JP2007321703A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor which suppresses noise and vibration due to delivery pulsation with a simple structure. <P>SOLUTION: An outer rotor type motor 1 arranged in a hermetic vessel 1 and driving a compression part 2 via a shaft 4, includes: a stator 21 including a coil 22; a roughly cylindrical rotor 25 arranged on an outer circumference of the stator 21 via an air gap; and a roughly disk shape rotor retaining member 26 for fixing one end of the rotor 25 on the shaft 4. The outer rotor type motor 1 is arranged in a high pressure region in the hermetic vessel 1 filled with high pressure refrigerant delivered from the compression part 2, and a delivery port 23 of the compression part 2 is arranged between the compression part 2 and the outer rotor type delivery port 23. A delivery pipe 12 for delivering high pressure refrigerant to an outside from the high pressure region in the hermetic vessel 1, is provided in an opposite side of the compression part 2 in relation to the outer rotor type motor 1. The rotor retaining member 26 is provided with a first though hole 30 in which refrigerant flows outward from an inside of the rotor 25. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a compressor, and more particularly, to a compressor using an outer rotor type motor.

  An inner rotor type motor is used in a conventional hermetic compressor. Since this inner rotor type motor holds the stator in a closed state inside the sealed container, vibration noise has been reduced by increasing the rigidity of the sealed container.

  On the other hand, there is one using an outer rotor type motor as a hermetic compressor (see, for example, Japanese Patent Application Laid-Open No. 2004-301038 (Patent Document 1)). In the compressor using the outer rotor type motor, since the stator of the outer rotor type motor is not rubbed over the entire length of the inside of the hermetic container, the rigidity of the hermetic container is lowered similarly to the hollow tube. Due to such a reduction in rigidity of the sealed container, there is a problem that the natural frequency of the sealed container is lowered and, for example, resonates with the first-order rotation and an integral multiple of the vibration to increase vibration and noise. In particular, the primary pulsation of the largest rotation in the compressor is the discharge pulsation.

In the compressor using the outer rotor type motor described in Patent Document 1, since the discharge pipe is provided in the upper part of the motor, when the configuration for discharging the refrigerant from the rotation shaft is selected, the rotation shaft Since the high-pressure refrigerant discharged from the lower end directly vibrates the inside of the sealed container, vibration and noise increase.
JP 2004-301038 A

  Accordingly, an object of the present invention is to provide a compressor capable of reducing vibration and noise due to discharge pulsation with a simple configuration.

In order to solve the above problems, the compressor of the present invention is:
A sealed container;
A compression section disposed in the sealed container;
An outer rotor type motor arranged in the sealed container and driving the compression part via a shaft;
The outer rotor type motor includes a stator having a coil, a substantially cylindrical rotor disposed on the outer periphery of the stator via an air gap, and a substantially disk shape for fixing one end of the rotor to the shaft. A rotor holding member,
Disposed in the high-pressure region in the closed container filled with the high-pressure refrigerant discharged from the compression unit,
A discharge port of the compression unit is disposed between the compression unit and the outer rotor type motor,
A discharge pipe for discharging the high-pressure refrigerant to the outside from a high-pressure region in the sealed container is provided on the side opposite to the compression unit with respect to the outer rotor type motor of the sealed container,
A refrigerant passage through which refrigerant flows from the inner side to the outer side of the rotor is provided in at least one of the rotor or the rotor holding member.

  According to the compressor having the above-described configuration, the high-pressure refrigerant discharged from the discharge port of the compression unit is once guided into the rotor, the discharge pulsation is reduced by using the inside of the rotor as a muffler, and then the refrigerant passage is provided from the inside to the outside of the rotor. By flowing through, the vibration and noise of the sealed container due to the discharge pulsation can be reduced with a simple configuration.

  Moreover, in the compressor of one Embodiment, the said rotor holding member is arrange | positioned with respect to the said rotor on the opposite side to the said compression part.

  According to the compressor of the above embodiment, the rotor holding member is disposed on the side opposite to the compression portion with respect to the rotor, thereby forming the substantially cylindrical rotor and the substantially disk-shaped rotor holding member. The bottomed cylindrical body is covered with the stator from the side opposite to the compression portion with respect to the stator, so that the high-pressure refrigerant from the discharge port of the compression portion is discharged into the bottomed cylindrical body, and the muffler effect Can be increased.

  In the compressor according to an embodiment, the refrigerant passage is at least a first through hole provided so as to penetrate in the axial direction at least radially inward of the coil of the stator of the rotor holding member. .

