WO2005108793A1 - 回転式圧縮機 - Google Patents
回転式圧縮機 Download PDFInfo
- Publication number
- WO2005108793A1 WO2005108793A1 PCT/JP2005/008633 JP2005008633W WO2005108793A1 WO 2005108793 A1 WO2005108793 A1 WO 2005108793A1 JP 2005008633 W JP2005008633 W JP 2005008633W WO 2005108793 A1 WO2005108793 A1 WO 2005108793A1
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- WO
- WIPO (PCT)
- Prior art keywords
- compression chamber
- cylinder
- stage compression
- chamber
- pressure
- Prior art date
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Classifications
-
- 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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/04—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal-axis type
- F04C18/045—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal-axis type having a C-shaped piston
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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
-
- 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
-
- 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
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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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
-
- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/05—Speed
- F04C2270/052—Speed angular
-
- 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
Definitions
- the present invention relates to a rotary compressor, and more particularly, to a rotary compressor that compresses a fluid in two stages.
- some rotary compressors include a first rotary compression element and a second rotary compression element to compress refrigerant in two stages. is there.
- the first rotary compression element and the second rotary compression element each have a rotor and a blade housed in a cylinder, and the rotor rotates in the cylinder to compress the refrigerant.
- the refrigerant is compressed by the first rotary compression element and then compressed by the second rotary compression element. That is, the refrigerant is two-stage compressed by the first rotary compression element and the second rotary compression element.
- efficient operation is performed.
- Patent Document 1 JP 2003-293971 A
- the first rotary compression element and the second rotary compression element are vertically arranged on different planes.
- the size was large and the number of parts was large. That is, since the first rotary compression element and the second rotary compression element are separately arranged vertically, there is a problem that the overall height is increased.
- the first rotary compression element and the second rotary compression element are completely separate from each other, and there is no common part. Therefore, there is a problem that the number of parts in the entire apparatus is large.
- the present invention has been made in view of the above points, and has as its object to reduce the number of parts and to downsize the overall shape.
- the first invention is a cylinder (21) having an annular cylinder chamber (50), An annular piston (22) which is housed in a cylinder chamber (50) eccentrically with respect to the cylinder (21), and partitions the cylinder chamber (50) into an outer compression chamber (51) and an inner compression chamber (52). And a blade (23) arranged in the cylinder chamber (50) to partition each compression chamber (51, 52) into a high-pressure side and a low-pressure side.
- the cylinder (21) and the piston (22) Has a rotation mechanism (20) for relatively rotating and compressing the fluid.
- One of the two compression chambers (51, 52) is configured as a low-stage compression chamber (51) for compressing the low-pressure fluid into an intermediate-pressure fluid.
- the other of the two working chambers (52, 51) is configured as a high-stage compression chamber (52) that compresses the intermediate-pressure fluid compressed in the low-stage compression chamber (51) into a high-pressure fluid.
- the outer compression chamber (51) is formed as a low-stage compression chamber (51), while the inner compression chamber (52) is formed as a high-stage compression chamber. Composed of rooms (52)! ,
- the capacity of the high-stage compression chamber (52) is necessarily smaller than the capacity of the low-stage compression chamber (51).
- the maximum compression torques of the low-stage compression chamber (51) and the high-stage compression chamber (52) become substantially equal, and vibration is suppressed.
- a third invention according to the first invention, further comprising a casing (10) in which the rotation mechanism (20) is housed, and a low-stage compression chamber ( An intermediate pressure space (4b) into which the intermediate pressure fluid compressed in 51) is introduced is formed.
- the casing (10) is connected to a gas injection pipe (lc) for performing gas injection into the intermediate pressure space (4b).
- the intermediate pressure fluid is supplied with the gas refrigerant from the intermediate cooler through the gas injection pipe (lc) and cooled. Is done.
- the driving mechanism for driving the rotation mechanism (20) is provided.
- the rotation speed of the drive mechanism (30) is variably controlled.
- the capacities of the low-stage compression chamber (51) and the high-stage compression chamber (52) are adjusted by controlling the rotation speed of the drive mechanism (30).
- a casing (10) in which the rotation mechanism (20) is housed. Further, inside the casing (10), an intermediate pressure space (4b) into which the intermediate pressure fluid compressed in the low-stage compression chamber (51) is introduced, and an intermediate pressure space (4b). A high-pressure space (4a) is formed in which the fluid is compressed in the high-stage compression chamber (52) and the high-pressure fluid discharged from the high-stage compression chamber (52) is introduced.
- the intermediate-pressure fluid compressed in the low-stage compression chamber (51) flows into the intermediate-pressure space (4b), and the intermediate-pressure fluid in the intermediate-pressure space (4b) is compressed by the high-stage compression. It flows into the chamber (52) and is further compressed into a high-pressure fluid. After that, the high-pressure fluid discharged from the high-stage compression chamber (52) flows into the high-pressure space (4a).
