact with the thrust bearing surface (26a) from being cut by the corner portion formed at the lower end portion of the side oil supply groove (72).
- FIG. 1 is a longitudinal sectional view of a compressor according to Embodiment 1 of the present invention.
- FIG. 2 is a cross-sectional view of the compression mechanism of the compressor of FIG.
- FIG. 3 is a plan view of the rear head of the compressor of FIG.
- FIG. 4 is a partially enlarged view of the compressor of FIG. 5 is a cross-sectional view taken along the line VV of FIG.
- FIG. 6 is a partially enlarged view of the compressor according to Embodiment 2 of the present invention.
- 7 is a sectional view taken along line VII-VII in FIG.
- FIG. 8 is a partial enlarged view of a compressor according to Embodiment 3 of the present invention.
- FIG. 9 is a partially enlarged view of a compressor according to Embodiment 4 of the present invention.
- Embodiment 1 of the Invention The rotary compressor (10) according to Embodiment 1 of the present invention is provided, for example, in a refrigerant circuit of an air conditioner, compresses refrigerant sucked from an evaporator, and discharges the refrigerant to a radiator.
- the rotary compressor (10) includes a casing (11), an electric motor (20), and a compression mechanism (30).
- the casing (11) includes a cylindrical body part (12), an upper end panel (13) that closes the upper end side of the body part (12), and a lower end panel that closes the lower end side of the body part (12). (14).
- a first suction pipe (15a) and a second suction pipe (15b) are attached to the trunk part (12) through the lower part of the trunk part (12).
- a discharge pipe (16) is attached to the upper part of the upper end plate (13) so as to penetrate the upper end plate (13).
- the electric motor (20) and the compression mechanism (30) are accommodated in the casing (11). Further, an oil reservoir (17) is formed at the bottom of the lower end plate (14) in which lubricating oil for lubricating the sliding portion of the compression mechanism (30) is stored.
- the electric motor (20) includes a cylindrical stator (21), a cylindrical rotor (22), and a drive shaft (23).
- the stator (21) is fixed to the body (12) of the casing (11).
- the rotor (22) is disposed in the hollow portion of the stator (21).
- a drive shaft (23) is fixed in the hollow portion of the rotor (22) so as to penetrate the rotor (22).
- the drive shaft (23) includes a main shaft portion (24) extending vertically and two eccentric portions (25, 26) formed integrally with the main shaft portion (24) near the lower end of the main shaft portion (24). have.
- the two eccentric parts (25, 26) are constituted by an upper upper eccentric part (25) and a lower eccentric part (26) provided below the upper eccentric part (25), both of which are main shaft parts. It has a larger diameter than (24).
- Each of the upper eccentric portion (25) and the lower eccentric portion (26) has an axis that is eccentric from the axis of the main shaft portion (24) by a predetermined distance.
- the eccentric directions of the upper eccentric portion (25) and the lower eccentric portion (26) with respect to the main shaft portion (24) are shifted by 180 degrees.
- a thrust bearing surface (26a) is formed on the lower end surface of the lower eccentric portion (26) so as to be in sliding contact with an upper end surface (35b) of a rear head (35) described later.
- a centrifugal pump (27) immersed in an oil sump (18) is provided at the lower end of the drive shaft (23).
- An oil supply passage (oil passage) (70) in which the lubricating oil pumped up by the centrifugal pump (27) flows is formed in the drive shaft (23) in the axial direction.
- First to fifth passages (70a to 70e) are connected to the oil supply passage (70).
- the first to fifth passages (70a to 70e) respectively extend in the radial direction of the drive shaft (23), and the respective outflow ends are opened on the outer peripheral surface of the drive shaft (23).
- the first passage (70a) is an exhaust gas passage for discharging the foamed refrigerant gas inside the oil supply passage (70), and the second to fifth passages (70b to 70e) are pumped to the oil supply passage (70). It is an oil outflow passage for flowing out the lubricating oil.
- the first passage (70a) is formed near the upper side of the upper end of the compression mechanism (30) of the drive shaft (23).
- the second passage (70b) is formed in the vicinity of the upper eccentric portion (25) of the drive shaft (23), and the third passage (70c) is formed in the upper eccentric portion (25).
- the fourth passage (70d) is formed inside the lower eccentric portion (26), and the fifth passage (70e) is formed near the lower side of the lower eccentric portion (26) of the drive shaft (23).
- the third passage (70c) formed in the upper eccentric portion (25) and the fourth passage (70d) formed in the lower eccentric portion (26) are in an eccentric direction of each eccentric portion (25, 26). 120 ° out of phase and 180 ° out of phase with each other.
- the first and second longitudinal grooves (71, 72) are formed on the outer peripheral surface of the drive shaft (23).
- the first vertical groove (71) extends in the axial direction on the outer peripheral surface of the upper eccentric portion (25) of the drive shaft (23), and the outflow end of the third passage (70c) is opened.
- the first vertical groove (71) guides the lubricating oil on the upper end surface of the upper eccentric portion (25) between the lower end surface and the upper end surface of a middle plate (33) described later.
- the second vertical groove (72) extends in the axial direction on the outer peripheral surface of the lower eccentric portion (26) of the drive shaft (23), and the outflow end of the fourth passage (70d) is opened.
- the second vertical groove (72) guides the lubricating oil on the upper end surface of the lower eccentric portion (26) between the lower end surface and the upper end surface (35b) of the rear head (35) described later.
