JP4618050B2 - Compressor - Google Patents

Description

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

  2. Description of the Related Art Conventionally, a compressor includes an axial gap type motor arranged in a vertical direction in an airtight container and a compression unit driven by the motor (Japanese Patent Laid-Open No. 61-185040). Patent Document 1).

  The motor includes a stator, a rotor disposed on both sides in the axial direction 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 refrigerant gas mainly flows through the passage on the outer peripheral side of the motor and the air gap.

  However, in the conventional compressor, the passage on the outer peripheral side of the motor and the air gap are narrow refrigerant passages, so that the refrigerant gas flows through the narrow refrigerant passage, and the upstream side of the motor And the pressure difference between the downstream side increases and the pressure loss of the compressor increases.

The lubricating oil contained in the refrigerant gas is blown to the outer peripheral side of the motor by the oil separator. Since the outer peripheral side of the motor is the refrigerant passage, the lubricating oil is supplied from the outer peripheral side of the motor to the refrigerant. The gas flows to the downstream side of the motor. For this reason, it becomes difficult to separate the lubricating oil from the refrigerant gas.
Japanese Patent Laid-Open No. 61-185040

  Therefore, an object of the present invention is to provide a compressor capable of separating oil while reducing pressure loss without increasing the number of parts.

In order to solve the above problems, the compressor of the present invention is:
An airtight container, a compression part disposed in the airtight container, an axial gap type motor disposed in the airtight container and driving the compression part via a shaft,
This motor has at least a pair of a stator and a rotor that are axially opposed to each other via an air gap,
At least one of the stator or the rotor is provided with 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.

  According to the compressor of the present invention, the oil separation mechanism that separates the oil by flowing the oil in a substantially crank shape from the opening at one axial end to the opening at the other axial end on at least one of the stator or the rotor. Since the oil separation mechanism is provided in addition to the air gap space and the outer peripheral passage of the motor, the differential pressure between the upstream side and the downstream side of the refrigerant gas flow of the motor is provided. The pressure loss of the compressor can be reduced. Thus, it is not necessary to separately provide a member for separating lubricating oil such as an oil separator, and oil separation can be performed while reducing pressure loss. In this specification, the crank shape means a shape having at least two bent portions, for example, a hook 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.

  In the compressor according to the embodiment, the oil separation mechanism includes a first passage and a second passage that extend in the axial direction and do not overlap with each other when viewed from the axial direction, the first passage, and the second passage. The third passage extends in a direction intersecting the passage and connects the first passage and the second passage.

  According to the compressor of this embodiment, the oil separation mechanism includes the first passage and the second passage that extend in the axial direction and do not overlap with each other when viewed from the axial direction, and the first passage and the second passage. Since it consists of a third passage that extends in a direction intersecting the passage and connects the first passage and the second passage, for example, in order from the upstream to the downstream of the refrigerant gas flow (or from the bottom to the top) If the first passage, the third passage, and the second passage are arranged, the mixture of the lubricating oil and the refrigerant gas passes through the first passage, and then the second passage. It hits the inner surface of 3 passages. At this time, the lubricating oil in the form of fine particles adheres to the inner surface of the third passage and becomes liquefied by becoming large particles and returns to the first passage, while the refrigerant gas flows into the third passage. After passing through the second passage. In this way, the oil can be reliably separated.

In the compressor of one embodiment,
The oil separation mechanism is provided in the stator,
The stator includes a first plate member and a second plate member arranged in the axial direction, and a coil sandwiched between the first plate member and the second plate member. And
The first passage is provided in the first plate member,
The second passage is provided in the second plate member,
The third passage is provided in a space between the first plate member and the second plate member.

  According to the compressor of this embodiment, the first passage is provided in the first plate member, and the second passage is provided in the second plate member. The first passage and the second passage can be easily manufactured, and can be easily adjusted so that the opening of the first passage and the opening of the second passage do not overlap.

  In addition, since the third passage is provided in a space between the first plate member and the second plate member, the third passage can be enlarged. That is, since this motor is an axial gap type motor, the first plate-like member and the second plate-like member can be largely formed in a direction orthogonal to the axial direction. For this reason, lubricating oil can be effectively separated from the refrigerant gas. Further, the separated lubricating oil is returned from the third passage to the place where the lubricating oil is present via the other passage (for example, the outer peripheral passage of the stator) in addition to the first passage. Oil separation can be performed more reliably.

In the compressor of one embodiment,
The oil separation mechanism is provided in the rotor,
The rotor includes a first plate member and a second plate member arranged in the axial direction, and a magnet sandwiched between the first plate member and the second plate member. And
The first passage is provided in the first plate member,
The second passage is provided in the second plate member,
The third passage is provided in a space between the first plate member and the second plate member.

  According to the compressor of this embodiment, the first passage is provided in the first plate member, and the second passage is provided in the second plate member. The first passage and the second passage can be easily manufactured, and can be easily adjusted so that the opening of the first passage and the opening of the second passage do not overlap.

  In addition, since the third passage is provided in a space between the first plate member and the second plate member, the third passage can be enlarged. That is, since this motor is an axial gap type motor, the first plate-like member and the second plate-like member can be largely formed in a direction orthogonal to the axial direction. For this reason, lubricating oil can be effectively separated from the refrigerant gas. Further, the separated lubricating oil is returned from the third passage to the place where the lubricating oil is present via the other passage (for example, the outer peripheral passage of the rotor) in addition to the first passage. Oil separation can be performed more reliably.

  Moreover, in the compressor of one Embodiment, the said 1st plate-shaped member or the said 2nd plate-shaped member is a stator yoke.

  According to the compressor of this embodiment, since the first plate-like member or the second plate-like member is a stator yoke, it is not necessary to provide new parts, and an increase in the number of parts can be suppressed.

  In the compressor according to the embodiment, the first plate member or the second plate member is a rotor yoke.

  According to the compressor of this embodiment, since the first plate-like member or the second plate-like member is a rotor yoke, it is not necessary to provide new parts, and an increase in the number of parts can be suppressed.

  In the compressor of one embodiment, the passage on the upstream side in the direction in which the refrigerant gas flows of the first passage or the second passage is the first passage or the second passage. It is on the radially outer side of the passage on the downstream side in the direction in which the refrigerant gas flows.

  According to the compressor of this embodiment, the passage on the upstream side of the refrigerant gas flow in the first passage or the second passage is the refrigerant gas in the first passage or the second passage. Since it is on the radially outer side than the passage on the downstream side of the flow, the separated lubricating oil is conveyed to the outside by the centrifugal force generated by the rotation of the rotor and returns to the upstream passage on the radially outer side. The refrigerant gas is guided to a downstream passage on the radially inner side. In this way, the lubricating oil can be reliably separated from the refrigerant gas.

  In the compressor of one embodiment, the lower passage of the first passage or the second passage is more than the upper passage of the first passage or the second passage. Located radially outside.

  According to the compressor of this embodiment, the lower passage of the first passage or the second passage is more than the upper passage of the first passage or the second passage. Since the separated lubricating oil is outside in the radial direction, the separated lubricating oil is carried outside by the centrifugal force generated by the rotation of the rotor, and returns to the lower passage on the outside in the radial direction, while the refrigerant gas is inside in the radial direction. It is led to a certain upper passage. In this way, the lubricating oil can be reliably separated from the refrigerant gas.

  Moreover, in the compressor of one Embodiment, the said 1st channel | path and the said 2nd channel | path are provided in the vicinity of the said shaft rather than the said airtight container.

  According to the compressor of this embodiment, the first passage and the second passage are provided in the vicinity of the shaft with respect to the sealed container, and therefore the first passage on the radially inner side in the negative pressure state. The refrigerant gas containing the lubricating oil easily flows into the first passage or the second passage, and the lubricating oil can be effectively separated from the refrigerant gas.

  Moreover, in the compressor of one Embodiment, the said 1st channel | path and the said 2nd channel | path are provided in the vicinity of the said airtight container rather than the said shaft.

