Patent Application
20170089624
The present invention relates to a hermetic compressor, and a vapor compression-type refrigeration cycle device including the hermetic compressor. In particular, the present invention relates to a hermetic compressor excellent in oil separation effect, and a vapor compression-type refrigeration cycle device including the hermetic compressor.
Hitherto, in a refrigerant compressor used in vapor compression-type refrigeration cycle devices (such as heat pump equipment and refrigeration cycle equipment), a rotational force of an electric motor is transmitted to a compression mechanism by a drive shaft so that refrigerant gas is compressed. In such a refrigerant compressor, the refrigerant gas compressed by the compression mechanism is discharged into a hermetic container, moved from a space below the electric motor into a space above the same through electric motor unit gas passages, and then discharged into a refrigerant circuit on an outside of the hermetic container. At this time, lubricating oil supplied to the compression mechanism and mixed with the refrigerant gas is discharged to the outside of the hermetic container. Hitherto, there is a problem in that an increase in amount of the oil to be discharged into the refrigerant circuit causes degradation in performance of a heat exchanger. In addition, there is another problem in that a decrease in amount of the oil stored in the hermetic container causes insufficient lubrication, resulting in degradation in reliability of the refrigerant compressor.
In recent years, there have been promoted development of refrigerant compressors having smaller sizes, and conversion to use of alternative refrigerants (including natural refrigerant) having a lower environmental load. Under the circumstances, advanced technology for separating the oil in the hermetic container has been demanded. However, how the refrigerant and the lubricating oil flow and how the oil separation occurs during high speed rotation of the electric motor in the hermetic container are significantly complicated, and observation experiments in the hermetic container under high pressure are not easy. Thus, there are a large number of unknown factors, and a large number of technical problems have not yet been solved.
In the high-pressure shell type scroll compressor disclosed in Patent Literature 1, sucked refrigerant is compressed by the compression mechanism arranged on an upper side in the hermetic container, and once caused to flow down to an oil reservoir at a bottom of the hermetic container. After that, the refrigerant is caused to flow up from a space below the electric motor to a space above the same through electric motor gas passages, and then discharged as high pressure gas through a discharge pipe of the compressor. The high-pressure shell type scroll compressor disclosed in Patent Literature 1 includes a fan arranged on an upper portion of a rotator of the electric motor, and partition walls for separating a stator side of the electric motor and a rotator side of the electric motor from each other above the fan. Then, the refrigerant and the lubricating oil are separated from each other by using a centrifugal force generated by rotation of the fan and by using pressure resistance generated through gaps between the partition walls. The lubricating oil is prevented from flowing directly into the discharge pipe without being separated from the refrigerant, in other words, the lubricating oil is prevented from flowing out from the hermetic container.
Further, in Patent Literature 2, there is disclosed an oil separation device for a hermetic electric compressor including: an electric component housed in an upper portion of a hermetic container; a compression component that is driven by the electric component; an oil separation plate arranged to face an upper end ring of a rotor of the electric component across a predetermined clearance; and stirring vanes arranged upright to the oil separation plate, in which the stirring vanes are arranged upright only to a lower surface of the oil separation plate.
Effects of improving an oil separation condition in the hermetic container of the compressor by using the fan and the partition walls in Patent Literature 1 and the oil separation plate and the stirring vanes in Patent Literature 2 are generally observed.
Further, in recent years, by using significantly advanced three-dimensional fluid simulation technology, flow conditions of the refrigerant and the lubricating oil in the hermetic container of the compressor can be visualized. Thus, new findings are obtained. Specifically, in Patent Literature 3, there is disclosed a refrigerant compressor in which an increase in head pressure that is generated near a leading end in a rotation direction of an upper balance weight at an upper end of the rotator of the electric motor arranged in the hermetic container is used to form an oil return passage from a vicinity of a leading end portion toward a lower end so that high density lubricating oil that appears around the rotator is returned below the electric motor, to thereby prevent the oil from flowing out.
