U.S. patent application number 15/126203 was filed with the patent office on 2017-03-30 for hermetic compressor and vapor compression-type refrigeration cycle device including the hermetic compressor.
This patent application is currently assigned to MITSUBISHI ELECTRIC CORPORATION. The applicant listed for this patent is MITSUBISHI ELECTRIC CORPORATION. Invention is credited to Taro KATO, Toshihide KODA, Shogo MOROE, Teruhiko NISHIKI, Shin SEKIYA, Keisuke SHINGU (Deceased), Tetsuhide YOKOYAMA.
Application Number | 20170089624 15/126203 |
Document ID | / |
Family ID | 54143956 |
Filed Date | 2017-03-30 |
United States Patent
Application |
20170089624 |
Kind Code |
A1 |
YOKOYAMA; Tetsuhide ; et
al. |
March 30, 2017 |
HERMETIC COMPRESSOR AND VAPOR COMPRESSION-TYPE REFRIGERATION CYCLE
DEVICE INCLUDING THE HERMETIC COMPRESSOR
Abstract
A hermetic compressor, includes: a hermetic container storing a
lubricating oil; an electric motor; a drive shaft; a compression
mechanism; a rotary pressure increasing mechanism increasing
pressure of refrigerant gas; a cylindrical lateral wall
partitioning a space above the electric motor into outer and inner
spaces; and a discharge pipe allowing refrigerant to flow out from
the inner space into an external circuit. The refrigerant gas
discharged from the compression mechanism into the hermetic
container is moved from a space below the electric motor up to an
upper end of the rotator through rotator vents of the rotator,
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.
Inventors: |
YOKOYAMA; Tetsuhide;
(Chiyoda-ku, JP) ; NISHIKI; Teruhiko; (Chiyoda-ku,
JP) ; MOROE; Shogo; (Chiyoda-ku, JP) ; KATO;
Taro; (Chiyoda-ku, JP) ; SHINGU (Deceased);
Keisuke; (US) ; SEKIYA; Shin; (Chiyoda-ku,
JP) ; KODA; Toshihide; (Chiyoda-ku, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
MITSUBISHI ELECTRIC CORPORATION |
Chiyoda-ku |
|
JP |
|
|
Assignee: |
MITSUBISHI ELECTRIC
CORPORATION
Chiyoda-ku
JP
|
Family ID: |
54143956 |
Appl. No.: |
15/126203 |
Filed: |
March 19, 2014 |
PCT Filed: |
March 19, 2014 |
PCT NO: |
PCT/JP2014/057464 |
371 Date: |
September 14, 2016 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04C 29/045 20130101;
F04C 23/02 20130101; F25B 1/04 20130101; F04B 39/04 20130101; F04C
29/028 20130101; F04C 18/0215 20130101; F04C 2240/60 20130101; F04C
23/008 20130101; F04B 39/0246 20130101; F25B 43/02 20130101; F25B
31/002 20130101; F04C 23/005 20130101 |
International
Class: |
F25B 43/02 20060101
F25B043/02; F04C 29/04 20060101 F04C029/04; F04C 23/02 20060101
F04C023/02; F04C 29/02 20060101 F04C029/02; F04C 18/02 20060101
F04C018/02; F04C 23/00 20060101 F04C023/00 |
Claims
1: A hermetic compressor, comprising: 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
scroll-type compression mechanism arranged in the hermetic
container, for compressing refrigerant by rotation of the drive
shaft and discharging the compressed refrigerant into the hermetic
container, a rotary pressure increasing mechanism arranged on an
upper portion of the rotator, for increasing a pressure of
refrigerant gas flowing from a space below the electric motor
through the rotator vent into the rotary pressure increasing
mechanism 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 a stator side and an
inner space on a rotator side in such a manner that the cylindrical
lateral wall surrounds the rotary pressure increasing mechanism;
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, the rotary
pressure increasing mechanism being configured to make a pressure
in the inner space larger than a pressure in the outer space.
2: The hermetic compressor of claim 1, wherein the rotary pressure
increasing mechanism comprises a centrifugal impeller that is
rotated about the drive shaft so that the refrigerant gas flows
into the centrifugal impeller through an inlet on an inner
peripheral side, and flows out through an outlet on an outer
peripheral side while being increased in pressure.
3: The hermetic compressor of claim 2, wherein the cylindrical
lateral wall is arranged to surround the outlet on the outer
peripheral side of the centrifugal impeller.
4: The hermetic compressor of claim 2, wherein the centrifugal
impeller comprises: a lower surface plate for blocking inflow of
the refrigerant gas from a region below vanes of the centrifugal
impeller into the centrifugal impeller; an upper surface plate for
blocking inflow of the refrigerant gas from a region above the
vanes of the centrifugal impeller into the centrifugal impeller;
and a partition plate for blocking inflow of the refrigerant gas
into the inlet on the inner peripheral side of the centrifugal
impeller through passages other than the rotator vents.