  According to the compressor of this embodiment, the first passage and the second passage are provided in the vicinity of the sealed container with respect to the shaft. The separated lubricating oil is easily returned to the second passage, and the lubricating oil can be effectively separated from the refrigerant gas.

  In the compressor according to an embodiment, the area of the opening on the third passage side of the passage on the upstream side in the flow direction of the refrigerant gas in the first passage or the second passage is the first passage. It is larger than the area of the opening part of the said 3rd channel | path side of the downstream channel | path of the flow direction of refrigerant gas among 1 channel | path or the said 2nd channel | path.

  According to the compressor of this embodiment, the area of the opening of the passage on the upstream side of the refrigerant gas flow of the first passage or the second passage is the first passage or the second passage. Since it is larger than the area of the opening of the passage downstream of the refrigerant gas flow in the passage, the separated lubricating oil can be reliably returned to the upstream side of the refrigerant gas flow from the passage upstream of the refrigerant gas flow. it can.

  In the compressor according to the embodiment, the area of the opening on the third passage side of the lower passage of the first passage or the second passage is the first passage or the second passage. It is larger than the area of the opening on the third passage side of the upper passage of the two passages.

  According to the compressor of this embodiment, the area of the opening of the lower passage of the first passage or the second passage is the upper side of the first passage or the second passage. Therefore, the separated lubricating oil can be reliably returned to the lower side from the lower side passage.

  In the compressor of one embodiment, the discharge port of the refrigerant gas discharged from the compression unit into the sealed container is upstream of the direction in which the refrigerant gas flows in the first passage or the second passage. Near the opening of the side passage.

  Here, the refrigerant gas discharge port includes a discharge hole of the casing of the compression unit, a pipe port connected to the discharge hole, and the like.

  According to the compressor of this embodiment, the discharge port for the refrigerant gas discharged from the compression unit into the sealed container is upstream of the direction in which the refrigerant gas flows in the first passage or the second passage. Since it is in the vicinity of the opening of the side passage, the refrigerant gas can be guided to the upstream side passage, and the lubricating oil can be effectively separated.

  In the compressor according to the embodiment, the first passage is a plurality of first slits radially provided in the first plate-like member, and the second passage is the second passage. A plurality of second slits provided radially on the plate-like member, and the plurality of first slits and the plurality of second slits do not overlap when viewed in the axial direction.

  According to the compressor of this embodiment, the first passage is a plurality of first slits provided radially on the first plate-like member, and the second passage is the second passage. Since it is a plurality of second slits provided radially on the plate-like member, in addition to the role of flowing the refrigerant gas through the plurality of first slits and the plurality of second slits, between adjacent magnetic poles It can have a role of magnetically insulating (interfering with the magnetic path).

  According to the compressor of the present invention, the oil separation mechanism that separates the oil by flowing the oil in a substantially crank shape from the opening at one axial end to the opening at the other axial end on at least one of the stator or the rotor. Since it is provided, oil separation can be performed while reducing pressure loss without increasing the number of parts.

  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 an embodiment of the compressor of the present invention. The compressor includes a compression unit 11 and an axial gap type 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 hermetic 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 that is filled with the high-pressure refrigerant discharged from the compression unit 11. 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 facing the stator 21 with an air gap 41 interposed therebetween. The shaft 20 is fixed to the rotor 31 and transmits the rotational force of the rotor 31 to the compression unit 11. The shaft 20 extends from the rotor 31 and is held by a bearing (not shown).

  As shown in FIGS. 2, 3 </ b> A, and 3 </ b> B, the stator 21 includes a stator core 27 attached to the sealed container 1 and a coil 23 attached to the stator core 27.

  The stator core 27 includes an annular stator yoke 24 (as a plate-like member) arranged so as to be substantially orthogonal to the shaft 20, and a protrusion provided on one surface of the stator yoke 24 on the rotor 31 side. And a stator plate 25 (as a plate member) sandwiching the coil 23 in cooperation with the stator yoke 24.

  The stator yoke 24 is a magnetic plate for magnetically connecting the opposite air gap side of the protrusion 26, and the magnetic flux that flows from the rotor 31 into the one protrusion 26 via the air gap 41. To the other protrusions 26.

  The protrusion 26 extends along the shaft 20, and a plurality of the protrusions 26 are provided around the shaft 20. The coil 23 is wound around the axis of each protrusion 26. The coil 23 is excited to generate an axial magnetic flux at the protrusion 26. The coil 23 is so-called “concentrated winding” around the stator core 27, so that the winding is simple and the amount of copper can be reduced.

  Each of the protrusions 26 and the coils 23 has six, and the stator 21 has four poles. That is, the stator 21 is considered to correspond to a concentrated winding 4 pole 6 slot of a radial gap type motor. The windings are three-phase, for example, star-connected and supplied with current from an inverter.

  The stator plate 25 is made of a magnetic material, and is provided with a belt-like slit 25a that magnetically insulates between the adjacent protrusions 26. The slits 25a extend radially outward from the center of the stator plate 25 in the radial direction. The slit 25 a is provided only in the stator plate 25 and is not provided in the stator yoke 24. With this configuration, since the area of the stator core 27 facing the air gap 41 is increased, the flux linkage can be increased.

  The stator 21 has a stator outer passage 21 e penetrating along the axis of the shaft 20 in the vicinity of the sealed container 1 rather than the shaft 20. The stator outer passage 21e includes a gap between the outer peripheral surface of the stator yoke 24 and the inner surface of the sealed container 1 (stator yoke outer passage), the outer peripheral surface of the stator plate 25, and the inner surface of the sealed container 1. And a gap between them (stator plate outer passage).

  The stator 21 has a stator inner passage 21 a penetrating along the axis of the shaft 20 in the vicinity of the shaft 20 rather than the sealed container 1. The stator inner passage 21a includes a circular hole 25c provided in the stator plate 25 (that is, a stator plate inner passage) and a circular hole 24c provided in the stator yoke 24 (ie, the stator yoke). An inner passage).

  Here, the vicinity of the shaft 20 is in the vicinity of the inner diameter of the stator 21, and generally has an inner portion closer to the rotating shaft than the coil 23. That is, it can be grasped that the rotor 31 and the stator 21 are on the inner peripheral side than the portion that generates torque by exchanging magnetic flux through the air gap 41.

  Specifically, a hole through which the shaft 20 is inserted is provided in the central portion of the stator plate 25, and a plurality of the hole portions 25c are provided at regular intervals around the shaft insertion hole. On the other hand, a hole through which the shaft 20 is inserted is provided in the central portion of the stator yoke 24, and a plurality of the holes 24c are provided around the shaft insertion hole at regular intervals.

  The hole 24c of the stator yoke 24 and the hole 25c of the stator plate 25 are not arranged in a substantially straight line in the axial direction, do not overlap each other when projected in the axial direction, and the coil 23 Does not overlap. Specifically, the hole 24c of the stator yoke 24 is located between the adjacent holes 25c and 25c of the stator plate 25 when viewed from the axial direction. The hole 24c of the stator yoke 24 and the hole 25c of the stator plate 25 are displaced in the circumferential direction when viewed from the axial direction.

  The hole 24c of the stator yoke 24, the space between the stator yoke 24 and the stator plate 25, and the hole 25c of the stator plate 25 are sequentially communicated to form an oil separation mechanism G. .

  In other words, the hole 24c of the stator yoke 24 is the first passage 51 of the stator 21 that opens in one axial direction and extends in the axial direction. The hole 25c of the stator plate 25 is a second passage 52 of the stator 21 that is open on the other side in the axial direction and extends in the axial direction. A space between the stator yoke 24 and the stator plate 25 is a third passage 53 of the stator 21 that extends in a direction orthogonal to the axial direction.

  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.

  Here, the stator plate 25 is preferably magnetically independent from the shaft 20 that is a magnetic material, and a four-pole magnetic field that appears on the surface of the stator plate 25 is transmitted through the shaft 20. It can be prevented from weakening due to a short circuit of magnetic flux. This is not the case when the shaft 20 is a nonmagnetic material.

