WO2013073182A1 - ロータリ圧縮機 - Google Patents
ロータリ圧縮機 Download PDFInfo
- Publication number
- WO2013073182A1 WO2013073182A1 PCT/JP2012/007301 JP2012007301W WO2013073182A1 WO 2013073182 A1 WO2013073182 A1 WO 2013073182A1 JP 2012007301 W JP2012007301 W JP 2012007301W WO 2013073182 A1 WO2013073182 A1 WO 2013073182A1
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- WIPO (PCT)
- Prior art keywords
- oil
- rotary compressor
- segment
- bearing member
- refrigerant
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/026—Lubricant separation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C18/0207—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 both members having co-operating elements in spiral form
- F04C18/0215—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 both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/809—Lubricant sump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
Definitions
- the present invention relates to a rotary compressor.
- Rotary compressors are widely used in electrical appliances such as air conditioners, heating devices, and water heaters.
- a technique for suppressing a reduction in efficiency due to the refrigerant (suction refrigerant) sucked into the compression chamber receiving heat from the surroundings, so-called heat loss, has been proposed. Yes.
- the rotary compressor of Patent Document 1 has a sealed space in the suction side portion of the cylinder as means for suppressing heat reception of the suction refrigerant. This sealed space suppresses the transfer of heat from the high-temperature refrigerant in the sealed container to the inner wall of the cylinder.
- An airtight container having an oil reservoir; A cylinder disposed inside the sealed container; A piston disposed inside the cylinder; A bearing member attached to the cylinder so as to form a cylinder chamber between the cylinder and the piston; A vane that partitions the cylinder chamber into a suction chamber and a discharge chamber; A suction port for leading the refrigerant to be compressed to the suction chamber; A discharge port that is formed in the bearing member and discharges the compressed refrigerant from the discharge chamber; A partition member that is attached to the bearing member and forms a refrigerant discharge space in which the refrigerant discharged from the discharge chamber through the discharge port can stay together with the bearing member;
- the bearing member has a first side on the same side as the inlet as viewed from a reference plane including the center of the vane when the vane protrudes most toward the center axis of the cylinder and the center axis of the cylinder.
- a recess is provided, Provided is a rotary compressor in which an oil holding portion is formed by part
- the oil retaining portion is formed by part of the oil in the oil reservoir entering the first recess provided in the bearing member.
- the oil holding part is located on the same side as the suction port as viewed from the reference plane.
- FIG. 1 is a longitudinal sectional view of a rotary compressor according to an embodiment of the present invention.
- Fig. 1 is a cross-sectional view of the rotary compressor shown in Fig. 1 taken along line IIA-IIA.
- the first aspect of the present disclosure is: An airtight container having an oil reservoir; A cylinder disposed inside the sealed container; A piston disposed inside the cylinder; A bearing member attached to the cylinder so as to form a cylinder chamber between the cylinder and the piston; A vane that partitions the cylinder chamber into a suction chamber and a discharge chamber; A suction port for leading the refrigerant to be compressed to the suction chamber; A discharge port that is formed in the bearing member and discharges the compressed refrigerant from the discharge chamber; A partition member that is attached to the bearing member and forms a refrigerant discharge space in which the refrigerant discharged from the discharge chamber through the discharge port can stay together with the bearing member;
- the bearing member has a first side on the same side as the inlet as viewed from a reference plane including the center of the vane when the vane protrudes most toward the center axis of the cylinder and the center axis of the cylinder.
- a recess is provided, Provided is a rotary compressor in
- the oil retaining portion may be formed by closing the first recess with the partition member or a member different from the partition member. I will provide a. According to such a structure, an excessive increase in the thickness of the bearing member can be avoided, so that it is possible not only to avoid an increase in parts cost but also to reduce the weight of the rotary compressor.
- the third aspect provides a rotary compressor in which the refrigerant discharge space may be formed by closing a second recess provided in the bearing member with the partition member.
- the partition member may be composed of a single plate member. Both the first recess and the second recess may be closed by the partition member.
- the fourth aspect provides a rotary compressor, in addition to any one of the first to third aspects, which may further include a communication path that communicates the oil reservoir and the oil holding portion. Oil in the oil reservoir can enter the oil holding portion through the communication path.
- two planes that include the central axis and that are in contact with the oil holding portion are defined as tangential planes, and the oil is formed out of angles formed by the tangential planes.
- the oil holding portion divided into two equal planes by defining a plane including the central axis as a bisected plane of the oil holding portion by dividing a corner of a region where the holding portion is located into two equal parts Of these two parts, the part located relatively near the suction port in the direction of rotation of the piston is the first half part, and the part located relatively far from the suction port in the direction of rotation of the piston The part is defined as the latter part.
- the fifth aspect provides a rotary compressor in which the oil in the oil reservoir may enter the first half part only through the second half part.
- the communication path may communicate the oil reservoir and the latter half portion. If the communication path is provided at such a position, the heat reception of the suction refrigerant can be more effectively suppressed.
- the oil holding portion is relatively close to the suction port in the rotational direction of the piston;
- a rotary that may have a rear half portion relatively far from the suction port in a rotation direction of the piston and a constriction portion located between the front half portion and the rear half portion.
- the constricted part suppresses the movement of oil between the first half part and the second half part. As a result, the oil flow in the first half is suppressed, and consequently the heat reception of the suction refrigerant is effectively suppressed.
- the 7th aspect provides the rotary compressor which may further be provided with the communicating path which connects the said oil reservoir and the said oil holding
- the communication path may communicate the oil reservoir and the latter half portion.
- the oil in the oil reservoir may enter the first half part only through the second half part and the constricted part. Thereby, the oil flow in the first half is effectively suppressed.
- the refrigerant discharge space is formed by closing a second recess provided in the bearing member by the partition member.
- a good rotary compressor is provided.
- the thickness of the bearing member in the first recess may be larger than the thickness of the bearing member in the second recess.
- a rotary compressor in which an area corresponding to the refrigerant discharge space may have an area smaller than an area corresponding to the oil holding portion. According to such a configuration, since a large heat insulating layer can be secured, heat reception of the suction refrigerant is effectively suppressed.
- the reference plane includes a first reference plane
- the segment including the suction port is defined as the first quadrant.
- a segment adjacent to is defined as a fourth quadrant segment.
- an area corresponding to the first quadrant segment in the projection obtained by projecting the first to fourth quadrant segments and the refrigerant discharge space onto a plane perpendicular to the central axis, an area corresponding to the first quadrant segment, provided is a rotary compressor in which the entire region corresponding to the refrigerant discharge space may be within the range of the region corresponding to the second quadrant segment and the region corresponding to the third quadrant segment. According to such a configuration, it is possible to suppress the heat reception of the suction refrigerant while suppressing an increase in pressure loss.