- the intermediate pressure space (4b) is formed below the high pressure space (4a), while the casing (10) is formed from the high pressure space (4a). With oil return passage (80) communicating with intermediate pressure space (4b)! / Puru.
- the lubricating oil in the high-pressure space (4a) of the casing (10), the lubricating oil is separated from the fluid, and the separated lubricating oil passes through the oil return passage (80) and passes through the intermediate pressure space (4b).
- the drive mechanism for driving the rotation mechanism (20) is provided.
- the drive mechanism (30) includes a stator (32), a rotor (31), and a drive shaft (33) connected to the rotor (31).
- the drive shaft (33) includes an eccentric portion (35) having an eccentric rotation center force, and the eccentric portion (35) is connected to the rotating mechanism (20).
- both axial portions of the eccentric portion (35) are held by the casing (10) via bearing members (18, 19).
- both axial portions of the eccentric portion (35) of the drive shaft (33) are held by the casing (10) by the bearing members (18, 19), and the sliding portion has one end. Is suppressed.
- the piston (22) is formed in a C-shape having a divided portion in which a part of a ring is divided, and the blade (23) is The cylinder chamber (50) extends from the inner peripheral wall surface to the outer peripheral wall surface, and is provided through a dividing portion of the piston (22).
- the dividing part of the piston (22) has the piston (22) and the blade (23).
- a swinging bush (27) in surface contact is provided so that the blade (23) can freely advance and retreat, and the blade (23) can freely swing relative to the piston (22).
- the blade (23) moves forward and backward between the swing bushes (27), and the blade (23) and the swing bush (27) are physically formed.
- the piston (22) performs a rotating operation. Thereby, the cylinder (21) and the piston (22) rotate while swinging relatively, and the rotating mechanism (20) performs a predetermined compression operation.
- the two compression chambers (51, 52) are formed on the outside and inside of the piston (22), the size of the entire apparatus can be reduced.
- the low-stage compression chamber (51) and the high-stage compression chamber (52) are adjacent to each other on the same plane, they can also serve as constituent members, thereby reducing the number of parts. be able to.
- the low-stage compression chamber (51) is formed outside and the high-stage compression chamber (52) is formed inside, so that the high-stage compression chamber (52) is formed. Is necessarily smaller than the capacity of the low-stage compression chamber (51). As a result, the maximum compression torques of the low-stage compression chamber (51) and the high-stage compression chamber (52) become substantially equal, vibration can be reduced, and noise can be reduced.
- the gas injection pipe (lc) for performing gas injection is provided in the intermediate pressure space (4b), external piping can be omitted. As a result, pressure loss is reduced, and a high efficiency cycle can be realized.
- the intermediate pressure space (4b) is formed inside the casing (10), the pressure resistance of the casing (10) can be reduced, and the pressure resistance design can be facilitated.
- the rotation of the drive mechanism (30) is controlled, so that the low-stage compression chamber is controlled.
- the flow rate between the (51) and the high-stage compression chamber (52) can be adjusted, so that the high performance of the two-stage compression can be energized and low cost such as power consumption can be achieved.
- the inside of the casing (10) is provided with the intermediate pressure space (4b) and the high pressure space.
- intermediate pressure space (4b) can be formed adjacent to the partition (4a) and the rotation mechanism (20), suction overheating can be reduced and efficiency can be improved.
- the oil return passage (80) since the oil return passage (80) is provided, the lubricating oil can be reliably returned to the bottom of the casing (10), and poor lubrication is prevented. be able to. Further, since the oil is separated in the high-pressure space (4a), it is possible to suppress the lubricating oil from being discharged together with the refrigerant, and to suppress so-called oil rising.
- the drive shaft (33) has the eccentric portion (35) in which both axial portions are held by the casing (10) via the bearing members (18, 19). Therefore, it is possible to suppress one-sided contact of the sliding portion, and to improve reliability.
- the swing bush (27) is provided as a connecting member for connecting the piston (22) and the blade (23), and the swing bush (27) is connected to the piston (22).
- the blades (23) are substantially in surface contact with each other, so that the pistons (22) and the blades (23) are worn out during operation and the contact parts are seized. Can be prevented.
- the swing bush (27) is provided so that the swing bush (27) is in surface contact with the piston (22) and the blade (23), the sealing property of the contact portion is improved. Is also excellent. Therefore, it is possible to reliably prevent the leakage of the refrigerant in the low-stage compression chamber (51) and the high-stage compression chamber (52), and to prevent a decrease in compression efficiency.
- the blade (23) is provided integrally with the cylinder (21), and the cylinder (21) is provided at both ends thereof.