  According to the compressor of the above embodiment, by providing the first through hole as the refrigerant passage so as to penetrate in the axial direction at least radially inward of the stator holding coil of the rotor holding member, the discharge port of the compression unit The high-pressure refrigerant discharged from the rotor into the rotor passes through, for example, the air gap, the refrigerant passage hole of the stator, the gap between the coils, and the like, and then passes through the first through hole of the rotor holding member positioned radially inward from the coil. And flows out from the inside of the rotor to the outside. Therefore, the flow of the refrigerant in the rotor is bent in a complicated manner to increase the muffler effect, and before the high-pressure refrigerant reaches the first through hole, the oil contained in the refrigerant is blown outward in the radial direction by the centrifugal force of the rotor holding member. Oil separation.

  In one embodiment of the compressor, the refrigerant passage is at least a second through hole provided in the rotor so as to penetrate from the radially inner side to the radially outer side.

  According to the compressor of the above embodiment, the high pressure discharged into the rotor from the discharge port of the compression unit by providing the second through hole as a refrigerant passage so as to penetrate the rotor from the radially inner side to the radially outer side. The refrigerant flows out from the inside of the rotor to the outside through the second through hole, for example, after passing through an air gap, a refrigerant passage hole of the stator, a gap between the coils, or the like. At this time, since the refrigerant flows obliquely downward from the second through hole of the rotor, the upward component of the flow of the high pressure refrigerant flowing from the inside of the rotor to the outside is reduced, and the high pressure refrigerant flowing out of the second through hole of the rotor is reduced by the rotor. The oil collides with the inner wall of the sealed container due to the centrifugal force, the oil contained in the refrigerant adheres to the inner wall of the sealed container, and the attached oil flows down to perform oil separation.

In the compressor of one embodiment,
The outer rotor type motor is disposed above the compression unit in the sealed container,
The second through hole is provided in the rotor obliquely downward from a radially inner side to a radially outer side.

  According to the compressor of the above embodiment, by providing the second through hole obliquely downward from the radially inner side to the radially outer side of the rotor, the refrigerant flows obliquely downward from the second through hole of the rotor. The upward component of the refrigerant flow can be reduced as much as possible to increase the downward component, and oil return downward can be promoted.

  Moreover, in the compressor of one Embodiment, the said 2nd through-hole is provided in the said rotor holding member side rather than the stator core of the said stator of the said rotor.

  According to the compressor of the above embodiment, by providing the second through hole on the rotor holding member side with respect to the stator of the rotor, the path of the refrigerant flowing in the rotor becomes longer, so the muffler effect can be enhanced. . Furthermore, since the refrigerant passes through the entire length of the stator, the effect of cooling the stator by the refrigerant is also obtained.

In the compressor of one embodiment,
The second through hole is plural,
The plurality of second through holes are arranged at irregular intervals in the circumferential direction on the rotor.

  According to the compressor of the above embodiment, by arranging the plurality of second through holes in the rotor at unequal intervals in the circumferential direction, vibration due to refrigerant discharge from the plurality of second through holes is inherent to the sealed container. It is difficult to enter the vibration mode, and vibration due to more effective discharge pulsation can be suppressed.

In the compressor of one embodiment,
The number of poles of the outer rotor type motor and the number of the second through holes are disjoint,
The second through holes are arranged at equal intervals in the circumferential direction on the rotor.

  According to the compressor of the above embodiment, the number of poles of the outer rotor type motor and the number of second through holes are relatively prime (a relationship in which two integers do not have a common divisor other than 1), By arranging the second through holes in the rotor at equal intervals in the circumferential direction, the vibration mode due to rotor deformation accompanying the magnetic pole change during rotor rotation does not match the vibration mode due to refrigerant discharge from the second through hole. Vibration and noise can be further reduced.

In the compressor of one embodiment,
The outer rotor type motor has permanent magnets arranged at intervals in the circumferential direction on the rotor,
The second through hole is disposed in a portion where the permanent magnet does not exist between the adjacent permanent magnets.

  According to the compressor of the above embodiment, by arranging the second through hole in a portion between the permanent magnets arranged at intervals in the circumferential direction on the rotor (portion where no permanent magnet exists), It is possible to reduce the influence on the magnetic circuit formed by the stator and the rotor without performing unnecessary processing on the magnetic pole surface.

In the compressor of one embodiment,
The second through hole is plural,
The plurality of second through holes are respectively arranged so that the positions in the axial direction are different from the rotor.

  According to the compressor of the above embodiment, by arranging the plurality of second through holes so that the positions in the axial direction are different from each other in the rotor, the vibration mode by the refrigerant discharge from the second through holes is complicated, By making it difficult to excite the vibration mode of a simple ring with a low natural frequency, vibration and noise can be further reduced.

  In the compressor according to an embodiment, the refrigerant passage may cancel the rotor or the rotor holding member so as to cancel at least a part of the imbalance of the rotation mechanism including the rotor, the rotor holding member, and the shaft. Of at least one of the two.