- the reference plane is a first reference plane
- a plane including the center of the inlet and the central axis is the first reference plane.
- 3 reference planes (c) of the two segments obtained by dividing the rotary compressor by the first reference plane, the segment including the discharge port is the first high temperature segment, and (d) the rotary compressor is Of the two segments obtained by dividing by the third reference plane, the segment including the discharge port is the second high temperature segment, and (e) the rotary compressor is the first reference plane and the third reference plane.
- the total of three segments included in either the first high temperature segment or the second high temperature segment is the total high temperature segment.
- the twelfth aspect provides a rotary compressor that may further include a shaft to which the piston is attached in addition to any one of the first to eleventh aspects.
- the rotary compressor may be a vertical rotary compressor in which the rotation axis of the shaft is parallel to the direction of gravity and the oil reservoir is formed at the bottom of the sealed container. According to the vertical rotary compressor, the swirl flow by the motor that drives the shaft hardly affects the oil holding portion.
- the rotary compressor 100 of this embodiment includes a hermetic container 1, a motor 2, a compression mechanism 102, and a shaft 4.
- the compression mechanism 102 is disposed at the lower part of the sealed container 1.
- the motor 2 is disposed on the compression mechanism 102 inside the sealed container 1.
- the compression mechanism 102 and the motor 2 are connected by the shaft 4.
- a terminal 21 for supplying electric power to the motor 2 is provided on the top of the sealed container 1.
- An oil reservoir 22 for holding lubricating oil is formed at the bottom of the sealed container 1.
- the motor 2 includes a stator 17 and a rotor 18.
- the stator 17 is fixed to the inner wall of the sealed container 1.
- the rotor 18 is fixed to the shaft 4 and rotates together with the shaft 4.
- a discharge pipe 11 is provided on the top of the sealed container 1.
- the discharge pipe 11 penetrates the upper part of the sealed container 1 and opens toward the internal space 13 of the sealed container 1.
- the discharge pipe 11 serves as a discharge flow path that guides the refrigerant compressed by the compression mechanism 102 to the outside of the sealed container 1.
- the internal space 13 of the sealed container 1 is filled with the compressed refrigerant.
- the compression mechanism 102 is moved by the motor 2 so as to compress the refrigerant.
- the compression mechanism 102 includes a first compression block 3, a second compression block 30, an upper bearing member 6, a lower bearing member 7, an intermediate plate 38, a first partition member 9 (a first muffler member or a first closing member). ) And a second partition member 10 (second muffler member or second closing member).
- the refrigerant is compressed by the first compression block 3 or the second compression block 30.
- the first compression block 3 and the second compression block 30 are immersed in oil stored in the oil reservoir 22.
- the first compression block 3 is composed of parts common to the parts constituting the second compression block 30. Accordingly, the first compression block 3 has a suction volume equal to the suction volume of the second compression block 30.
- the first compression block 3 includes a first cylinder 5, a first piston 8, a first vane 32, a first suction port 19, a first discharge port 40, and a first spring 36.
- the second compression block 30 includes the second cylinder 15, the second piston 28, the second vane 33, the second suction port 20, the second discharge port 41, and the second spring 37.
- the first cylinder 5 and the second cylinder 15 are arranged concentrically in the vertical direction.
- the shaft 4 has a first eccentric part 4a and a second eccentric part 4b.
- the eccentric parts 4a and 4b each protrude outward in the radial direction.
- the first piston 8 and the second piston 28 are disposed inside the first cylinder 5 and the second cylinder 15, respectively. Inside the first cylinder 5, a first piston 8 is attached to the first eccentric part 4a. Inside the second cylinder 15, a second piston 28 is attached to the second eccentric portion 4b.
- a first vane groove 34 and a second vane groove 35 are formed in the first cylinder 5 and the second cylinder 15, respectively. In the rotation direction of the shaft 4, the position of the first vane groove 34 coincides with the position of the second vane groove 35.
- the first eccentric portion 4a protrudes in a direction opposite to the protruding direction of the second eccentric portion 4b by 180 degrees. That is, the phase difference between the first piston 8 and the second piston 28 is 180 degrees. This configuration has an effect of reducing vibration and noise.
- the upper bearing member 6 is attached to the first cylinder 5 so as to form a first cylinder chamber 25 between the inner peripheral surface of the first cylinder 5 and the outer peripheral surface of the first piston 8.
- the lower bearing member 7 is attached to the second cylinder 15 so as to form a second cylinder chamber 26 between the inner peripheral surface of the second cylinder 15 and the outer peripheral surface of the second piston 28.
- the upper bearing member 6 is attached to the upper part of the first cylinder 5, and the lower bearing member 7 is attached to the lower part of the second cylinder 15.
- An intermediate plate 38 is disposed between the first cylinder 5 and the second cylinder 15.
- the first suction port 19 and the second suction port 20 are formed in the first cylinder 5 and the second cylinder 15, respectively.
- the first suction port 19 and the second suction port 20 open toward the first cylinder chamber 25 and the second cylinder chamber 26, respectively.
- a first suction pipe 14 and a second suction pipe 16 are connected to the first suction port 19 and the second suction port 20, respectively.
- the first discharge port 40 and the second discharge port 41 are formed in the upper bearing member 6 and the lower bearing member 7, respectively.
- the first discharge port 40 and the second discharge port 41 open toward the first cylinder chamber 25 and the second cylinder chamber 26, respectively.
- a first discharge valve 43 is provided at the first discharge port 40 so as to open and close the first discharge port 40.
- a second discharge valve 44 is provided at the second discharge port 41 so as to open and close the second discharge port 41.
- the first vane groove 34 is arranged so that the first vane 32 (blade) can slide.
- the first vane 32 partitions the first cylinder chamber 25 along the circumferential direction of the first piston 8. That is, the first cylinder chamber 25 is partitioned into the first suction chamber 25a and the first discharge chamber 25b.
- the second vane groove 35 is arranged so that the second vane 33 (blade) can slide.
- the second vane 33 partitions the second cylinder chamber 26 along the circumferential direction of the second piston 28. That is, the second cylinder chamber 26 is partitioned into the second suction chamber 26a and the second discharge chamber 26b.
- the first suction port 19 and the first discharge port 40 are located on the left and right sides of the first vane 32, respectively.
- the second suction port 20 and the second discharge port 41 are located on the left and right of the second vane 33, respectively.
- the refrigerant to be compressed is supplied to the first cylinder chamber 25 (first suction chamber 25 a).
- the refrigerant to be compressed is supplied to the second cylinder chamber 26 (second suction chamber 26a).
- the refrigerant compressed in the first cylinder chamber 25 pushes open the first discharge valve 43 and is discharged from the first discharge chamber 25b through the first discharge port 40.