In general, to provide a high-performance centrifugal air-sending device, as described in Non Patent Literature 1, the shape of the impeller itself, the shape of the passage of flow extending into the impeller, the shape of the passage of flow extending outside of the impeller, and the like need to be theoretically designed.
However, in Patent Literatures 1 and 2, no theoretical design methods are disclosed for the fan and the vanes that are each attached on the upper portion of the rotator (rotor) of the electric motor disclosed therein, and optimum configurations for the fan and the vanes for improving the oil separation condition have not yet been specified.
Specifically, in the high-pressure shell type scroll compressor disclosed in Patent Literature 1, unless the fan and the partition walls to be attached on the upper portion of the rotator of the electric motor are appropriately designed and arranged, the fan and the partition walls cannot prevent the refrigerant, which flows from the compression mechanism into the space above the electric motor (refrigerant mixed with fine oil particles), from flowing from the stator side of the electric motor directly into the rotator side of the electric motor. Thus, there is a problem in that the oil separation effect cannot be fully exerted.
The present invention has been made to solve the problem as described above, and it is an object thereof to provide a hermetic compressor capable of reducing an amount of oil flowing to an outside of a hermetic container than that in the related art by using rotation of a rotator of an electric motor arranged in the hermetic container, and to provide a vapor compression-type refrigeration cycle device including the hermetic compressor.
According to one embodiment of the present invention, there is provided a hermetic compressor, including: a hermetic container having a bottom portion for storing lubricating oil; an electric motor arranged in the hermetic container, the electric motor including: a stator and a rotator through which a rotator vent is formed in a vertical direction; a drive shaft attached to the rotator; a compression mechanism arranged in the hermetic container, for compressing refrigerant by using rotation of the drive shaft; a rotary pressure increasing mechanism arranged on an upper portion of the rotator, for increasing a pressure of refrigerant gas by allowing the refrigerant gas to flow through the rotary pressure increasing mechanism while rotating about the drive shaft; a cylindrical lateral wall for partitioning a space above the electric motor into an outer space on the stator side and inner space on the rotator side in such a manner that the cylindrical lateral wall surrounds the rotary pressure increasing mechanism positioned in the inner space; and a discharge pipe communicated to the inner space, for allowing the refrigerant to flow out from the inner space into an external circuit that is external to the hermetic container, in which the refrigerant gas that is compressed by the compression mechanism and discharged into the hermetic container is moved from a space below the electric motor up to an upper end of the rotator through the rotator vents, flows into the rotary pressure increasing mechanism to be increased in pressure, flows into the inner space to increase a pressure in the inner space, and is discharged to an outside through the discharge pipe while suppressing inflow of the refrigerant gas from the outer space to the inner space.
Further, according to one embodiment of the present invention, there is provided a vapor compression-type refrigeration cycle device, including: the hermetic compressor of the one embodiment of the present invention; a radiator for transferring heat of refrigerant that is compressed by the hermetic compressor; an expansion mechanism for expanding the refrigerant that flows out from the radiator; and an evaporator for causing the refrigerant that flows out from the expansion mechanism to receive heat.
The one embodiment of the present invention can prevent a decrease in amount of lubricating oil stored in the hermetic container and can obtain an effect of suppressing reliability degradation to be caused by insufficient lubrication, and an effect of achieving high energy-saving performance.
First, with reference to
<Fundamental structure and operation of hermetic compressor 100>
The hermetic compressor 100 according to Embodiment 1 is a high-pressure shell hermetic scroll compressor, which includes a hermetic container 1 having a bottom portion in which a lower oil reservoir 2 for storing lubricating oil is formed, and an electric motor 8, a drive shaft 3, a compression mechanism 60, and a rotary pressure increasing mechanism 49 that are housed in the hermetic container 1.
