JP4810961B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor used in an air conditioner, a refrigerator, or the like.

  2. Description of the Related Art Conventionally, there is a compressor provided with a radial gap type motor arranged in a vertical direction in an airtight container and a compression unit driven by this motor (Japanese Patent Laid-Open No. 2004-232625: Patent). Reference 1).

  The motor includes a stator, a rotor disposed on the radially inner side of the stator via an air gap, and a shaft that is fixed to the rotor and transmits the rotational force of the rotor to the compression unit. Yes.

  The rotor is provided with a communication hole penetrating from one end of the rotor to the other end. An oil separator is attached to the other end of the rotor. A mixture of refrigerant gas and oil is allowed to flow from one end of the rotor to the other end through the communication hole, and the oil is separated from the mixture by the oil separator.

However, in the conventional compressor, it is necessary to separately attach the oil separator to the rotor in order to separate the oil, so that the number of parts increases and the apparatus becomes large.
JP 2004-232625 A

  Therefore, an object of the present invention is to provide a compressor capable of separating oil while reducing the number of parts and downsizing the apparatus.

According to the compressor of the present invention, the sealed container, the compression unit disposed in the sealed container, and the radial gap type motor disposed in the sealed container and driving the compression unit via the shaft. Prepared,
This motor has a stator and a rotor that face each other in a direction (radial direction) perpendicular to the axis via an air gap,
An oil separation mechanism that separates the oil by flowing oil in a substantially crank shape from the opening at one axial end to the opening at the other axial end is provided inside the motor,
The oil separation mechanism is
A first passage and a second passage that extend in the axial direction with the same width along the axial direction in the longitudinal section and do not overlap with each other when viewed from the axial direction;
A third passage extending in a direction orthogonal to the first passage and the second passage and connecting the first passage and the second passage;
The cross-sectional area of the cross section of the third passage is the area of the opening of the first passage on the side of the third passage and the area of the opening of the second passage on the side of the third passage. It is characterized by being larger than.

Here, in this specification, the crank shape refers to a shape having at least two bent portions, for example, a saddle shape, an engine crankshaft shape, and the like. Further, when the oil separation mechanism has two bent portions, the passage from the opening at one axial end to the first bent portion is defined as the first passage, and from the opening at the other axial end to the second bent portion. Is the second passage, and the passage between the first bent portion and the second bent portion is the third passage, the first passage and the second passage are connected to the shaft. It is preferable that the third passage is provided in a direction substantially perpendicular to the axis.
Here, the “cross-sectional area of the cross section of the third passage” means that the third passage in a plane parallel to the first passage and the second passage and orthogonal to the third passage. It is a cross-sectional area of the passage.

According to the compressor of the present invention, an oil separation mechanism for separating oil by flowing oil in a substantially crank shape from the opening at one axial end to the opening at the other axial end is provided inside the motor. Therefore, it is not necessary to separately provide a member for separating oil such as an oil separator, so that oil separation can be performed while reducing the number of parts and downsizing the apparatus.
The oil separation mechanism extends in the axial direction and extends in a direction orthogonal to the first passage and the second passage and the first passage and the second passage that do not overlap each other when viewed from the axial direction. Since the first passage and the third passage are connected to the second passage, for example, the refrigerant gas flow from the upstream to the downstream (or from the bottom to the top) in order, Assuming that the passage, the third passage, and the second passage are disposed, the mixture of oil and refrigerant gas passes through the first passage and then hits the inner surface of the third passage. At this time, the oil in the form of fine particles adheres to the inner surface of the third passage and liquefies by becoming large particles and returns to the first passage, while the refrigerant gas passes through the third passage. After passing through the second passage. In this way, the oil can be reliably separated.
The cross-sectional area of the cross section of the third passage is larger than the area of the opening of the first passage and the area of the opening of the second passage. It can also be used as a muffler that cancels out the pulsation of the refrigerant gas.

In the compressor according to an embodiment, the first passage is upstream and lower in the direction in which the refrigerant gas flows than the second passage.
The area of the opening portion on the third passage side of the first passage is larger than the area of the opening portion on the third passage side of the second passage.

  According to the compressor of this embodiment, the separated oil can be reliably returned to the upstream side and the lower side of the refrigerant gas flow from the first passage on the upstream side and the lower side of the refrigerant gas flow. .

  In the compressor of one embodiment, the oil separation mechanism is provided inside the rotor.

  According to the compressor of this embodiment, since the oil separation mechanism is provided inside the rotor, the centrifugal force generated by the rotation of the rotor can also be used for oil separation.

Further, in the compressor of one embodiment, the first passage, the than the second passage located at an upstream side and lower side of the direction of flow of the refrigerant gas, the first passage, the upper Symbol first 2 of the passage by remote lies radially outward.

In the compressor of this embodiment, the first through passage, the top Symbol second through passage by remote, since the radially outward, separated oil is centrifugal force generated by rotation of the rotor The refrigerant gas is returned to the upstream first passage on the radially outer side, while the refrigerant gas is guided to the downstream second passage on the radially inner side. In this way, the oil can be reliably separated from the refrigerant gas.

Further, the first through passage, the top Symbol second through passage by remote, since the radially outward, separated oil is transported to the outside by the centrifugal force generated by rotation of the rotor, diameter While returning to the lower first passage on the outer side in the direction, the refrigerant gas is guided to the upper second passage on the inner side in the radial direction. In this way, the oil can be reliably separated from the refrigerant gas.

In the compressor of one embodiment,
The rotor has a first rotor core and a second rotor core arranged along an axis, and a third rotor core sandwiched between the first rotor core and the second rotor core,
Magnets are attached to the insides of the first rotor core and the second rotor core,
The first passage is provided in the first rotor core,
The second passage is provided inside the second rotor core,
The third passage is provided inside the third rotor core,
By shifting the first rotor core and the second rotor core in the circumferential direction, the first passage, the second passage, the magnet on the first rotor core side, and the second rotor core side The magnets are shifted in the circumferential direction.

  According to the compressor of this embodiment, by shifting the first rotor core and the second rotor core in the circumferential direction, the first passage and the second passage are respectively shifted in the circumferential direction. Therefore, even if the first rotor core and the second rotor core are formed in the same shape, the first passage and the second rotor core are shifted in the circumferential direction by shifting the first rotor core and the second rotor core in the circumferential direction. The second passages do not overlap each other when viewed from the axial direction. Therefore, the manufacturing cost can be reduced.

  Further, by shifting the first rotor core and the second rotor core in the circumferential direction, the magnet on the first rotor core side and the magnet on the second rotor core side are shifted in the circumferential direction. Therefore, it has a so-called skew effect. That is, the magnetic pulsation (so-called cogging torque) generated between the stator and the rotor is shifted by shifting the phases of the magnet on the first rotor core side and the magnet on the second rotor core side. Pulsation can be reduced.