- the refrigerant compressed in the second cylinder chamber 26 pushes the second discharge valve 44 open and is discharged from the second discharge chamber 26b through the second discharge port 41.
- the first piston 8 and the first vane 32 may be composed of a single part, that is, a swing piston.
- the second piston 28 and the second vane 33 may be constituted by a single component, that is, a swing piston.
- the first vane 32 and the second vane 33 may be coupled to the first piston 8 and the second piston 28, respectively.
- the detailed model of the rotary compressor is not particularly limited, and various models such as a rolling piston type and a swing piston type can be widely adopted.
- a first spring 36 and a second spring 37 are disposed behind the first vane 32 and the second vane 33, respectively.
- the first spring 36 and the second spring 37 push the first vane 32 and the second vane 33 toward the center of the shaft 4, respectively.
- the rear part of the first vane groove 34 and the rear part of the second vane groove 35 are each in communication with the internal space 13 of the sealed container 1. Accordingly, the pressure in the internal space 13 of the sealed container 1 is applied to the back surface of the first vane 32 and the back surface of the second vane 33.
- the oil stored in the oil reservoir 22 is supplied to the first vane groove 34 and the second vane groove 35.
- the first partition member 9 has the first cylinder chamber 25 as viewed from the upper bearing member 6 in the refrigerant discharge space 51 in which the refrigerant discharged from the first discharge chamber 25 b through the first discharge port 40 can stay. Is attached to the upper bearing member 6 so as to be formed on the opposite side. Specifically, the first partition member 9 is attached to the upper portion of the upper bearing member 6 so that the refrigerant discharge space 51 is formed above the upper bearing member 6. The first partition member 9 forms a refrigerant discharge space 51 together with the upper bearing member 6. The first discharge valve 43 is covered with the first partition member 9.
- the first partition member 9 is formed with a discharge port 9 a for guiding the refrigerant from the refrigerant discharge space 51 to the internal space 13 of the sealed container 1.
- the second partition member 10 forms a refrigerant discharge space 52 in which the refrigerant discharged from the second discharge chamber 26 b through the second discharge port 41 can stay on the opposite side of the second cylinder chamber 26 when viewed from the lower bearing member 7. Further, it is attached to the lower bearing member 7. Specifically, the second partition member 10 is attached to the lower portion of the lower bearing member 7 so that the refrigerant discharge space 52 is formed below the lower bearing member 7.
- the second partition member 10 forms a refrigerant discharge space 52 together with the lower bearing member 7.
- the second discharge valve 44 is covered with the second partition member 10.
- the refrigerant discharge spaces 51 and 52 each serve as a refrigerant flow path.
- the shaft 4 passes through the central portion of the first partition member 9 and the central portion of the second partition member 10, and is rotatably supported by the upper bearing member 6 and the lower bearing member 7.
- the refrigerant discharge space 52 communicates with the refrigerant discharge space 51 through the through flow path 46.
- the through passage 46 penetrates the lower bearing member 7, the second cylinder 15, the intermediate plate 38, the first cylinder 5, and the upper bearing member 6 in a direction parallel to the rotation axis of the shaft 4.
- the refrigerant compressed in the second compression block 30 merges with the refrigerant compressed in the first compression block 3 in the internal space of the first partition member 9, that is, in the refrigerant discharge space 51. Therefore, even if the volume of the refrigerant discharge space 52 is insufficient, a noise reduction effect by the refrigerant discharge space 51 can be obtained inside the first partition member 9.
- the cross-sectional area (flow area) of the through flow path 46 is larger than the cross-sectional area (flow area) of the second discharge port 41. Thereby, increase in pressure loss can be prevented.
- the first reference plane H 1 , the second reference plane H 2, and the third reference plane H 3 are defined as follows.
- a plane including the center of the second vane 33 and the center axis O 1 of the second cylinder 15 when the second vane 33 protrudes most toward the center axis O 1 of the second cylinder 15 is a first reference plane H 1 .
- the first reference plane H 1 passes through the center of the second vane groove 35.
- a plane including the central axis O 1 and perpendicular to the first reference plane H 1 is defined as a second reference plane H 2 .
- a plane including the center of the second inlet 20 and the central axis O 1 is defined as a third reference plane H 3 .
- the central axis O 1 of the second cylinder 15 substantially coincides with the rotation axis of the shaft 4 and the central axis of the first cylinder 5.
- the second vane groove 35 has an opening facing the second cylinder chamber 26.
- the first reference plane H 1 passes through this reference position and passes through the center axis O 1. It may be a plane including That is, “the center of the second vane groove 35” means the center of the opening of the second vane groove 35.
- the first reference plane H 1 includes the central axis O 1 of the second cylinder 15 and the second cylinder 15 and the second piston 28 when the second vane 33 protrudes most toward the central axis O 1 of the second cylinder 15. And a contact point (in detail, a tangent line). Further, the central axis O 1 of the second cylinder 15 means the central axis of the cylindrical inner peripheral surface of the second cylinder 15 in detail.
- the compression mechanism 102 further includes an oil holding portion 53.
- the oil retaining portion 53 is located on the same side as the second suction port 20 as viewed from the first reference plane H 1, and includes a first recess 7 t provided in the lower bearing member 7.
- the oil retaining portion 53 is formed on the opposite side of the second cylinder chamber 26 when viewed from the lower bearing member 7. Specifically, the oil retaining portion 53 is in contact with the lower surface of the lower bearing member 7.
- the oil retaining portion 53 is formed by a part of the oil accumulated in the oil reservoir 22 entering the first recess 7t through a communication passage 7p described later.
- the oil holding part 53 is configured such that the oil flow in the oil holding part 53 is suppressed more than the oil flow in the oil reservoir 22.
- the oil flow in the oil holding portion 53 is gentler than the oil flow in the oil reservoir 22.
- the oil level of the oil reservoir 22 is located above the lower surface of the first cylinder 5.
- the oil level of the oil reservoir 22 is desirably higher than the upper surface of the first cylinder 5 and lower than the lower end of the motor 2 during operation.
- the second cylinder 15, the lower bearing member 7 and the second partition member 10 are immersed in the oil in the oil reservoir 22. Therefore, the oil in the oil reservoir 22 can enter the oil holding portion 53 (first recess 7t).
- the refrigerant to be compressed is in a low temperature and low pressure state.
- the compressed refrigerant is in a high temperature and high pressure state. Therefore, a specific temperature distribution is generated in the lower bearing member 7 during the operation of the rotary compressor 100.
- the suction side portion is a portion including a portion directly below the second suction port 20 out of two portions obtained by dividing the lower bearing member 7 by the first reference plane H 1 .
- a discharge side part is a part in which the 2nd discharge port 41 is provided among two parts.