  In this case, the gap between the shaft 20 and the stator plate 25 can also be grasped as a part of the area of the stator plate inner passage 25c. Therefore, the stator yoke inner passage 24 c is provided outside at least the inner diameter of the stator plate 25.

  When a bearing for supporting the shaft 20 is provided in the central portion of the stator yoke 24, there is no gap between the stator yoke 24 and the shaft 20, so the stator plate inner passage 25c is connected to the stator yoke 24. Even when projected onto the stator yoke 24 in the axial direction, the stator yoke inner passage 24c does not overlap.

  If there is no bearing that supports the shaft 20 at the center of the stator yoke 24, a gap is formed between the stator yoke 24 and the shaft 20 and partially overlaps the stator plate inner passage 25c. Is provided with a circular guide (not shown) around the inner diameter of the stator yoke 24 so that the lubricating oil does not easily enter the gap between the stator yoke 24 and the shaft 20 and is discharged from the compression unit 11. Lubricating oil may be guided outside the guide.

  As shown in FIGS. 2, 4A and 4B, the rotor 31 includes an annular rotor yoke 34 (as a plate member) attached to the shaft 20 and a surface of the rotor yoke 34 on the stator 21 side. A permanent magnet 33 provided and a rotor plate 35 (as a plate-like member) sandwiching the permanent magnet 33 in cooperation with the rotor yoke 34 are provided.

  The permanent magnet 33 has different magnetic poles alternately in the circumferential direction of the shaft 20. The permanent magnet 33 generates a magnetic flux in a direction along the shaft 20.

  The rotor yoke 34 is made of a magnetic material, and plays a role of increasing permeance by short-circuiting different magnetic poles adjacent to each other generated on the side opposite to the air gap of the permanent magnet 33.

  Since the rotor 31 has the permanent magnet 33, when the motor 2 is stopped, the rotor 31 can be attracted to the stator 21 to prevent reverse rotation of the rotor 31 and the shaft 20. Moreover, since the magnetic flux density of the air gap 41 can be increased during the operation of the motor 2, high output and high efficiency of the compressor can be realized. The permanent magnet 33 is not essential.

  The rotor plate 35 is made of a magnetic material, and is provided with a strip-shaped slit 35 a that magnetically insulates between the adjacent magnetic poles of the permanent magnet 33. The slits 35a extend radially outward from the center of the rotor plate 35 in the radial direction. Here, since the area of the rotor 31 facing the air gap 41 is increased by this configuration, the flux linkage can be increased. Further, since the demagnetizing field is not directly applied to the permanent magnet 33, the demagnetization resistance is also increased. Further, when the permanent magnet 33 is a sintered rare earth magnet or the like, the high-frequency component of the magnetic flux does not easily reach the inside of the permanent magnet 33, so that the generation of eddy current inside the permanent magnet 33 is suppressed. Further, loss reduction and temperature rise reduction can be achieved.

  The rotor plate 35 also has a role of preventing the permanent magnet 33 from shifting in the axial direction by providing mechanical coupling with the rotor yoke 34. The rotor plate 35 may be a non-magnetic thin plate as long as strength can be ensured. In this case, however, the magnetic air gap is enlarged.

  The rotor 31 has a rotor outer passage 31 e penetrating along the axis of the shaft 20 in the vicinity of the sealed container 1 rather than the shaft 20. The rotor outer passage 31e is formed between a clearance (rotor yoke outer passage) between the outer peripheral surface of the rotor yoke 34 and the inner surface of the sealed container 1, and between the outer peripheral surface of the rotor plate 35 and the inner surface of the sealed container 1. And a gap (a rotor plate outer passage).

  The rotor 31 has a rotor inner passage 31 a penetrating along the axis of the shaft 20 in the vicinity of the shaft 20 rather than the sealed container 1. The rotor inner passage 31a includes a circular hole 35c (that is, a rotor plate inner passage) provided in the rotor plate 35 and a circular hole 34c (that is, a rotor yoke inner passage provided in the rotor yoke 34). ).

  Here, the vicinity of the shaft 20 is the vicinity of the inner diameter of the rotor 31, and generally refers to a portion on the inner side of the rotating shaft side than the permanent magnet 33. That is, it can be grasped that the rotor 31 and the stator 21 are on the inner peripheral side than the portion that generates torque by exchanging magnetic flux through the air gap 41.

  Specifically, the hole portion 35 c that also serves as a hole through which the shaft 20 is inserted is provided in the central portion of the rotor plate 35. On the other hand, a hole through which the shaft 20 is inserted is provided at the center of the rotor yoke 34, and a plurality of the holes 34c are provided around the shaft insertion hole.

  The hole 34c of the rotor yoke 34 and the hole 35c of the rotor plate 35 are not arranged on a substantially straight line in the axial direction, do not overlap each other when projected in the axial direction, and the permanent magnet 33. Does not overlap. Specifically, the hole 34c of the rotor yoke 34 is located radially outside the hole 35c of the rotor plate 35 when viewed from the axial direction.

  The hole 35c of the rotor plate 35, the space between the rotor yoke 34 and the rotor plate 35, and the hole 34c of the rotor yoke 34 are sequentially communicated to form an oil separation mechanism G '.

  In other words, the gap between the inner surface of the hole 35c of the rotor plate 35 and the shaft 20 is the first passage 51 ′ of the rotor 31 that opens in one axial direction and extends in the axial direction. . The hole 34c of the rotor yoke 34 is a second passage 52 'of the rotor 31 that opens in the other axial direction and extends in the axial direction. A space between the rotor yoke 34 and the rotor plate 35 is a third passage 53 ′ of the rotor 31 extending in a direction orthogonal to the axial direction.

  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 downstream and on the upper side in the direction in which the refrigerant gas flows. It is larger than the area of the opening 52a ′ on the third passage 53 ′ side in the second passage 52 ′.

  Here, it is desirable that the rotor plate 35 be magnetically independent from the shaft 20 that is a magnetic material, and a four-pole magnetic field that appears on the surface of the rotor plate 35 is transmitted through the shaft 20. It can be prevented from weakening due to a short circuit of magnetic flux. This is not the case when the shaft 20 is a nonmagnetic material.

  Here, the slit 35 a is provided only in the rotor plate 35 and is not provided in the rotor yoke 34. The slit 35a is a rotor plate inner passage (provided near the shaft 20 rather than the sealed vessel 1) or a rotor plate outer passage (provided closer to the sealed vessel 1 than the shaft 20). Whether or not the slit 35a is grasped as one by the permanent magnet 33 or other member.

  That is, if the slit 35a is completely closed by the permanent magnet 33 or other member (for example, resin), the slit 35a does not work as any passage. Further, if the slit 35a is not closed at both sides, the slit 35a is grasped as the rotor plate inner passage, the rotor plate outer passage, or a combination of both.

  Further, if only a part of the slit 35a is not blocked, only the unblocked part is grasped as the rotor plate inner passage or the rotor plate outer passage.

  It is not important whether the rotor plate inner passage or the rotor plate outer passage is grasped, and when these passages are projected on the rotor yoke 34 in the axial direction, the passages of the rotor yoke 34 The hole 34c may not overlap with the hole 34c when viewed from the axial direction. In the first embodiment, as shown in FIGS. 4A and 4B, the slit 35a is not closed at all.

  This concept can also be applied to the slit 25a provided in the stator plate 25. In the first embodiment, as shown in FIGS. 3A and 3B, the slit 25a of the stator plate 25 is partially blocked by the coil 23. The inner portion (provided closer to the shaft 20 than the sealed container 1) is part of the stator plate inner passage, and the outer portion (provided closer to the sealed container 1 than the shaft 20). It can be grasped as part of the stator plate outer passage.