The electric motor 8 includes a substantially cylindrical stator 7 having an inner peripheral portion through which a through-hole is formed in a vertical direction, and a substantially cylindrical rotator 6 arranged on an inner peripheral side of the stator 7 across a predetermined air gap 27a. The electric motor 8 according to Embodiment 1 is, for example, a DC brushless motor. The stator 7 is formed of laminated steel plates, and includes a core 7c that is formed into a wound coil block by winding a coil therearound at a high density. Further, at an upper end of the stator 7, coil parts projecting from the wound coil block toward an upper side of the stator 7, that is, a plurality of electric motor upper coil-interconnecting portion 7a are formed. At a lower end of the stator 7, coil parts projecting from the wound coil block toward a lower side of the stator 7, that is, a plurality of electric motor lower coil-interconnecting portions 7b are formed. This stator 7 is attached to an inner peripheral surface of the hermetic container 1 by press fitting, welding, and the like. Note that, an outer peripheral portion of the core 7c of the stator 7 is partially cut out so that stator outer peripheral passages 25 are formed between the core 7c and the hermetic container 1 under a state in which the stator 7 is attached to the inner peripheral surface of the hermetic container 1.
The rotator 6 is formed by laminating steel plates and sandwiching uppermost and lowermost ones of the laminated steel plates respectively with a rotator upper end fixing substrate 33 and a rotator lower end fixing substrate 34. Further, magnets are arranged in the rotator 6. Still further, respectively on an upper surface of the rotator upper end fixing substrate 33 and a lower surface of the rotator lower end fixing substrate 34, an upper balance weight 31 and a lower balance weight 32, which have a predetermined thickness and are arranged in reverse phases, are arranged along outer rims of the rotator 6. Yet further, four rotator vents 26 are formed in the vertical direction through the rotator 6 according to Embodiment 1. Note that, the number of the rotator vents 26 is not particularly limited as long as at least one rotator vent 26 is formed.
A lower end portion of the drive shaft 3 is attached to the rotator 6 of the electric motor 8, and an upper end portion thereof is attached to the compression mechanism 60 described below. In other words, the drive shaft 3 is configured to transmit a driving force of the electric motor 8 to the compression mechanism 60. An upper side of the drive shaft 3 is held in a freely rotatable manner by a main bearing unit 55 of an upper bearing member 11 arranged above the electric motor 8, and a lower side thereof is held in a freely rotatable manner by a sub bearing unit 54 of a lower bearing member 12 arranged below the electric motor 8.
The compression mechanism 60 is arranged above the electric motor 8, and includes a fixed scroll 51 and an orbiting scroll 52. Plate-like scroll teeth are formed on a lower surface of the fixed scroll 51, which is attached to a compression mechanism casing 50 that is fixed to the inner peripheral surface of the hermetic container 1. Plate-like scroll teeth to mesh with the plate-like scroll teeth of the fixed scroll 51 are formed on an upper surface of the orbiting scroll 52, which is provided in a freely slidable manner at the upper end portion of the drive shaft 3. When the plate-like scroll teeth of the fixed scroll 51 and the plate-like scroll teeth of the orbiting scroll 52 mesh with each other, compression chambers 4 are formed between the plate-like scroll teeth on both sides. A lower surface of the orbiting scroll 52 is supported in a freely slidable manner by an upper surface portion of the upper bearing member 11. An outer peripheral surface of the upper bearing member 11 is supported in a freely slidable manner by an inner peripheral surface of the compression mechanism casing 50. With this configuration, the upper bearing member 11 can be retracted downward in response to application of pressure of a predetermined value or more in the compression chamber 4, and thus an abnormal pressure increase in the compression chamber 4 can be avoided.
Note that, a refrigerant passage 57 is formed between an outer peripheral portion of the compression mechanism casing 50 and the hermetic container 1. Further, a discharge cover 56 for partitioning an electric motor superjacent space 9 (more specifically, upper part of a cylindrical lateral wall 37 described below) into an electric motor stator superjacent space 9a (outer space) and an electric motor rotator superjacent space 9b (inner space) is arranged under the compression mechanism casing 50.