- FIG. 1 is a longitudinal sectional view of a compressor according to Embodiment 1 of the present invention.
- FIG. 2 is a transverse sectional view showing a compression mechanism according to the first embodiment.
- FIG. 3 is a cross-sectional view showing the operation of the compression mechanism of the first embodiment.
- FIG. 4 is a circuit diagram showing a refrigerant circuit having the compressor of the first embodiment.
- FIG. 5 is a circuit diagram showing a modification of the refrigerant circuit of the first embodiment.
- FIG. 6 is a longitudinal sectional view of a compressor according to a second embodiment.
- FIG. 7 is a longitudinal sectional view of a compressor according to a third embodiment.
- FIG. 8 is a longitudinal sectional view of a compressor according to a fourth embodiment.
- FIG. 9 is a longitudinal sectional view of a compressor according to a fifth embodiment.
- a rotary compressor (1) of the present invention is applied to a refrigerant circuit (100) of a vapor compression refrigeration cycle.
- the above rotary compressor (1) includes a low-stage compression chamber (51) and a high-stage compression chamber (52), and is configured to compress the refrigerant in two stages.
- the refrigerant circuit (100) is configured in a two-stage compression one-stage expansion cycle using, for example, diacid carbon (C02) or the like as a refrigerant.
- a compressor (1), a condenser (101), a receiver (102), an intercooler (103), a main expansion valve (104), and an evaporator (105) are sequentially arranged by refrigerant piping.
- the intercooler (103) includes a cooling heat exchanger (106), and is connected to the low-stage compression chamber (51) and the high-stage compression chamber (52). Further, the intercooler (103) is connected to a branch pipe (107) for branching a part of the liquid refrigerant from the receiver (102), and the branch pipe (107) is provided with a branch expansion valve (108). Have been killed.
- the high-pressure refrigerant discharged from the high-stage compression chamber (52) of the compressor (1) condenses in the condenser (101), and then flows to the receiver (102).
- the liquid refrigerant of the receiver (102) expands at the main expansion valve (104) via the cooling heat exchanger (106), evaporates at the evaporator (105), and evaporates at the low-stage compression chamber (1) of the compressor (1). 51).
- the intermediate-pressure refrigerant compressed in the low-stage-side compression chamber (51) flows into the intercooler (103), and a part of the liquid refrigerant from the receiver (102) is supplied to the branch expansion valve (108). Inflates and flows in.
- the intermediate cooler (103) the intermediate-pressure refrigerant of the low-stage compression chamber (51) is cooled, and the liquid refrigerant flowing through the cooling heat exchanger (106) is cooled.
- the intermediate-pressure refrigerant cooled by the intermediate cooler (103) returns to the high-stage compression chamber (52) and is compressed into a high-pressure refrigerant. This circulation is repeated, and the indoor air is cooled, for example, by the evaporator (105).
- the rotary compressor (1) has a casing (10) in which a compression mechanism (20) and an electric motor (30) are housed, and is configured as a hermetic type.
- the casing (10) includes a cylindrical body (11), an upper end plate (12) fixed to the upper end of the body (11), and a lower end of the body (11). It is composed of a fixed lower end plate (13).
- the body (11) is provided with a suction pipe (14), an inflow pipe (la), and an outflow pipe (lb) penetrating the body (11).
- the suction pipe (14) is connected to an evaporator (105), and the inlet pipe (la) and the outlet pipe (lb) are connected to an intercooler (103).
- the upper end plate (12) is provided with a discharge pipe (15) penetrating the end plate (12).
- the above discharge pipe (15 ) Is connected to the condenser (101).
- the electric motor (30) includes a stator (31) and a rotor (32), and constitutes a drive mechanism.
- the stator (31) is disposed below the compression mechanism (20), and has a body (
- a drive shaft (33) is connected to the rotor (32), and the drive shaft (33) is configured to rotate together with the rotor (32).
- the drive shaft (33) has an oil supply passage (not shown) extending in the axial direction inside the drive shaft (33).
- An oil supply pump (34) is provided at the lower end of the drive shaft (33).
- the oil supply passage extends upward from the oil supply pump (34).
- the oil supply passage is provided with a lubricating oil stored in the bottom of the casing (10) by a compression pump (34).
- the drive shaft (33) has an eccentric part (35) formed at the upper part.
- the eccentric part (35) is formed at the upper part.
- the eccentric portion (35) is formed to have a larger diameter than the upper and lower portions and is eccentric by a predetermined amount from the axis of the drive shaft (33).
- the compression mechanism (20) constitutes a rotation mechanism, and is configured between the upper housing (16) fixed to the casing (10) and the lower housing (17).