  According to the compressor of the above embodiment, the refrigerant passage is provided in at least one of the rotor and the rotor holding member so as to cancel at least a part of the imbalance of the rotation mechanism including the rotor, the rotor holding member, and the shaft. Thus, for example, by adjusting the position, number, and size of the refrigerant passage, it can serve as a balance weight, and the configuration can be simplified.

  As is clear from the above, according to the compressor of the present invention, the high-pressure refrigerant discharged from the discharge port of the compression unit is guided into the rotor, and flows through the refrigerant passage from the inside to the outside of the rotor. With a simple structure, vibration and noise of the sealed container due to discharge pulsation can be reduced.

  Further, according to the compressor of one embodiment, the rotor holding member is disposed on the side opposite to the compression portion with respect to the rotor, and is formed by a substantially cylindrical rotor and a substantially disc-shaped rotor holding member. The muffler effect which suppresses discharge pulsation can be heightened by making the bottomed cylindrical body cover the stator from the side opposite to the compression portion with respect to the stator.

  Further, according to the compressor of one embodiment, the first through hole is provided as the refrigerant passage so as to penetrate in the axial direction at least radially inward of the stator holding coil of the rotor holding member. The muffler effect is enhanced by the complicated bending of the flow of the refrigerant, and the oil contained in the refrigerant is blown outward in the radial direction by the centrifugal force of the rotor holding member, so that the oil can be separated.

  Further, according to the compressor of one embodiment, the second through hole is provided as a refrigerant passage so as to penetrate the rotor from the radially inner side to the radially outer side, whereby the high-pressure refrigerant flowing out from the inner side of the rotor to the outer side. While reducing the upward component of the flow, the high-pressure refrigerant that has flowed from the inside of the rotor to the outside through the second through-hole collides with the inner wall of the sealed container due to the centrifugal force of the rotor, and the oil attached to the inner wall of the sealed container Oil can be separated by flowing down.

  Further, according to the compressor of one embodiment, by providing the second through hole in the rotor obliquely downward from the radially inner side to the radially outer side, the upward component of the refrigerant flow is reduced as much as possible to increase the downward component. , The oil return downward can be promoted.

  Further, according to the compressor of one embodiment, since the second through hole of the rotor is provided on the rotor holding member side with respect to the stator, the path of the refrigerant flowing in the rotor becomes longer, so that the muffler effect is enhanced. In addition, since the refrigerant passes through the entire length of the stator, the effect of cooling the stator by the refrigerant is also obtained.

  Moreover, according to the compressor of one embodiment, the plurality of second through holes are arranged in the rotor at irregular intervals in the circumferential direction, so that vibration due to refrigerant discharge from the plurality of second through holes is hermetically sealed. The natural vibration mode is less likely to occur, and vibration due to more effective discharge pulsation can be suppressed.

  Further, according to the compressor of one embodiment, the number of poles of the outer rotor type motor and the number of second through holes are mutually prime, and the second through holes are arranged in the rotor at equal intervals in the circumferential direction. As a result, the vibration mode due to the rotor deformation accompanying the magnetic pole change during the rotation of the rotor and the vibration mode due to the refrigerant discharge from the second through hole can be prevented from matching, and vibration and noise can be further reduced.

  Further, according to the compressor of one embodiment, by arranging the second through hole in a portion between the permanent magnets arranged at intervals in the circumferential direction of the rotor (portion where no permanent magnet is present), Unnecessary processing is not performed on the magnetic pole surface of the magnet, and the influence on the magnetic circuit formed by the stator and the rotor can be reduced.

  Further, according to the compressor of one embodiment, the plurality of second through holes are arranged in the rotor so that the positions in the axial direction are different from each other, thereby complicating the vibration mode due to the refrigerant discharge from the second through holes. Thus, vibration and noise can be further reduced by making it difficult to excite a simple ring vibration mode having a low natural frequency.

  According to the compressor of one embodiment, the refrigerant passage is provided in at least one of the rotor and the rotor holding member so as to cancel at least a part of the unbalance of the rotating mechanism including the rotor, the rotor holding member, and the shaft. By providing, it can play the role of a balance weight, and the configuration can be simplified.

  Hereinafter, the compressor of the present invention will be described in detail with reference to the illustrated embodiments.

(First embodiment)
FIG. 1 shows a sectional view of a compressor according to a first embodiment of the present invention.

  As shown in FIG. 1, the compressor according to the first embodiment is disposed in a sealed container 1, a compression unit 2 disposed in the sealed container 1, and in the sealed container 1 and above the compression unit 2. And an outer rotor type motor 3 that drives the compression unit 2 via a shaft 4. A suction pipe 11 is connected to the lower side of the sealed container 1, while a discharge pipe 12 is connected to the upper side of the sealed container 1. The refrigerant gas supplied from the suction pipe 11 is guided to the suction side of the compression unit 2. The outer rotor type motor 3 is disposed in a high-pressure region in the sealed container 1 that is filled with a high-pressure refrigerant discharged from the discharge port 13 of the compression unit 3. This compressor is a high-pressure dome type.