- first and second annular grooves (73, 74) are formed on the outer peripheral surface of the drive shaft (23).
- the first annular groove (73) extends in the circumferential direction on the outer peripheral surface near the upper side of the upper eccentric portion (25) of the drive shaft (23), and the outflow end of the second passage (70b) is opened.
- the first annular groove (73) guides the lubricating oil flowing out from the second passage (70b) in the circumferential direction between the upper end surface of the upper eccentric portion (25) and the lower end surface of the front head (31) described later. Let it flow.
- the second annular groove (74) constitutes an oil groove according to the present invention, and extends in the circumferential direction on the outer peripheral surface near the lower side of the lower eccentric portion (26) of the drive shaft (23), and the fifth passage ( The outflow end of 70e) is open.
- the second annular groove (74) guides the lubricating oil flowing out from the fifth passage (70e) in the circumferential direction, and supplies the lubricating oil to a pressure reducing groove (65) (see FIG. 4) described later.
- the lubricating oil in the oil reservoir (17) is pumped up to the oil supply passage (70) by the centrifugal pump (27) as the drive shaft (23) rotates.
- Lubricating oil pumped into the oil supply passage (70) flows out from each of the second to fifth passages (70b to 70e), and the first and second longitudinal grooves (71, 72) and the first and second annular grooves. It flows to the sliding part of the compression mechanism (30) through (73, 74) and lubricates and cools the sliding part.
- the compression mechanism (30) includes an annular front head (31), an upper cylinder (32), a middle plate (33), a lower cylinder (34), and a rear head (lower end plate) (35). Yes. These annular members (31 to 35) are stacked in order from the upper side to the lower side, and are fastened by a plurality of bolts extending in the axial direction.
- the drive shaft (23) vertically penetrates the annular member (31 to 35).
- the upper cylinder (32) and the lower cylinder (34) are each composed of a thick cylindrical member.
- the front head (31), the middle plate (33), and the rear head (35) are constituted by thick disk members, each having a hole through which the drive shaft (23) is inserted. ing.
- Inner peripheral edge portions that form holes in the front head (31) and the rear head (35) have sliding bearing portions (31a, 35a) that rotatably support the main shaft portion (24) of the drive shaft (23), respectively. It is composed.
- the front head (31) constitutes the main bearing
- the rear head (35) constitutes the auxiliary bearing.
- the upper cylinder (32) has its upper end closed by the front head (31) while its lower end is closed by the middle plate (33), and the internal closed space constitutes the upper cylinder chamber (C1).
- the upper cylinder chamber (C1) accommodates an upper piston (40) slidably fitted on the upper eccentric portion (25) of the drive shaft (23).
- an upper blade (41) extending radially outward from the outer peripheral surface is integrally formed on the outer peripheral surface of the upper piston (40).
- the upper cylinder chamber (C1) is partitioned by an upper blade (41) into a low pressure chamber (C11) communicating with the first suction pipe (15a) and a high pressure chamber (C12) in which an upper discharge port (46) described later opens. ing.
- FIG. 2 is a cross-sectional view of the compression mechanism (30) in the vicinity of the upper cylinder chamber (C1), but the cross-sectional configuration in the vicinity of the lower cylinder chamber (C2) is also a cross-section in the vicinity of the upper cylinder chamber (C1). Since it is almost the same as the configuration of the surface, the reference numerals of the constituent members in the lower cylinder chamber (C2) are shown in parentheses and are not shown.
- the lower cylinder (34) is closed at the upper end by the middle plate (33) and closed at the lower end by the rear head (35).
- the lower cylinder chamber (C2) accommodates a lower piston (50) slidably fitted on the lower eccentric portion (26) of the drive shaft (23).
- a lower blade (51) extending radially outward from the outer peripheral surface is integrally formed on the outer peripheral surface of the lower piston (50).
- the lower cylinder chamber (C2) includes a low pressure chamber (C21) communicated with the second suction pipe (15b) by a lower blade (51), and a high pressure chamber (C22) in which a lower discharge port (56) described later opens. It is divided into.
- the upper cylinder (32) has a circular groove formed in a plan view.
- the circular groove is formed in a bush groove (42) that accommodates the pair of bushes (43, 43).
- a pair of bushes (43, 43) formed in a half-moon shape in plan view are fitted in a state of sandwiching the upper blade (41).
- the lower cylinder (34) is also formed with a circular groove in plan view.
- the circular groove is formed in a bush groove (52) that accommodates a pair of bushes (53, 53).
- a pair of bushes (53, 53) formed in a half-moon shape in plan view is fitted in a state of sandwiching the lower blade (51).
- the upper cylinder (32) is formed with a suction passage (44) that penetrates between the inner peripheral surface and the outer peripheral surface in the radial direction.
- the end of the first suction pipe (15a) is inserted into the suction through passage (44) (see FIG. 1).
- the lower cylinder (34) is formed with a suction through passage (54) penetrating radially between the inner peripheral surface and the outer peripheral surface.
- the end of the second suction pipe (15b) is inserted into the suction through path (54).
- a concave portion that opens upward is formed on the upper surface of the front head (31), and the concave portion is covered with an inner cover (36).
- the upper surface of the inner cover (36) is covered with the outer cover (37).
