JP2020186654A - Rotary compressor - Google Patents

Abstract

To provide a rotary compressor which is further improved in efficiency.SOLUTION: A rotary compressor has: a piston rotor 13A which turns around an eccentric shaft; a circular cylinder 12A for covering the piston rotor 13A; an upper bearing and a lower bearing which form a compression chamber C1 together with the cylinder 12A; and a blade B extending in a radial direction, movable in the radial direction in a state that a tip Bt abuts on an external peripheral face of the piston rotor 13A, and separating the compression chamber C1 to a low-pressure space Vl and a high-pressure space Vh. A plurality of fins F protruding from the external peripheral face are arranged in a range being a discharge part of a refrigerant, and when setting a rotation direction of a crankshaft as a forward direction, and a position in which the blade B is arranged as 0°, the range being the discharge part E is 180° to 360°.SELECTED DRAWING: Figure 2

Description

The present invention relates to a rotary compressor.

For example, a rotary compressor is known as a device used for compressing a refrigerant in an air conditioner. The rotary compressor includes a shaft, a piston rotor mounted on the eccentric portion of the shaft, a cylinder having a cylinder chamber for accommodating the piston rotor, and upper bearings and lower bearings arranged on both axial sides of the cylinder chamber. It is provided with a housing for accommodating these. In such a rotary compressor, it is known that the refrigerant becomes hot as it is compressed. If the heat of the high-temperature refrigerant propagates to, for example, the refrigerant before compression, the efficiency of the rotary compressor may decrease.

Therefore, for example, as described in Patent Document 1 below, it is conceivable to adopt a configuration in which fins as heat dissipation means are provided in the housing. In the compressor described in Patent Document 1, a plurality of heat radiation fins are provided on the outer peripheral surface of the housing accommodating the electric compression unit including the motor and the compressor main body.

Japanese Unexamined Patent Publication No. 2004-251133

By the way, in the rotary compressor as described above, the temperature of the refrigerant rises particularly at the portion (discharge portion) where the refrigerant is discharged in the cylinder chamber. This is because the compressed and high temperature refrigerant circulates in the portion. Therefore, it is expected that the thermal efficiency may be further improved by providing the heat radiating means to the portion where the temperature becomes particularly high. However, in the device described in Patent Document 1, heat radiation fins are provided only on the outer peripheral surface of the housing. Therefore, there is a possibility that the heat of the discharge portion cannot be efficiently dissipated. As a result, the efficiency of the rotary compressor is limited.

The present invention has been made to solve the above problems, and an object of the present invention is to provide a rotary compressor with further improved efficiency.

The rotary compressor according to one aspect of the present invention includes a crankshaft that can rotate around an axis, a compression unit in which a compression chamber that compresses a refrigerant by the rotation of the crankshaft is formed, the crankshaft, and the compression unit. A piston rotor that is provided on the crankshaft and swivels around the axis at a position eccentric from the axis, and an annular cylinder that covers the piston rotor from the outer peripheral side. The upper bearing and the lower bearing that form the compression chamber together with the cylinder by covering the cylinders from the axial direction, respectively, are arranged in the compression chamber, extend in the radial direction with respect to the axis, and the tip thereof is described. It has a blade that is movable in the radial direction while in contact with the outer peripheral surface of the piston rotor and separates the compression chamber into a low pressure space and a high pressure space, and serves as a discharge portion of the refrigerant in the compression portion. A plurality of fins protruding from the outer peripheral surface of the compression portion are provided in the range at intervals in the circumferential direction with respect to the axis line, and angular coordinates in which the rotation direction of the crankshaft is positive in a cross-sectional view orthogonal to the axis line. In the system, when the position where the blade is provided is 0 °, the range of the discharge portion is 180 ° to 360 °.