- the compression mechanism (20) includes a cylinder (21) having an annular cylinder chamber (50), and a cylinder chamber (50) arranged in the cylinder chamber (50) to connect the cylinder chamber (50) to the low-stage compression chamber (51). ) And a high-stage compression chamber (52), and a low-stage compression chamber (51) and a high-stage compression chamber (52) are connected to a high-pressure side as shown in FIG. And a blade (23) for partitioning into a low pressure side.
- the piston (22) is configured to make an eccentric rotation relative to the cylinder (21) in the cylinder chamber (50). That is, the piston (22) and the cylinder (21) relatively rotate eccentrically.
- a cylinder (21) having a cylinder chamber (50) constitutes a movable-side cooperating member
- a piston (22) disposed in the cylinder chamber (50) is a fixed-side cooperating member. Is composed.
- the cylinder (21) includes an outer cylinder (24) and an inner cylinder (25).
- the outer cylinder (24) and the inner cylinder (25) are integrated by connecting their lower ends with a head plate (26).
- the inner cylinder (25) is slidably fitted in the eccentric part (35) of the drive shaft (33). That is, the drive shaft (33) moves the cylinder chamber (50) upward and downward. Penetrates in the direction.
- the piston (22) is formed integrally with the upper housing (16).
- the upper housing (16) and the lower housing (17) are formed with bearing portions (18, 19) as bearing members for supporting the drive shaft (33), respectively.
- the drive shaft (33) penetrates the cylinder chamber (50) in the up-down direction, and the eccentric portion (35) has two bearing portions in the axial direction.
- the through shaft structure is held by the casing (10) via (18, 19).
- the compression mechanism (20) includes an oscillating bush (27) for movably connecting the piston (22) and the blade (23) to each other.
- the piston (22) is formed in a C-shape in which a part of a ring is cut off.
- the blade (23) extends on the radial line of the cylinder chamber (50) from the inner peripheral wall surface to the outer peripheral wall surface of the cylinder chamber (50), passing through the divided portion of the piston (22). And fixed to the outer cylinder (24) and the inner cylinder (25).
- the rocking bush (27) forms a connecting member for connecting the piston (22) and the blade (23) at the dividing portion of the piston (22).
- the inner peripheral surface of the outer cylinder (24) and the outer peripheral surface of the inner cylinder (25) are cylindrical surfaces disposed on the same center, and one cylinder chamber (50) is formed therebetween. ing.
- the outer circumference of the piston (22) is smaller than the inner circumference of the outer cylinder (24), and the inner circumference is larger than the outer circumference of the inner cylinder (25).
- a low-stage compression chamber (51) as a working chamber is formed between the outer peripheral surface of the piston (22) and the inner peripheral surface of the outer cylinder (24), and the inner peripheral surface of the piston (22) is formed.
- a high-stage compression chamber (52), which is a working chamber, is formed between the inner cylinder (25) and the outer peripheral surface of the inner cylinder (25).
- the piston (22) and the cylinder (21) are in a state where the outer peripheral surface of the piston (22) and the inner peripheral surface of the outer cylinder (24) are substantially in contact at one point (strictly speaking, a gap on the order of microns).
- the inner peripheral surface of the piston (22) and the outer peripheral surface of the inner cylinder (25) are 1 They are practically in contact with each other.
- the swing bush (27) includes a discharge-side bush (2a) positioned on the discharge side with respect to the blade (23) and a suction-side bush (2b) positioned on the suction side with respect to the blade (23). ) And consists of Let's do it.
- the discharge-side bush (2a) and the suction-side bush (2b) are formed in the same shape with a substantially semicircular cross section, and are arranged so that the flat surfaces face each other.
- the space between the facing surfaces of the discharge-side bush (2a) and the suction-side bush (2b) forms a blade groove (28).
- the blade (23) is inserted into the blade groove (28), the flat surface of the swinging bush (27) is substantially in surface contact with the blade (23), and the arc-shaped outer peripheral surface is formed by the piston (22). ) Is in substantial surface contact.
- the swinging bush (27) is configured such that the blade (23) advances and retreats in the blade groove (28) in the plane direction with the blade (23) sandwiched between the blade grooves (28). At the same time, the swing bush (27) is configured to swing integrally with the blade (23) with respect to the piston (22).
- the swinging bush (27) can relatively swing the blade (23) and the piston (22) around the center point of the swinging bush (27) as the swing center, and (23) is configured to be able to advance and retreat in the surface direction of the blade (23) with respect to the piston (22).
- the force described in the example in which the discharge-side bush (2a) and the suction-side bush (2b) are separated from each other is such that the two bushes (2a, 2b) are partially connected. It may be an integral structure.
- the volume of the low-stage compression chamber (51) decreases in the order of FIGS. 3 (C), (D), (A) and (B) outside the piston (22).
- the volume of the high-stage compression chamber (52) decreases in the order of 03 (A), (B), (C), and (D) inside the piston (22).