- An inner discharge space (81) is formed between the upper surface of the front head (31) in which the concave portion is formed and the inner cover (36), and between the inner cover (36) and the outer cover (37). Is formed with an outer discharge space (82).
- the front head (31) is formed with an upper discharge port (46) penetrating in the vertical direction and communicating the inner discharge space (81) with the high pressure chamber (C12) of the upper cylinder chamber (C1).
- a discharge valve (47) for opening and closing the upper discharge port (46) is attached to the front head (31). As the discharge valve (47) opens and closes, the upper discharge port (46) intermittently communicates with a high pressure chamber (C12) formed in the upper cylinder (32).
- the inner cover (36) has a through-hole (not shown) communicating the inner discharge space (81) and the outer discharge space (82), and the outer cover (37) has an outer discharge space (82). ) And a through hole (not shown) that communicates with the internal space of the casing (11).
- a concave portion that extends in the circumferential direction and opens downward is formed on the lower surface of the rear head (35).
- the concave portion is covered with a closing plate (38), and a closed space is formed inside.
- the closed space constitutes a lower discharge space (83).
- the lower discharge space (83) is connected to the rear head (35), the lower cylinder (34), the middle plate (33), the upper cylinder (32), and a refrigerant through hole (84) that passes through the front head (31). And communicates with an inner discharge space (81) formed between the front head (31) and the inner cover (36).
- the rear head (35) is formed with a lower discharge port (56) penetrating in the vertical direction to communicate the lower discharge space (83) and the high pressure chamber (C22) in the lower cylinder chamber (C2). Yes.
- a discharge valve (57) for opening and closing the lower discharge port (56) is attached to the rear head (35). As the discharge valve (57) opens and closes, the lower discharge port (56) intermittently communicates with a high pressure chamber (C22) formed in the lower cylinder (34).
- the inner peripheral edge portion forming the hole portion of the rear head (35) is a sliding bearing portion (35a) that rotatably supports the lower end portion of the main shaft portion (24) of the drive shaft (23). It is configured.
- the rear head (35) is formed with an annular groove (61) in plan view at the upper part of the central portion of the upper end surface (35b).
- the elastic bearing (62) is configured to elastically support the shaft (23). That is, when a load is applied to the lower end portion of the main shaft portion (24) of the drive shaft (23) in the direction of the groove portion (61), the elastic bearing (62) bends and enters into the groove portion (61).
- the drive shaft (23) is elastically supported.
- a thrust bearing surface (26a) that is in sliding contact with the upper end surface (35b) of the rear head (35) is formed on the lower end surface of the lower eccentric portion (26).
- the thrust bearing surface (26a) is configured by an end surface of a protruding portion that protrudes downward so as to be positioned below other portions of the lower end surface of the lower eccentric portion (26).
- the thrust bearing surface (26a) of the lower eccentric portion (26) and the upper end surface (35b) of the rear head (35) slide the thrust bearing that supports the thrust load. Make up surface.
- the lower eccentric portion (26) is formed with a decompression groove (65) whose lower end opens in the thrust bearing surface (26a) and extends in the circumferential direction.
- the decompression groove (65) is formed so as to surround the main shaft portion (24) of the drive shaft (23).
- the decompression groove (65) is connected to the second annular groove (74) formed between the rear head (35) and the drive shaft (23). It is comprised so that it may communicate via.
- the pressure reducing groove (65) and the second annular groove (74) are configured such that the communicating portion (65a) serves as a throttle portion for reducing the pressure of the lubricating oil supplied from the second annular groove (74) to the pressure reducing groove (65).
- the lower end of the decompression groove (65) communicates with the upper end of the second annular groove (74), and the cross-sectional area of the communication portion (65a) is the cross-sectional area of the decompression groove (65) (decompression groove).
- the decompression groove (65) is formed at a position overlapping the elastic bearing (62) in plan view.
- the decompression groove (65) has an outer peripheral edge located on the outer peripheral side of the outer peripheral edge (inner peripheral edge of the groove (61)) of the elastic bearing (62) and an inner peripheral edge of the elastic bearing (62). It is formed so as to be located at the same position as the inner peripheral edge (the inner peripheral edge of the rear head (35)).
- the decompression groove (65) may be formed such that the inner peripheral edge is located slightly on the inner peripheral side of the inner peripheral edge of the elastic bearing (62) (the inner peripheral edge of the rear head (35)).
- the decompression groove (65) is formed so that the outer peripheral edge is located on the inner peripheral side with respect to the outer peripheral edge of the groove (61). That is, the decompression groove (65) is formed on the inner peripheral side with respect to the groove part (61), and has a smaller diameter than the groove part (61).
- the decompression groove (65) is formed such that the lower end of the second longitudinal groove (72) formed on the outer peripheral surface of the lower eccentric part (26) opens into the decompression groove (65).
- the lower end of the second vertical groove (72) opens to the decompression groove (65), but does not overlap with the portion of the thrust bearing surface (26a) other than the portion where the decompression groove (65) opens. Is formed.
- the refrigerant sucked from the suction pipes (15a, 15b) into the low pressure chambers (C11, C21) of the cylinder chambers (C1, C2) is supplied to the high pressure chambers (C12, C22) of the cylinder chambers (C1, C2).
- the liquid is discharged from the discharge ports (46, 56).
- the refrigerant discharged from the upper discharge port (46) flows into the inner discharge space (81).