According to the above configuration, a plurality of fins protruding from the outer peripheral surface of the compression portion are provided at intervals in the circumferential direction in the range to be the discharge portion of the compression portion. The range of the discharge portion referred to here is a range of 180 ° to 360 ° when the position where the blade is provided is 0 ° and the rotation direction of the crankshaft is positive. In the discharge section of the compression section, the refrigerant that has been compressed to a high temperature and high pressure flows, so that the temperature is particularly likely to rise as compared with other sections. If this heat propagates, for example, to the refrigerant before compression, the efficiency of the rotary compressor will decrease. However, according to the above configuration, a plurality of fins are provided in the range of such a discharge portion. With these fins, the heat of the discharge portion can be dissipated. As a result, the possibility of heat being transferred to the refrigerant before compression can be reduced. Further, since the fins are provided in the discharge portion where the temperature becomes particularly high as described above, heat can be dissipated more efficiently than in the case where such fins are provided in other portions.

In the rotary compressor, the fins may have a plate shape extending in a direction orthogonal to the outer peripheral surface of the compression portion.

According to the above configuration, the fin has a plate shape extending in a direction orthogonal to the outer peripheral surface of the compression portion. As a result, a large fin area can be secured. As a result, the effect of heat dissipation by each fin can be further enhanced.

In the rotary compressor, the range of the discharge portion may be 240 ° to 360 °.

According to the above configuration, the range of the discharge portion is in the range of 240 ° to 360 °, where the position where the blade is provided is 0 °. In the compression section, the compression of the refrigerant progresses toward the front side in the rotation direction of the crankshaft with reference to the 0 ° position. Therefore, in the above range of 240 ° to 360 °, the temperature of the refrigerant becomes particularly high. By using this range as the discharge portion and providing, for example, fins or the like in the compression portion, the heat dissipation effect can be further enhanced.

The rotary compressor may further have a plurality of bearing fins provided at least one of the upper bearing and the lower bearing on a surface facing outward in the radial direction at intervals in the axial direction.

According to the above configuration, a plurality of bearing fins are provided at least one of the upper bearing and the lower bearing at intervals in the axial direction. Here, the upper bearing and the lower bearing form a part of the inner surface of the compression chamber. That is, the high-temperature and high-pressure refrigerant circulating in the compression chamber comes into contact with the upper bearing and the lower bearing. As a result, the heat of the refrigerant propagates, and the upper bearing and the lower bearing may also become hot. According to the above configuration, since the bearing fins are provided on at least one of the upper bearing and the lower bearing, the heat generated by the refrigerant can be efficiently dissipated through the bearing fins.

The rotary compressor further includes a plurality of first outer peripheral fins provided on the outer peripheral surface of the housing in a region corresponding to the compression portion in the axial direction and arranged at intervals in the axial direction. You may.

According to the above configuration, a plurality of first outer peripheral fins are provided on the outer peripheral surface of the housing in a region corresponding to the compression portion in the axial direction. As a result, the heat of the high-temperature and high-pressure refrigerant flowing through the compression portion can be efficiently dissipated toward the outside of the housing.

The rotary compressor further includes a motor for rotationally driving the crankshaft, is provided on the outer peripheral surface of the housing in a region corresponding to the motor in the axial direction, and is arranged at intervals in the axial direction. It may further have a plurality of second outer peripheral fins.

Here, with the continuous operation of the rotary compressor, the motor also generates heat correspondingly due to various factors such as internal resistance. If this heat propagates to, for example, the refrigerant before compression, it may hinder the efficient operation of the rotary compressor. However, according to the above configuration, the second outer peripheral fin is provided on the outer peripheral surface of the housing in the region corresponding to the motor in the axial direction. The second outer peripheral fin can efficiently dissipate the heat generated by the motor toward the outside of the housing.

According to the present invention, it is possible to provide a rotary compressor with further improved efficiency.