- the upper housing (16) is provided with an upper cover plate (40).
- the upper part of the upper cover plate (40) is formed in the high pressure space (4a), and the lower part of the lower housing (17) is formed in the intermediate pressure space (4b).
- One end of a discharge pipe (15) is open in the high-pressure space (4a), and in the intermediate-pressure space (4b), One end of the outflow tube (lb) is open.
- An intermediate pressure chamber is provided between the upper housing (16) and the upper cover plate (40).
- the pocket (4f) is connected to the suction pipe (14) to form a low-pressure atmosphere of suction pressure. ing.
- the outer cylinder (24) is formed with a first suction port (43) penetrating in the radial direction, and the first suction port (42) is formed on the right side of the blade (23) in FIG. Have been.
- the first suction port (42) of the outer cylinder (24) communicates the low-stage compression chamber (51) with the pocket (4f), and communicates the low-stage compression chamber (51) with the suction pipe (14). Let me.
- the other end of the intermediate pressure passage (4e) is formed in the second suction port (42).
- the second suction port (42) is formed on the right side of the blade (23), opens to the high-stage compression chamber (52), and connects the high-stage compression chamber (52) with the intermediate pressure space (4b). Communicate.
- a first discharge port (44) and a second discharge port (45) are formed in the upper housing (16) in the axial direction.
- One end of the first discharge port (44) faces the high pressure side of the low-stage compression chamber (51), and the other end communicates with the intermediate pressure chamber (4c).
- One end of the second discharge port (44) faces the high-pressure side of the high-stage compression chamber (52), and the other end communicates with the high-pressure chamber (4d).
- An outer end of the first discharge port (44) and the second discharge port (44) is provided with a discharge valve (46) which is a reed valve for opening and closing the respective discharge ports (44, 45). .
- the intermediate pressure chamber (4c) and the intermediate pressure space (4b) communicate with each other by a communication passage (4g) formed in the upper housing (16) and the lower housing (17).
- the high-pressure chamber (4d) communicates with the high-pressure space (4a) through a high-pressure passage formed in the upper cover plate (40).
- the lower housing (17) is provided with a seal ring (6a).
- the seal ring (6a) is loaded in the annular groove of the lower housing (17) and is pressed against the lower surface of the end plate (26) of the cylinder (21). Furthermore, the contact surface between the cylinder (21) and the lower housing (17) Intermediate pressure lubricating oil is introduced into the radially inner part of the seal ring (6a)!
- the seal ring (6a) forms a compliance mechanism (60) for adjusting the axial position of the cylinder (21), and the piston (22), the cylinder (21), and the upper housing (16) The axial gap between them is reduced.
- the motor (30) is configured such that the rotation speed is controlled by a controller (70) having a control circuit such as an inverter! RU
- one low-stage compression chamber (51) is formed outside the piston (22). In this state, the capacity of the low-stage compression chamber (51) is almost maximum.
- This state force also causes the drive shaft (33) to rotate clockwise and changes to the state shown in FIGS. 3 (D), 3 (A), and 3 (B), and the low-stage compression chamber (51) As a result, the volume is reduced and the refrigerant is compressed.
- the pressure in the low-stage compression chamber (51) reaches a predetermined intermediate pressure and the differential pressure with the intermediate-pressure chamber (4c) reaches a set value, the medium is discharged by the intermediate-pressure refrigerant in the low-stage compression chamber (51).
- the valve (46) is opened, the intermediate-pressure refrigerant is discharged into the intermediate-pressure chamber (4c), and flows out of the intermediate-pressure space (4b) into the outlet pipe (lb).
- the discharge valve ( 46) is opened and the high-pressure refrigerant is discharged into the high-pressure chamber (4d) and flows out of the high-pressure space (4a) to the discharge pipe (15).
- the refrigerant circuit (100) After the high-pressure refrigerant discharged from the high-stage compression chamber (52) of the compressor (1) is condensed in the condenser (101), ).
- the liquid refrigerant of the receiver (102) expands at the main expansion valve (104) via the cooling heat exchanger (106), evaporates at the evaporator (105), and evaporates at the low-stage compression chamber (1) of the compressor (1). 51).
- the intermediate-pressure refrigerant compressed in the low-stage-side compression chamber (51) flows into the intercooler (103), and a part of the liquid refrigerant from the receiver (102) is supplied to the branch expansion valve (108). Inflates and flows in.
- the intermediate cooler (103) the intermediate-pressure refrigerant of the low-stage compression chamber (51) is cooled, and the liquid refrigerant flowing through the cooling heat exchanger (106) is cooled.
- the intermediate-pressure refrigerant cooled by the intermediate cooler (103) returns to the high-stage compression chamber (52) and is compressed into a high-pressure refrigerant. This circulation is repeated, and the indoor air is cooled, for example, by the evaporator (105).