- an oil holding portion 53 is formed on the same side as the second suction port 20 as viewed from the first reference plane H 1 .
- the oil holding portion 53 is in contact with the lower surface of the lower bearing member 7.
- the oil in the oil holding part 53 suppresses the refrigerant (suction refrigerant) sucked into the second cylinder chamber 26 from receiving heat from the surroundings.
- maintenance part 53 suppresses the heat reception of an inhalation refrigerant
- Oil is a liquid and has a large viscosity.
- the oil can be swollen in the first concave portion 7t. Therefore, the oil flow rate in the oil holding portion 53 is slower than the oil flow rate in the oil reservoir 22.
- the heat transfer coefficient at the surface of the object is proportional to the square root of the fluid velocity, the heat transfer coefficient at the lower surface of the lower bearing member 7 is also small when the oil flow rate of the oil holding portion 53 is slow. As a result, the heat gently moves from the oil in the oil holding portion 53 to the lower bearing member 7.
- the oil holding unit 53 suppresses heat reception of the suction refrigerant. Even if another member is disposed between the oil retaining portion 53 and the lower surface of the lower bearing member 7, such another member can be regarded as a part of the lower bearing member 7.
- the effect of suppressing the heat reception of the sucked refrigerant is that not only the oil retaining portion 53 but also most of the refrigerant discharge space 52 is formed on the same side as the second discharge port 41 as viewed from the first reference plane H 1. Is also attributed.
- the heat transfer path is relatively long.
- the amount of heat transfer is inversely proportional to the distance of the heat transfer path. That is, according to the present embodiment, it is possible to increase the thermal resistance when heat is transferred from the discharged refrigerant to the sucked refrigerant.
- the oil holding part 53 an amount of oil corresponding to the volume of the oil holding part 53 can be stored in the closed container 1 in excess. Therefore, the oil holding part 53 contributes to the improvement of the reliability of the rotary compressor 100.
- the oil retaining portion 53 is formed by closing the first recess 7 t provided in the lower bearing member 7 with the second partition member 10. According to such a structure, an increase in the thickness of the lower bearing member 7 can be avoided, so that an increase in component costs can be avoided, and it is advantageous for reducing the weight of the rotary compressor 100.
- the oil retaining portion 53 may be formed by closing the first recess 7 t with a member different from the second partition member 10.
- the lower bearing member 7 is further provided with a communication path 7p.
- the communication path 7p extends in the lateral direction so as to allow the oil reservoir 22 and the oil holding portion 53 to communicate with each other.
- the oil in the oil reservoir 22 can enter the oil holding portion 53 through the communication passage 7p (communication hole).
- the size of the communication path 7 p is adjusted to a size that is necessary and sufficient for the oil in the oil reservoir 22 to enter the oil holding portion 53. Therefore, the oil flow in the oil holding portion 53 is gentler than the oil flow in the oil reservoir 22. Therefore, the oil forms a relatively stable temperature stratification in the oil holding portion 53.
- only one communication path 7p may be provided in the lower bearing member 7.
- the communication path 7p is configured by a small through hole.
- the communication path 7p may be configured by another structure such as a slit. As shown in FIG. 3, the upper end of the communication path 7 p coincides with the lower surface 7 h of the lower bearing member 7 or is higher than the lower surface 7 h of the lower bearing member 7 in the direction parallel to the rotation axis of the shaft 4. positioned. According to such a structure, it is possible to prevent air from remaining in the oil holding portion 53.
- the second recess 7s provided in the lower bearing member 7 is closed by the second partition member 10, whereby the refrigerant discharge space 52 is formed. That is, the lower bearing member 7 is formed with a first recess 7t that functions as the oil holding portion 53 and a second recess 7s that functions as the refrigerant discharge space 52.
- the 2nd division member 10 is comprised with the single plate-shaped member. Both the first recess 7 t and the second recess 7 s are closed by the second partition member 10.
- the lower surface of the second partition member 10 is a plane. The opening end face of the first recess 7t and the opening end face of the second recess 7s are present on the same plane so as to be closed by the second partition member 10. Such a structure is very simple and an increase in the number of parts can be avoided.
- an oil retaining portion 53 is formed in a part of the angular range around the shaft 4, and a refrigerant discharge space 52 is formed in the other part of the angular range.
- part of the oil holding part 53 and part of the refrigerant discharge space may overlap.
- the oil retaining portion 53 is completely isolated from the refrigerant discharge space 52 by the rib 7 k provided on the lower bearing member 7.
- Most of the refrigerant discharge space 52 is formed on the same side as the second discharge port 41 when viewed from the first reference plane H 1 .
- the oil retaining portion 53 is formed on the same side as the second suction port 20 as viewed from the first reference plane H 1 . According to such a positional relationship, heat transfer from the refrigerant discharged into the refrigerant discharge space 52 to the refrigerant sucked into the second cylinder chamber 26 can be suppressed.
- a part of the oil retaining portion 53 is formed on the same side as the second discharge port 41 as viewed from the first reference plane H 1 .
- the entire oil retaining portion 53 may be formed on the same side as the second suction port 20 as viewed from the first reference plane H 1 .
- the thickness of the lower bearing member 7 in the portion (first recess 7t) where the oil retaining portion 53 is formed is the same as that in the portion (second recess 7s) where the refrigerant discharge space 52 is formed. It is larger than the wall thickness of the lower bearing member 7. Thereby, the volume of the 2nd discharge outlet 41 can fully be reduced. That is, the dead volume derived from the second discharge port 41 can be reduced.
- the minimum thickness of the lower bearing member 7 in the portion forming the refrigerant discharge space 52 (second recess 7s) is D1
- the “thickness of the lower bearing member 7” means a thickness in a direction parallel to the rotation axis of the shaft 4. Further, as shown in FIG. 1, a counterbore for accommodating the second discharge valve 44 is formed in a portion (second recess 7 s) forming the refrigerant discharge space 52 of the lower bearing member 7. May be.
- the occupation ratio of the refrigerant discharge space 52 and the oil retaining portion 53 in the lower bearing member 7 is not particularly limited.
- a region corresponding to the refrigerant discharge space 52 is the oil holding portion 53.
- the area of the region corresponding to the refrigerant discharge space 52 is S 3
- the area S 3 of the region corresponding to the refrigerant discharge space 52 may be smaller than the area S 4 of the region corresponding to the oil retaining portion 53.
- the area S 3 and the area S 4 satisfy a relationship of 1.1 ⁇ (S 4 / S 3 ) ⁇ 5.
- the volume of the refrigerant discharge space 52 is V 3 and the volume of the oil retaining portion 53 is V 4 , for example, the relationship of 1.1 ⁇ (V 4 / V 3 ) ⁇ 10 is satisfied.