  The permanent magnet 33 communicates with the stator inner passage 21a via the rotor inner passage 31a and the air gap 41, and has a space 33a that extends in the radial direction and opens to the outer periphery. Specifically, the permanent magnet 33 has a plurality of magnets having one magnetic pole, and the plurality of magnets are arranged so that the magnetic poles are alternately different in the circumferential direction of the shaft 20. The space 33a (that is, a passage between magnets) is formed between the adjacent magnets. However, this intermagnet passage 33a is not essential.

  However, in the case where the intermagnet passage 33a is used as the third passage 53 'of the oil separation mechanism G' of the rotor 31, the intermagnet passage 33a is essential.

  Here, the communication means a state in which refrigerant gas and lubricating oil can sequentially pass through the stator inner passage 21a, the air gap 41, the rotor inner passage 31a, and the intermagnet passage 33a. That is, there is nothing clearly obstructing the flow of refrigerant gas and lubricating oil between these passages. For example, the entrances of these passages are not prevented by iron or resin.

  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 crankpin 17 provided on the shaft 20 is disposed inside the main body portion 12 so as to be able to revolve, and a compression action is performed by the revolving motion of the roller 13. 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.

  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 rotatably supported by the stator 21.

  On the lower side in the sealed container 1, there is a lubricating oil 8 in which the lower part of the shaft 20 is immersed. The lubricating oil 8 goes up inside 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.

  A refrigerant 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. The compressed refrigerant, together with lubricating oil, is discharged into the sealed container 1 from the discharge hole 11a of the compression unit 11 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, the refrigerant gas mainly flows through the stator inner passage 21a and the rotor inner passage 31a in addition to the conventional outer passage on the motor 2 as shown by the solid arrows in FIG.

  More specifically, the refrigerant gas passes through the hole 24c (the first passage 51) of the stator yoke 24 and then passes through the hole 24c (the first passage 51) of the stator yoke 24 and the above. Since the hole 25c (the second passage 52) of the stator plate 25 does not overlap with the hole 25c (the second passage 52) when viewed from the axial direction, the refrigerant gas hits the stator plate 25 (the inner surface of the third passage 53).

  Then, the lubricating oil contained in the refrigerant gas adheres to the stator plate 25 in the form of fine particles and becomes liquefied by becoming large particles, and as shown by the broken arrow in FIG. It returns to the upstream side of the refrigerant gas flow of the motor 2 through the hole 24c (the first passage 51) and the stator outer passage 21e.

  If the lower surface of the stator plate 25 is orthogonal to the hole 24c of the stator yoke 24, the lubricating oil adhering to the stator plate 25 in the form of fine particles when the refrigerant hits the lower surface of the stator plate 25 is reduced. The non-rotation of the stator 21 does not have a velocity component in a direction perpendicular to the axis, and can only fall down due to gravity or reaction force.

  On the other hand, the refrigerant gas passes through the space (the third passage 53) between the stator yoke 24 and the stator plate 25, and then the hole 25c (the second passage 52) of the stator plate 25. Pass through.

  Thereafter, the refrigerant gas passes through the hole 35c (the first passage 51 ′) of the rotor plate 35, and then the hole 35c (the first passage 51 ′) of the rotor plate 35 and the above Since the hole 34c (the second passage 52 ′) of the rotor yoke 34 does not overlap with the hole 34c when viewed from the axial direction, the refrigerant gas hits the rotor yoke 34 (the inner surface of the third passage 53 ′).

  The lubricating oil contained in the refrigerant gas is liquefied by adhering to the rotor yoke 34 in the form of fine particles, and the intermagnet passage 33a is caused by the centrifugal force of the rotor 31 as shown by the broken arrow in FIG. It passes through (the third passage 53 ′) and is blown to the outer peripheral side of the rotor 31, and returns to the upstream side of the refrigerant gas flow of the motor 2 through the rotor outer passage 31e.

  On the other hand, the refrigerant gas passes through the space (the third passage 53 ′) between the rotor yoke 34 and the rotor plate 35, and then the hole 35c (the second passage 52 ′) of the rotor plate 35. )

  According to the compressor having the above configuration, since the oil separation mechanism G is provided in the stator 21, the mixture of lubricating oil and refrigerant gas passes through the first passage 51 and then passes through the third passage 53. Bump into the inside. At this time, the lubricating 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 manner, the oil separation mechanism G passes through the third passage 53 from the opening at one axial end (opening of the first passage 51) and the opening at the other axial end (opening of the second passage 52). ) To flow the refrigerant gas in a substantially crank shape to separate the lubricating oil contained in the refrigerant gas.

  Further, since the oil separation mechanism G ′ is provided in the rotor 31, the mixture of the lubricating oil and the refrigerant gas hits the inner surface of the third passage 53 ′ after passing through the first passage 51 ′. . At this time, the lubricating 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 G ′ passes from the opening at one axial end (the opening of the first passage 51 ′) through the third passage 53 ′ to the opening at the other axial end (the second passage). The coolant gas flows in a substantially crank shape toward the opening 52 ′ and the lubricating oil contained in the coolant gas is separated.

  In addition to the space of the air gap 41 and the passage on the outer peripheral side of the motor 2 (the stator outer passage 21e and the rotor outer passage 31e), the oil separation mechanisms G and G ′ are provided. The differential pressure between the upstream side and the downstream side of the refrigerant gas flow of the motor 2 can be reduced, and the pressure loss of the compressor can be reduced.

  Therefore, it is not necessary to separately provide a member for separating the lubricating oil such as an oil separator, and the oil can be separated while reducing the pressure loss.

  In the stator 21, the first passage 51 is provided in the stator yoke 24 as a first plate member, and the second passage 52 is the stator plate as a second plate member. 25, the first passage 51 and the second passage 52 are easy to manufacture, and the opening 51a of the first passage 51 and the opening 52a of the second passage 52 do not overlap. Easy to adjust.

  In the stator 21, the third passage 53 is provided in a space between the stator yoke 24 and the stator plate 25, so that the third passage 53 can be enlarged. That is, since the motor 2 is an axial gap type motor, the stator yoke 24 and the stator plate 25 can be formed large in a direction orthogonal to the axial direction. For this reason, lubricating oil can be effectively separated from the refrigerant gas. In addition to the first passage 51, the separated lubricating oil passes through the third passage 53 through another passage (for example, the passage on the outer peripheral side of the stator 21), and the place where the lubricating oil is present. The oil can be separated more reliably.

  In the rotor 31, the first passage 51 ′ is provided in the rotor plate 35 as a first plate member, and the second passage 52 ′ is the second plate member. Since it is provided in the rotor yoke 34, the first passage 51 ′ and the second passage 52 ′ can be easily manufactured, and the opening 51a ′ of the first passage 51 ′ and the second passage 52 ′ can be easily formed. The opening 52a ′ can be easily adjusted so as not to overlap.

  Further, in the rotor 31, the third passage 53 'is provided in the space between the rotor plate 35 and the rotor yoke 34, so that the third passage 53' can be enlarged. That is, since the motor 2 is an axial gap type motor, the rotor plate 35 and the rotor yoke 34 can be formed large in a direction orthogonal to the axial direction. For this reason, lubricating oil can be effectively separated from the refrigerant gas. In addition to the first passage 51 ′, the separated lubricating oil is supplied from the third passage 53 ′ through another passage (for example, the passage on the outer peripheral side of the rotor 31). It can be returned to a certain place, and oil separation can be performed more reliably.

  Further, since the stator yoke 24 is used as the first plate member in the stator 21, it is not necessary to provide new parts, and an increase in the number of parts can be suppressed.

  Further, since the rotor yoke 34 is used as the second plate member in the rotor 31, it is not necessary to provide new parts, and an increase in the number of parts can be suppressed.