It is a vertical sectional view of the rotary compressor which concerns on 1st Embodiment of this invention. It is sectional drawing which shows the structure of a part of the compression part which concerns on 1st Embodiment of this invention. It is a vertical sectional view which shows a part of the rotary compressor which concerns on 2nd Embodiment of this invention. It is a vertical sectional view of the rotary compressor which concerns on 3rd Embodiment of this invention.

[First Embodiment]
The first embodiment of the present invention will be described with reference to FIGS. 1 and 2. As shown in FIG. 1, the rotary compressor 100 according to the present embodiment includes an accumulator 24, suction pipes 26A and 26B, and a compressor main body 10. The compressor body 10 includes a crankshaft 16 extending along the axis O, a motor 18 for rotating the crankshaft 16, a compression unit 10A for compressing a refrigerant as the crankshaft 16 rotates, a crankshaft 16, and a motor 18. And a housing 11 that covers the compression portion 10A.

The compression unit 10A includes piston rotors 13A and 13B (first piston rotor 13A, second piston rotor 13B) that rotate (rotate) at a position eccentric from the axis O as the crankshaft 16 rotates, and these first piston rotors. The cylinders 12A and 12B accommodating the 13A and the second piston rotor 13B, respectively, the upper bearing 17A and the lower bearing 17B rotatably supporting the crankshaft 16, and the compression chamber C formed in the cylinders 12A and 12B are provided. It has a blade B that separates into two spaces, and a plurality of fins F provided on the outer peripheral surface of the compression portion 10A.

The compression unit 10A is a so-called two-cylinder type rotary compressor in which disc-shaped cylinders 12A and 12B are provided in two upper and lower stages in a cylindrical housing 11. The housing 11 surrounds the cylinders 12A and 12B to form a discharge space V from which the compressed refrigerant is discharged. Inside the cylinders 12A and 12B, a cylindrical first piston rotor 13A and a second piston rotor 13B having an outer shape smaller than the inside of the inner wall surface of the cylinder are arranged, respectively. The first piston rotor 13A and the second piston rotor 13B are inserted and fixed to the crankshafts 14A and 14B (first crankshaft 14A, second crankshaft 14B) of the crankshaft 16, respectively.

The first piston rotor 13A of the cylinder 12A on the upper stage side and the second piston rotor 13B on the lower stage side are provided so that their phases differ from each other by 180 °. That is, the first piston rotor 13A is eccentric in the direction opposite to the eccentric direction of the second piston rotor 13B. Further, a disc-shaped partition plate 15 is provided between the upper and lower cylinders 12A and 12B. The space R in the cylinder 12A on the upper stage side and the space R on the lower stage side are partitioned from each other by the partition plate 15 to form compression chambers C1 and C2, respectively.

The cylinders 12A and 12B are fixed to the housing 11 by the upper bearing 17A and the lower bearing 17B. More specifically, the upper bearing 17A has a disk shape fixed to the upper part of the compression portion 10A, and its outer peripheral surface is fixed to the inner peripheral surface of the housing 11. The lower bearing 17B has a disk shape fixed to the lower part of the compression portion 10A, and its outer peripheral surface is fixed to the inner peripheral surface of the housing 11. The upper bearing 17A covers the cylinder 12A on the upper stage side from above (one side in the axis O direction). Further, the lower bearing 17B covers the lower cylinder 12B from below (the other side in the axis O direction). That is, the upper bearing 17A forms the above-mentioned compression chamber C1 together with the cylinder 12A and the partition plate 15, and the lower bearing 17B forms the above-mentioned compression chamber C2 together with the cylinder 12B and the partition plate 15. The rotary compressor 100 may have one cylinder instead of such two cylinders. In the case of one cylinder, the upper bearing 17A and the lower bearing 17B respectively cover both sides of the cylinder in the O-direction without providing the partition plate 15.