In the compressor of one embodiment,
The rotor has a first rotor core and a second rotor core arranged along an axis, and a third rotor core sandwiched between the first rotor core and the second rotor core,
Magnets are attached to the insides of the first rotor core and the second rotor core,
The first rotor core has a magnet fitting hole that fits the magnet and has a space larger than a cross-sectional area of the magnet in a plane perpendicular to the axis;
The second rotor core has a magnet fitting hole that fits the magnet and has a space larger than the cross-sectional area of the magnet in a plane perpendicular to the axis,
The first passage is a space where the magnet is not present in the magnet fitting hole of the first rotor core,
The second passage is a space where the magnet does not exist in the magnet fitting hole of the second rotor core,
The third passage is provided inside the third rotor core.

  According to the compressor of this embodiment, the first passage is a space where the magnet is not present in the magnet fitting hole of the first rotor core, and the second passage is the second passage. Since the magnet does not exist among the magnet fitting holes of the rotor core, even if the first rotor core and the second rotor core are formed in the same shape, the magnet to the magnet fitting hole Is different between the first rotor core and the second rotor core, the first passage and the second passage do not overlap each other when viewed in the axial direction. Therefore, the manufacturing cost can be reduced. Moreover, since the said magnet fitting hole fits the said magnet and serves also as a refrigerant path, it is not necessary to provide a refrigerant path separately.

  Moreover, in the compressor of one Embodiment, the said 3rd channel | path is connected to the radial direction outer side of the said rotor.

  According to the compressor of this embodiment, since the third passage communicates with the outer side in the radial direction of the rotor, the oil adhering to the third passage is utilized by centrifugal force generated by the rotation of the rotor. And it can fly to the radial outside of the rotor. Therefore, oil can be returned to the oil sump from another passage outside the rotor in the radial direction.

  In one embodiment of the compressor, the rotor rotates together with the rotor on the downstream side of the first passage or the second passage in the direction in which the refrigerant gas flows in the first passage. A rotating plate is provided.

  According to the compressor of this embodiment, the rotor rotates together with the rotor on the downstream side of the downstream side passage in the refrigerant gas flowing direction of the first passage or the second passage. Since the rotating plate is provided, the rotation of the rotating plate due to the rotation of the rotor can make the downstream passage of the first passage or the second passage a negative pressure, and the oil separation mechanism A mixture of refrigerant gas and oil can be forced. Therefore, the oil separation mechanism can be used effectively and oil can be reliably separated.

  Moreover, in the compressor of one Embodiment, the said oil separation mechanism is provided in the said air gap.

  According to the compressor of this embodiment, since the oil separation mechanism is provided in the air gap, it is possible to eliminate unnecessary magnetic path interference in the rotor and the stator.

  In the compressor according to an embodiment, the stator is disposed radially outside the rotor, and the stator communicates with the third passage and has an inner peripheral surface and an outer peripheral surface of the stator. It has a through passage that penetrates.

  According to the compressor of this embodiment, the stator is disposed radially outside the rotor, and the stator communicates with the third passage and connects the inner peripheral surface and the outer peripheral surface of the stator. Since the through-passage penetrates, the oil separated in the third passage of the air gap can be returned to the oil sump also from the outer peripheral side of the stator via the through-passage.

  In the compressor of one embodiment, the oil separation mechanism is provided inside the stator.

  According to the compressor of this embodiment, since the oil separation mechanism is provided inside the stator, the oil separation mechanism can be provided on the outer peripheral side of the stator, and obstruction of the magnetic path is eliminated. be able to.

  According to the compressor of the present invention, an oil separation mechanism for separating oil by flowing oil in a substantially crank shape from the opening at one axial end to the opening at the other axial end is provided inside the motor. Therefore, oil separation can be performed while reducing the number of parts and downsizing the apparatus.

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

(First embodiment)
FIG. 1 is a longitudinal sectional view showing a first embodiment of a compressor according to the present invention. The compressor includes a compression unit 11 and a radial gap motor 2 that drives the compression unit 11 via a shaft 20, which are arranged in order from the bottom to the top in the sealed container 1. Here, the upward direction refers to an upward direction along the central axis of the sealed container 1 regardless of whether or not the central axis of the sealed container 1 is inclined with respect to a horizontal plane.

  The motor 2 is disposed in a region in the sealed container 1 where the high-pressure refrigerant gas discharged from the compression unit 11 is filled. Specifically, the inside of the sealed container 1 is a high-pressure region H, and this compressor is a so-called high-pressure dome type.

  The motor 2 includes a stator 21 and a rotor 31 that are opposed to each other in a direction (radial direction) perpendicular to the axis via an air gap 41. The rotor 31 is fixed to the shaft 20. The stator 21 is disposed on the radially outer side of the rotor 31 and is fixed to the sealed container 1. The shaft 20 transmits the rotational force of the rotor 31 to the compression unit 11.

  The stator 21 includes a stator core 22 attached to the sealed container 1 and a coil 23 attached to the stator core 22. The stator core 22 is made of an iron core and is formed in a substantially cylindrical shape. The coil 23 is wound around the stator core 22 along the shaft 20. Coil ends 23 a of the coil 23 protrude from both ends of the stator core 22.

  As shown in FIGS. 1 and 2A to 2C, the rotor 31 includes a rotor core 32 and a magnet 33 embedded in the rotor core 32.

  The rotor core 32 is formed in a substantially cylindrical shape. The rotor core 32 is formed by laminating a plurality of thin plates such as electromagnetic steel plates.

  A shaft insertion hole 37 through which both ends of the rotor core 32 in the axial direction are inserted and the shaft 20 is inserted is provided at the axial position of the rotor core 32.

  A plurality of rivet holes 35 penetrating both ends of the rotor core 32 in the axial direction are provided on the outer peripheral portion of the rotor core 32. The plurality of rivet holes 35 are arranged at equal intervals in the circumferential direction at a predetermined center angle. A rivet 60 is inserted into the rivet hole 35, and the plurality of laminated thin plates are integrally fixed by the rivet 60.

  A plurality of magnet fitting holes 36 penetrating both ends of the rotor core 32 are provided in a central portion between the inner peripheral surface and the outer peripheral surface of the rotor core 32. The plurality of magnet fitting holes 36 are arranged at equal intervals in the circumferential direction at a predetermined center angle. The magnet fitting hole 36 is formed in a cross section and a band shape. The magnet 33 is fitted in the magnet fitting hole 36.

  The magnet 33 is, for example, a permanent magnet and is formed in a plate shape. The plurality of magnets 33 are arranged so that the magnetic poles of the adjacent magnets 33 and 33 are alternately different in the circumferential direction.

  The inner periphery of the rotor core 32 is provided with an upper hole portion 34a, an intermediate hole portion 34b, and a lower hole portion 34c that communicate in order from the top to the bottom in the axial direction. The upper hole portion 34 a opens at one end (upper end) in the axial direction of the rotor core 32, and the lower hole portion 34 c opens at the other end (lower end) in the axial direction of the rotor core 32. The upper hole portion 34a, the middle hole portion 34b, and the lower hole portion 34c are arranged at equal intervals in the circumferential direction at a predetermined center angle.