  The outer rotor type motor 3 has a part on the outer peripheral side fixed inside the sealed container 1, a stator 21 through which the shaft 4 penetrates the center part, and a radial outer side of the stator 21, and is fitted on the shaft 4. And a fixed rotor 25. The rotor 25 is fixed to the shaft 4 via a rotor holding member 26 on the side opposite to the compression portion 2 with respect to the rotor 25. The lower end side of the shaft 4 is connected to the compression unit 2.

  The stator 21 has a stator core 23 attached to the inner wall of the hermetic container 1 via a stator holding mechanism 24 and a spacer 29, and a coil 22 attached to the stator core 23. The spacer 29 is provided with a plurality of refrigerant passages (not shown) in the radial direction. A plurality of holes 24 a penetrating in the axial direction are provided on the inner side of ½ of the outer diameter of the stator holding mechanism 24. Further, a notch 24 b serving as an oil return passage is provided outside the stator holding mechanism 24. The high-pressure refrigerant discharged from the discharge port 13 of the compression unit 3 flows into the rotor 25 through the muffler unit 10 and the plurality of holes 24 a of the stator holding mechanism 24. The stator core 23 is provided with a coil end storage portion in which a portion around which the coil 22 is wound has a smaller axial length than other portions.

  The rotor 25 has an annular rotor core 28 and a plurality of permanent magnets 27 embedded in a plurality of permanent magnet embedding holes (not shown) provided in the rotor core 28 in the axial direction. When the rotor holding member 26 is a magnetic body, the permanent magnet 27 and the portion on the inner peripheral side of the permanent magnet of the rotor core are separated from the member holding the stator 21 in order to prevent leakage of the magnetic flux of the permanent magnet. Is desirable.

  The rotor core 28 is made of a magnetic material and is made of a plurality of electromagnetic steel plates stacked in the axial direction. The permanent magnet 27 has different magnetic poles alternately in the circumferential direction toward the inner peripheral surface of the rotor 25. The permanent magnet 27 generates a magnetic flux toward the radially inner side.

  A plurality of first through holes 30 (only two are shown in FIG. 1) penetrating in the axial direction are provided as refrigerant passages on the inner side in the radial direction than the coil 22 of the stator 21 of the rotor holding member 26.

  The compression unit 2 includes a cylindrical main body 20 and an upper end plate 8 and a lower end plate 9 attached to the upper and lower open ends of the main body 20. The shaft 4 passes through the upper end plate 8 and the lower end plate 9 and is inserted into the main body 20. The shaft 4 is rotatably supported by a bearing 41 provided on the upper end plate 8 of the compression unit 2 and a bearing 42 provided on the lower end plate 9 of the compression unit 2. A crank pin 5 is provided on the shaft 4 in the main body 20, and a roller 6 fitted to the crank pin 5 is arranged so as to be capable of revolving. By the revolving motion of the roller 6, the compression is performed by the compression chamber 7 formed between the outer peripheral surface of the roller 6 and the inner peripheral surface of the main body portion 20. Note that, depending on the mechanism, the roller 6 may be rotated instead of revolving.

  In the compressor configured as described above, when the compression unit 2 is driven by rotating the outer rotor type motor 3, the refrigerant gas is supplied from the suction pipe 11 to the compression unit 2, and the refrigerant gas is compressed by the compression unit 2. Thus, the high-pressure refrigerant gas compressed by the compression unit 2 is discharged into the rotor 25 from the discharge port 13 of the compression unit 2. The high-pressure refrigerant gas discharged from the discharge port 13 of the compression unit 2 into the rotor 25 is a hole penetrating in the axial direction between the muffler unit 10, the air gap, and the coil 22 as shown by an arrow R <b> 1 in FIG. 1. (Not shown), an upper space of the outer rotor type motor 3 through the first through hole 30 of the rotor holding member 26 through a hole (not shown) penetrating in the axial direction in the vicinity of the shaft 4 of the stator 21. And then discharged to the outside of the sealed container 1 through the discharge pipe 12.

  In FIG. 1, the refrigerant flow in the right portion in the rotor 25 is indicated by the arrow R <b> 1, but the refrigerant flow in the left portion in the rotor 25 is the same.

  According to the compressor of the first embodiment, the high-pressure refrigerant discharged from the discharge port 13 of the compression unit 2 is guided to the inside of the rotor 25 and flows from the inside of the rotor 25 to the outside through the first through hole 30. Thus, vibration and noise of the sealed container due to discharge pulsation can be reduced with a simple configuration.