In the compressor main body 10, an accumulator 24 for gas-liquid separation of the refrigerant prior to supply to the compressor main body 10 is fixed to the housing 11 via a stay 25. Suction pipes 26A and 26B for sucking the refrigerant in the accumulator 24 into the compressor main body 10 are provided between the accumulator 24 and the compressor main body 10. One end of the suction pipes 26A and 26B is connected to the lower part of the accumulator 24, and the other end communicates with the suction ports 23A and 23B formed in the cylinders 12A and 12B through the openings 22A and 22B, respectively. A rotor 19A of a motor 18 for rotationally driving the crankshaft 16 is integrally provided on one end side of the crankshaft 16. A stator 19B is fixedly provided on the inner peripheral surface of the housing 11 so as to face the outer peripheral portion of the rotor 19A.

Subsequently, the internal configuration of the compression unit 10A will be described with reference to FIG. Since the cylinder 12A on the upper stage and the cylinder 12B on the lower stage have the same configuration as each other, the cylinder 12A on the upper stage will be typically described below. As shown in FIG. 2, the cylinder 12A has an annular cylinder body 12H centered on the axis O, and two overhanging portions P1 and P2 provided on the outer peripheral surface 12S of the cylinder body 12H. There is. The overhanging portions P1 and P2 extend in a fan shape from the outer peripheral surface 12S toward the outer side in the radial direction with respect to the axis O. The outer peripheral surfaces of the overhanging portions P1 and P2 are brought into contact with and fixed to the inner peripheral surface of the housing 11 by, for example, shrink fitting. The two overhanging portions P1 and P2 are provided at intervals in the circumferential direction with respect to the axis O. Further, the overhanging portion P1 has a larger size in the circumferential direction than the overhanging portion P2. The number and shape of these overhanging portions P1 and P2 may be appropriately determined according to the design and specifications.

The inner peripheral side of the cylinder body 12H is formed as the above-mentioned compression chamber C1 by opening in a circular shape about the axis O. The first piston rotor 13A is housed in the compression chamber C1. The blade B is supported in a state of being urged by an elastic member G with respect to the cylinder body 12H. The blade B is urged inward in the radial direction with respect to the axis O by the elastic member G. As a result, the tip Bt of the blade B is in a state of being in normal contact with the outer peripheral surface of the first piston rotor 13A. That is, when the first piston rotor 13A rotates eccentrically, the tip Bt of the blade B is in sliding contact with the outer peripheral surface of the first piston rotor 13A in a state of being urged by the elastic member G. The blade B itself is movable (movable) in the radial direction with respect to the axis O. The compression chamber C1 is separated into two spaces (high pressure space Vh and low pressure space Vl) by the blade B. More specifically, when the rotation direction (swivel direction) of the first piston rotor 13A is positive, the space on the front side of the rotation direction R with respect to the blade B is the high pressure space Vh, and the space on the rear side in the rotation direction is low pressure. It is said to be space Vl.

In the high-pressure space Vh, the refrigerant sent from the low-pressure space Vl side is compressed and distributed at a high temperature and high pressure. This high-temperature and high-pressure refrigerant is taken out from a discharge port (not shown) formed in the cylinder body 12H via a discharge space V in the housing 11. That is, the high-pressure space Vh side of the cylinder body 12H is exposed to the refrigerant having a higher temperature than the low-pressure space Vl side. In the present embodiment, the range exposed to such a high temperature refrigerant (the range referred to as the discharge portion E) is the first piston rotor 13A (crankshaft 16) with the circumferential position of the blade B set to 0 °. In the angular coordinate system in which the rotation direction of is positive, the range is 180 ° to 360 °. More preferably, the range of the discharge portion E is 240 ° to 360 °. That is, in the range of the discharge portion E in the cylinder body 12H, the temperature may be higher than that of other portions.