  In the stator 21 and the rotor 31, the first passages 51, 51 ′ and the second passages 52, 52 ′ are provided closer to the shaft 20 than the sealed container 1. The refrigerant gas containing the lubricating oil easily flows into the first passages 51 and 51 ′ and the second passages 52 and 52 ′ that are radially inward in the negative pressure state. It can be separated effectively. That is, the centrifugal force generated by the rotation of the rotor 31 causes the refrigerant gas to fly outward in the radial direction, whereby the radially inner side becomes negative pressure. For this reason, the refrigerant gas containing the lubricating oil easily flows into the first passages 51 and 51 ′ and the second passages 52 and 52 ′ that are radially inward of the negative pressure state. The lubricating oil can be effectively separated from the oil.

  In the stator 21 and the rotor 31, the areas of the openings 51 a and 51 a ′ on the third passages 53 and 53 ′ in the first passages 51 and 51 ′ on the upstream side in the refrigerant gas flow direction. Is larger than the area of the openings 52, 52a ′ on the third passages 53, 53 ′ side in the second passages 52, 52 ′ on the downstream side in the flow direction of the refrigerant gas. The separated lubricating oil can be reliably returned to the upstream side of the refrigerant gas flow from the first passages 51 and 51 ′ on the upstream side in the direction.

  In the stator 21 and the rotor 31, the areas of the openings 51 a and 51 a ′ on the third passages 53 and 53 ′ side in the first passages 51 and 51 ′ on the lower side in the sealed container 1 are as follows. Since the area of the openings 52, 52a ′ on the third passages 53, 53 ′ side in the second passages 52, 52 ′ on the upper side in the closed vessel 1 is larger, the lower side in the closed vessel 1 The separated lubricating oil can be reliably returned to the lower side from the first passages 51 and 51 ′.

  In the stator 21 and the rotor 31, the first passages 51, 51 ′ and the second passages 52, 52 ′ may be provided closer to the hermetic container 1 than the shaft 20. The separated lubricating oil is easily returned to the first passages 51, 51 ′ or the second passages 52, 52 ′ located on the outer side in the direction, so that the lubricating oil can be effectively separated from the refrigerant gas. That is, since the lubricating oil flies radially outward due to the centrifugal force generated by the rotation of the rotor 31, the first passages 51, 51 ′ and the second passages 52, 52 ′ that are radially outward, Lubricating oil can be reliably separated.

  At this time, the passages 51, 51 ′, 52, 52 ′ on the outer side in the radial direction are holes provided in the outer peripheral portions of the plate-like members 24, 25, 34, 35, and the plate-like members. This is a gap between the outer peripheral surfaces of 24, 25, 34 and 35 and the inner surface of the sealed container 1.

  Since the rotor 31 should not come into contact with the sealed container 1, the outer passage of the rotor yoke 34 and the outer passage of the rotor plate 35 overlap each other when viewed from the axial direction. Therefore, in order to further prevent the oil from rising, an annular oil separator may be attached to the inner surface of the hermetic container 1 at a certain distance above the rotor 31. The inner diameter of the oil separator may be smaller than the outer diameter of the rotor yoke 34.

  In the rotor 31, the first passage 51 ′ on the upstream side of the refrigerant gas flow (or the lower side in the sealed container 1) is connected to the downstream side of the refrigerant gas flow (or the upper side in the sealed container 1). It may be provided on the radially outer side than the second passage 52 ′, and the separated lubricating oil is conveyed to the outside by the centrifugal force generated by the rotation of the rotor 31, and the second lubricating passage is located on the radially outer side. While returning to the first passage 51 ', the refrigerant gas is guided to the second passage 52' on the radially inner side. In this way, the lubricating oil can be reliably separated from the refrigerant gas.

  In addition, an outlet for the refrigerant gas discharged from the compressor 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 direction in which the refrigerant gas flows. Alternatively, the refrigerant gas can be guided to the first passage 51, and the lubricating 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.

  In addition, a guide may be provided to cover the stator inner passage 21a from the discharge hole 11a so as to guide more lubricating oil and refrigerant gas to the stator inner passage 21a than the passage on the outer peripheral side of the motor 2. This is because the passage on the outer peripheral side of the stator 21 is mainly used as a passage for returning the lubricating oil separated from the refrigerant to the lower portion of the sealed container 1.

(Second Embodiment)
FIG. 5 shows a second embodiment of the compressor of the present invention. The difference from the first embodiment (FIG. 2) will be described. In the second embodiment, the configuration of the motor is different. Since other structures are the same as those of the first embodiment, description thereof is omitted.

  The motor 2 includes a rotor 31 and a stator 21 that are arranged in order from the upstream to the downstream in the direction in which the refrigerant gas flows.

  As in the first embodiment (FIG. 2), the stator 21 includes the stator yoke 24, the stator plate 25, and the coil 23 sandwiched between the stator yoke 24 and the stator plate 25. And have.

  The stator 21 has the stator plate inner passage 25c and the stator yoke inner passage 24c as in the first embodiment (FIG. 2).

  The stator 21 has a stator outer passage 21 e penetrating along the axis of the shaft 20 in the vicinity of the sealed container 1 rather than the shaft 20. The stator outer passage 21e includes a gap (stator plate outer passage) between the outer peripheral surface of the stator plate 25 and the inner surface of the sealed container 1, and a hole (stator yoke) provided in the outer peripheral portion of the stator yoke 24. Outer passage).

  A gap between the outer peripheral surface of the stator plate 25 and the inner surface of the sealed container 1 is the first passage 51. A hole provided in the outer peripheral portion of the stator yoke 24 is the second passage 52. A space between the stator yoke 24 and the stator plate 25 is the third passage 53.

  The first passage 51 and the second passage 52 do not overlap when viewed from the axial direction. Specifically, the second passage 52 is displaced radially inward from the first passage 51 as viewed in the axial direction.

  As described above, the stator yoke 24 on the uppermost side (downstream side of the refrigerant gas flow) is brought into close contact with the hermetic container 1 over almost the entire circumference, and the radially inner side of the outer periphery of the stator plate 25 By providing the stator yoke outer passage, the lubricating oil carried to the outer peripheral side by the centrifugal force in the air gap 41 and the lubricating oil carried to the upper portion together with the refrigerant gas through the rotor outer passage 31e are temporarily Since it hits the lower surface of the stator yoke 24, it is possible to effectively prevent oil from rising. Therefore, it is possible to reliably prevent the lubricating oil from flowing out into the upper space of the motor 2 beyond the stator yoke 24.

  As shown in FIGS. 6 and 7, the rotor 31 includes an annular rotor yoke 34 attached to the shaft 20, and an annular permanent magnet 33 provided on one surface of the rotor yoke 34 on the stator 21 side. And a rotor plate 35 sandwiching the permanent magnet 33 in cooperation with the rotor yoke 34.

  The permanent magnet 33 has an annular shape and is not divided for each pole. The permanent magnet 33 has different magnetic poles alternately at a predetermined interval in the circumferential direction of the shaft 20. The magnetic poles of the permanent magnet 33 are multipolarized by magnetization. The permanent magnet 33 generates a magnetic flux in a direction along the shaft 20.

  The rotor yoke 34 is made of a magnetic material. The rotor plate 35 is made of a magnetic material, and is divided into a plurality of portions in the circumferential direction with a constant gap 35d so as to magnetically insulate between the adjacent magnetic poles of the permanent magnet 33. The gap 35d extends radially outward from the center of the rotor plate 35 in the radial direction.

  With this configuration, the area of the rotor 31 facing the air gap 41 increases, so that the flux linkage can be increased. Furthermore, since the rotor plate 35 is magnetically independent for each pole, magnetic flux leakage between adjacent poles can be prevented, and the magnetic flux of the permanent magnet 33 can be used effectively without waste. Further, since the demagnetizing field is not directly applied to the permanent magnet 33, the demagnetization resistance is also increased. Further, when the permanent magnet 33 is a sintered rare earth magnet or the like, the high-frequency component of the magnetic flux does not easily reach the permanent magnet interior 33. Therefore, by suppressing the generation of eddy current inside the magnet, loss reduction, and Also, the temperature rise can be reduced.