- the refrigerant discharged from the lower discharge port (56) into the lower discharge space (83) flows into the inner discharge space (81) through the refrigerant through hole (84), and the inner discharge space (81 ) And the refrigerant discharged from the upper cylinder chamber (C1).
- the refrigerant discharged from the upper cylinder chamber (C1) and the lower cylinder chamber (C2) merged in the inner discharge space (81) flows into the outer discharge space (82) through a through hole formed in the inner cover (36). After that, it flows into the internal space of the casing (11) through the through hole formed in the outer cover (37), and eventually flows out from the discharge pipe (16) to the outside of the casing (11).
- a thrust bearing surface (26a) is formed on the lower end surface of the lower eccentric portion (26) so as to be in sliding contact with the upper end surface (35b) of the rear head (35). (26a) and the upper end surface (35b) of the rear head (35) constitute the sliding surface of the thrust bearing.
- the internal pressure of each cylinder chamber (C1, C2) acts on each eccentric part (25, 26) of the drive shaft (23) via each piston (40, 50). . Therefore, when the internal pressure of each cylinder chamber (C1, C2) is relatively high during high load operation, the drive shaft (23) may be greatly bent.
- the elastic bearing (62) is provided at the inner peripheral edge of the periphery of the hole through which the drive shaft (23) is inserted in the upper end surface (35b) of the rear head (35).
- An annular groove (61) to be formed is formed, and the drive shaft (23) is elastically supported by the elastic bearing (62).
- Lubricating oil that has flowed out of the second passage (70b) accumulates in the first annular groove (73).
- the lubricating oil accumulated in the first annular groove (73) is guided to the upper end of the front head (31) through a spiral groove (not shown) formed on the inner peripheral surface of the sliding bearing (31a) of the front head (31).
- the sliding surface between the sliding bearing portion (31a) of the front head (31) and the main shaft portion (24) of the drive shaft (23) is lubricated and cooled.
- the lubricating oil accumulated in the first annular groove (73) flows into the sliding surface between the upper end surface of the upper piston (40) and the lower end surface of the front head (31). Lubricate and cool.
- Lubricating oil that has flowed out of the third passage (70c) accumulates in the first vertical groove (71).
- the lubricating oil accumulated in the first vertical groove (71) flows into the sliding surface between the upper eccentric portion (25) of the drive shaft (23) and the sliding bearing portion of the upper piston (40), and the sliding Lubricate and cool between the surfaces.
- the lubricating oil accumulated in the first vertical groove (71) is a sliding surface between the upper end surface of the upper piston (40) and the lower end surface of the front head (31), and the lower end surface of the upper piston (40). And flows between the sliding surfaces between the upper end surface of the middle plate (33) and lubricates and cools the sliding surfaces.
- Lubricating oil that has flowed out of the fourth passage (70d) accumulates in the second vertical groove (72).
- the lubricating oil accumulated in the second vertical groove (72) flows into the sliding surface between the lower eccentric portion (26) of the drive shaft (23) and the sliding bearing portion of the lower piston (50), and Lubricate and cool between the sliding surfaces.
- the lubricating oil accumulated in the second vertical groove (72) is the sliding surface between the upper end surface of the lower piston (50) and the lower end surface of the middle plate (33), under the lower piston (50).
- Lubricating oil that has flowed out of the fifth passage (70e) accumulates in the second annular groove (74).
- the lubricating oil accumulated in the second annular groove (74) is the sliding surface between the sliding bearing portion (35a) of the rear head (35) and the main shaft portion (24) of the drive shaft (23), the lower piston (50 ) Between the lower end surface of the rear head (35) and the upper end surface of the rear head (35) and the thrust bearing surface (26a) of the lower end surface of the lower eccentric part (26) of the drive shaft (23) and the rear head (35). It flows between the sliding surfaces between the upper end surfaces (35b), that is, the sliding surfaces of the thrust bearing, and lubricates and cools between the sliding surfaces.
- the lubricating oil in the second annular groove (74) flows into the pressure reducing groove (65) through the communication portion (65a) and then flows between the sliding surfaces of the thrust bearing.
- the cross-sectional area of the communication portion (65a) is formed to be narrower than the cross-sectional area of the decompression groove (65). Therefore, the lubricating oil that has flowed into the decompression groove (65) through the communication portion (65a) is rapidly decompressed. As a result, the gas refrigerant dissolved in the lubricating oil is separated from the lubricating oil and foamed.
- the specific gravity of the lubricating oil is larger than that of the gas refrigerant, the centrifugal force received by the lubricating oil is larger than the centrifugal force received by the gas refrigerant. Therefore, when the gas refrigerant is separated from the lubricating oil in the decompression groove (65), the gas refrigerant accumulates in the upper part of the decompression groove (65), while the lubricant having a higher specific gravity than the gas refrigerant receives a large centrifugal force and depressurizes.
- the gas refrigerant is not separated and foamed from the lubricating oil subjected to the thrust load between the sliding surfaces of the thrust bearing, and the sliding surface of the thrust bearing is cooled by the lubricating oil after the gas refrigerant is separated. Will be.