- the area S 3 may coincide with the area S 4 .
- the volume V 3 may coincide with the volume V 4 .
- the segment including the second inlet 20 is defined as the first quadrant. This is defined as segment Q 1 .
- segment Q 1 a segment containing a second discharge port 41 and the second quadrant segment Q 2.
- a segment opposite to the first quadrant segment Q 1 and adjacent to the second quadrant segment Q 2 is defined as a third quadrant segment Q 3 .
- a segment opposite to the second quadrant segment Q 2 and adjacent to the first quadrant segment Q 1 is defined as a fourth quadrant segment Q 4 .
- FIG. 4 is a bottom view of the lower bearing member 7. If the left and right inversion is ignored, FIG. 4 projects (orthographic projection) the first to fourth quadrant segments Q 1 to Q 4 , the refrigerant discharge space 52 and the oil holding portion 53 on a plane perpendicular to the central axis O 1. It corresponds to the projection figure obtained by this.
- the region corresponding to the first quadrant segment Q 1 , the region corresponding to the second quadrant segment Q 2 , and the region corresponding to the third quadrant segment Q 3 are within the range of the region. The entire region corresponding to the refrigerant discharge space 52 is accommodated.
- the region corresponding to the oil retaining portion 53 is within the range of the region corresponding to the first quadrant segment Q 1 , the region corresponding to the third quadrant segment Q 3 , and the region corresponding to the fourth quadrant segment Q 4. Is all in place.
- the regions corresponding to the second quadrant segment Q 2 and the third quadrant segment Q 3 correspond to the discharge side portion having a relatively high temperature as described above. Therefore, there is a certain rationality that the refrigerant discharge space 52 is formed in the second quadrant segment Q 2 and the third quadrant segment Q 3 .
- the through-flow channel 46 opens toward the refrigerant discharge space 52 in, for example, the third quadrant segment Q 3 .
- Through channel 46 may be open toward the refrigerant discharge space 52 in the second quadrant segment Q 2.
- the refrigerant discharge space 52 crosses the first reference plane H 1 and further overlaps the third reference plane H 3 . That is, the refrigerant discharge space 52 is also formed directly below the second suction port 20.
- Such a configuration is not necessarily preferable from the viewpoint of suppressing heat transfer (heat loss) from the refrigerant in the refrigerant discharge space 52 to the refrigerant in the second cylinder chamber 26.
- heat loss heat transfer
- the suction port and the discharge port are provided as close to the vane as possible.
- the refrigerant discharge space is formed below the lower bearing member, and the discharge port opens toward the refrigerant discharge space.
- the refrigerant discharge space is formed only on the same side as the discharge port as viewed from the first reference plane H 1 .
- the refrigerant discharge space 52 is allowed to be present directly below the second suction port 20. If the refrigerant discharge space 52 does not exist at least in the region corresponding to the fourth quadrant segment Q 4 , an effect of suppressing heat loss can be obtained.
- the position of the refrigerant discharge space 52 can be specified as follows.
- the segment including the second discharge port 41 is defined as the first high temperature segment SG 1 (shaded portion). It is defined as As shown in FIG. 5B, of the two segments obtained by dividing the rotary compressor 100 by the third reference plane H 3 , the segment including the second discharge port 41 is defined as the second high temperature segment SG 2 (shaded portion). It is defined as As shown in FIG. 5C, among the four segments obtained by dividing the rotary compressor 100 by the first reference plane H 1 and the third reference plane H 3 , the first high-temperature segment SG 1 and the second high-temperature segment SG.
- the total of the three segments included in any one of 2 is defined as a total high-temperature segment SG total (shaded portion).
- a total high-temperature segment SG total shaded portion.
- 70% or more of the region corresponding to the refrigerant discharge space 52 is the total high temperature segment SG. It may overlap with the area corresponding to total . That is, when the refrigerant discharge space 52 is also formed directly under the second suction port 20, the total loss taking into account heat loss and pressure loss is minimized, and the rotary compressor 100 has the highest efficiency. There is a possibility of exerting.
- corresponding to the refrigerant discharge space 52 whole regions may be accommodated in a region corresponding to the first high-temperature segment SG 1. That is, the refrigerant discharge space 52 may be formed only on the same side as the second discharge port 41 when viewed from the first reference plane H 1 .
- two planes including the central axis O 1 and in contact with the oil retaining portion 53 are defined as tangential planes ⁇ 1 and ⁇ 2 .
- the angle of the region where the oil holding portion 53 is located is divided into two equal parts, and the plane including the central axis O 1 is divided into two equal planes ⁇ of the oil holding portion 53.
- the part located relatively near the second suction port 20 in the rotational direction of the second piston 28 is the first half part.
- a portion located relatively far from the second suction port 20 in the rotation direction of the second piston 28 is defined as a rear half portion 53b.
- the communication path 7p communicates the oil reservoir 22 with the rear half 53b of the oil retaining portion 53.
- the oil in the oil reservoir 22 cannot directly enter the first half portion 53 a of the oil holding portion 53.
- the oil in the oil reservoir 22 enters the first half portion 53a of the oil holding portion 53 through the second half portion 53b (preferably only through the second half portion 53b). If the communication path 7p is provided at such a position, the heat reception of the suction refrigerant can be more effectively suppressed.
- the second piston 28 rotates around the center axis O 1 shown in FIG. 6 counterclockwise.
- the refrigerant is compressed while moving through the first to fourth quadrant segments in the order of Q 1 , Q 4 , Q 3 and Q 2 . Therefore, the temperature of the lower bearing member 7 tends to be lowest in the first quadrant segment Q 1 and highest in the second quadrant segment Q 2 . If the communication path 7p is formed only in the second half portion 53b of the oil holding portion 53 as in the present embodiment, the oil mainly moves between the oil reservoir 22 and the second half portion 53b.
- the oil in the first half portion 53a can be actively stagnated, the oil flow rate in the first half portion 53a is slower than the oil flow rate in the second half portion 53b. Since the first half portion 53a is located near the second suction port 20, the slower the oil flow rate in the first half portion 53a, the more the refrigerant sucked into the second cylinder chamber 26 from the second suction port 20 is heated. Can be effectively suppressed.
- the oil retaining portion 53 may have a front half portion 53a, a rear half portion 53b, and a constricted portion 53c.
- the front half portion 53 a is a portion that is positioned relatively close to the second suction port 20 in the rotation direction of the second piston 28.
- the second half portion 53b is a portion that is located relatively far from the second suction port 20 in the rotational direction of the second piston 28.
- the constricted portion 53c is a portion located between the first half portion 53a and the second half portion 53b.
- the width of the constricted portion 53c is smaller than the width of the oil retaining portion 53 in the front half portion 53a (and the rear half portion 53b).