  Further, the rotor holding member 26 is disposed on the side opposite to the compression portion 2 with respect to the rotor 25, thereby forming a bottomed portion formed by the substantially cylindrical rotor 25 and the substantially disc-shaped rotor holding member 26. The muffler effect for suppressing discharge pulsation can be enhanced by covering the stator 21 with the stator 21 from the side opposite to the compression portion 2 with respect to the stator 21. In addition, although the muffler part 10 is provided in the discharge port 13, this muffler is arbitrary. When the muffler unit 10 is provided, the muffler has two stages, and the silencing effect is increased.

  In addition, the flow of the refrigerant in the rotor 25 is complicated by providing the first through hole 30 as a refrigerant passage so as to penetrate in the axial direction inward of the coil 22 of the stator 21 of the rotor holding member 26 in the radial direction. The muffler effect is enhanced by bending, and the oil contained in the refrigerant is blown outward in the radial direction by the centrifugal force of the rotor holding member 26, so that oil separation can be performed. Furthermore, since the refrigerant penetrates the stator 21, the stator can be cooled.

(Second embodiment)
FIG. 2A shows a cross-sectional view of a compressor according to a second embodiment of the present invention. The compressor of this 2nd Embodiment is carrying out the structure same as the compressor of 1st Embodiment except an outer rotor type | mold motor, and the same structure part attaches | subjects the same reference number.

  As shown in FIG. 2A, the compressor according to the second embodiment is disposed in a sealed container 1, a compression unit 2 disposed in the sealed container 1, and in the sealed container 1 and above the compression unit 2. And an outer rotor type motor 103 that drives the compression unit 2 via the shaft 4. A suction pipe 11 is connected to the lower side of the sealed container 1, while a discharge pipe 12 is connected to the upper side of the sealed container 1. The refrigerant gas supplied from the suction pipe 11 is guided to the suction side of the compression unit 2. The outer rotor type motor 103 is arranged in a high pressure region in the sealed container 1 filled with a high pressure refrigerant discharged from the discharge port 13 of the compression unit 3.

  The outer rotor type motor 103 is partly fixed to the inner side of the sealed container 1, and is arranged on the upper side in the axial direction of the stator 121 and the stator 121 through which the shaft 4 penetrates the center portion. And a rotor 125 fitted and fixed. The rotor 125 is fixed to the shaft 4 via a rotor holding member 126 on the side opposite to the compression portion 2 with respect to the rotor 125. The lower end side of the shaft 4 is connected to the compression unit 2.

  The stator 121 includes a stator core 123 attached to the inner wall of the hermetic container 1 via a stator holding mechanism 24 and a spacer 129, and a coil 122 attached to the stator core 123. The spacer 29 is provided with a plurality of refrigerant passages (not shown) in the radial direction. Unlike FIG. 1, the stator core 123 has the same axial length in both the coil winding portion and the other portions, and can be easily manufactured by laminating steel plates in the axial direction.

  The rotor 125 has an annular rotor core 128 and a plurality of permanent magnets 127 attached to the inner peripheral side of the rotor core 128. Permanent magnet 127 is provided only at a portion facing stator core 123.

  The rotor 125 is provided with a plurality of second through holes 131 and 132 (only two are shown in FIG. 2A) penetrating from the radially inner side to the radially outer side as refrigerant passages.

  In the compressor configured as described above, when the compression unit 2 is driven by rotating the outer rotor type motor 103, the refrigerant gas is supplied from the suction pipe 11 to the compression unit 2, and the compression unit 2 compresses the refrigerant gas. Thus, the high-pressure refrigerant gas compressed by the compression unit 2 is discharged into the rotor 125 from the discharge port 13 of the compression unit 2. The high-pressure refrigerant gas discharged from the discharge port 13 of the compression unit 2 into the rotor 125 passes through the muffler unit 10, the air gap, and the coil 122 in the axial direction as shown by an arrow R <b> 2 in FIG. 2A. (Not shown), an upper space of the outer rotor type motor 103 through the second through holes 131 and 132 of the rotor 125 through a hole (not shown) passing through the vicinity of the shaft 4 of the stator 121 in the axial direction. And then discharged to the outside of the sealed container 1 through the discharge pipe 12.

  In FIG. 2A, the refrigerant flow in the right part in the rotor 125 is indicated by the arrow R2, but the refrigerant flow in the left part in the rotor 125 is the same. In addition, as shown in FIG. 1, you may have a refrigerant | coolant channel | path also inside a stator coil of a stator holding member.

  The compressor according to the second embodiment has the same effect as the compressor according to the first embodiment.

  Further, by providing a plurality of second through holes 131 and 132 as refrigerant passages so as to penetrate the rotor 125 from the radially inner side to the radially outer side, the upward flow of the high-pressure refrigerant flowing from the inner side to the outer side of the rotor 125 is increased. While reducing the components, the high-pressure refrigerant that flows out from the inside of the rotor 125 through the second through holes 131 and 132 collides with the inner wall of the sealed container 1 by the centrifugal force of the rotor 125 and adheres to the inner wall of the sealed container 1. Oil separation can be performed by the oil flowing down.