  Here, the inner diameter of the permanent magnet 33 is larger than the inner diameter of the rotor yoke 34 and the inner diameter of the rotor plate 35, and the outer diameter of the permanent magnet 33 is equal to the outer diameter of the rotor yoke 34 and the rotor plate 35. It is smaller than the outer diameter.

  The rotor yoke 34 has an arc-shaped inner hole 34 a in the vicinity of the shaft 20, and an arc-shaped outer hole 34 b in the vicinity of the sealed container 1. The rotor plate 35 has an inner hole portion 35 b penetrating along the axis of the shaft 20 in the vicinity of the shaft 20.

  The inner hole 34 a and the outer hole 34 b of the rotor yoke 34 and the inner hole 35 b of the rotor plate 35 are not blocked by the permanent magnet 33 or the like on both surfaces of the rotor yoke 34 and the rotor plate 35. , Refrigerant or the like can pass through.

  Specifically, the inner hole 35b of the rotor plate 35 also serves as a hole through which the shaft 20 is inserted, and the inner hole 35b is smaller than the outer diameter of the shaft 20 in order to prevent leakage of magnetic flux. Largely, there is a gap between the inner surface of the inner hole portion 35 b and the outer surface of the shaft 20. In addition, the refrigerant can pass through a portion of the gap 35 d of the rotor plate 35 that is inside the permanent magnet 33.

  Therefore, the gap between the inner hole 35b of the rotor plate 35 and the shaft 20 plus the portion of the gap 35d of the rotor plate 35 that is inside the permanent magnet 33 is the inner side of the rotor plate. It becomes a passage.

  A hole through which the shaft 20 is inserted is provided in the central portion of the rotor yoke 34, and the shaft 20 is inserted therein. If the insertion of the shaft 20 is press-fitting or shrink fitting, there is no gap between the shaft 20 and the rotor yoke 34. The plurality of inner hole portions 34a are provided at regular intervals around the shaft insertion hole.

  The inner hole 34a of the rotor yoke 34 and the rotor plate inner passage do not overlap each other when viewed in the axial direction. That is, the inner hole 34a of the rotor yoke 34 is the first passage 51 '. The rotor plate inner passage is the second passage 52 '. The space between the rotor yoke 34 and the rotor plate 35 is the third passage 53 '.

  Therefore, the refrigerant gas hits the rotor plate 35 (the inner surface of the third passage 53 ′) after passing through the inner hole 34 a (the first passage 51 ′) of the rotor yoke 34.

  The lubricating oil contained in the refrigerant gas is liquefied by adhering to the rotor plate 35 in the form of fine particles, passes through the inner hole 34a (the first passage 51 ′) of the rotor yoke 34, and passes through the motor. 2 returns to the upstream side of the refrigerant gas flow.

  On the other hand, the refrigerant gas passes through the space between the rotor yoke 34 and the rotor plate 35 (the third passage 53 ') and then passes through the rotor plate inner passage (the second passage 52'). .

  Further, the outer hole 34b of the rotor yoke 34 and the rotor plate outer passage do not overlap each other when viewed in the axial direction. That is, the outer hole 34b of the rotor yoke 34 is the first passage 51 '. The rotor plate outer passage is the second passage 52 '. The space between the rotor yoke 34 and the rotor plate 35 is the third passage 53 '.

  Therefore, the refrigerant gas hits the rotor plate 35 (the inner surface of the third passage 53 ′) after passing through the outer hole 34 b (the first passage 51 ′) of the rotor yoke 34.

  The lubricating oil contained in the refrigerant gas is liquefied by adhering to the rotor plate 35 in the form of fine particles, passes through the outer hole 34b (the first passage 51 ′) of the rotor yoke 34, etc. It returns to the upstream side of the refrigerant gas flow of the motor 2.

  On the other hand, the refrigerant gas passes through the space between the rotor yoke 34 and the rotor plate 35 (the third passage 53 ') and then passes through the rotor plate outer passage (the second passage 52'). .

  According to the compressor having this configuration, the differential pressure between the upstream side and the downstream side of the motor 2 can be reduced, and the pressure loss of the compressor can be reduced. The liquefied lubricating oil can be reliably separated from the refrigerant.

(Third embodiment)
8 and 9 show a third embodiment of the compressor of the present invention. The difference from the first embodiment (FIG. 2) will be described. In the third embodiment, the configuration of the motor is different. Since other structures are the same as those of the first embodiment, description thereof is omitted.

  The motor 2 includes a first rotor 31, a stator 21, and a second rotor 32 that are arranged in order from the upstream to the downstream in the direction in which the refrigerant gas flows. Thus, since the motor 2 includes the two rotors 31 and 32 and the single stator 21, the magnetic flux of the rotors 31 and 32 can be doubled, the yoke of the stator 21 can be eliminated, and the thrust force can be increased. Can be balanced.

  The stator 21 includes two annular stator plates 25 and 25 arranged so as to be substantially orthogonal to the shaft 20 and a plurality of protrusions provided between the two stator plates 25 and 25. And a coil 23 wound around the protrusion 26.

  Since the stator 21 generates magnetic flux in the axial direction, the magnetic poles of the permanent magnets 33 of the first rotor 31 and the magnetic poles of the permanent magnets 33 of the second rotor 32 that face each other via the stator 21. Are of opposite polarity.

  Since the stator 21 can reduce the axial force applied to the shaft 20, the life of the bearing can be extended, and vibration and noise due to the axial force can be suppressed.

  The stator plate 25 is made of a magnetic material, and is provided with a slit 25a that magnetically insulates the adjacent protrusions 26 and 26 from each other. The slits 25a extend radially outward from the center of the stator plate 25 in the radial direction. Since the slit 25a increases the area of the stator 21 facing the air gaps 41 and 42, the flux linkage can be increased.

  Further, the slits 25a of the two stator plates 25, 25 do not overlap each other when viewed from the axial direction. That is, if the two stator plates 25, 25 have the same shape, one stator plate 25 is rotated by a certain angle with respect to the other stator plate 25, and the so-called skewed effect is also combined. can get. In other words, the magnetic pulsation (so-called cogging torque) of the upper and lower air gaps 41 and 42 can be shifted in the upper and lower phases by shifting the upper and lower slits 25a and 25a, thereby reducing the pulsation.

  When the slit 25a has a portion that is blocked by the coil 23, the outside of the portion of the slit 25a that is blocked by the coil 23 serves as a stator plate outer passage, and the coil 23 of the slit 25a. The inside of the portion covered by the stator plate is a stator plate inner passage, and one stator plate outer passage and the other stator plate outer passage do not overlap each other when viewed from the axial direction, and one stator plate inner passage and the other stator plate The inner passages do not overlap when viewed from the axial direction.

  In addition, it is desirable from the viewpoint of preventing oil rising when the inner surface of the stator plate 25 is in close contact with the shaft 20 or the outer surface of the stator plate 25 is in close contact with the sealed container 1. You should stay away from the leak.

  In this case, the gap between the inner surface of the stator plate 25 and the shaft 20, or the gap between the outer surface of the stator plate 25 and the shaft 20, is a shaft in one stator plate 25 and the other stator plate 25. Seeing from the direction, overlapping is inevitable.

  Therefore, when the above configuration is applied to the stator inner passage or the stator outer passage, the gap between the inner surface of the stator plate 25 and the shaft 20 or between the outer surface of the stator plate 25 and the shaft 20 is used. This gap should be excluded. This is not the case when the gap is filled with a non-magnetic material.

  The slit 25a of the lower stator plate 25 and the slit 25a of the upper stator plate 25 do not overlap when viewed from the axial direction. That is, the slit 25 a of the lower stator plate 25 is the first passage 51. The slit 25 a of the upper stator plate 25 is the second passage 52. A space between the lower stator plate 25 and the upper stator plate 25 is the third passage 53.

  Accordingly, the refrigerant gas hits the upper stator plate 25 (the inner surface of the third passage 53) after passing through the slit 25a (the first passage 51) of the lower stator plate 25.