The rotary pressure increasing mechanism 49 is arranged on an upper portion of the rotator 6. The rotary pressure increasing mechanism 49 according to Embodiment 1 is a centrifugal impeller 40, which includes a plurality of vanes 41 arranged in a manner of extending from an inner peripheral side to an outer peripheral side about the drive shaft 3. Further, the centrifugal impeller 40 according to Embodiment 1 also includes a vane superjacent disk 43 (upper surface plate) for blocking inflow of refrigerant gas from above the vanes 41 into the centrifugal impeller 40, and a vane subjacent disk 44 (lower surface plate) for blocking inflow of refrigerant gas from below the vanes 41 into the centrifugal impeller 40. Further, to prevent inflow of refrigerant gas through passages other than the rotator vents 26 into an inlet on an inner peripheral side of the centrifugal impeller 40, an inner peripheral flow guide 42 (partition plate) is extended downward from a rim of an opening portion of the vane subjacent disk 44, which is formed at a position on an inner peripheral side of the vanes 41, in a manner that an outer peripheral portion of the rotator vents 26 is surrounded. The centrifugal impeller 40 is rotated about the drive shaft 3 through, for example, connection between the drive shaft 3 and the vane superjacent disk 43, connection between the cylindrical lateral wall 37 described below and the vane subjacent disk 44, or connection between the rotator 6 and the inner peripheral flow guide 42. With this configuration, the refrigerant that flows in through the inlet on the inner peripheral side is increased in pressure and is caused to flow out through an outlet on the outer peripheral side.
Further, in the hermetic compressor 100 according to Embodiment 1, the cylindrical lateral wall 37 is arranged to surround the centrifugal impeller 40 (more specifically, refrigerant outlet on the outer peripheral side), in other words, to partition the electric motor superjacent space 9 into the electric motor stator superjacent space 9a (outer space) and the electric motor rotator superjacent space 9b (inner space). Further, in the cylindrical lateral wall 37, an oil drain hole 39 is formed on a rotation direction leading end portion 31 a side of the upper balance weight 31. This cylindrical lateral wall 37 is attached to an upper surface portion of a disk portion 38a of a balancer fixing bottom plate 38 for fixing the upper balance weight 31 to the rotator upper end fixing substrate 33. Further, in Embodiment 1, a stator inner peripheral passage closing portion 38b (closing member) is arranged to project from an outer peripheral portion of the disk portion 38a of the balancer fixing bottom plate 38. This stator inner peripheral passage closing portion 38b is arranged to close an upper part of a stator inner peripheral passage 27 formed between the rotator 6 and the stator 7 (specifically, air gap 27a between the rotator 6 and the stator 7, and core inner peripheral portion cut-out passage 27b formed by cutting out the inner peripheral side of the stator 7).