- the low-stage compression chamber (51) and the high-stage compression chamber (52) are formed outside and inside the piston (22), the overall device The size can be reduced.
- the low-stage compression chamber (51) and the high-stage compression chamber (52) are adjacent to each other on the same plane, they can also serve as constituent members, thus reducing the number of parts. Can be achieved.
- the capacity of the high-stage compression chamber (52) is reduced. Inevitably smaller than the capacity of the room (51) Become. As a result, the maximum compression torques of the low-stage compression chamber (51) and the high-stage compression chamber (52) become substantially equal, vibration can be reduced, and noise can be reduced.
- the upper cover plate (40) is provided so as to partition the high-pressure space (4a).
- the inside of the casing (10) is partitioned into an intermediate pressure space (4b) and a high pressure space (4a), and an intermediate pressure space (4b) can be formed adjacent to the compression mechanism (20). Therefore, suction overheating can be reduced, and efficiency can be improved.
- the withstand voltage of (10) can be reduced, and the withstand voltage design can be facilitated.
- an oscillating bush (27) is provided as a connecting member for connecting the piston (22) and the blade (23), and the oscillating bush (27) is substantially connected to the piston (22) and the blade (23). Since it is configured so as to make surface contact, it is possible to prevent the piston (22) and the blade (23) from being worn out during operation, and to prevent seizure of the contact portion.
- the swing bush (27) is provided so that the swing bush (27) is in surface contact with the piston (22) and the blade (23), the sealing performance of the contact portion is improved. Is also excellent. Therefore, it is possible to reliably prevent the leakage of the refrigerant in the low-stage compression chamber (51) and the high-stage compression chamber (52), and to prevent a decrease in compression efficiency.
- the blade (23) is provided integrally with the cylinder (21).
- the blade (23) receives abnormal concentrated load during operation.
- the drive shaft (33) has a bearing member (18, 19) in which both axial portions of the eccentric portion (35) are axially opposed. Since it is held in the casing (10) through the fin, it is possible to suppress one-sided contact of the sliding portion, and to improve reliability.
- the refrigerant circuit (100) of the first embodiment may be configured in a two-stage compression and two-stage expansion cycle.
- the refrigerant circuit (100) (100) includes a compressor (1), a condenser (101), a receiver (102), a first expansion valve (109), an intercooler (103), and a second expansion.
- the valve (110) and the evaporator (105) are connected in order by a refrigerant pipe.
- a low-stage compression chamber (51) and a high-stage compression chamber (52) are connected to the intercooler (103).
- the high-pressure refrigerant discharged from the high-stage compression chamber (52) of the compressor (1) condenses in the condenser (101) and then flows to the receiver (102).
- the liquid refrigerant of the receiver (102) expands to intermediate-pressure refrigerant at the first expansion valve (109), expands at the second expansion valve (110) via the intercooler (103), and evaporates (105) And flows into the low-stage compression chamber (51) of the compressor (1).
- the intermediate-pressure refrigerant compressed in the low-stage compression chamber (51) flows into the intermediate cooler (103), and is cooled by the refrigerant expanded in the first expansion valve (109). Is cooled.
- the intermediate-pressure refrigerant cooled by the intermediate cooler (103) returns to the high-stage compression chamber (52) and is compressed into a high-pressure refrigerant. This circulation is repeated, and the indoor air is cooled, for example, by the evaporator (105).
- a gas injection pipe (lc) is provided in place of the inflow pipe (la) and the outflow pipe (lb) in the first embodiment.
- the gas injection pipe (lc) is connected to the body (11) of the casing (10), and communicates with the intermediate pressure space (4b).
- the gas injection pipe (lc) is connected, for example, to the intercooler (103) in FIG. 5 in the first embodiment, and the intermediate pressure refrigerant from the intercooler (103) to the intermediate pressure of the casing (10). Lead to space (4b).
- the inflow pipe (la) and the outflow pipe (lb) in the first embodiment are not provided, and the intermediate pressure passage (4e) includes the upper housing (16) and the lower housing ( 17) and are formed. One end of the intermediate pressure passage (4e) is connected to the intermediate pressure space (4b). Communicating.
- the intermediate-pressure refrigerant compressed in the low-stage compression chamber (51) flows into the intermediate-pressure chamber (4c), the intermediate-pressure space (4b), and from the intermediate-pressure passage (4e) to the high-stage compression chamber. It flows into (52) and is compressed. Then, in the intermediate pressure space (4b), the gas refrigerant from the intermediate cooler (103) is supplied to the intermediate pressure refrigerant via the gas injection pipe (ic) and cooled.
- the cylinder chamber (50) of the cylinder (21) in the previous embodiment 2 opens upward, instead of the cylinder chamber (50) of the cylinder (21). 50) is designed to open downward. That is, the cylinder (21) of the present embodiment is arranged upside down as in the second embodiment.