  The upper hole portion 34a and the lower hole portion 34c extend in the axial direction and do not overlap each other when viewed from the axial direction. The middle hole portion 34b extends in a direction orthogonal to the upper hole portion 34a and the lower hole portion 34c, and connects the upper hole portion 34a and the lower hole portion 34 to each other.

  The lower hole portion 34 c forms a first passage 51, the upper hole portion 34 a forms a second passage 52, and the middle hole portion 34 b forms a third passage 53. The first passage 51, the second passage 52, and the third passage 53 form an oil separation mechanism G1.

  The oil separation mechanism G1 is provided inside the rotor 31, and is configured to move refrigerant gas from the opening of the first passage 51 at one end in the axial direction toward the opening of the second passage 52 at the other end in the axial direction. The oil mixture is run in a generally crank shape to separate the oil from the mixture.

  The area of the opening 51a on the third passage 53 side in the first passage 51 on the upstream side and the lower side in the direction in which the refrigerant gas flows is the downstream side and the upper side in the direction in which the refrigerant gas flows. The area of the second passage 52 is larger than the area of the opening 52a on the third passage 53 side.

  The cross-sectional area of the cross section of the third passage 53 is the area of the opening 51 a on the third passage 53 side of the first passage 51 and the third passage 53 of the second passage 52. It is larger than the area of the opening 52a on the side. The third passage 53 is a so-called expansion chamber.

  Here, “the cross-sectional area of the cross section of the third passage 53” is a plane parallel to the first passage 51 and the second passage 52 and perpendicular to the third passage 53. , A sectional area of the third passage 53.

  The first passage 51 on the upstream side and the lower side in the direction in which the refrigerant gas flows is located radially outside the second passage 52 on the downstream side and in the upper side in the direction in which the refrigerant gas flows.

  The rotor 31 is provided with a rotating plate 61 that rotates together with the rotor 31 on the downstream side of the second passage 52 on the downstream side in the flow direction of the refrigerant gas. The rotating plate 61 is fixed to the end surface of the rotor core 32 so as to overlap the second passage 52 when viewed from the axial direction. The rotating plate 61 is not essential.

  As shown in FIG. 1, the compression unit 11 includes a cylindrical main body 12 and an upper end plate 15 and a lower end plate 16 attached to upper and lower open ends of the main body 12. The shaft 20 penetrates the upper end plate 15 and the lower end plate 16 and enters the main body 12.

  A roller 13 fitted to a crank pin 17 provided on the shaft 20 is disposed inside the main body 12 so as to be able to revolve or eccentrically rotate, and a compression action is achieved by the revolving or eccentric rotational movement of the roller 13. Like to do. That is, a compression chamber 14 is formed between the outer surface of the roller 13 and the inner surface of the main body portion 12.

  The sealed container 1 has a suction pipe 6 that opens to the compression chamber 14 on the low pressure side of the compression section 11 and a discharge pipe 7 that opens to the upper side (downstream side) of the motor 2. The compression unit 11 has a discharge hole 11a that opens to the motor 2 side. The discharge hole 11a is disposed inside the coil end 23a when viewed from the axial direction.

  One end side of the shaft 20 is rotatably supported by the lower end plate 16 of the compression unit 11, and the other end side of the shaft 20 is fixed to the rotor 31 so as not to rotate.

  An oil 8 in which a lower portion of the shaft 20 is immersed is provided on the lower side in the sealed container 1. The oil 8 moves up the shaft 20 by the rotation of the shaft 20 and lubricates the sliding portion of the compression portion 11 and the like.

  Next, the operation of the compressor will be described.

  Refrigerant gas is supplied from the suction pipe 6 to the compression chamber 14 of the compression unit 11, and the compression unit 11 is driven by the motor 2 to compress the refrigerant gas. The compressed refrigerant gas is discharged together with oil from the discharge hole 11a of the compression unit 11 into the sealed container 1 and is carried to the upper space of the compression unit 11 through the motor 2 and the discharge pipe. 7 is discharged to the outside of the sealed container 1.

  At this time, as shown by the solid line arrow in FIG. 3, after the refrigerant gas passes through the first passage 51, the first passage 51 and the second passage 52 are viewed from the axial direction. Since they do not overlap, the refrigerant gas hits the inner surface of the third passage 53.

  The oil contained in the refrigerant gas is liquefied by adhering to the inner surface of the third passage 53 in the form of fine particles, and is broken by the broken line in FIG. 3 due to the action of gravity and the action of the centrifugal force of the rotor 31. As shown by the arrow, the first gas passes through the first passage 51 and returns to the upstream side of the refrigerant gas flow of the motor 2.

  On the other hand, the refrigerant gas passes through the second passage 52 after passing through the third passage 53 as indicated by the solid line arrow in FIG.

  According to the compressor having the above configuration, since the oil separation mechanism G1 is provided in the motor 2, the mixture of oil and refrigerant gas passes through the first passage 51, and then the third. It hits the inner surface of the passage 53. At this time, the oil liquefies and returns to the first passage 51, while the refrigerant gas passes through the second passage 52 after passing through the third passage 53. In this way, the oil separation mechanism G1 passes through the third passage 53 from the opening at one axial end (the opening of the first passage 51) and the opening at the other axial end (the opening of the second passage 52). ) Oil flows in a generally crank shape toward

  Therefore, it is not necessary to separately provide a member for separating oil such as an oil separator, so that oil separation can be performed while reducing the number of parts and downsizing the apparatus. In the present embodiment, the rotary plate 61 is provided and can be grasped as an oil separator. However, as will be described later, by increasing the negative pressure, the refrigerant gas is supplied to the oil separation mechanism G1. It has the function of making it easier to guide the mixture of oil and oil. Therefore, the rotating plate 61 can be omitted if this effect is unnecessary.

  As a comparative example, when the third passage 53 is curved or when the oil separation mechanism G1 has no bent portion, the inner surface of the third passage 53 becomes smooth, and the oil It will flow with this gas along this curved inner surface. Therefore, the oil cannot be hit against the inner surface of the third passage 53, and the oil cannot be separated.

  Further, since the area of the opening 51a of the first passage 51 on the upstream side of the refrigerant gas flow is larger than the area of the opening 52a of the second passage 52 on the downstream side of the refrigerant gas flow, The separated oil can be reliably returned to the upstream side of the refrigerant gas flow from the first passage 51 on the upstream side of the refrigerant gas flow.

  Further, since the area of the opening 51a of the first passage 51 on the lower side is larger than the area of the opening 52a of the second passage 52 on the upper side, the first passage 51 on the lower side. Therefore, the separated oil can be reliably returned to the lower side. As in the present embodiment, the shaft 20 only needs to lubricate the compression chamber 14 and the inner periphery of the lower end plate 16 as long as the lower end is only held by the lower end plate 16. This is particularly preferable because it is not necessary to guide oil to the top of the motor 2.

  The cross-sectional area of the cross section of the third passage 53 is larger than the area of the opening 51a of the first passage 51 and the area of the opening 52a of the second passage 52. The third passage 53 can also be used as a muffler that cancels out the pulsation of the refrigerant gas. That is, by acting as a reactive silencer called an inflatable chamber, it is possible to mute a wide range of frequencies.