In the hermetic compressor 100 configured as described above, the orbiting scroll 52 of the compression mechanism 60 performs eccentric orbital operation along with rotation of the drive shaft 3, causing sucked low-pressure refrigerant to enter the compression chamber 4 through a compressor suction pipe 21. Then, the sucked pressure refrigerant is increased in pressure through a compression step of gradually decreasing a volume of the compression chamber 4, and is discharged into a discharge space 10 ((1) in
Further, along with the rotation of the drive shaft 3, the lubricating oil stored in the lower oil reservoir 2 is sucked upward from a lower end of the drive shaft 3, and flows into a hollow hole 3a. Part of the lubricating oil is supplied, for example, to the sub bearing unit 54 and the main bearing unit 55 through oil supply holes (not shown). Further, part of the lubricating oil flows out from an upper end of the drive shaft 3, and then is supplied into the compression chamber 4 through, for example, a gap between the upper bearing member 11 and the orbiting scroll 52 and an oil supply hole 3b, increasing effects of lubrication of the compression mechanism 60 and sealing of the compressed gas. The lubricating oil that is supplied in the compression chamber 4 is discharged into the discharge space 10 ((1) in
<Flow of Refrigerant in Hermetic Container>
The refrigerant that is discharged through the discharge port 18 flows downward through the refrigerant passage 57 formed of a gap between an outer peripheral side of the compression mechanism casing 50 and the hermetic container 1, and reaches the electric motor stator superjacent space 9a ((2) in
Meanwhile, the refrigerant that flows in the electric motor stator subjacent space in the electric motor subjacent space 5 flows up from an electric motor rotator subjacent space ((4) in
<Flow in Short Circuit Passage 23 and Short-Circuit Prevention>
To prevent electrical short-circuiting between the electric motor upper coil-interconnecting portions 7a and the discharge cover 56, a gap between the electric motor upper coil-interconnecting portions 7a and the discharge cover 56, that is, a short circuit passage 23 needs to be formed. Thus, during the process from the discharge space 10 ((1) in
In view of the circumstances, to reduce an amount of the flow of the refrigerant that short-circuits to be directly discharged through the short circuit passage 23, the following measures need to be taken.
(1) Set a passage resistance of the short circuit passage 23 to the electric motor rotator superjacent space 9b ((6) in
(2) Increase a pressure in the electric motor rotator superjacent space 9b ((6) in
Thus, in Embodiment 1, the cylindrical lateral wall 37 is arranged upright to the balancer fixing bottom plate 38 so that a passage area of the short circuit passage 23 is reduced, and thus the passage resistance is increased. Further, a lower end portion of the discharge cover 56 is bent so that a passage shape of the short circuit passage 23 is made complicated, and thus the passage resistance of the short circuit passage 23 is further increased.
In addition, in Embodiment 1, the cylindrical lateral wall 37 is interposed to separate the centrifugal impeller 40 arranged on the rotator 6 and the electric motor upper coil-interconnecting portions 7a from each other. With this, the refrigerant gas that is increased in pressure by the centrifugal impeller 40 can be suppressed from reversely flowing into the electric motor stator superjacent space 9a ((2) in
Note that, other than the rotator vents 26, the stator inner peripheral passage 27 (air gap 27a and core inner peripheral portion cut-out passage 27b) is formed as an upward refrigerant passage from the electric motor subjacent space 5 ((3) or (4) in
<Design of Centrifugal Impeller>
To increase the pressure in the electric motor rotator superjacent space 9b ((6) in
According to Non Patent Literature 2 (p. 132), of centrifugal fans, a turbofan (having vanes that are formed rearward with respect to a rotation direction) is advantageous in terms of efficiency. Thus, the shape of the vanes 41 of the centrifugal impeller 40 is determined to be rearward with respect to the rotation direction, and eight vanes 41 formed into this shape are arranged in axial symmetry with respect to the drive shaft 3. Further, an inlet angle of each of the vanes 41 is determined such that the vanes 41 each form an angle within a range of ±5 degrees with respect to a circle formed by connecting end positions on the inner peripheral side of the vanes 41. This is because, according to Non Patent Literature 1 (p. 216), a collision loss occurs when an entry angle ib that is equal to a difference between a relative inflow angle 131 and a vane inlet angle β1b at an inlet of the impeller ranges from 2 degrees to 5 degrees or more, causing losses in the compressor. Note that, to increase a percentage by which the refrigerant that flows through the rotator vents 26 flows into the inner peripheral side of the centrifugal impeller 40, and then flows out to the outer peripheral side thereof (passage rate), the following configurations are devised.