- the ratio (Dmax / Dmin) is in the range of 1.2 to 50, for example.
- the constricted portion 53c suppresses the movement of oil between the first half portion 53a and the second half portion 53b. As a result, the oil flow in the first half portion 53a is further suppressed, and as a result, the heat reception of the suction refrigerant is effectively suppressed.
- the communication path 7p communicates the oil reservoir 22 with the latter half 53b of the oil retaining portion 53.
- the oil in the oil reservoir 22 enters the first half 53a only through the second half 53b and the constricted portion 53c. Thereby, the oil flow in the first half portion 53a is effectively suppressed.
- the oil retaining portion 53 is formed by closing the first recess 7 t provided in the lower bearing member 7 with the second partition member 10.
- the oil retaining portion 53 may be formed only by the first recess 7 t provided in the lower bearing member 7. That is, a structure in which the second partition member 10 is not essential is also conceivable.
- the first concave portion 7t has a function of squeezing oil, so that the oil flow rate in the first concave portion 7t is Slower than oil flow rate. Further, as shown in FIG.
- the rotary compressor 100 of this embodiment is a vertical rotary compressor.
- the rotation axis of the shaft 4 is parallel to the direction of gravity, and the oil reservoir 22 is formed at the bottom of the sealed container 1.
- the upper layer portion of the oil in the oil reservoir 22 is relatively hot, and the lower layer portion of the oil in the oil reservoir 22 is relatively cold. Therefore, in the vertical rotary compressor 100, it is desirable to form the oil retaining portion 53 below the lower bearing member 7.
- the rotary compressor 200 according to Modification 1 includes a lower bearing member 70, a second partition member 61, and an oil cup 62.
- the basic structure necessary for compressing the refrigerant is common to the rotary compressor 200 and the rotary compressor 100 shown in FIG. The difference is in the structure for suppressing heat loss.
- the lower bearing member 70 includes a disc portion 70a and a bearing portion 70b.
- the disc part 70 a is a part adjacent to the second cylinder 15.
- a second discharge port 41 is formed in the disc portion 70a.
- a second discharge valve 44 that opens and closes the second discharge port 41 is attached to the disc portion 70a.
- the bearing portion 70b is a hollow cylindrical portion formed integrally with the disc portion 70a so as to support the shaft 4.
- the second partition member 61 is a member having a bowl-shaped structure, and is attached to the lower bearing member 70 so that the refrigerant discharge space 52 is formed on the opposite side of the second cylinder chamber 26 when viewed from the lower bearing member 70. ing.
- the second partition member 61 covers the lower surface of the lower bearing member 70 so that the refrigerant discharge space 52 is formed below the lower bearing member 70.
- a through hole for exposing the lower end of the shaft 4 to the oil reservoir 22 is formed at the center of the second partition member 61.
- the refrigerant discharge space 52 is basically formed all around the bearing portion 70b.
- an oil cup 62 is further disposed inside the second partition member 61.
- a specific portion of the lower surface of the lower bearing member 70 is covered with the oil cup 62, thereby forming an oil holding portion 53.
- the position of the oil retaining portion 53 is as described above with reference to FIGS.
- the oil cup 62 is formed with one or a plurality of communication passages 62p.
- the oil in the oil reservoir 22 can enter the oil holding portion 53 through the communication passage 62p.
- a double shell structure is adopted as a structure for forming the oil retaining portion 53. That is, the means and structure for forming the oil retaining portion 53 are not particularly limited.
- the same effect as that obtained by the rotary compressor 100 with reference to FIG. 1 can be obtained.
- oil holding portion 53 may be formed by a structure described below.
- the structure of the lower bearing member 70 is as described with reference to FIG. 9.
- the second partition member 67 is attached to the lower bearing member 70 so that the refrigerant discharge space 52 is formed on the opposite side of the second cylinder chamber 26 when viewed from the lower bearing member 70.
- the 2nd division member 67 is comprised by the hook-shaped part 67a and the flange part 67b.
- the hook-shaped portion 67a and the flange portion 67b are formed of a single part.
- the hook-shaped portion 67 a covers the lower surface of the lower bearing member 70 so that the refrigerant discharge space 52 is formed below the lower bearing member 70.
- the flange portion 67 b has a shape along the disc portion 70 a and the bearing portion 70 b of the lower bearing member 70.
- the flange portion 67 b is in close contact with the lower bearing member 70.
- the oil cup 68 covers the flange portion 67b so that the oil retaining portion 53 is formed on the opposite side of the second cylinder chamber 26 when viewed from the lower bearing member 70.
- the oil holding portion 53 is in contact with the lower surface of the flange portion 67b.
- the oil retaining portion 53 is in contact with the lower surface of the lower bearing member 70.
- the oil cup 68 is provided with a communication path 68p.
- the shape and position of the communication path 68p may be the same as the communication path 7p shown in FIGS.
- the oil retaining portion 53 can be formed while using the lower bearing member 70 having the same structure as the lower bearing member of the conventional rotary compressor. Even with such a structure, the refrigerant discharge space 52 and the oil retaining portion 53 can be formed.
- the flange portion 67b can more effectively suppress heat conduction from the oil in the oil holding portion 53 to the refrigerant in the second cylinder chamber 26.
- the lower bearing member 72 has the structure shown in FIG. 11C.
- the lower bearing member 72 includes a disc portion 70a, a bearing portion 70b, and a bank portion 70c.
- the structure of the disc part 70a and the bearing part 70b is as having demonstrated with reference to FIG.
- the bank portion 70c is a portion protruding from the disc portion 70a so as to surround the recess 72t to be the refrigerant discharge space 52.
- the opening end surface of the bank portion 70c is a flat surface.
- the second partition member 64 has a circular shape in plan view, and has a through-hole through which the shaft 4 passes. Specifically, the 2nd division member 64 is comprised by the plate-shaped part 64a and the circular arc-shaped part 64b.
- the second partition member 64 is attached to the lower bearing member 72 such that the refrigerant discharge space 52 and the oil retaining portion 53 are formed on the opposite side of the second cylinder chamber 26 when viewed from the lower bearing member 72.
- the second partition member 64 (or a member different from the second partition member 64) is attached to the lower bearing member 72, so that the second partition member 64 (or the second partition member 64 is positioned at a position adjacent to the lower bearing member 72).
- a space surrounded by a lower bearing member 72 and a member separate from the two-partition member 64 is formed.
- An oil holding portion 53 is formed by a part of the oil stored in the oil reservoir 22 entering the enclosed space.
- a part of the plate-like portion 64a is in contact with the bank portion 70c and closes the recess 72t surrounded by the bearing portion 70b and the bank portion 70c.
- the remaining portion of the plate-like portion 64a faces the disc portion 70a of the lower bearing member 72 so that the oil retaining portion 53 is formed.