Therefore, in the present embodiment, a plurality of fins F are provided only in the range of the discharge portion E on the outer peripheral surface 12S of the cylinder body 12H. More specifically, these fins F have a plate shape extending in the radial direction from the outer peripheral surface 12S with respect to the axis O, and are arranged at equal intervals in the circumferential direction. Although the example of FIG. 2 shows a configuration in which eight fins F are provided, the number of fins F is not limited to eight, and may be seven or less or nine or more. Further, in the example of FIG. 2, a configuration in which the plurality of fins F are provided in a range of 240 ° to 360 °, which is more desirable as the angle range of the discharge portion E, is shown. However, the fin F may be provided at any circumferential position as long as it is within the range of 180 ° to 360 °, which is the discharge portion E.

Next, the operation of the rotary compressor 100 according to the present embodiment will be described. When operating the rotary compressor 100, the motor 18 is first driven by an external power supply. As the motor 18 is driven, the crankshaft 16 rotates around the axis O. As the crankshaft 16 rotates, the first crankshaft 14A and the second crankshaft 14B rotate around the central axis (axis O) of the crankshaft 16. The first piston rotor 13A and the second piston rotor 13B rotate eccentrically in the compression chambers C1 and C2 so as to follow this turning. The volume of the compression chambers C1 and C2 changes due to the eccentric rotation of the first piston rotor 13A and the second piston rotor 13B, and the refrigerant taken into the compression chambers C1 and C2 is compressed. The compressed refrigerant is taken out to the outside through the discharge space V in the housing 11.

Here, as described above, in the portion corresponding to the discharge portion E in the compression chambers C1 and C2, the temperature rise due to the high temperature and high pressure refrigerant is more likely to occur than in the other portions. If such heat propagates to, for example, the refrigerant before compression, the efficiency of the rotary compressor 100 may decrease. However, in the present embodiment, as described above, a plurality of fins F are provided in the range of the discharge portion E in the cylinder body 12H. The heat generated in the discharge portion E by these fins F is dissipated into the space inside the housing 11.

As described above, according to the above configuration, a plurality of fins F protruding from the outer peripheral surface of the compression portion 10A (the outer peripheral surface 12S of the cylinder body 12H) are peripheral to the range of the discharge portion E of the compression portion 10A. It is provided at intervals in the direction. The range of the discharge portion E referred to here is a range of 180 ° to 360 ° when the position where the blade B is provided is 0 ° and the rotation direction of the crankshaft 16 is positive. In the discharge section E of the compression section 10A, since the compressed refrigerant having a high temperature and high pressure flows, the temperature tends to rise particularly easily as compared with other sections. If this heat propagates to, for example, the refrigerant before compression, the efficiency of the rotary compressor 100 will decrease. However, according to the above configuration, a plurality of fins F are provided in a range that becomes such a discharge portion E. These fins F can dissipate the heat of the discharge portion E. As a result, the possibility of heat being transferred to the refrigerant before compression can be reduced. Further, since the fins are provided in the discharge portion E which becomes particularly hot as described above, the heat can be dissipated more efficiently as compared with the case where such fins F are provided in other parts. it can.

Further, according to the above configuration, the fin F has a plate shape extending in a direction orthogonal to the outer peripheral surface of the compression portion 10A (the outer peripheral surface 12S of the cylinder body 12H). As a result, a large area of the fin F can be secured. As a result, the effect of heat dissipation by each fin F can be further enhanced.

In addition, in the above configuration, the range of the discharge portion E is set to the range of 240 ° to 360 °, where the position where the blade is provided is 0 °. In the compression unit 10A, the compression of the refrigerant progresses toward the front side in the rotation direction of the crankshaft 16 with reference to the 0 ° position. Therefore, in the above range of 240 ° to 360 °, the temperature of the refrigerant becomes particularly high. By setting this range as the discharge portion E and providing the fins F along the discharge portion E, the heat dissipation effect can be further enhanced.

The first embodiment of the present invention has been described above. It should be noted that various changes and modifications can be made to the above configuration as long as the gist of the present invention is not deviated.