With this, the pressure increasing effect by the centrifugal impeller 40 can be further increased, and the pressure in the electric motor rotator superjacent space 9b ((6) in
<Effects>
In the hermetic compressor 100 configured as in Embodiment 1, the pressure in the electric motor rotator superjacent space 9b ((6) in
Now, with reference to
(1) Embodiment 2 is different from Embodiment 1 in that only four of the eight vanes 41 of the centrifugal impeller 40 in Embodiment 1 that are positioned on one side on which the upper balance weight 31 is absent are left, and that a height of each of the four vanes 41 is designed to be equal to a height of the upper balance weight 31. In Embodiment 1, to allow the refrigerant flowing through the rotator vents 26 to flow out from the centrifugal impeller 40 through the vane inner passage 46, the inner peripheral flow guide 42 and the vane subjacent disk 44 are needed. In contrast, in Embodiment 2, there is an advantage in that the inner peripheral flow guide 42 and the vane subjacent disk 44 can be omitted, and hence the centrifugal impeller 40 is easily processed.
Note that, in a case where the centrifugal impeller 40 is configured as in Embodiment 2, fan efficiency is lower than that of the centrifugal impeller 40 according to Embodiment 1, in which the vanes 41 are arranged in axial symmetry. Further, in the case where the centrifugal impeller 40 is configured as in Embodiment 2, pressure pulsation by the centrifugal impeller 40 is increased in comparison with that by the centrifugal impeller 40 according to Embodiment 1, in which the vanes 41 are arranged in axial symmetry. As a result, vibration and noise may occur. Thus, in a case where the fan efficiency and prevention of the vibration and noise are regarded as important, it is preferred that the centrifugal impeller 40 be configured as in Embodiment 1.
(2) In Embodiment 1, the cylindrical lateral wall 37 for preventing short-circuit flow of the refrigerant through the short circuit passage 23, and the balancer fixing bottom plate 38 for fixing the cylindrical lateral wall 37 are formed as separate members. Meanwhile, in Embodiment 2, the cylindrical lateral wall 37 and the balancer fixing bottom plate 38 according to Embodiment 1 are provided as an oil separating cup 36 obtained by a process of integrating a cylindrical lateral wall 36a and a bottom plate 36b with each other. Note that, similarly to Embodiment 1, an oil drain hole 36c is formed in the oil separating cup 36 on the rotation direction leading end portion 31 a side of the upper balance weight 31. When the oil separating cup 36 obtained by the process of integrating the cylindrical lateral wall 36a and the bottom plate 36b with each other is provided instead of the cylindrical lateral wall 37 and the balancer fixing bottom plate 38 according to Embodiment 1, there is an advantage in that a process of assembling the hermetic compressor 100 can be facilitated.
In this way, according to the hermetic compressor 100 configured as in Embodiment 2, the decrease in amount of the lubricating oil stored in the hermetic container 1 can be prevented. In addition, an effect of suppressing reliability degradation caused by insufficient lubrication and an effect of suppressing energy-saving performance degradation, which are comparably less than those in Embodiment 1 but are equivalent thereto, can be obtained. Meanwhile, according to the hermetic compressor 100 configured as in Embodiment 2, there is an advantage in that a manufacturing cost for the centrifugal impeller 40 is lower than that in Embodiment 1.
(3) Note that, other differences between the hermetic compressor 100 according to Embodiment 2 and the hermetic compressor 100 described in Embodiment 1 are as follows.
Now, with reference to
(1) Similarly to Embodiment 2, in the centrifugal impeller 40 according to Embodiment 3, only four of the eight vanes 41 of the centrifugal impeller 40 in Embodiment 1 that are positioned on the one side on which the upper balance weight 31 is absent are left, and the height of each of the four vanes 41 is designed to be equal to the height of the upper balance weight 31. However, the centrifugal impeller 40 according to Embodiment 3 is different from that according to Embodiment 2 in that the vanes 41 are arranged in a radial direction (direction orthogonal to the rotation direction of the drive shaft 3). With this, although fan efficiency is lower than that of the turbofan, there is an advantage in that the centrifugal impeller 40 can be easily manufactured.