- Embodiment 1- a part of the lubricating oil flowing through the oil supply passage (70) in the drive shaft (23) is supplied to the pressure reducing groove (65) opened in the thrust bearing surface (26a) to reduce the pressure. It was. As a result, the gas refrigerant dissolved in the lubricating oil is separated in the decompression groove (65), and only the lubricating oil that receives a centrifugal force larger than that of the gas refrigerant flows out of the decompression groove (65) to the outside in the radial direction. It can be supplied between the thrust bearing surface (26a) constituting the sliding surface and the upper end surface (35b) of the rear head (35). Therefore, since generation
- the second annular groove (74) that guides the lubricating oil in the oil supply passage (70) to the decompression groove (65) and the decompression groove (65) communicate with each other via the communication portion (65a).
- the communication portion (65a) is configured to be a throttle portion for reducing the pressure of the lubricating oil supplied from the second annular groove (74) to the pressure reducing groove (65). Therefore, with a simple configuration, the lubricating oil in which the gas refrigerant has melted in the decompression groove (65) can be rapidly depressurized, and the gas refrigerant can be reliably separated from the lubricating oil.
- each cylinder chamber (C1, C2) acts on each eccentric part (25, 26) of the drive shaft (23) via each piston (40, 50). . Therefore, when the internal pressure of each cylinder chamber (C1, C2) is relatively high during high load operation, the drive shaft (23) may be greatly bent.
- corner contact occurs in which the corner portion formed by the upper end surface and the inner peripheral surface of the rear head (35) is in sliding contact with the main shaft portion (24) of the drive shaft (23).
- the contact surface pressure increases, the sliding loss and wear at the sliding bearing portion (35a) of the rear head (35) increase, and the operating efficiency and reliability of the rotary compressor are reduced. End up.
- an elastic bearing (62) is formed at the inner peripheral edge in the periphery of the hole portion through which the drive shaft (23) is inserted in the upper end surface (35b) of the rear head (35).
- An annular groove (61) is formed, and the drive shaft (23) is elastically supported by the elastic bearing (62), thereby suppressing an increase in contact surface pressure due to angular contact.
- the elastic bearing (62) elastically supports the drive shaft (23) by bending, but when bent, a part of the upper end is caught on the thrust bearing surface (26a) of the lower eccentric part (26). The thrust bearing surface (26a) may be damaged.
- the decompression groove (65) is provided at a position overlapping the elastic bearing (62) in plan view.
- the elastic bearing (62) is formed at the inner peripheral edge of the rear head (35)
- the pressure reducing groove (65) is formed by providing the pressure reducing groove (65) at a position overlapping the elastic bearing (62) in plan view. It will be formed at the inner peripheral end of the thrust bearing surface (26a).
- the pressure reducing groove (65) When the pressure reducing groove (65) is thus formed at the inner peripheral end of the thrust bearing surface (26a), the lubricating oil flowing out from the pressure reducing groove (65) can be spread over the entire thrust bearing surface (26a). Therefore, the entire thrust bearing surface (26a) can be cooled by the lubricating oil.
- the decompression groove (65) is formed such that the outer peripheral edge is located on the inner peripheral side with respect to the outer peripheral edge of the groove (61). That is, the decompression groove (65) is formed to have a smaller diameter than the groove part (61) that forms the elastic bearing (62).
- the decompression groove (65) opened to the thrust bearing surface (26a) is increased, the area of the thrust bearing surface (26a) is reduced.
- the decompression groove (65) is formed to have a smaller diameter than the groove part (61) forming the elastic bearing (62). Therefore, the reduction in the area of the thrust bearing surface (26a) due to the formation of the decompression groove (65) opening in the thrust bearing surface (26a) can be suppressed to the minimum necessary.
- the second vertical groove (72) extending from the upper end to the lower end of the lower eccentric portion (26) is formed on the side surface of the lower eccentric portion (26).
- the lower end of the second vertical groove (72) is opened in the thrust bearing surface (26a)
- a corner portion is generated between the wall surface forming the second vertical groove (72) and the thrust bearing surface (26a).
- the thrust bearing surface (26a) slides with respect to the upper end surface (35b) of the rear head (35), the upper end surface (35b) of the rear head (35) may be scraped off.
- the decompression groove (65) is formed so that the lower end of the second longitudinal groove (72) formed on the side surface of the lower eccentric portion (26) opens in the decompression groove (65). It was decided. Therefore, it is possible to prevent the upper end surface (35b) of the rear head (35) that is in sliding contact with the thrust bearing surface (26a) from being cut by the corner portion formed at the lower end portion of the second vertical groove (72).
- Embodiment 2 of the Invention In the rotary compressor (10) of the second embodiment, the groove (61) forming the elastic bearing (62) of the first embodiment is omitted, and the decompression groove (65) and the second annular groove (74) are directly provided. However, it is formed so as to communicate indirectly through a gap (65b) between the thrust bearing surface (26a) and the upper end surface (35b) of the rear head (35).
- the decompression groove (65) is formed such that the inner peripheral edge is located on the outer peripheral side with respect to the inner peripheral edge of the thrust bearing surface (26a).
- the pressure reducing groove (65) and the second annular groove (74) do not directly communicate with each other, but the thrust bearing surface (26a ) And an upper end surface (35b) of the rear head (35), and is configured to communicate indirectly through a gap (65b).
- the gap (65b) between the two is slight. Therefore, the lubricating oil supplied from the second annular groove (74) to the decompression groove (65) is rapidly decompressed in the gap (65b) that connects the decompression groove (65) and the second annular groove (74). It will be.