- the piston (22) is formed integrally with the lower housing (17), while the lower housing (17) is provided with a lower cover plate (41) and an intermediate pressure chamber (4c ), A high pressure chamber (4d) and an intermediate pressure passage (4e) are formed.
- the lower housing (17) is provided with a first discharge port (44) and a second discharge port (45).
- the first discharge port (44) communicates the low stage compression chamber (51) with the intermediate pressure chamber (4c), and the second discharge port (45) communicates with the high stage compression chamber (52) and the high pressure chamber. (4d) is communicated.
- the intermediate pressure chamber (4c) communicates with the intermediate pressure space (4b), and the intermediate pressure passage (4e) communicates the intermediate pressure space (4b) with the high-stage compression chamber (52).
- the high-pressure chamber (4d) communicates with the high-pressure space (4a) via the high-pressure passage (4h).
- the configuration, operation, and effects of the gas injection pipe (lc) and the like are the same as in Embodiment 2.
- an oil return passage (80) is added to the first embodiment.
- the oil return passage (80) is provided along the trunk (11) of the casing (10). Yes. One end of the oil return passage (80) is open on the upper surface of the upper cover plate (40). On the other hand, the other end of the oil return passage (80) is opened below the stator (32) of the electric motor (30).
- the oil return passage (80) is configured to return the lubricating oil separated in the high-pressure space (4a) to the bottom in the casing (10).
- the lubricating oil separated in the high-pressure space (4a) and accumulated on the upper cover plate (40) passes through the oil return passage (80) and returns to the bottom of the casing (10).
- the oil is separated in the high-pressure space (4a), so that it is possible to suppress the lubricating oil from being discharged together with the refrigerant, and to suppress so-called oil rising.
- the oil return passage (80) of the previous embodiment 4 returns lubricating oil to the bottom of the casing (10), instead of the drive shaft (33).
- the inside of the oil tank is returned to an oil supply passage (81) extending in the axial direction.
- the oil supply passage (81) is formed in the drive shaft (81)) in the axial direction, and lubricating oil at the bottom of the casing (10) is compressed by the oil supply pump (34) into the compression mechanism (20). ) Is supplied to the sliding part.
- One end of the oil return passage (80) is opened on the upper surface of the upper cover plate (40), is introduced into the oil supply passage (81), and the other end is opened in the middle of the oil supply passage (81). Therefore, the lubricating oil separated in the high-pressure space (4a) and accumulated on the upper cover plate (40) passes through the oil return passage (80) and returns to the middle of the oil supply passage (81).
- Other configurations, operations, and effects are the same as those of the fourth embodiment.
- the present invention may be configured as follows in the above embodiment.
- the cylinder (21) may be fixed and the piston (22) may be movable.
- the cylinder (21) is formed by connecting the outer cylinder (24) and the inner cylinder (25) to the upper end thereof with a head plate (26), and the piston (22) is Lower housing (17) May be integrally formed.
- the piston (22) has no dividing part! / ⁇ While the piston (22) is formed in a complete ring shape, the blade (23) is divided into an outer blade (23) and an inner blade (23). The outer blade (23) may advance and retreat from the outer cylinder and contact the piston (22), and the inner blade (23) may advance and retreat from the inner cylinder and contact the piston (22)!
- the refrigerant circuit (100) may perform only the heating operation, or may perform the operation by switching between the cooling operation and the heating operation.
- the refrigerant in the refrigerant circuit (100) is not limited to C02.