- the arc-shaped part 64b is a part formed integrally with the plate-like part 64a, and is formed along the outer periphery of the plate-like part 64a.
- the arc-shaped portion 64b further extends in the thickness direction of the plate-shaped portion 64a (a direction parallel to the rotation axis of the shaft 4).
- a gap 64 p is formed between the end of the arcuate portion 64 b and the lower bearing member 72 as a communication path that connects the oil reservoir 22 and the oil retaining portion 53.
- the lower bearing member 72 described with reference to FIG. 11C is used.
- the refrigerant discharge space 52 is formed by attaching the plate-shaped and fan-shaped second partition member 65 to the lower bearing member 72.
- the second partition member 65 is in contact with the bank portion 70c and closes the recess 72t surrounded by the bearing portion 70b and the bank portion 70c.
- an oil cup 60 that is a member different from the second partition member 65 is further used.
- the oil cup 60 is attached to the lower bearing member 72 so that the oil holding portion 53 is formed.
- the oil cup 60 is composed of a plate-shaped portion 60a and an arc-shaped portion 60b.
- the plate-like portion 60 a is a portion facing the disc portion 70 a of the lower bearing member 72.
- the arc-shaped portion 60b is a portion formed integrally with the plate-like portion 60a, and is formed along the outer periphery of the plate-like portion 60a.
- the arc-shaped portion 60b further extends in the thickness direction of the plate-shaped portion 60a (direction parallel to the rotation axis of the shaft 4).
- a gap 66 p is formed between the end of the arc-shaped portion 60 b and the lower bearing member 72 as a communication path that connects the oil reservoir 22 and the oil holding portion 53.
- the rotary compressor 300 according to the second modification has a structure in which the first compression block 3 is omitted from the rotary compressor 100 shown in FIG. That is, the rotary compressor 300 is a one-piston rotary compressor provided with only one cylinder. Thus, the present invention can also be applied to the one-piston rotary compressor 300.
- the rotary compressor 400 according to the modification 3 has an oil holding portion 53 provided inside the upper bearing member 6. Further, according to the structure described with reference to FIG. 9, the oil holding portion 53 can be formed above the upper bearing member 6. As described above, the oil holding portion 53 may be formed upward as viewed from the cylinder chamber 26 or may be formed below.
- the rotary compressor 500 according to Modification 5 is a one-piston rotary compressor.
- the compressed refrigerant is discharged from the compression chamber 26 to the refrigerant discharge space 51 through the discharge port 41 formed in the upper bearing member 6.
- An oil cup 63 is attached to the lower bearing member 74. Thereby, a space surrounded by the lower bearing member 74 and the oil cup 63 is formed below the lower bearing member 74.
- An oil holding portion 53 is formed by the oil entering the enclosed space.
- the oil holding part 53 can also be provided in the 1-piston rotary compressor 500.
- the oil holding part 53 may be formed in the entire angle range around the shaft 4, or the oil holding part 53 may be formed only in a part of the angle range around the shaft 4.
- the present invention is useful for a compressor of a refrigeration cycle apparatus that can be used for electrical products such as a water heater, a hot water heater, and an air conditioner.
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Abstract
Description
オイル溜まりを有する密閉容器と、
前記密閉容器の内部に配置されたシリンダと、
前記シリンダの内部に配置されたピストンと、
前記シリンダと前記ピストンとの間にシリンダ室を形成するように、前記シリンダに取り付けられた軸受部材と、
前記シリンダ室を吸入室と吐出室とに仕切るベーンと、
圧縮されるべき冷媒を前記吸入室に導く吸入口と、
前記軸受部材に形成され、圧縮された冷媒を前記吐出室から吐出させる吐出口と、
前記軸受部材に取り付けられ、前記軸受部材とともに、前記吐出口を通じて前記吐出室から吐出された冷媒が滞在できる冷媒吐出空間を形成している区画部材と、を備え、