[Second Embodiment]
Next, the second embodiment of the present invention will be described with reference to FIG. The same components as those in the first embodiment are designated by the same reference numerals, and detailed description thereof will be omitted. As shown in FIG. 3, in the present embodiment, in addition to the fins F described above, bearing fins Fb are provided on the surfaces (outer peripheral surfaces Sa, Sb) of the upper bearing 17A and the lower bearing 17B facing outward in the radial direction. Has been done. It is also possible to adopt a configuration in which the bearing fins Fb are provided only on one of the upper bearing 17A and the lower bearing 17B. That is, the bearing fins F may be provided on at least one of the upper bearing 17A and the lower bearing 17B. The bearing fins Fb are arranged on the outer peripheral surfaces Sa and Sb at intervals in the axis O direction. That is, each bearing fin Fb has an annular shape centered on the axis O when viewed from the axis O direction.

According to the above configuration, a plurality of bearing fins Fb are provided on at least one of the upper bearing 17A and the lower bearing 17B at intervals in the axis O direction. Here, the upper bearing 17A and the lower bearing 17B form a part of the inner surface of the compression chamber C1 or C2. That is, the high-temperature and high-pressure refrigerant circulating in the compression chambers C1 and C2 comes into contact with the upper bearing 17A and the lower bearing 17B. As a result, the heat of the refrigerant propagates, and the upper bearing 17A and the lower bearing 17B may also become hot. According to the above configuration, since the bearing fins Fb are provided on at least one of the upper bearing 17A and the lower bearing 17B, the heat from the refrigerant can be efficiently dissipated through the bearing fins Fb. As a result, the efficiency of the rotary compressor 100 can be further improved.

The second embodiment of the present invention has been described above. It should be noted that various changes and modifications can be made to the above configuration as long as the gist of the present invention is not deviated.

[Third Embodiment]
Next, the third embodiment of the present invention will be described with reference to FIG. The same components as those of the above embodiments are designated by the same reference numerals, and detailed description thereof will be omitted. As shown in FIG. 4, in the present embodiment, in addition to the fins F of the discharge portion E described in the first embodiment, the outer peripheral surface 11S of the housing 11 has a plurality of first outer peripheral fins Fc1 and a plurality of first outer peripheral fins Fc1. Two outer peripheral fins Fc2 are provided. Specifically, these first outer peripheral fins Fc1 are provided on the outer peripheral surface 11S of the housing 11 in a region corresponding to (overlapping) the compression portion 10A in the axis O direction. Each of the first outer peripheral fins Fc1 forms an annular shape about the axis O and along the outer peripheral surface 11S of the housing 11. Such first outer peripheral fins Fc1 are arranged at equal intervals in the axis O direction.

Further, a plurality of second outer peripheral fins Fc2 are provided on the outer peripheral surface 11S of the housing 11 and in a region corresponding to (overlapping) the motor 18 in the axis O direction. Like the first outer peripheral fin Fc1, each second outer peripheral fin Fc2 has an annular shape centered on the axis O and along the outer peripheral surface 11S of the housing 11. Such second outer peripheral fins Fc2 are arranged at equal intervals in the axis O direction.

According to the above configuration, in addition to the heat dissipation effect of the fin F described in the first embodiment, the heat of the high-temperature and high-pressure refrigerant flowing through the compression portion 10A is dissipated toward the outside of the housing 11 through the first outer peripheral fin Fc1. Can be made to. Thereby, the efficiency of the rotary compressor 100 can be further improved.

Here, with the continuous operation of the rotary compressor 100, the motor 18 also generates heat correspondingly due to various factors such as internal resistance. If this heat propagates to, for example, the refrigerant before compression, it may hinder the efficient operation of the rotary compressor 100. However, according to the above configuration, the second outer peripheral fin Fc2 is provided on the outer peripheral surface 11S of the housing 11 in the region corresponding to the motor 18 in the axis O direction. The second outer peripheral fin Fc2 can efficiently dissipate the heat generated by the motor 18 toward the outside of the housing 11. As a result, the efficiency of the rotary compressor 100 can be further improved.