- the pressure reducing groove (65) and the second annular groove (74) are such that the gap (65b) between the thrust bearing surface (26a) and the upper end surface (35b) of the rear head (35) communicate with each other. It is comprised so that it may become a throttle part which decompresses.
- Other configurations are the same as those of the first embodiment.
- the lubricating oil in the oil supply passage (70) that has flowed into the second annular groove (74) through the fifth passage (70e) is subjected to centrifugal force and is radially outward. It flows out, passes through the gap (65b) between the thrust bearing surface (26a) and the upper end surface (35b) of the rear head (35), and is supplied to the decompression groove (65).
- the gap (65b) connecting the second annular groove (74) and the decompression groove (65) decompresses the lubricating oil supplied from the second annular groove (74) to the decompression groove (65). It is comprised so that it may become an aperture part.
- the lubricating oil flowing into the decompression groove (65) through the gap (65b) between the thrust bearing surface (26a) and the upper end surface (35b) of the rear head (35) is rapidly decompressed.
- the gas refrigerant dissolved in the lubricating oil is separated from the lubricating oil and foamed.
- the specific gravity of the lubricating oil is larger than that of the gas refrigerant, the centrifugal force received by the lubricating oil is larger than the centrifugal force received by the gas refrigerant. Therefore, when the gas refrigerant is separated from the lubricating oil in the decompression groove (65), the gas refrigerant accumulates in the upper part of the decompression groove (65), while the lubricant having a higher specific gravity than the gas refrigerant receives a large centrifugal force and depressurizes. Between the sliding surface between the thrust bearing surface (26a) at the lower end surface of the lower eccentric part (26) and the upper end surface (35b) of the rear head (35), flowing out from the groove (65) in the radial direction Flow into.
- Embodiment 3 of the Invention The rotary compressor (10) of the third embodiment is obtained by changing the shape of the decompression groove (65) of the first embodiment.
- the decompression groove (65) is formed so that the axial length is shorter (the groove depth is shallower) than in the first embodiment.
- the outer peripheral edge is positioned on the outer peripheral side of the outer peripheral edge (inner peripheral edge of the groove (61)) of the elastic bearing (62), and the inner peripheral edge is the inner peripheral edge (rear head (35)) of the elastic bearing (62).
- the inner peripheral edge) is located at the same position.
- the portion of the decompression groove (65) facing the upper end surface of the elastic bearing (62) is formed in the communication portion (65a), and the decompression groove (65) is formed via the communication portion (65a). It communicates with the second annular groove (74).
- the decompression groove (65) is formed so that the groove depth is uniform between the communication portion (65a) and the non-communication portion radially outside the communication portion (65a).
- the non-communication portion of the decompression groove (65) is formed so as to face the groove portion (61) and forms a larger space than the communication portion (65a) integrally with the groove portion (61). Yes.
- the lubricating oil flowing from the second annular groove (74) into the pressure reducing groove (65) through the communication portion (65a) passes through the communication portion (65a) and flows into the non-communication portion. The pressure is suddenly reduced.
- the communication portion (65a) is configured to be a throttle portion that depressurizes the lubricating oil supplied from the second annular groove (74) to the pressure reducing groove (65).
- Other configurations are the same as those of the first embodiment.
- the lubricating oil in the oil supply passage (70) that has flowed out into the second annular groove (74) through the fifth passage (70e) is depressurized through the communication portion (65a). Supplied to the groove (65).
- the space formed by the non-communication portion of the decompression groove (65) and the groove portion (61) is formed in a larger space than the communication portion (65a) of the decompression groove (65).
- the communication part (65a) of the decompression groove (65) is formed in a space smaller than the space composed of the non-communication part of the decompression groove (65) and the groove part (61), and the second annular groove (74)
- the pressure reducing groove (65) so as to be a throttle portion for reducing the pressure of the lubricating oil. Therefore, when the lubricating oil that has flowed into the pressure reducing groove (65) through the communication portion (65a) flows into the non-communication portion from the communication portion (65a), the pressure is rapidly reduced. As a result, the gas refrigerant dissolved in the lubricating oil is separated from the lubricating oil and foamed.
- the specific gravity of the lubricating oil is larger than that of the gas refrigerant, the centrifugal force received by the lubricating oil is larger than the centrifugal force received by the gas refrigerant. Therefore, when the gas refrigerant is separated from the lubricating oil in the decompression groove (65), the gas refrigerant accumulates in the upper part of the decompression groove (65), while the lubricant having a higher specific gravity than the gas refrigerant receives a large centrifugal force and depressurizes. Between the sliding surface between the thrust bearing surface (26a) at the lower end surface of the lower eccentric part (26) and the upper end surface (35b) of the rear head (35), flowing out from the groove (65) in the radial direction Flow into.
- the rotary compressor (10) according to the fourth embodiment has a gas vent hole (10) that guides the gas refrigerant accumulated in the upper part of the decompression groove (65) to the oil supply passage (70) to the rotary compressor (10) according to the first embodiment. 66).
- the gas vent hole (66) is configured as a communication path that connects the upper portion of the decompression groove (65) and the oil supply path (70).
- the rotary compressor (10) is configured as a so-called two-cylinder compression mechanism in which the compression mechanism (30) has two cylinder chambers (C1, C2).
- the compression mechanism of the rotary compressor according to the present invention may be a so-called one-cylinder compression mechanism having only the lower cylinder chamber (C2).