  Further, since the oil separation mechanism G1 is provided in the rotor 31, the centrifugal force generated by the rotation of the rotor 31 can also be used for oil separation.

  Further, since the first passage 51 on the upstream side of the refrigerant gas flow is radially outside of the second passage 52 on the downstream side of the refrigerant gas flow, the separated oil is removed from the rotor. While being transported outward by centrifugal force generated by the rotation of 31 and returning to the first passage 51 on the upstream side in the radial direction, the refrigerant gas flows to the second passage 52 on the downstream side in the radial direction. Led to. In this way, the oil can be reliably separated from the refrigerant gas.

  In addition, since the first passage 51 on the lower side is radially outside the second passage 52 on the upper side, the separated oil is moved outward by the centrifugal force generated by the rotation of the rotor. While being carried back to the first passage 51 on the lower side in the radial direction, the refrigerant gas is guided to the second passage 52 on the upper side in the radial direction. In this way, the oil can be reliably separated from the refrigerant gas.

  The rotor 31 is provided with a rotating plate 61 that rotates together with the rotor 31 on the downstream side of the second passage 52 on the downstream side in the direction in which the refrigerant gas flows. Due to the rotation of the rotating plate 61, the second passage 52 on the downstream side can be set to a negative pressure, and the mixture of refrigerant gas and oil can be forcibly guided to the oil separation mechanism G1. Therefore, the oil separation mechanism G1 can be used effectively and the oil can be reliably separated.

  In addition, the discharge port of the refrigerant gas discharged from the compression unit 11 into the sealed container 1 is provided in the vicinity of the opening (inlet) of the first passage 51 on the upstream side in the flow direction of the refrigerant gas. Alternatively, the refrigerant gas can be guided to the first passage 51, and the oil can be effectively separated. Here, the discharge port of the refrigerant gas includes a discharge hole 11a of the casing of the compression unit 11 shown in FIG. 1, a piping port connected to the discharge hole 11a, and the like.

  Further, a passage that penetrates both ends of the stator 21 in the axial direction may be provided in the outer peripheral portion of the stator 21. Refrigerant gas and oil pass through this passage.

  Further, a guide member for guiding a large amount of refrigerant gas from the discharge hole 11a to the oil separation mechanism G1 may be provided. At this time, the passage provided in the outer peripheral portion of the stator 21 can be used as a passage for returning mainly the oil separated from the refrigerant gas to the lower portion of the sealed container 1.

(Second Embodiment)
FIG. 4 shows a second embodiment of the compressor of the present invention. The difference from the first embodiment (FIG. 1) will be described. In the second embodiment, the configuration of the rotor is different. Since other structures are the same as those of the first embodiment, description thereof is omitted.

  The rotor 130 includes a first rotor core 131 and a second rotor core 132 arranged along an axis, and a third rotor core 133 sandwiched between the first rotor core 131 and the second rotor core 132. Have The first rotor core 131 is disposed below the second rotor core 132.

  The magnets 33 are attached to the insides of the first rotor core 131 and the second rotor core 132, respectively.

  The first passage 51 is provided in the first rotor core 131, the second passage 52 is provided in the second rotor core 132, and the third passage 53 is formed in the first rotor core 131. 3 of the rotor core 133.

  By shifting the first rotor core 131 and the second rotor core 132 in the circumferential direction, the first passage 51 and the second passage 52, and the magnet 33 on the first rotor core 131 side, The magnets 33 on the second rotor core 132 side are respectively shifted in the circumferential direction.

  Specifically, as shown in FIGS. 4 and 5A, the first rotor core 131 is fitted with the hole 131a as the first passage 51 and the magnet 33 in order from the radially outer side to the inner side. A mating magnet fitting hole 131b and a rivet hole 131c for inserting the rivet 60 are provided.

  As shown in FIGS. 4 and 5B, the second rotor core 132 has a hole 132a as the second passage 52 and a magnet fitting hole into which the magnet 33 is fitted in order from the radially outer side to the inner side. 132b and a rivet hole 132c into which the rivet 60 is inserted are provided.

  As shown in FIGS. 4 and 5C, the third rotor core 133 has a hole 133a as the third passage 53 and a rivet hole 133c into which the rivet 60 is inserted in order from the radially outer side to the inner side. Is provided.

  The first passage 51 and the second passage 52 extend in the axial direction and do not overlap each other when viewed from the axial direction. The third passage 53 extends in a direction orthogonal to the first passage 51 and the second passage 52, and connects the first passage 51 and the second passage 52. The rivet holes 131c, 132c, and 133c overlap each other when viewed from the axial direction. The cross sections of the first passage 51 and the second passage 52 are the same.

  That is, the first rotor core 131 and the second rotor core 132 have the same shape and are rotated by a predetermined angle. Since the relative positions of the holes 131a and 132a and the magnet fitting holes 131b and 132b are the same, the same mold can be used. It is necessary to provide the rivet holes 131c and 132c separately.

  The third rotor core 133 is a nonmagnetic material and is made of, for example, polyphenylene sulfide resin. The third rotor core 133 prevents leakage of magnetic flux between the magnet 33 on the first rotor core 131 side and the magnet 33 on the second rotor core 132 side.

  According to the compressor having this structure, the first passage 51 and the second passage 52 are respectively circumferentially moved by shifting the first rotor core 131 and the second rotor core 132 in the circumferential direction. Since the first rotor core 131 and the second rotor core 132 are formed in the same shape, the first rotor core 131 and the second rotor core 132 can be shifted in the circumferential direction. The first passage 51 and the second passage 52 do not overlap each other when viewed in the axial direction. Therefore, the manufacturing cost can be reduced.

  Further, by shifting the first rotor core 131 and the second rotor core 132 in the circumferential direction, the magnet 33 on the first rotor core 131 side and the magnet 33 on the second rotor core 132 side can be connected to each other. Since it is shifted in the circumferential direction, it has a so-called skew effect. That is, the magnetic pulsation (so-called cogging torque) generated between the stator 21 and the rotor 130 is caused by the phase of the magnet 33 on the first rotor core 131 side and the magnet 33 on the second rotor core 132 side. The pulsation can be reduced by shifting.

  For example, when the rotor 130 has 4 poles and the stator 21 has 6 poles, the deviation of the center angle between the first rotor core 131 and the second rotor core 132 (that is, the skew angle) is 15 degrees mechanical angle. If so, a so-called skew effect can be obtained.

  The skew angle has an optimum angle depending on the number of poles and the like, but even when the skew angle is small, the first passage 51 and the second passage 52 have a diameter larger than that of the magnet 33. Since it is on the outer side in the direction, the amount of deviation between the first passage 51 and the second passage 52 is the amount of deviation between the magnet 33 on the first rotor core 131 side and the magnet 33 on the second rotor core 132 side. Than can be larger.

  In the second embodiment, the rotor core to which the magnet 33 is attached has two stages, but the rotor core may have three or more stages.