The third embodiment of the present invention has been described above. It should be noted that various changes and modifications can be made to the above configuration as long as the gist of the present invention is not deviated. For example, as a modification common to each embodiment, it is also possible to adopt a configuration in which the configurations of the above-mentioned first embodiment, second embodiment, and third embodiment are combined together. According to such a configuration, the efficiency of the rotary compressor 100 can be further improved.

100 ... Rotary compressor 10 ... Compressor body 10A ... Compressor 11 ... Housing 11S ... Outer surface 12A, 12B ... Cylinder 12H ... Cranker body 12S ... Outer surface 13A ... First piston rotor 13B ... Second piston rotor 14A ... First crankshaft 14B ... Second crankshaft 16 ... Crankshaft 17A ... Upper bearing 17B ... Lower bearing 18 ... Motor 19A ... Rotor 19B ... Stator 22A, 22B ... Opening 23A, 23B ... Suction port 24 ... Accumulator 25 ... Stay 26A, 26B ... Suction pipe B ...・ ・ Blade Bt ・ ・ ・ Tip C, C1, C2 ・ ・ ・ Compressor chamber E ・ ・ ・ Discharge part F ・ ・ ・ Fin Fb ・ ・ ・ Bearing fin Fc1 ・ ・ ・ First outer peripheral fin Fc2 ・ ・ ・ Second outer circumference Fin G ... Elastic member O ... Axis lines P1, P2 ... Overhanging part R ... Rotation direction Sa, Sb ... Outer peripheral surface V ... Discharge space Vh ... High pressure space Vl ...・ Low pressure space

Claims (6)

A crankshaft that can rotate around the axis and
A compression unit in which a compression chamber for compressing the refrigerant is formed by the rotation of the crankshaft, and
A housing that houses the crankshaft and the compression unit,
With
The compression unit is
A piston rotor provided on the crankshaft and swiveling around the axis at a position eccentric from the axis.
An annular cylinder that covers the piston rotor from the outer peripheral side,
An upper bearing and a lower bearing that form the compression chamber together with the cylinder by covering the cylinder from the axial direction, respectively.
The compression chamber is separated into a low pressure space and a high pressure space by being arranged in the compression chamber, extending in the radial direction with respect to the axis, and being movable in the radial direction with the tip abutting on the outer peripheral surface of the piston rotor. Blade and
Have,
A plurality of fins protruding from the outer peripheral surface of the compression portion are provided in the range of the compression portion to be the discharge portion of the refrigerant at intervals in the circumferential direction with respect to the axis.
In a cross-sectional view orthogonal to the axis, in an angular coordinate system in which the rotation direction of the crankshaft is positive, when the position where the blade is provided is 0 °, the range of the discharge portion is 180 ° to 360 °. A rotary compressor that is. The rotary compressor according to claim 1, wherein the fins have a plate shape extending in a direction orthogonal to the outer peripheral surface of the compression portion. The rotary compressor according to claim 1 or 2, wherein the discharge portion has a range of 240 ° to 360 °. The invention according to any one of claims 1 to 3, further comprising a plurality of bearing fins provided at least one of the upper bearing and the lower bearing facing outward in the radial direction at intervals in the axial direction. Rotary compressor. The first to fourth aspects of the housing, further comprising a plurality of first outer peripheral fins provided in a region corresponding to the compression portion in the axial direction and arranged at intervals in the axial direction. The rotary compressor according to any one item. Further equipped with a motor for rotationally driving the crankshaft,
Any of claims 1 to 5, which is an outer peripheral surface of the housing and further has a plurality of second outer peripheral fins provided in a region corresponding to the motor in the axial direction and arranged at intervals in the axial direction. The rotary compressor described in item 1.

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