  The lubricating oil contained in the refrigerant gas is liquefied by adhering to the upper stator plate 25 in the form of fine particles, and passes through the slit 25a (the first passage 51) of the lower stator plate 25. Returning to the upstream side of the refrigerant gas flow of the motor 2.

  On the other hand, the refrigerant gas passes through the space (the third passage 53) between the lower stator plate 25 and the upper stator plate 25, and then the slit 25a (the second second) of the upper stator plate 25. Through the passage 52).

  According to the compressor having this configuration, the differential pressure between the upstream side and the downstream side of the motor 2 can be reduced, and the pressure loss of the compressor can be reduced. The liquefied lubricating oil can be reliably separated from the refrigerant.

  The first passage 51 is a plurality of slits 25 a provided radially on the lower stator plate 25, and the second passage 52 is provided radially on the upper stator plate 25. Since there are a plurality of slits 25a, the slit 25a can have a role of magnetically insulating between adjacent magnetic poles (blocking the magnetic path) in addition to the role of flowing the refrigerant gas.

(Fourth embodiment)
10 and 11 show a fourth embodiment of the compressor of the present invention. The difference from the first embodiment (FIG. 2) will be described. In the fourth embodiment, the configuration of the motor is different. Since other structures are the same as those of the first embodiment, description thereof is omitted.

  The motor 2 includes a first stator 21, a rotor 31, and a second stator 22 that are arranged in order from the upstream to the downstream in the direction in which the refrigerant gas flows. Thus, since the motor 2 includes the two stators 21 and 22 and the single rotor 31, the interlinkage magnetic flux of the stators 21 and 22 can be doubled, both surfaces of the rotor 31 can be used, and the thrust is further increased. Balance the power.

  The rotor 31 includes two annular upper and lower rotor plates 35 and 35 and the permanent magnet 33 sandwiched between the two rotor plates 35 and 35.

  The rotor plate 35 is made of a magnetic material, and is provided with a slit 35 a that magnetically insulates between the adjacent magnetic poles of the permanent magnet 33. The slits 35a extend radially outward from the center of the rotor plate 35 in the radial direction. The slit 35a increases the area of the rotor 31 facing the air gaps 41 and 42, so that the flux linkage can be increased.

  Further, the slits 35 a of the two rotor plates 35, 35 do not overlap each other and do not overlap the permanent magnet 33 when viewed from the axial direction. That is, if the two rotor plates 35 and 35 have the same shape, one rotor plate 35 is rotated by an angle with respect to the other rotor plate 35, and so-called skewed effect is also added. can get. In other words, the magnetic pulsation (so-called cogging torque) of the upper and lower air gaps 41 and 42 can be shifted in the upper and lower phases by shifting the upper and lower slits 35a and 35a, thereby reducing the pulsation. For example, when the rotor 31 has 4 poles and the stators 21 and 22 have 6 poles, a so-called skew effect can be obtained if the deviation of the center angle between the upper and lower slits 35a, 35a is about 15 degrees. .

  The slit 35a of the lower rotor plate 35 and the slit 35a of the upper rotor plate 35 do not overlap when viewed from the axial direction. That is, the slit 35a of the lower rotor plate 35 is the first passage 51 '. The slit 35a of the upper rotor plate 35 is the second passage 52 '. A space between the lower rotor plate 35 and the upper rotor plate 35 is the third passage 53 '.

  Therefore, the refrigerant gas passes through the slit 35a (the first passage 51 ') of the lower rotor plate 35 and then hits the upper rotor plate 35 (the inner surface of the third passage 53').

  The lubricating oil contained in the refrigerant gas is liquefied by adhering to the upper rotor plate 35 in the form of fine particles, and passes through the slit 35a (the first passage 51 ′) of the lower rotor plate 35. Thus, the motor 2 returns to the upstream side of the refrigerant gas flow.

  On the other hand, the refrigerant gas passes through the space (the third passage 53 ′) between the lower rotor plate 35 and the upper rotor plate 35, and then the slit 35a (the first passage) of the upper rotor plate 35. 2 passage 52 ').

  According to the compressor having this configuration, the differential pressure between the upstream side and the downstream side of the motor 2 can be reduced, and the pressure loss of the compressor can be reduced. The liquefied lubricating oil can be reliably separated from the refrigerant.

  The first passage 51 ′ is a plurality of slits 35 a provided radially on the lower rotor plate 35, and the second passage 52 ′ is provided radially on the upper rotor plate 35. Since the plurality of slits 35a are formed, the slit 35a can have a role of magnetically insulating adjacent magnetic poles (blocking the magnetic path) in addition to the role of flowing the refrigerant gas.

  In the fourth embodiment, instead of the rotor 31 shown in FIG. 11, another rotor 31A shown in FIGS. 12 and 13 may be used. The difference from the rotor 31 shown in FIG. 11 will be described. As shown in FIGS. 12 and 13, in this other rotor 31A, the upper and lower rotor plates 35, 35 are provided in the outer peripheral portion in the circumferential direction. The circular hole 35e is provided.

  The hole 35e of the lower rotor plate 35 is displaced radially inward from the hole 35e of the upper rotor plate 35. The upper and lower slits 35 a and 35 a and the upper and lower hole portions 35 e and 35 e do not overlap each other and do not overlap the permanent magnet 33 when viewed from the axial direction.

  That is, the lower slit 35a and the lower hole 35e are the first passage 51 '. The upper slit 35a and the lower hole 35e are the second passage 52 '. Thus, in this other rotor 31A, oil separation can be effectively performed by increasing the refrigerant passage.

  In the fourth embodiment, another rotor 31B shown in FIG. 14 may be used instead of the rotor 31 shown in FIG. The difference from the rotor 31 shown in FIG. 11 will be described. As shown in FIG. 14, in this other rotor 31B, the upper and lower rotor plates 35 and 35 are replaced by two annular upper and lower end plates 36 and 36, respectively. It is sandwiched.

  The upper and lower end plates 36 and 36 are each provided with a plurality of circular hole portions 36a in the circumferential direction on the outer peripheral portion. The hole portion 36 a of the lower end plate 36 is displaced outward in the radial direction from the hole portion 36 a of the upper rotor plate 36.

  The upper and lower slits 35a, 35a overlap each other when viewed from the axial direction. The upper hole 36a and the upper slit 35a overlap each other when viewed from the axial direction, and the lower hole 36a and the lower slit 35a overlap each other when viewed from the axial direction.

  The upper and lower holes 36 a and 36 a do not overlap each other and do not overlap the permanent magnet 33 when viewed from the axial direction. That is, the lower hole 36a is the first passage 51 '. The upper hole 36a is the second passage 52 '. Thus, in this other rotor 31B, oil separation can be effectively performed by increasing the refrigerant passage. Further, the upper and lower slits 35a, 35a are not displaced at the center angle, do not reduce the torque, and do not reduce the operation efficiency.

  In the compressors of the first to fourth embodiments, the axial magnetic force between the stator and the rotor is the upstream side of the refrigerant gas flow acting on the end surface of the rotor. At least a part is canceled by the gas pressure that differs from the downstream side.

  According to the compressor having this configuration, the axial gap type motor does not generate a radial force on the rotating shaft as compared with the radial gap type motor, and the stator is deformed or the sealed container is interposed via the stator. Is not deformed, and the rotation axis is not bent in the radial direction.

  Furthermore, the axial force between the stator and the rotor of the axial gap motor is used to generate a thrust force against the gas pressure acting on the end surfaces on the upstream side and the downstream side due to the flow of the refrigerant gas in the sealed container. generate. Thus, the thrust force and gas pressure peculiar to the axial gap type motor are at least partially canceling each other, so that the thrust force peculiar to the axial gap type motor is made extremely small and the fixed part of the compression part is movable. The sliding loss of the contact portion of the portion can be minimized, and the compression efficiency is improved.

  Therefore, while reducing the size by using the axial gap type motor, the force acting in the axial direction on the rotor can be reduced by at least partially canceling out the gas pressure and the thrust force with a simple configuration.