- the lower cylinder (34) is closed at the upper end by the front head (31) and closed at the lower end by the rear head (35), and the lower cylinder chamber (C2) is constituted by the internal closed space. It may be done.
- the present invention is useful for rotary compressors.
- Rotating compressor 20 Electric motor (drive mechanism) 23 Drive shaft 26 Lower eccentric part (Eccentric part) 26a Thrust bearing surface 30 Compression mechanism 31 Front head (upper end plate) 34 Lower cylinder (cylinder) 35 Rear head (bottom plate) 35b Upper end surface 50 Lower piston (piston) 61 Groove portion 62 Elastic bearing 65 Depressurization groove 65a Communication portion 65b Clearance 66 Gas vent hole (communication passage) 70 Oil supply passage (oil passage) 72 Second vertical groove (side oil groove) 74 Second annular groove (oil groove)
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Abstract
Description
本発明の実施形態1に係る回転式圧縮機(10)は、例えば空気調和装置の冷媒回路に設けられ、蒸発器から吸入した冷媒を圧縮して放熱器へ吐出する。図1に示すように、回転式圧縮機(10)は、ケーシング(11)と電動機(20)と圧縮機構(30)とを備えている。
上記回転式圧縮機(10)では、上記電動機(20)が起動されて駆動軸(23)が回転に伴って、各偏心部(25,26)に外嵌された各ピストン(40,50)が各シリンダ室(C1,C2)内において偏心回転する。これにより、各ピストン(40,50)と各シリンダ室(C1,C2)の低圧室(C11,C21)と高圧室(C12,C22)との容積が周期的に変動し、該高圧室(C12,C22)において冷媒の吸入動作、圧縮動作及び吐出動作が連続的に行われる。
上記駆動軸(23)が回転すると、遠心ポンプ(27)によって油溜まり(17)の潤滑油が駆動軸(23)の内部の給油通路(70)に汲み上げられる。給油通路(70)に汲み上げられた潤滑油は、下方から上方に向かって流れた後、遠心力を受けて第2~第5通路(70b~70e)から駆動軸(23)の外周面に流出する。
上記実施形態1によれば、駆動軸(23)内の給油通路(70)を流れる潤滑油の一部を、スラスト軸受面(26a)において開口する減圧溝(65)に供給して減圧することとした。その結果、減圧溝(65)において潤滑油に溶け込んだガス冷媒が分離され、ガス冷媒よりも大きな遠心力を受ける潤滑油のみを減圧溝(65)から径方向の外側へ流出させてスラスト軸受の摺動面を構成するスラスト軸受面(26a)とリアヘッド(35)の上端面(35b)との間に供給することができる。よって、スラスト軸受の摺動面間におけるガス冷媒の発生を抑制することができるため、スラスト軸受の摺動面を潤滑油によって効果的に冷却することができ、焼き付きを抑制することができる。
実施形態2の回転式圧縮機(10)は、実施形態1の弾性軸受(62)を形成する溝部(61)を省略すると共に、減圧溝(65)と第2環状溝(74)とが直接的には連通せず、スラスト軸受面(26a)とリアヘッド(35)の上端面(35b)との間の隙間(65b)を介して間接的に連通するように形成したものである。
実施形態3の回転式圧縮機(10)は、実施形態1の減圧溝(65)の形状を変更したものである。
実施形態4の回転式圧縮機(10)は、実施形態1の回転式圧縮機(10)に、減圧溝(65)の上部に溜まったガス冷媒を給油通路(70)に導くガス抜き穴(66)を加えたものである。具体的には、図9に示すように、ガス抜き穴(66)は、減圧溝(65)の上部と給油通路(70)とを連通する連通路に構成されている。このようにガス抜き穴(66)を形成することにより、減圧溝(65)の上部に溜まったガス冷媒がガス抜き穴(66)を介して給油通路(70)に排出される。そのため、高回転数で長時間運転されるような場合であっても、ガス冷媒が分離された潤滑油のみをスラスト軸受の摺動面間に供給することができる。従って、スラスト軸受の摺動面となるスラスト軸受面(26a)とリアヘッド(35)の上端面(35b)とを確実に冷却することができる。
上記各実施形態では、回転式圧縮機(10)は、圧縮機構(30)が2つのシリンダ室(C1,C2)を有する所謂2気筒の圧縮機構に構成されていた。しかしながら、本発明に係る回転式圧縮機の圧縮機構は、下側シリンダ室(C2)のみを有する所謂1気筒の圧縮機構であってもよい。具体的には、下側シリンダ(34)は、上端がフロントヘッド(31)によって閉塞される一方、下端がリアヘッド(35)によって閉塞され、内部の閉空間によって下側シリンダ室(C2)が構成されるものであってもよい。このような1気筒の圧縮機構であってもリアヘッド(35)の上端面(35b)と摺接する下側偏心部(26)にスラスト軸受面(26a)に開口して周方向に延びる減圧溝(65)を形成することにより、上記各実施形態と同様の効果を奏することができる。
20 電動機(駆動機構)
23 駆動軸
26 下側偏心部(偏心部)
26a スラスト軸受面
30 圧縮機構
31 フロントヘッド(上端板)
34 下側シリンダ(シリンダ)
35 リアヘッド(下端板)
35b 上端面
50 下側ピストン(ピストン)
61 溝部
62 弾性軸受
65 減圧溝
65a 連通部分
65b 隙間
66 ガス抜き穴(連通路)
70 給油通路(油通路)
72 第2縦溝(側方給油溝)
74 第2環状溝(油溝)