(Third embodiment)
FIG. 6 shows a third embodiment of the compressor of the present invention. The difference from the second embodiment (FIG. 4) will be described. In the second embodiment, the configuration of the third rotor core of the rotor is different. Since other structures are the same as those of the second embodiment, description thereof is omitted.

  The rotor 230 includes the first rotor core 131 (having the same configuration as that of the second embodiment), the second rotor core 132 (having the same configuration as that of the second embodiment), and the first rotor core. 131 and a third rotor core 233 sandwiched between the second rotor core 132.

  The third rotor core 233 is a magnetic body. As shown in FIGS. 6 and 7, the third rotor core 233 includes a hole 233 a as the third passage 53, a magnetic flux leakage prevention hole 233 d, and the above in order from the radially outer side to the inner side. A rivet hole 233c for inserting the rivet 60 is provided.

  The hole 233a has the same configuration as the hole 133a of the third rotor core 133 of the second embodiment. The rivet hole 233c has the same configuration as the rivet hole 133c of the third rotor core 133 of the second embodiment.

  The magnetic flux leakage prevention hole 233d is provided between the magnet 33 on the first rotor core 131 side and the magnet 33 on the second rotor core 132 side. The cross-sectional area of the magnetic flux leakage prevention hole 233d is the cross-sectional area of the magnet fitting hole 131b of the first rotor core 131 (shown in the second embodiment) and the cross-sectional area of the second rotor core 132. It is larger than the cross-sectional area of the magnet fitting hole 132b.

  Therefore, since the magnetic flux leakage prevention hole 233d is provided, even if the third rotor core 233 is a magnetic body, the magnet 33 on the first rotor core 131 side and the second rotor core 132 side are provided. Leakage of magnetic flux between the magnet 33 is prevented.

  In order to prevent the upper and lower magnets 33 and 33 from entering the magnetic flux leakage prevention hole 233d, the upper and lower magnets 33 and 33 are attached to the first rotor core 131 and the second rotor core 132, respectively. You may magnetize beforehand. Alternatively, the upper and lower magnets 33 and 33 may be locked to the third rotor core 233. At this time, the third rotor core 233 is slightly in contact with the magnets 33 and 33 at such a degree that the magnetic flux of the magnets 33 and 33 does not leak, for example, less than half the thickness direction of the magnets 33 and 33. It is good to make it.

(Fourth embodiment)
FIG. 8 shows a fourth embodiment of the compressor of the present invention. The difference from the third embodiment (FIG. 7) will be described. In the fourth embodiment, the configuration of the third rotor core is different. Since other structures are the same as those of the third embodiment, description thereof is omitted.

  The hole 233a as the third passage 53 of the third rotor core 333 communicates with the third rotor core 333 on the radially outer side. That is, the hole 233a communicates with the outside of the rotor 230 via the lateral hole 333e.

  Therefore, the oil adhering to the third passage 53 can be blown to the outside in the radial direction of the rotor 230 as shown by the solid line in FIG. 8 by utilizing the centrifugal force generated by the rotation of the rotor 230. In other words, the oil can be returned to the oil sump from another passage outside the rotor 230 in the radial direction.

  The lateral hole 333e may be formed so as to be inclined downward toward the radially outer side, and when the oil blown from the lateral hole 333e reaches the air gap, It has speed and can effectively drop the oil drops.

  Further, while providing the horizontal hole 333e in the horizontal direction, a convex portion may be provided near the outlet of the horizontal hole 333e (near the air gap), and a downward velocity is given to the oil droplets near the outlet. be able to.

(Fifth embodiment)
9 and 10 show a fifth embodiment of the compressor of the present invention. The difference from the first embodiment (FIG. 1) will be described. In the fifth embodiment, the configuration of the rotor is different. Since other structures are the same as those of the first embodiment, description thereof is omitted.

  The rotor 430 includes a first rotor core 431 and a second rotor core 432 arranged along an axis, and a third rotor core 433 sandwiched between the first rotor core 431 and the second rotor core 432. Have The first rotor core 431 is disposed below the second rotor core 432.

  The magnet 33 is attached to each of the inside of the first rotor core 431 and the second rotor core 432.

  The first passage 51 is provided in the first rotor core 431, the second passage 52 is provided in the second rotor core 432, and the third passage 53 is provided in the first rotor core 431. 3 of the rotor core 433.

  The refrigerant gas passes through the first passage 51, the third passage 53, and the second passage 52 as shown by the solid arrows in FIG. 10, while the oil contained in the refrigerant gas is As shown by the broken line arrow in FIG. 10, it strikes the inner surface of the third passage 53 and liquefies, and returns to the upstream side of the refrigerant gas flow through the first passage 51.

  Specifically, the first rotor core 431 includes a rivet hole 431c into which the rivet 60 is inserted in order from the radially outer side to the inner side, and the magnet, as shown in FIGS. 9, 10 and 11A. A magnet fitting hole 431a for fitting 33 is provided.

  The magnet fitting hole 431a has a space larger than the cross-sectional area of the magnet 33 in a plane orthogonal to the axis. The magnet 33 is arranged close to the magnet fitting hole 431a in one direction perpendicular to the radial direction when viewed from the axial direction. The first passage 51 is a space where the magnet 33 is not present in the magnet fitting hole 431a.

  As shown in FIGS. 9, 10 and 11B, the second rotor core 432 has a rivet hole 432c into which the rivet 60 is inserted in order from the radially outer side to the inner side, and a magnet into which the magnet 33 is fitted. A fitting hole 432a is provided.

  The magnet fitting hole 432a has a space larger than the cross-sectional area of the magnet 33 in a plane orthogonal to the axis. The magnet 33 is arranged close to the magnet fitting hole 432a in the other direction perpendicular to the radial direction when viewed from the axial direction. The second passage 52 is a space where the magnet 33 is not present in the magnet fitting hole 432a. Here, since the first passage 51 and the second passage 52 are provided, the magnetic flux of the magnet 33 is not reduced. That is, since the magnetization direction of the magnet 33 is the thickness direction, the magnetic pole surface of the magnet 33 does not contact the first passage 51 and the second passage 52. Therefore, there is no influence on the magnetic resistance without increasing the air gap length. On the other hand, a clearance for inserting a magnet is also provided in the thickness direction of the magnet 33. However, this minute gap is not considered because it does not actively pass refrigerant gas and oil.

  As shown in FIGS. 9, 10 and 11C, the third rotor core 433 includes a rivet hole 433c into which the rivet 60 is inserted in order from the radially outer side to the inner side, and the third passage 53 as the third passage 53. A hole 433b is provided.

  The first passage 51 and the second passage 52 extend in the axial direction and do not overlap each other when viewed from the axial direction. The third passage 53 extends in a direction orthogonal to the first passage 51 and the second passage 52, and connects the first passage 51 and the second passage 52.

  The magnet fitting holes 431a and 432a and the hole 433b overlap each other when viewed from the axial direction. The rivet holes 431c, 432c, 433c overlap each other when viewed from the axial direction.