  In the compressor according to the second embodiment, the plurality of second through holes are arranged in the rotor at irregular intervals in the circumferential direction so that the vibration caused by the refrigerant discharge from the plurality of second through holes is a natural vibration mode. This makes it possible to suppress the discharge pulsation more effectively.

  FIG. 2B shows a modification of the outer rotor type motor of the compressor, and this outer rotor type motor has the same configuration as the outer rotor type motor shown in FIG. 2A except for the second through hole. .

  As shown in FIG. 2B, the outer rotor type motor 203 has a stator 221 in which a part of the outer peripheral side is fixed inside the sealed container 1, the shaft 4 passes through the center portion, and an axially upper side of the stator 221. And a rotor 225 that is externally fitted and fixed to the shaft 4. The rotor 225 is fixed to the shaft 4 via a rotor holding member 226. The lower end side of the shaft 4 is connected to the compression portion 2 (see FIG. 2A).

  The stator 221 has a stator core 223 attached to the inner wall of the hermetic container 1 via the stator holding mechanism 24 and a coil 222 attached to the stator core 223.

  The rotor 225 includes an annular rotor core 228 and a plurality of permanent magnets 227 embedded on the inner peripheral side of the rotor core 228.

  The rotor 225 is provided with a plurality of second through holes 231 and 232 that penetrate obliquely downward from the radially inner side to the radially outer side as refrigerant passages.

  By providing the rotor 225 with second through holes 231 and 232 (only two are shown in FIG. 2B) obliquely downward from the radially inner side to the radially outer side, the upward component of the refrigerant flow is reduced as much as possible. Can be increased to promote downward oil return.

(Third embodiment)
FIG. 3 is an exploded perspective view of the main part of the outer rotor type motor of the compressor according to the third embodiment of the present invention. The compressor of the third embodiment has the same configuration as that of the compressor of the first embodiment except for the outer rotor type motor.

  This outer rotor type motor has a stator 21 (shown in FIG. 1) in which a part of the outer peripheral side is fixed inside the sealed container 1 (shown in FIG. 1), and a shaft 4 (shown in FIG. 1) passes through the center. And a rotor 325 which is disposed on the upper side of the stator 21 in the axial direction and is fitted on and fixed to the shaft 4. The rotor 325 is fixed to the shaft 4 via a rotor holding member 326.

  As shown in FIG. 3, the rotor 325 includes an annular rotor core 328 and a plurality of permanent magnets 327 embedded in a plurality of permanent magnet embedding holes 340 provided in the rotor core 328 in the axial direction. ing. The rotor core 328 may be made of steel plates laminated in the axial direction, but in that case, at least two types of molds are required. Alternatively, the portion excluding the yoke portion may be made of a steel plate laminated in the axial direction, and only the yoke portion may be a separate member.

  At the end of the rotor 325 on the rotor holding member 326 side, notches 330 as an example of a plurality of second through holes that are refrigerant passages penetrating from the radially inner side to the radially outer side are provided.

  Further, the number of poles 8 of the outer rotor type motor and the number 5 of the second through holes 330 are relatively prime, and the second through holes 330 are arranged in the rotor core 328 at equal intervals in the circumferential direction.

  FIG. 4 is an exploded perspective view showing a state where a permanent magnet is incorporated in the rotor of the outer rotor type motor, and FIG. 5 is a perspective view after the rotor of the outer rotor type motor is assembled.

  The compressor according to the third embodiment has the same effects as the compressor according to the first embodiment.

  Further, by providing the second through hole (notch 330) on the rotor holding member 326 side of the rotor 325 from the stator 321, the path of the refrigerant flowing through the rotor 325 becomes longer, so that the muffler effect can be enhanced. it can.

  Further, the number of poles of the outer rotor type motor and the number of second through holes are prime to each other, and the number of poles of the outer rotor type motor is set to 8 and the number of second through holes is set to 5. By arranging the through-holes (notches 330) in the rotor 325 at equal intervals in the circumferential direction, the vibration mode due to the rotor deformation accompanying the magnetic pole change during the rotation of the rotor and the refrigerant from the second through-holes (notches 330). The vibration mode by discharge can be made not to match, and vibration and noise can be further reduced.

(Fourth embodiment)
FIG. 6 is an exploded perspective view of the main part of the outer rotor type motor of the compressor according to the fourth embodiment of the present invention. The compressor of this 4th Embodiment is carrying out the structure same as the compressor of 1st Embodiment except an outer rotor type | mold motor, and attaches | subjects the same structure part to the same reference number, and abbreviate | omits description. The suction force of the rotor and stator of the outer rotor type motor of the compressor of the fourth embodiment acts at eight locations at equal intervals in the circumferential direction, but the excitation force due to discharge acts at five locations to excite vibrations. The mode is complicated to avoid resonance with a low-order (small natural frequency) mode. Or even if it is the same 8 places or 4 places, it is not provided at equal intervals, but the same effect is acquired.