  In addition, this invention is not limited to the above-mentioned embodiment. For example, the oil separation mechanisms G and G ′ provided on the stator or the rotor in the first to fourth embodiments are different from the stators of the first to fourth embodiments, You may use for a rotor. Further, the compressor only needs to include at least one stator and one rotor. The oil separation mechanisms G and G 'may be provided in at least one of the stator or the rotor.

  The oil separation mechanisms G and G 'may have any configuration as long as oil flows in a substantially crank shape from the opening at one axial end to 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.

  The third passages 53 and 53 ′ may not extend in a direction perpendicular to the axial direction, and extend in a direction intersecting the first passage and the second passage. What is necessary is just to connect 51,51 'and the said 2nd channel | path 52,52'.

  Moreover, the structure of the said compression part 11 is not restricted to a rotary, A scroll may be sufficient and it is applicable even if it is another form. If an air gap is not opened with respect to the space surrounded by the discharge pipe 7 and the motor 2, not only the axial gap but also a radial gap may be used in combination with the air gap. Further, only one of the rotors on both sides may be the rotor yoke.

  Further, the motor 2 may be disposed in a region in a hermetically sealed container filled with a low-pressure refrigerant to be sucked into the compression unit. In this case, the compressor is a so-called low-pressure dome type. In the case of the low-pressure dome type, the refrigerant gas and the lubricating oil are directly discharged from the compression unit. Therefore, it is necessary to sufficiently return the lubricating oil when being sucked into the compression unit.

  Moreover, the central axis of the said airtight container 1 may incline with respect to a horizontal surface. The same applies when the compression unit is above the motor. That is, the same effect can be obtained with a compressor in which a motor is placed in an atmosphere of refrigerant and lubricating oil.

It is a longitudinal section showing a 1st embodiment of a compressor of the present invention. It is sectional drawing of the principal part expansion of a compressor. It is a top view of a stator. It is a top view of the stator except a stator plate. It is a top view of a rotor. It is a top view of the rotor except a rotor board. It is a principal part expanded sectional view which shows 2nd Embodiment of the compressor of this invention. It is a disassembled perspective view of a rotor. It is a top view of a rotor. It is a principal part expanded sectional view which shows 3rd Embodiment of the compressor of this invention. It is a disassembled perspective view of a stator. It is a principal part expanded sectional view which shows 4th Embodiment of the compressor of this invention. It is a disassembled perspective view of a rotor. It is a disassembled perspective view of another rotor. It is a top view of another rotor. It is a disassembled perspective view of another rotor.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Motor 8 Lubricating oil 11 Compression part 20 Shaft 21 1st stator 21a Stator inner side passage 21e Stator outer side passage 22 Second stator 23 Coil 24 Stator yoke 24c Hole part 25 Stator plate 25a Slit 25c Hole part 26 Projection part 27 Stator cores 31, 31A, 31B First rotor 31a Rotor inner passage 31e Rotor outer passage 32 Second rotor 33 Permanent magnet 33a Intermagnet passage 34 Rotor yoke 34a Inner hole 34b Outer hole 34c Hole 35 Rotor plate 35a Slit 35b Inner hole 35c Hole 35d Clearance 35e Hole 36 End plate 36a Hole 41 First air gap 42 Second air gap 51, 51 'First passage 51a, 51a' Opening 52, 52 'Second Passage 52a, 52a 'opening 53, 53 ′ Third passage G, G ′ Oil separation mechanism H High pressure region

Claims (14)

A sealed container (1);
A compression section (11) disposed in the sealed container (1);
An axial gap type motor (2) disposed in the hermetic container (1) and driving the compression part (11) via a shaft (20);
The motor (2) has at least a pair of stators (21, 22) and rotors (31, 32) that are axially opposed to each other via air gaps (41, 42).
An oil separation mechanism that separates the oil by flowing oil into at least one of the stator (21, 22) or the rotor (31, 32) in a substantially crank shape from the opening at one axial end to the opening at the other axial end. A compressor provided with (G, G ′). The compressor according to claim 1,
The oil separation mechanism (G, G ′)
A first passage (51, 51 ') and a second passage (52, 52') that extend in the axial direction and do not overlap each other when viewed from the axial direction;
The first passage (51, 51 ′) and the second passage (52, 52) extend in a direction intersecting the first passage (51, 51 ′) and the second passage (52, 52 ′). 52 ') and a third passage (53, 53'). The compressor according to claim 2, wherein
The oil separation mechanism (G) is provided in the stator (21, 22),
The stator (21, 22) is sandwiched between the first plate member and the second plate member disposed in the axial direction, and the first plate member and the second plate member. A coil (23),
The first passage (51) is provided in the first plate member,
The second passage (52) is provided in the second plate member,
The compressor, wherein the third passage (53) is provided in a space between the first plate member and the second plate member. The compressor according to claim 2, wherein
The oil separation mechanism (G ′) is provided in the rotor (31, 32),
The rotors (31, 32) are sandwiched between the first plate member and the second plate member arranged in the axial direction, and the first plate member and the second plate member. Magnet (33),
The first passage (51 ′) is provided in the first plate member,
The second passage (52 ′) is provided in the second plate member,
The compressor, wherein the third passage (53 ') is provided in a space between the first plate-like member and the second plate-like member. The compressor according to claim 3, wherein
The compressor according to claim 1, wherein the first plate member or the second plate member is a stator yoke (24). The compressor according to claim 4, wherein
The compressor according to claim 1, wherein the first plate member or the second plate member is a rotor yoke (34). The compressor according to claim 4, wherein
Of the first passage (51 ′) or the second passage (52 ′), the upstream passage in the direction in which the refrigerant gas flows is the first passage (51 ′) or the second passage ( 52 ′), the compressor is located radially outside the passage on the downstream side in the flow direction of the refrigerant gas. The compressor according to claim 4, wherein
The lower passage of the first passage (51 ′) or the second passage (52 ′) is the lower portion of the first passage (51 ′) or the second passage (52 ′). A compressor characterized by being located radially outside the upper passage. The compressor according to claim 2, wherein
The first passage (51, 51 ′) and the second passage (52, 52 ′) are provided closer to the shaft (20) than the sealed container (1). Compressor. The compressor according to claim 2, wherein
The first passage (51, 51 ′) and the second passage (52, 52 ′) are provided closer to the hermetic container (1) than the shaft (20). Compressor. The compressor according to claim 2, wherein
Of the first passage (51, 51 ′) or the second passage (52, 52 ′), on the third passage (53, 53 ′) side of the upstream passage in the direction in which the refrigerant gas flows. The area of the opening (51a, 51a ′, 52a, 52a ′) is downstream in the direction in which the refrigerant gas flows in the first passage (51, 51 ′) or the second passage (52, 52 ′). The compressor characterized by being larger than the area of the opening part (51a, 51a ', 52a, 52a') by the side of the said 3rd channel | path (53, 53 ') side channel | path. The compressor according to claim 2, wherein
The opening (51a, 51a) on the third passage (53, 53 ') side of the lower passage of the first passage (51, 51') or the second passage (52, 52 '). The area of ', 52a, 52a') is the third passage (53, 53) of the upper passage of the first passage (51, 51 ') or the second passage (52, 52'). A compressor characterized in that it is larger than the area of the opening (51a, 51a ', 52a, 52a') on the ') side. The compressor according to claim 2, wherein
The discharge port for the refrigerant gas discharged from the compression section (11) into the sealed container (1) is the first passage (51, 51 ′) or the second passage (52, 52 ′). A compressor in the vicinity of the opening of the passage on the upstream side in the direction in which the refrigerant gas flows. The compressor according to claim 3 or 4,
The first passages (51, 51 ′) are a plurality of first slits provided radially on the first plate member,
The second passages (52, 52 ′) are a plurality of second slits provided radially on the second plate-shaped member,
The compressor, wherein the plurality of first slits and the plurality of second slits do not overlap when viewed in the axial direction.

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