(2) In Embodiments 1 and 2, the cylindrical lateral wall (cylindrical lateral wall 37 or cylindrical lateral wall 36a) for preventing the short-circuit flow of the refrigerant through the short circuit passage 23 is arranged on the upper portion of the rotator 6 so that the cylindrical lateral wall is rotated together with the rotator 6. In contrast, in Embodiment 3, a closing cover 29 (more specifically, cylindrical portion 29a) as a counterpart of the cylindrical lateral wall is arranged on an inner side of the electric motor upper coil-interconnecting portions 7a of the stator 7 so that the radial passages 28 are closed. Further, in the closing cover 29, on an inner peripheral side of the cylindrical portion 29a, a projecting portion 29b for closing the upper part of the stator inner peripheral passage 27 is formed. This projecting portion 29b is a counterpart of the stator inner peripheral passage closing portion 38b in Embodiment 1, and is designed such that a smallest gap 29c between the projecting portion 29b and the disk portion 38a of the balancer fixing bottom plate 38 is narrowed (for example, approximately 1 mm to 2 mm) within a range in which electrical short-circuiting does not occur. Note that, in a case where this design is employed, a pressure increasing effect by rotation of the cylindrical lateral wall about the drive shaft cannot be obtained.
In this way, according to the hermetic compressor 100 configured as in Embodiment 3, the decrease in amount of the lubricating oil stored in the hermetic container 1 can be prevented. In addition, the effect of suppressing reliability degradation caused by insufficient lubrication and the effect of suppressing energy-saving performance degradation, which are comparably less than those in Embodiment 1 but are equivalent thereto, can be obtained.
Now, with reference to
(1) The configuration of the hermetic compressor 100 according to Embodiment 4 is the same as the configuration of the hermetic compressor 100 described in Embodiment 2 except the configuration of the rotary pressure increasing mechanism 49. Specifically, the rotary pressure increasing mechanism 49 according to Embodiment 4 is obtained by removing all the vanes 41 from the centrifugal impeller 40 described in Embodiment 1. In other words, the rotary pressure increasing mechanism 49 according to Embodiment 4 includes an oil separating rotary disk 35 as a counterpart of the vane superjacent disk 43 in Embodiment 1, and a balancer cover 30 including a rotary disk 30b and an inner peripheral flow guide 30c as respective counterparts of the vane subjacent disk 44 and the inner peripheral flow guide 42 in Embodiment 1. In the rotary pressure increasing mechanism 49 configured in this way, the refrigerant that flows out from the rotator vents 26 flows into an inner passage 30a formed on an inner peripheral side of the inner peripheral flow guide 30c, flows between the rotary disk 30b and the oil separating rotary disk 35, and flows out into the electric motor rotator superjacent space 9b ((6) in
In this way, according to the hermetic compressor 100 configured as in Embodiment 4, the decrease in amount of the lubricating oil stored in the hermetic container 1 can be prevented. In addition, the effect of suppressing reliability degradation caused by insufficient lubrication and the effect of suppressing energy-saving performance degradation, which are comparably less than (for example, less than half of) those in Embodiment 1 but are equivalent thereto, can be obtained. Meanwhile, according to the hermetic compressor 100 configured as in Embodiment 4, there is an advantage in that a manufacturing cost for the rotary pressure increasing mechanism 49 is lower than that in Embodiment 1.
In Embodiments 1 to 4, the present invention is described with an example of the high-pressure shell hermetic scroll compressor. In this context, also when other rotary compression types (such as sliding-vane type and swing type) are employed, the same effects as those in Embodiments 1 to 4 can be obtained as long as the arrangement of the rotator 6 and the stator 7 of the electric motor 8, and the flow of the refrigerant from the electric motor subjacent space 5 to the electric motor superjacent space 9 are unchanged.
In Embodiment 5, an example of the vapor compression-type refrigeration cycle device including the hermetic compressor 100 described in any one of Embodiments 1 to 4 is described.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2014/057464 | 3/19/2014 | WO | 00 |