  This outer rotor type motor has a stator 21 (shown in FIG. 1) in which a part of the outer peripheral side is fixed inside the sealed container 1 (shown in FIG. 1), and a shaft 4 (shown in FIG. 1) passes through the center. And a rotor 425 which is disposed on the upper side of the stator 21 in the axial direction and is fitted on and fixed to the shaft 4. The rotor 425 is fixed to the shaft 4 via a rotor holding member 426.

  As shown in FIG. 6, the rotor 425 includes a substantially cylindrical rotor core 428 in which six C-shaped core members 428 </ b> A to 428 </ b> F are stacked, and a substantially rectangular plate-like shape attached to the inside of the rotor core 428. Eight permanent magnets 427 are included. The C-shaped core members 428A to 428F are provided with notches (only 428B, 428C, 428D, and 428E are shown in FIG. 6) as second through holes, and the notches (428B, 428C, 428D, and 428E) are provided. ) Are stacked so that the positions in the circumferential direction are different. The inner circumference of the rotor core 428 in which the core members 428A to 428F are stacked has a substantially 16-corner cross section in which long sides and short sides are alternately arranged in the circumferential direction, and a permanent magnet 427 is attached to the long side. The second through holes (notches 428B, 428C, 428D, 428E) are arranged on the short side. Note that the cutout may be surrounded by a thin portion at the top and bottom. If it does so, the intensity | strength of core member 428A-428F can be increased.

  FIG. 7 is an exploded perspective view showing a state in which the rotor 428 and the permanent magnet 427 of the outer rotor type motor are incorporated. As shown in FIG. 7, the notches 428A to 428F of the core members 428A to 428F are shown. Are arranged in a portion where the permanent magnet 427 does not exist between the permanent magnets 427.

  In addition, second through holes (notches 428B, 428C, 428D, and 428E) are disposed in a portion between the permanent magnets 427 (a portion where the permanent magnet 427 does not exist) that are spaced apart in the circumferential direction on the rotor 428. As a result, the influence on the magnetic circuit formed by the stator 21 and the rotor 428 can be reduced.

  In addition, a plurality of second through holes (notches 428B, 428C, 428D, and 428E) are arranged in the rotor 428 so that the positions in the axial direction are different from each other, so that a vibration mode due to refrigerant discharge from the second through holes can be achieved. It is possible to further reduce vibration and noise by making it complicated.

  In the first to fourth embodiments, the rotary compressor has been described. However, the compressor is not limited to this, and the present invention may be applied to a compressor having another configuration such as a scroll type.

  Further, in the compressor of the present invention, by providing a refrigerant passage in at least one of the rotor or the rotor holding member so as to cancel at least a part of the imbalance of the rotation mechanism including the rotor, the rotor holding member, and the shaft, It can play the role of a balance weight, and the configuration can be simplified.

For example, in the compressor shown in FIG. 2A, as shown in the schematic diagram on the lower right side of FIG. 2A, the unbalance amount of the compression unit 2 is M1, and the mass of the main balancer by the second through hole provided in the rotor 125 Is M2, the mass of the auxiliary balancer is M3, and the eccentric distances from the center of rotation are L1, L2, and L3,
M1 ・ L1 + M3 ・ L3 = M2 ・ L2
So that the position, number, and size of the second through holes provided in the rotor 125 may be set as appropriate. Specifically, a large second through hole is provided on the lower side of the rotor 125 in the direction in which the clamp pin is biased to form a main balancer, and on the upper side of the rotor 125, the direction is opposite to the direction in which the clamp pin is biased. A second through hole is provided to serve as a secondary balancer. In addition to the balancer as a separate part, a balancer with the through hole may be used as an auxiliary. In this case, the balancer can be reduced in size, and effects such as motor size reduction, use material reduction, and windage loss reduction can be obtained.

  The compressor of the present invention is particularly suitable when an outer rotor type motor is used in a one-piston type rotary compressor or a reciprocating compressor having a large discharge pulsation.