Claims (7)
- 偏心部(26)が形成されて上下に延びる駆動軸(23)を有する駆動機構(20)と、
上記偏心部(26)の外周を覆う筒状のシリンダ(34)と、該シリンダ(34)内に配置されて上記偏心部(26)に外嵌されたピストン(50)と、上記シリンダ(34)の上端を閉塞する上端板(31)と、上記シリンダ(34)の下端を閉塞する下端板(35)とを有する圧縮機構(30)とを備え、
上記偏心部(26)の下端面に上記下端板(35)の上端面(35b)と摺接するスラスト軸受面(26a)が形成されると共に、上記駆動軸(23)内に潤滑油が流通する油通路(70)が形成された回転式圧縮機であって、
上記偏心部(26)には、上記スラスト軸受面(26a)に開口して周方向に延び、上記油通路(70)の潤滑油が供給されて該潤滑油を減圧する減圧溝(65)が形成されている
ことを特徴とする回転式圧縮機。 - 請求項1において、
上記下端板(35)と上記駆動軸(23)との間には、周方向に延びて上記油通路(70)の潤滑油が供給される油溝(74)が形成され、
上記減圧溝(65)は、上記油溝(74)に連通部分(65a)を介して連通し、該連通部分(65a)は上記油溝(74)から上記減圧溝(65)に供給される潤滑油を減圧する絞り部となるように構成されている
ことを特徴とする回転式圧縮機。 - 請求項1において、
上記下端板(35)と上記駆動軸(23)との間には、周方向に延びて上記油通路(70)の潤滑油が供給される油溝(74)が形成され、
上記減圧溝(65)と上記油溝(74)とは、上記スラスト軸受面(26a)と上記下端板(35)の上端面(35b)との間の隙間(65b)を介して連通すると共に該隙間(65b)が上記油溝(74)から上記減圧溝(65)に供給される潤滑油を減圧する絞り部となるように構成されている
ことを特徴とする回転式圧縮機。 - 請求項1又は2において、
上記下端板(35)の上端面(35b)における上記駆動軸(23)が挿通される孔部の周辺部には、周方向に延びて内周縁部に弾性軸受(62)を形成する溝部(61)が形成され、
上記減圧溝(65)は、平面視において上記弾性軸受(62)と重なる位置に形成されている
ことを特徴とする回転式圧縮機。 - 請求項4において、
上記減圧溝(65)は、外周縁が上記溝部(61)の外周縁よりも内周側に位置するように形成されている
ことを特徴とする回転式圧縮機。 - 請求項1乃至5のいずれか1つにおいて、
上記偏心部(26)には、上記減圧溝(65)の上部と上記油通路(70)とを連通する連通路(66)が形成されている
ことを特徴とする回転式圧縮機。 - 請求項1乃至6のいずれか1つにおいて、
上記偏心部(26)の側面には、上記油通路(70)から上記偏心部(26)の上方に供給された潤滑油を上記偏心部(26)の下方に導く側方給油溝(72)が形成され、
上記減圧溝(65)は、上記側方給油溝(72)の下端が上記減圧溝(65)に開口するように形成されている
ことを特徴とする回転式圧縮機。
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CN201280047307.6A CN103827499B (zh) | 2011-09-28 | 2012-09-24 | 压缩机 |
BR112014006692-2A BR112014006692B1 (pt) | 2011-09-28 | 2012-09-24 | Compressor giratório |
US14/348,047 US9115715B2 (en) | 2011-09-28 | 2012-09-24 | Compressor with pressure reduction groove formed in eccentric part |
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JP6758867B2 (ja) * | 2016-03-04 | 2020-09-23 | 三菱重工サーマルシステムズ株式会社 | 流体機械 |
CN105952649B (zh) * | 2016-06-17 | 2018-03-23 | 广东美芝制冷设备有限公司 | 压缩机 |
JP2018123691A (ja) * | 2017-01-30 | 2018-08-09 | ダイキン工業株式会社 | 圧縮機 |
JP6768553B2 (ja) * | 2017-02-21 | 2020-10-14 | 東芝キヤリア株式会社 | 回転式圧縮機及び冷凍サイクル装置 |
FR3102792B1 (fr) * | 2019-11-05 | 2021-10-29 | Danfoss Commercial Compressors | Compresseur à spirales comportant un maneton ayant un évidement supérieur |
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JPS58120897U (ja) * | 1982-02-12 | 1983-08-17 | ダイキン工業株式会社 | 回転式圧縮機 |
JPS6049287U (ja) * | 1983-09-13 | 1985-04-06 | ダイキン工業株式会社 | ロ−タリ−圧縮機 |
JPS60145290U (ja) * | 1984-03-07 | 1985-09-26 | 三菱電機株式会社 | 回転式圧縮機 |
JPS6125586U (ja) * | 1984-07-20 | 1986-02-15 | 三洋電機株式会社 | 密閉型圧縮機の給油装置 |
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US9115715B2 (en) | 2015-08-25 |
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CN103827499B (zh) | 2015-07-08 |
US20140234147A1 (en) | 2014-08-21 |
JP5370450B2 (ja) | 2013-12-18 |
JP2013072365A (ja) | 2013-04-22 |
BR112014006692B1 (pt) | 2021-09-08 |
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