前記軸受部材には、前記ベーンが前記シリンダの中心軸に向かって最も突出したときの前記ベーンの中心と前記シリンダの前記中心軸とを含む基準平面から見て前記吸入口と同じ側に第1凹部が設けられており、
前記オイル溜まりに溜められたオイルの一部が前記第1凹部に浸入することによってオイル保持部が形成されている、ロータリ圧縮機を提供する。
オイル溜まりを有する密閉容器と、
前記密閉容器の内部に配置されたシリンダと、
前記シリンダの内部に配置されたピストンと、
前記シリンダと前記ピストンとの間にシリンダ室を形成するように、前記シリンダに取り付けられた軸受部材と、
前記シリンダ室を吸入室と吐出室とに仕切るベーンと、
圧縮されるべき冷媒を前記吸入室に導く吸入口と、
前記軸受部材に形成され、圧縮された冷媒を前記吐出室から吐出させる吐出口と、
前記軸受部材に取り付けられ、前記軸受部材とともに、前記吐出口を通じて前記吐出室から吐出された冷媒が滞在できる冷媒吐出空間を形成している区画部材と、を備え、
前記軸受部材には、前記ベーンが前記シリンダの中心軸に向かって最も突出したときの前記ベーンの中心と前記シリンダの前記中心軸とを含む基準平面から見て前記吸入口と同じ側に第1凹部が設けられており、
前記オイル溜まりに溜められたオイルの一部が前記第1凹部に浸入することによってオイル保持部が形成されている、ロータリ圧縮機を提供する。
図9に示すように、変形例1に係るロータリ圧縮機200は、下軸受部材70、第2区画部材61及びオイルカップ62を備えている。冷媒を圧縮するために必要な基本的構造は、ロータリ圧縮機200と図1に示すロータリ圧縮機100とで共通している。相違点は、熱ロスを抑制するための構造にある。
図12に示すように、変形例2に係るロータリ圧縮機300は、図1に示すロータリ圧縮機100から第1圧縮ブロック3を省略した構造を有する。つまり、ロータリ圧縮機300は、シリンダを1つのみ備えた1ピストンロータリ圧縮機である。このように、1ピストンロータリ圧縮機300にも本発明を適用することができる。
図13に示すように、変形例3に係るロータリ圧縮機400は、上軸受部材6の内部に設けられたオイル保持部53を有する。また、図9を参照して説明した構造によれば、上軸受部材6の上方にオイル保持部53を形成することも可能である。このように、オイル保持部53は、シリンダ室26から見て上方に形成されていてもよいし、下方に形成されていてもよい。
図14に示すように、変形例5に係るロータリ圧縮機500は、1ピストンロータリ圧縮機である。圧縮された冷媒は、上軸受部材6に形成された吐出口41を通じて、圧縮室26から冷媒吐出空間51に吐出される。下軸受部材74には、オイルカップ63が取り付けられている。これにより、下軸受部材74の下方に下軸受部材74とオイルカップ63とで囲まれた空間が形成されている。その囲まれた空間にオイルが浸入することによってオイル保持部53が形成されている。このように、1ピストンロータリ圧縮機500にオイル保持部53を設けることもできる。本変形例では、下軸受部材74の下方に冷媒吐出空間が存在しない。従って、シャフト4の周囲の全角度範囲にオイル保持部53が形成されていてもよいし、シャフト4の周囲の一部の角度範囲にのみオイル保持部53が形成されていてもよい。
Claims (12)
- オイル溜まりを有する密閉容器と、
前記密閉容器の内部に配置されたシリンダと、
前記シリンダの内部に配置されたピストンと、
前記シリンダと前記ピストンとの間にシリンダ室を形成するように、前記シリンダに取り付けられた軸受部材と、
前記シリンダ室を吸入室と吐出室とに仕切るベーンと、
圧縮されるべき冷媒を前記吸入室に導く吸入口と、
前記軸受部材に形成され、圧縮された冷媒を前記吐出室から吐出させる吐出口と、
前記軸受部材に取り付けられ、前記軸受部材とともに、前記吐出口を通じて前記吐出室から吐出された冷媒が滞在できる冷媒吐出空間を形成している区画部材と、を備え、
前記軸受部材には、前記ベーンが前記シリンダの中心軸に向かって最も突出したときの前記ベーンの中心と前記シリンダの前記中心軸とを含む基準平面から見て前記吸入口と同じ側に第1凹部が設けられており、
前記オイル溜まりに溜められたオイルの一部が前記第1凹部に浸入することによってオイル保持部が形成されている、ロータリ圧縮機。 - 前記第1凹部が前記区画部材又は前記区画部材とは別の部材で閉じられることによって前記オイル保持部が形成されている、請求項1に記載のロータリ圧縮機。
- 前記軸受部材に設けられた第2凹部が前記区画部材で閉じられることによって前記冷媒吐出空間が形成されており、
前記区画部材が単一の板状部材で構成されており、
前記第1凹部及び前記第2凹部の両方が前記区画部材によって閉じられている、請求項2に記載のロータリ圧縮機。 - 前記オイル溜まりと前記オイル保持部とを連通する連通路をさらに備えた、請求項1に記載のロータリ圧縮機。
- 前記中心軸を含む平面であって、前記オイル保持部に接する2つの平面を接平面と定義し、前記接平面のなす角のうち、前記オイル保持部が位置している領域の角を2等分し、かつ前記中心軸を含む平面を前記オイル保持部の2等分平面と定義し、前記2等分平面によって分けられた前記オイル保持部の2つの部分のうち、前記ピストンの回転方向において相対的に前記吸入口の近くに位置している部分を前半部分、前記ピストンの回転方向において相対的に前記吸入口から遠くに位置している部分を後半部分と定義したとき、
前記連通路は、前記オイル溜まりと前記後半部分とを連通しており、
前記前半部分には、前記後半部分のみを通じて、前記オイル溜まりのオイルが浸入する、請求項4に記載のロータリ圧縮機。 - 前記オイル保持部は、前記ピストンの回転方向において相対的に前記吸入口の近くに位置している前半部分と、前記ピストンの回転方向において相対的に前記吸入口から遠くに位置している後半部分と、前記前半部分と前記後半部分との間に位置しているくびれ部分と、を有する、請求項1に記載のロータリ圧縮機。
- 前記オイル溜まりと前記オイル保持部とを連通する連通路をさらに備え、
前記連通路は、前記オイル溜まりと前記後半部分とを連通しており、
前記前半部分には、前記後半部分及び前記くびれ部分のみを通じて、前記オイル溜まりのオイルが浸入する、請求項6に記載のロータリ圧縮機。 - 前記軸受部材に設けられた第2凹部が前記区画部材で閉じられることによって前記冷媒吐出空間が形成されており、
前記第1凹部における前記軸受部材の肉厚が、前記第2凹部における前記軸受部材の肉厚よりも大きい、請求項1に記載のロータリ圧縮機。 - 前記中心軸に垂直な平面に前記冷媒吐出空間及び前記オイル保持部を投影することによって得られた投影図において、前記冷媒吐出空間に対応する領域の面積が前記オイル保持部に対応する領域の面積よりも小さい、請求項1に記載のロータリ圧縮機。
- (i)前記基準平面を第1基準平面、(ii)前記中心軸を含み、かつ前記第1基準平面に垂直な平面を第2基準平面、(iii)当該ロータリ圧縮機を前記第1基準平面及び前記第2基準平面で分けることによって得られた4つのセグメントのうち、前記吸入口を含むセグメントを第1象限セグメント、前記吐出口を含むセグメントを第2象限セグメント、前記第1象限セグメントの向かい側かつ前記第2象限セグメントに隣接するセグメントを第3象限セグメント、前記第2象限セグメントの向かい側かつ前記第1象限セグメントに隣接するセグメントを第4象限セグメントと定義したとき、
前記中心軸に垂直な平面に前記第1~第4象限セグメント及び前記冷媒吐出空間を投影することによって得られた投影図において、前記第1象限セグメントに対応する領域、前記第2象限セグメントに対応する領域及び前記第3象限セグメントに対応する領域を合計した領域の範囲内に前記冷媒吐出空間に対応する領域の全部が収まっている、請求項1に記載のロータリ圧縮機。 - (a)前記基準平面を第1基準平面、(b)前記吸入口の中心及び前記中心軸を含む平面を第3基準平面、(c)当該ロータリ圧縮機を前記第1基準平面で分けることによって得られた2つのセグメントのうち、前記吐出口を含むセグメントを第1高温セグメント、(d)当該ロータリ圧縮機を前記第3基準平面で分けることによって得られた2つのセグメントのうち、前記吐出口を含むセグメントを第2高温セグメント、(e)当該ロータリ圧縮機を前記第1基準平面及び前記第3基準平面で分けることによって得られた4つのセグメントのうち、前記第1高温セグメント及び前記第2高温セグメントのいずれかに含まれた3つのセグメントの合計を合計高温セグメントと定義したとき、
前記中心軸に垂直な平面に前記合計高温セグメント及び前記冷媒吐出空間を投影することによって得られた投影図において、前記冷媒吐出空間に対応する領域の70%以上が前記合計高温セグメントに対応する領域に重複している、請求項1に記載のロータリ圧縮機。 - 前記ピストンが取り付けられたシャフトをさらに備え、
前記ロータリ圧縮機は、前記シャフトの回転軸が重力方向に平行であり、かつ前記オイル溜まりが前記密閉容器の底部に形成されている縦型のロータリ圧縮機である、請求項1に記載のロータリ圧縮機。
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