  Since the upper and lower magnets 33, 33 are moved toward the opposite sides in the upper and lower magnet fitting holes 431a, 432a, the first passage 51 and the second passage 52 are arranged in the axial direction. Do not overlap each other.

  That is, since the first rotor core 431, the second rotor core 432, and the third rotor core 433 have the same shape, the same mold can be used.

  The third passage 53 is provided between the magnet 33 on the first rotor core 431 side and the magnet 33 on the second rotor core 432 side. Therefore, even if the third rotor core 433 is a magnetic body, magnetic flux leakage between the magnet 33 on the first rotor core 431 side and the magnet 33 on the second rotor core 432 side is prevented.

  According to the compressor of this configuration, the first passage 51 is a space where the magnet 33 is not present in the magnet fitting hole 431a of the first rotor core 431, and the second passage 52 is Since the magnet 33 does not exist in the magnet fitting hole 432a of the second rotor core 432, even if the first rotor core 431 and the second rotor core 432 are formed in the same shape, By making the arrangement of the magnet 33 in the magnet fitting holes 431a and 432a different between the first rotor core 431 and the second rotor core 432, the first passage 51 and the second passage 52 are , Do not overlap each other when viewed from the axial direction. Therefore, the manufacturing cost can be reduced. Further, since the magnet fitting holes 431a and 432a fit the magnet 33 and also serve as a refrigerant passage, there is no need to provide a separate refrigerant passage.

  In order to prevent the upper and lower magnets 33 and 33 from entering the hole 433b, the upper and lower magnets 33 and 33 are pre-magnetized on the first rotor core 431 and the second rotor core 432, respectively. May be. Alternatively, the hole 433b may be made smaller than the upper and lower magnets 33 and 33 so that the upper and lower magnets 33 and 33 are engaged with the third rotor core 433.

(Sixth embodiment)
FIG. 12 shows a sixth embodiment of the compressor of the present invention. Explaining the difference from the fifth embodiment (FIG. 11B), in the sixth embodiment, end plates 62 are attached to both ends of the rotor 430 in the axial direction of the fifth embodiment. Since other structures are the same as those of the fifth embodiment, description thereof is omitted. Further, in the plan view of FIG. 12, the magnet 33 is indicated by hatching for easy understanding.

  The end plate 62 is formed in a square shape when viewed from the plane. The corners of the end plate 62 are attached to the rotor 430 by the rivets 60. The end plate 62 overlaps the magnet 33 on the second rotor core 432 side, but does not overlap the second passage 52.

  Although not shown, the end plate 62 is also attached to the first rotor core 431 side, and the end plate 62 overlaps the magnet 33 on the first rotor core 431 side, while the end plate 62 overlaps the first passage 51. Do not overlap. The end plate 62 may be circular instead of square, and the circular end plate is provided with a hole only in a portion overlapping the first passage 51 and the second passage 52. Just do it.

  According to the compressor having this configuration, since the end plate 62 is provided, it is possible to prevent the magnet 33 from being displaced in the axial direction without disturbing the flow of the refrigerant gas in the oil separation mechanism G1.

(Seventh embodiment)
13A and 13B show a seventh embodiment of the compressor of the present invention. The difference from the fifth embodiment (FIGS. 11A and 11B) will be described. In the seventh embodiment, the magnet 33 in the magnet fitting hole 431a of the first rotor core 431 is present. The space where the magnet 33 does not exist is made smaller than the thickness of the magnet 33 and the space where the magnet 33 does not exist in the magnet fitting hole 432a of the second rotor core 432 is made smaller than the thickness of the magnet 33. Yes. Since other structures are the same as those of the fifth embodiment, description thereof is omitted.

  Therefore, the first passage 51 and the second passage 52 can be secured while preventing the magnet 33 from being displaced.

(Eighth embodiment)
FIG. 14 shows an eighth embodiment of the compressor of the present invention. The difference from the first embodiment (FIG. 1) will be described. In the eighth embodiment, the configuration of the motor is different.

  The motor 502 includes a rotor 531 and a stator 521 arranged on the outer side in the radial direction than the rotor 531.

  A magnet 533 is attached to the rotor 531, and a coil 523 is attached to the stator 521. An oil separation mechanism G2 is provided in an air gap 541 between the rotor 531 and the stator 521.

  The stator 521 includes a first stator core 522a located on the lower side upstream of the refrigerant gas flow, and a second stator core 522b located on the upper side of the first stator core 522a and located downstream of the refrigerant gas flow. The inner diameter of the first stator core 522a is larger than the inner diameter of the second stator core 522b.

  The rotor 531 has a first rotor core 532a located on the lower side upstream of the refrigerant gas flow, and a second rotor core 532b located on the upper side of the first rotor core 532a and located downstream of the refrigerant gas flow. The outer diameter of the first rotor core 532a is larger than the outer diameter of the second rotor core 532b.

  The axial height of the first stator core 522a is larger than the axial height of the first rotor core 532a. The axial height of the second stator core 522b is smaller than the axial height of the second rotor core 532b.

  An air gap 541a between the first stator core 522a and the first rotor core 532a forms a first passage 551. An air gap 541b between the second stator core 522b and the second rotor core 532b forms a second passage 552. An air gap 541c between the first stator core 522a and the second rotor core 532b forms a third passage 553.

  The first passage 551 and the second passage 552 extend in the axial direction and do not overlap with each other when viewed from the axial direction. The third passage 553 extends in a direction orthogonal to the first passage 551 and the second passage 552 and connects the first passage 551 and the second passage 552.

  That is, the oil separation mechanism G2 is formed by the first passage 551, the second passage 552, and the third passage 553. When the refrigerant gas flows through the oil separation mechanism G2, the refrigerant gas hits the inner surface of the third passage 553 after passing through the first passage 551 as shown by the solid line arrow in FIG. .

  At this time, the oil contained in the refrigerant gas is liquefied by adhering to the inner surface of the third passage 553 in the form of fine particles, and, as shown by the broken arrow in FIG. , And returns to the upstream side of the refrigerant gas flow of the motor 2. On the other hand, the refrigerant gas passes through the second passage 552 after passing through the third passage 553 as indicated by the solid line arrow in FIG.

  According to the compressor having this configuration, in addition to the effects of the first embodiment. Since the oil separation mechanism G2 is provided in the air gap 541, it is possible to eliminate unnecessary magnetic path interference in the rotor 531 and the stator 521.

  The mutual relationship between the first passage 551, the second passage 552, and the third passage 553 is the same as the first passage 51, the second passage 553, and the second passage 553 shown in the first embodiment. The relationship between the size and position of the passage 52 and the third passage 53 may be the same.

(Ninth embodiment)
FIG. 15 shows a ninth embodiment of the compressor of the present invention. The difference from the eighth embodiment (FIG. 14) will be described. In the ninth embodiment, the stator 521 communicates with the third passage 553 and has an inner peripheral surface and an outer periphery of the stator 521. A through passage 524 penetrating the surface. The through passage 524 is formed by cutting out the first stator core 522a.