FIG. 1 is a sectional view of a compressor according to a first embodiment of the present invention. FIG. 2A is a sectional view of a compressor according to a second embodiment of the present invention. FIG. 2B is a cross-sectional view of a main part showing a modification of the outer rotor type motor of the compressor. FIG. 3 is an exploded perspective view of the main part of the outer rotor type motor of the compressor according to the third embodiment of the present invention. FIG. 4 is an exploded perspective view of a state in which a permanent magnet is incorporated in the rotor of the outer rotor type motor. FIG. 5 is a perspective view after assembly of the rotor of the outer rotor type motor. FIG. 6 is an exploded perspective view of an outer rotor type motor of a compressor according to a fourth embodiment of the present invention. FIG. 7 is an exploded perspective view showing a state in which the rotor and permanent magnet of the outer rotor type motor are incorporated.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Sealed container 2 ... Compression part 3,103,203 ... Outer rotor type motor 4 ... Shaft 5 ... Crank pin 6 ... Roller 7 ... Compression chamber 8 ... Upper end plate 9 ... Lower end plate 10 ... Muffler part 11 ... Suction pipe 12 ... Discharge pipe 13 ... Discharge port 21, 121, 221 ... Stator 22, 122, 222 ... Coil 23, 123, 223 ... Stator core 24 ... Stator holding mechanism 25, 125, 225, 325, 425 ... Rotor 26, 126, 226, 326 , 426 ... Rotor holding member 27, 127, 227, 327, 427 ... Permanent magnet 28, 128, 228, 328, 428 ... Rotor core 29, 129 ... Spacer 30 ... First through hole 41, 42 ... Bearing 131, 132, 231 232: Second through hole 330, 430B, 430C, 430D, 430E ... Notch 428A to 428F ... Core member

Claims (11)

A sealed container (1);
A compression section (2) disposed in the sealed container (1);
An outer rotor type motor (1, 103, 203) disposed in the hermetic container (1) and driving the compression part (2) via a shaft (4);
The outer rotor type motor (1, 103, 203) includes a stator (21, 121, 221) having coils (22, 122, 222) and an outer periphery of the stator (21, 121, 221) via an air gap. A substantially cylindrical rotor (25, 125, 225, 325, 425) arranged in a circle and a substantially circular shape for fixing one end of the rotor (25, 125, 225, 325, 425) to the shaft (4) A plate-shaped rotor holding member (26, 126, 226, 326, 426),
Disposed in the high-pressure region in the closed container (1) filled with the high-pressure refrigerant discharged from the compression unit (2);
A discharge port (23) of the compression section (2) is disposed between the compression section (2) and the outer rotor type motor (1, 103, 203),
The high-pressure refrigerant is externally introduced from the high-pressure region in the sealed container (1) to the opposite side of the compression section (2) with respect to the outer rotor type motor (1, 103, 203) of the sealed container (1). A discharge pipe (12) for discharging to
At least one of the rotor (25, 125, 225, 325, 425) or the rotor holding member (26, 126, 226, 326, 426) is inserted into the rotor (25, 125, 225, 325, 425) from the inside. A compressor comprising a refrigerant passage through which refrigerant flows toward the outside. The compressor according to claim 1,
The rotor holding member (26, 126, 226, 326, 426) is disposed on the side opposite to the compression portion (2) with respect to the rotor (25, 125, 225, 325, 425). Features compressor. The compressor according to claim 2, wherein
The refrigerant passage is at least a first through hole (30) provided so as to penetrate in the axial direction at least radially inward of the coil (22) of the stator (21) of the rotor holding member (26). The compressor characterized by being. The compressor according to claim 2 or 3,
The refrigerant passage includes at least second through holes (131, 132, 231, 232, 330, 430B, provided in the rotor (125, 225, 325, 425) so as to penetrate from the radially inner side to the radially outer side. 430C, 430D, 430E). The compressor according to claim 4, wherein
The outer rotor type motor (203) is disposed above the compression part (2) in the sealed container (1),
The compressor, wherein the second through holes (231, 232) are provided in the rotor (225) obliquely downward from the radially inner side to the radially outer side. The compressor according to claim 4, wherein
The compressor, wherein the second through hole (330) is provided closer to the rotor holding member (326) than the stator core (23) of the stator (21) of the rotor (325). The compressor according to any one of claims 4 to 6,
The second through hole is plural,
The compressor, wherein the plurality of second through holes are arranged at irregular intervals in the circumferential direction of the rotor. The compressor according to claim 6, wherein
The number of poles of the outer rotor type motor (1) and the number of the second through holes (330) are relatively prime,
The compressor characterized in that the second through holes (330) are arranged in the rotor (325) at equal intervals in the circumferential direction. The compressor according to any one of claims 4 to 6,
The outer rotor type motor (1) has permanent magnets (427) arranged on the rotor (425) at intervals in the circumferential direction,
The compressor is characterized in that the second through holes (430B, 430C, 430D, 430E) are arranged in a portion where the permanent magnet (427) does not exist between the permanent magnets (427) adjacent to each other. The compressor according to claim 9, wherein
The second through holes (430B, 430C, 430D, 430E) are plural,
The compressor characterized in that the plurality of second through holes (430B, 430C, 430D, 430E) are respectively arranged on the rotor (425) so as to have different axial positions. The compressor according to any one of claims 4 to 10,
The refrigerant passage is configured to cancel the rotor (125) or the rotor so as to cancel at least a part of the imbalance of the rotation mechanism including the rotor (125), the rotor holding member (126), and the shaft (4). A compressor provided on at least one of the holding members (126).

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