- the present invention is useful for a rotary compressor that compresses refrigerant in two stages, and in particular, a rotary compressor that forms a low-stage compression chamber and a high-stage compression chamber on the same plane. Suitable for compressors.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP05739308A EP1746289A4 (en) | 2004-05-11 | 2005-05-11 | ROTARY COMPRESSOR |
US10/572,511 US7563080B2 (en) | 2004-05-11 | 2005-05-11 | Rotary compressor |
AU2005240929A AU2005240929B2 (en) | 2004-05-11 | 2005-05-11 | Rotary compressor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004140691A JP3778203B2 (ja) | 2004-05-11 | 2004-05-11 | 回転式圧縮機 |
JP2004-140691 | 2004-05-11 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005108793A1 true WO2005108793A1 (ja) | 2005-11-17 |
Family
ID=35320285
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/008633 WO2005108793A1 (ja) | 2004-05-11 | 2005-05-11 | 回転式圧縮機 |
Country Status (7)
Country | Link |
---|---|
US (1) | US7563080B2 (ja) |
EP (1) | EP1746289A4 (ja) |
JP (1) | JP3778203B2 (ja) |
KR (1) | KR100857977B1 (ja) |
CN (1) | CN1950608A (ja) |
AU (1) | AU2005240929B2 (ja) |
WO (1) | WO2005108793A1 (ja) |
Cited By (1)
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JP2009139037A (ja) * | 2007-12-07 | 2009-06-25 | Mitsubishi Heavy Ind Ltd | 冷媒回路 |
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WO2006123519A1 (ja) * | 2005-05-17 | 2006-11-23 | Daikin Industries, Ltd. | 回転式圧縮機 |
JP4929951B2 (ja) * | 2006-09-27 | 2012-05-09 | ダイキン工業株式会社 | 回転式圧縮機 |
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JP5181463B2 (ja) * | 2006-10-31 | 2013-04-10 | ダイキン工業株式会社 | 流体機械 |
US20100119378A1 (en) * | 2007-02-28 | 2010-05-13 | Daikin Industries, Ltd. | Rotary compressor |
EP2096378B8 (en) * | 2007-06-22 | 2017-05-31 | Panasonic Intellectual Property Management Co., Ltd. | Refrigeration cycle apparatus |
JP4396773B2 (ja) * | 2008-02-04 | 2010-01-13 | ダイキン工業株式会社 | 流体機械 |
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US8225767B2 (en) * | 2010-03-15 | 2012-07-24 | Tinney Joseph F | Positive displacement rotary system |
SE534992C2 (sv) * | 2010-07-16 | 2012-03-06 | Bae Systems Haegglunds Ab | Elektrisk drivanordning för motorfordon |
US9267504B2 (en) | 2010-08-30 | 2016-02-23 | Hicor Technologies, Inc. | Compressor with liquid injection cooling |
EP2612035A2 (en) | 2010-08-30 | 2013-07-10 | Oscomp Systems Inc. | Compressor with liquid injection cooling |
JP5141759B2 (ja) * | 2010-12-27 | 2013-02-13 | ダイキン工業株式会社 | 回転式流体機械 |
SE536235C2 (sv) * | 2011-12-06 | 2013-07-09 | Bae Systems Haegglunds Ab | Elektrisk drivanordning för motorfordon |
JP2014005775A (ja) * | 2012-06-25 | 2014-01-16 | Nippon Soken Inc | 圧縮機 |
US9309862B2 (en) * | 2013-11-25 | 2016-04-12 | Halliburton Energy Services, Inc. | Nutating fluid-mechanical energy converter |
CA2934615C (en) | 2014-01-30 | 2019-10-22 | Halliburton Energy Services, Inc. | Nutating fluid-mechanical energy converter to power wellbore drilling |
CN104533791B (zh) * | 2014-11-07 | 2016-06-29 | 广东美芝制冷设备有限公司 | 压缩机 |
CN106080117A (zh) * | 2016-07-29 | 2016-11-09 | 珠海格力节能环保制冷技术研究中心有限公司 | 压缩机的控制器安装结构及电动汽车 |
CN108533490A (zh) * | 2018-06-22 | 2018-09-14 | 珠海格力电器股份有限公司 | 压缩机及空调系统 |
BE1026651B1 (nl) * | 2018-09-25 | 2020-04-28 | Atlas Copco Airpower Nv | Oliegeïnjecteerde meertraps compressorinrichting en werkwijze om een dergelijke compressorinrichting aan te sturen |
BE1026654B1 (nl) | 2018-09-25 | 2020-04-27 | Atlas Copco Airpower Nv | Oliegeïnjecteerde meertraps compressorinrichting en werkwijze voor het aansturen van een compressorinrichting |
CN112746959B (zh) * | 2019-10-31 | 2023-05-23 | 广东美的白色家电技术创新中心有限公司 | 压缩机构、压缩机、压缩机组件、热交换系统及电器设备 |
TWI726764B (zh) * | 2020-07-07 | 2021-05-01 | 楊進煌 | 迴轉式流體傳送裝置 |
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- 2005-05-11 US US10/572,511 patent/US7563080B2/en active Active
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- 2005-05-11 AU AU2005240929A patent/AU2005240929B2/en not_active Ceased
- 2005-05-11 EP EP05739308A patent/EP1746289A4/en not_active Withdrawn
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Also Published As
Publication number | Publication date |
---|---|
JP3778203B2 (ja) | 2006-05-24 |
CN1950608A (zh) | 2007-04-18 |
KR20070012547A (ko) | 2007-01-25 |
AU2005240929B2 (en) | 2009-04-23 |
KR100857977B1 (ko) | 2008-09-10 |
US20070041852A1 (en) | 2007-02-22 |
JP2005320927A (ja) | 2005-11-17 |
AU2005240929A1 (en) | 2005-11-17 |
US7563080B2 (en) | 2009-07-21 |
EP1746289A1 (en) | 2007-01-24 |
EP1746289A4 (en) | 2012-05-02 |
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