  Therefore, the oil separated in the third passage 553 of the air gap G2 can be returned to the oil sump also from the outer peripheral side of the stator 521 through the through passage 524.

  The upper part of the inner surface of the through-passage 524 and the upper part of the inner surface of the third passage 553 are preferably connected in the horizontal direction and attached to the upper part of the inner surface of the third passage 553. Oil droplets can be effectively guided to the through-passage 524.

(Tenth embodiment)
FIG. 16 shows a tenth embodiment of the compressor of the present invention. The difference from the ninth embodiment (FIG. 15) will be described. In the tenth embodiment, a plurality of spacers 63 are provided between the first stator core 522a and the second stator core 522b. A space is formed, and this space becomes the through passage 524. The plurality of spacers 63 are arranged at predetermined intervals in the circumferential direction.

  Therefore, since the spacer 63 is provided, it is not necessary to process the first stator core 522a and the second stator core 522b.

(Eleventh embodiment)
FIG. 17 shows an eleventh embodiment of the compressor of the present invention. The difference from the first embodiment (FIG. 1) will be described. In the eleventh embodiment, the configuration of the compression unit and the motor and the positional relationship between the compression unit and the motor are different.

  A motor 602 and a compression unit 70 are arranged in the sealed container 1 in order from the bottom to the top.

  The motor 602 is disposed in a region in the sealed container 1 that is filled with a low-pressure refrigerant gas to be sucked into the compression unit 70. Specifically, the inside of the sealed container 1 is partitioned into a high pressure region H and a low pressure region L with the compression unit 70 interposed therebetween, and the motor 602 is disposed in the low pressure region L. This compressor is a so-called low-pressure dome type.

  The compression unit 70 includes a main body 74 attached to the sealed container 1, a fixed scroll 71 fixed to and supported by the main body 74, and a turning scroll 72 that meshes with the fixed scroll 71.

  The main body 74 holds one end side of the shaft 20 while inserting the shaft 20 through a bearing, for example.

  The fixed scroll 71 has a spiral wrap on the end plate, and meshes with the orbiting scroll 72 to form a plurality of compression chambers 73. The orbiting scroll 72 is attached to one end of the shaft 20 of the motor 2 so as to freely rotate, and revolves as the shaft 20 rotates.

  The main body 74 has a suction hole 74 a that communicates the low pressure region L and the compression chamber 73, and the fixed scroll 71 has a discharge hole 71 a that communicates the high pressure region H and the compression chamber 73. .

  The sealed container 1 is provided with a refrigerant gas suction pipe 6 and a refrigerant gas discharge pipe 7. The suction pipe 6 is open to the low pressure region L between the stator 21 of the motor 2 and the compression unit 70. The discharge pipe 7 is open to the high pressure region H.

  The motor 602 includes a rotor 631 and a stator 621 disposed on the outer side in the radial direction than the rotor 631. A magnet 633 is attached to the rotor 631, and a coil 623 is attached to the stator 621. An oil separation mechanism G3 is provided inside the stator 621.

  Specifically, the first passage 651, the second passage 652, and the third passage 653 are formed in the stator core 622 of the stator 621 by forming holes and grooves on the outer peripheral side of the coil 623. . The first passage 651 and the second passage 652 respectively extend in the axial direction and do not overlap with each other when viewed from the axial direction. The third passage 653 extends in a direction orthogonal to the first passage 651 and the second passage 652 and connects the first passage 651 and the second passage 652. That is, the oil separation mechanism G3 is formed by the first passage 651, the second passage 652, and the third passage 653.

  Next, the operation of the compressor having this configuration will be described.

  The refrigerant gas is sucked into the low pressure region L in the sealed container 1 from the suction pipe 6, sucked into the compression chamber 73 from the suction hole 74 a, and compressed by the operation of the motor 2. The compressed refrigerant gas is discharged from the discharge hole 71a to the high-pressure region H in the sealed container 1 and discharged from the discharge pipe 7 to the outside of the sealed container 1.

  Further, as shown by the solid line arrow in FIG. 17, the refrigerant gas hits the inner surface of the third passage 653 after passing through the first passage 651. At this time, the oil contained in the refrigerant gas is liquefied by adhering to the inner surface of the third passage 653 in the form of fine particles, and by the action of gravity, as shown by the broken arrow in FIG. Through the passage 651 and return to the lower side of the motor 602. On the other hand, the refrigerant gas passes through the second passage 652 after passing through the third passage 653 as indicated by the solid line arrow in FIG.

  According to the compressor having this configuration, in addition to the effects of the first embodiment, the oil separation mechanism G3 is provided inside the stator 621. Therefore, the oil separation mechanism G3 is connected to the stator 621. It can be provided on the outer peripheral side, and obstruction of the magnetic path can be eliminated.

  The mutual relationship between the first passage 651, the second passage 652, and the third passage 653 is the same as the first passage 51, the second passage, and the second passage 653. The relationship between the size and position of the passage 52 and the third passage 53 may be the same.

  In addition, this invention is not limited to the above-mentioned embodiment. For example, the oil separation mechanism G1, G2, G3 is connected to at least one of the stator 21, 521, 621, the rotor 31, 130, 230, 430, 531, 631, and the air gap 41, 541, 641. What is necessary is just to provide. At this time, it is preferable to form the adjacent third passages 53, 553, and 653 so as to communicate with each other, so that oil can be effectively separated.

  Further, the stator 21, 521, 621 is fixed to the sealed container 1 on the radially inner side, and the rotor 31, 130, 230, 430, 531, 631 is fixed to the shaft 20 on the radially outer side. It may be.

  Further, the oil separation mechanism G1, G2, G3 of the present invention is applied to a brushless DC motor (whether or not the drive current waveform is a sine wave) in which a magnet is provided on the rotor side and a coil is provided on the stator side. However, you may apply to the DC motor with a brush which provided the magnet in the stator side and provided the coil in the rotor side.

  In the rotor, the laminated thin plates are integrally fixed by the rivet 60, but the laminated thin plates may be integrally fixed by caulking.

  The oil separation mechanisms G1, G2, and G3 may have any configuration as long as oil flows in a substantially crank shape from the opening at one axial end toward the opening at the other axial end. Here, the crank shape refers to a shape having at least two bent portions, for example, a saddle shape, an engine crankshaft shape, and the like.

  Further, the third passages 53, 553, 653 may not extend in a direction orthogonal to the axial direction, and the first passages 51, 551, 651 and the second passages 52, 552, 652 are connected to each other. It suffices if the first passages 51, 551, 651 and the second passages 52, 552, 652 are connected to each other so as to extend in the intersecting direction.

  Moreover, the central axis of the said airtight container 1 may incline with respect to a horizontal surface. Moreover, the compression part and the motor may be arranged horizontally. In other words, the same effect can be obtained with a compressor in which a motor is placed in an atmosphere of refrigerant gas and oil.

  Further, in an embodiment in which a permanent magnet is not a constituent element, the present invention can be applied to a switched reluctance motor, an induction motor, or the like.

It is a longitudinal section showing a 1st embodiment of a compressor of the present invention. It is AA sectional drawing of FIG. It is BB sectional drawing of FIG. It is CC sectional drawing of FIG. It is effect | action explanatory drawing which shows a refrigerant gas flow. It is a longitudinal cross-sectional view which shows 2nd Embodiment of the compressor of this invention. It is a cross-sectional view of the first rotor core. It is a cross-sectional view of a second rotor core. It is a cross-sectional view of a third rotor core. It is a longitudinal cross-sectional view which shows 3rd Embodiment of the compressor of this invention. It is a cross-sectional view of a third rotor core. It is a cross-sectional view which shows 4th Embodiment of the compressor of this invention. It is a longitudinal cross-sectional view which shows 5th Embodiment of the compressor of this invention. It is a longitudinal cross-sectional view of a rotor. It is a cross-sectional view of the first rotor core. It is a cross-sectional view of a second rotor core. It is a cross-sectional view of a third rotor core. It is a top view which shows 6th Embodiment of the compressor of this invention. It is a cross-sectional view of the 1st rotor core while showing a 7th embodiment of the compressor of the present invention. It is a cross-sectional view of a second rotor core. It is a longitudinal cross-sectional view which shows 8th Embodiment of the compressor of this invention. It is a longitudinal cross-sectional view which shows 9th Embodiment of the compressor of this invention. It is a longitudinal cross-sectional view which shows 10th Embodiment of the compressor of this invention. It is a longitudinal cross-sectional view which shows 11th Embodiment of the compressor of this invention.

DESCRIPTION OF SYMBOLS 1 Airtight container 11,70 Compression part 2,502,602 Motor 20 Shaft 21,521,621 Stator 31,130,230,430,531,631 Rotor 33 Magnet 41,541,641 Air gap 51,551,651 Above 1 passage 52, 552, 652 The second passage 53, 553, 653 The third passage 51a, 52a Opening 61 Rotating plate 131 First rotor core 132 Second rotor core 133, 233, 333 Third rotor core 431 First rotor core 431a Magnet fitting hole 432 Second rotor core 432a Magnet fitting hole 433 Third rotor core 524 Through passage G1, G2, G3 Oil separation mechanism

Claims (11)

A sealed container (1);
A compression section (11, 70) disposed in the sealed container (1);
A radial gap type motor (2, 502, 602) disposed in the sealed container (1) and driving the compression part (11, 70) via the shaft (20),
The motor (2, 502, 602) includes a stator (21, 521, 621) and a rotor (31, 130, 230,) facing each other in a direction orthogonal to the axis via an air gap (41, 541, 641). 430, 531, 631)
An oil separation mechanism (G1, G2, G3) for separating oil by flowing oil in a substantially crank shape from the opening at one axial end to the opening at the other axial end inside the motor (2, 502, 602). )
The oil separation mechanism (G1, G2, G3)
A first passage (51, 551, 651) and a second passage (52, 552, 652) that extend in the axial direction with the same width along the axial direction in the longitudinal section and do not overlap each other when viewed from the axial direction;
The first passage (51, 551, 651) and the second passage extending in a direction orthogonal to the first passage (51, 551, 651) and the second passage (52, 552, 652). (52, 552, 652) and a third passage (53, 553, 653) connecting the two,
The cross-sectional area of the cross-section of the third passage (53,553,653) is the opening (on the third passage (53,553,653) side of the first passage (51,551,651) ( 51a) and the area of the opening (52a) on the third passage (53,553,653) side of the second passage (52,552,652). Compressor. The compressor according to claim 1,
The first passage (51, 551, 651) is upstream and lower in the direction in which the refrigerant gas flows than the second passage (52, 552, 652).
The area of the opening (51a, 52a) on the side of the third passage (53, 553, 653) of the first passage (51, 551, 651) is the same as that of the second passage (52, 552, 652). A compressor characterized by being larger than the area of the opening (51a, 52a) on the side of the third passage (53, 553, 653). The compressor according to claim 1,
The compressor characterized in that the oil separation mechanism (G1) is provided inside the rotor (31, 130, 230, 430). The compressor according to claim 3, wherein
The first passage (51) is more upstream and lower than the second passage (52) in the direction in which the refrigerant gas flows,
Said first passage (51) includes a compressor, characterized in that the upper Symbol second passage (52) good remote, radially outward there. The compressor according to claim 3, wherein
The rotor (130, 230) includes a first rotor core (131) and a second rotor core (132) arranged along an axis, the first rotor core (131), and the second rotor core (132). A third rotor core (133, 233, 333) sandwiched between
A magnet (33) is attached to each of the inside of the first rotor core (131) and the second rotor core (132),
The first passage (51) is provided inside the first rotor core (131),
The second passage (52) is provided in the second rotor core (132),
The third passage (53) is provided inside the third rotor core (133, 233, 333),
By shifting the first rotor core (131) and the second rotor core (132) in the circumferential direction, the first passage (51), the second passage (52), and the first passage The compressor characterized in that the magnet (33) on the rotor core (131) side and the magnet (33) on the second rotor core (132) side are respectively shifted in the circumferential direction. The compressor according to claim 3, wherein
The rotor (430) includes a first rotor core (431) and a second rotor core (432) arranged along an axis, and between the first rotor core (431) and the second rotor core (432). A third rotor core (433) sandwiched between
A magnet (33) is attached to each of the first rotor core (431) and the second rotor core (432),
The first rotor core (431) has a magnet fitting hole (431a) that fits the magnet (33) and has a space larger than the cross-sectional area of the magnet (33) in a plane orthogonal to the axis. ,
The second rotor core (432) has a magnet fitting hole (432a) that fits the magnet (33) and has a space larger than the cross-sectional area of the magnet (33) in a plane orthogonal to the axis. ,
The first passage (51) is a space where the magnet (33) in the magnet fitting hole (431a) of the first rotor core (431) does not exist,
The second passage (52) is a space where the magnet (33) in the magnet fitting hole (432a) of the second rotor core (432) does not exist,
The compressor characterized in that the third passage (53) is provided in the third rotor core (433). The compressor according to claim 3, wherein
The compressor characterized in that the third passage (53) communicates with a radially outer side of the rotor (230). The compressor according to claim 3, wherein
In the rotor (31, 130, 230, 430), a downstream side of the first passage (51) or the second passage (52) on the downstream side in the flow direction of the refrigerant gas, A compressor comprising a rotating plate (61) that rotates together with the rotor (31, 130, 230, 430). The compressor according to claim 1,
The compressor characterized in that the oil separation mechanism (G2) is provided in the air gap (541). The compressor according to claim 9 , wherein
The stator (521) is disposed radially outside the rotor (531),
The compressor characterized in that the stator (521) has a through passage (524) communicating with the third passage (553) and penetrating the inner peripheral surface and the outer peripheral surface of the stator (521). The compressor according to claim 1,
The compressor characterized in that the oil separation mechanism (G3) is provided inside the stator (621).

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