5: The hermetic compressor of claim 1, wherein the stator comprises
a plurality of electric motor upper coil-interconnecting portions
formed of projecting parts of a coil wound around a core, the
projecting parts projecting from an upper end of the stator, and
wherein the cylindrical lateral wall is interposed to separate the
rotary pressure increasing mechanism and the electric motor upper
coil-interconnecting portions from each other.
6: The hermetic compressor of claim 1, further comprising a closing
member for closing an upper part of a passage formed between the
rotator and the stator.
7: The hermetic compressor of claim 1, wherein the cylindrical
lateral wall is arranged to an upper end of the rotator, and is
rotated together with the rotator.
8: The hermetic compressor of claim 1, wherein the compression
mechanism is arranged above the electric motor, and wherein the
refrigerant gas that is compressed by the compression mechanism and
discharged into the hermetic container flows from the outer space
into the space below the electric motor through stator outer
peripheral passages formed between the stator and the hermetic
container, is moved from the 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 the 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.
9: The hermetic compressor of claim 8, further comprising a
discharge cover for partitioning a part of the space above the
electric motor, which is positioned above the cylindrical lateral
wall, into the outer space and the inner space, the discharge cover
being arranged under the compression mechanism, wherein the
discharge cover and the cylindrical lateral wall are used to
increase a passage resistance of a short circuit passage that
communicates the outer space and the inner space to each other.
10: A vapor compression-type refrigeration cycle device,
comprising: the hermetic compressor of claim 1; 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.
Description
TECHNICAL FIELD
[0001] 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.
BACKGROUND ART
[0002] 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.
[0003] 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.
[0004] 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.
[0005] 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.
[0006] 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.
[0007] 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.
CITATION LIST
Patent Literature
[0008] Patent Literature 1: Japanese Patent No. 3925392 [0009]
Patent Literature 2: Japanese Unexamined Utility Model Application
Publication No. Hei 5-61487 [0010] Patent Literature 3: Japanese
Unexamined Patent Application Publication No. 2009-264175
Non Patent Literature
[0010] [0011] Non Patent Literature 1: "Turbofan and compressor",
Corona Publishing Co., Ltd. (1988) [0012] Non Patent Literature 2:
"Fluid mechanical engineering", Corona Publishing Co., Ltd.
(1983)
SUMMARY OF INVENTION
Technical Problem
[0013] 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.
[0014] 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.
[0015] 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.
[0016] 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.
Solution to Problem
[0017] 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.
[0018] 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.
Advantageous Effects of Invention
[0019] 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.
BRIEF DESCRIPTION OF DRAWINGS
[0020] FIG. 1 is a vertical sectional view of a structure of a
hermetic compressor according to Embodiment 1 of the present
invention.
[0021] FIG. 2 is a horizontal sectional view of the structure of
the hermetic compressor according to Embodiment 1 of the present
invention (sectional view taken along the line A-A in FIG. 1).
[0022] FIG. 3 is a perspective view of a rotary pressure increasing
mechanism that is arranged on an upper portion of a rotator of the
hermetic compressor according to Embodiment 1 of the present
invention.
[0023] FIG. 4 is a vertical sectional view of a structure of a
hermetic compressor according to Embodiment 2 of the present
invention.
[0024] FIG. 5 is a horizontal sectional view of the structure of
the hermetic compressor according to Embodiment 2 of the present
invention (sectional view taken along the line A-A in FIG. 4).
[0025] FIG. 6 is a perspective view of a rotary pressure increasing
mechanism that is arranged on an upper portion of a rotator of the
hermetic compressor according to Embodiment 2 of the present
invention.
[0026] FIG. 7 is a vertical sectional view of a structure of a
hermetic compressor according to Embodiment 3 of the present
invention.
[0027] FIG. 8 is a horizontal sectional view of the structure of
the hermetic compressor according to Embodiment 3 of the present
invention (sectional view taken along the line A-A in FIG. 7).
[0028] FIG. 9 is a vertical sectional view of a structure of a
hermetic compressor according to Embodiment 4 of the present
invention.
[0029] FIG. 10 is a horizontal sectional view of the structure of
the hermetic compressor according to Embodiment 4 of the present
invention (sectional view taken along the line A-A in FIG. 9).
[0030] FIG. 11 is a perspective view of a rotary pressure
increasing mechanism that is arranged on an upper portion of a
rotator of the hermetic compressor according to Embodiment 4 of the
present invention.
[0031] FIG. 12 is a configuration diagram of a vapor
compression-type refrigeration cycle device according to Embodiment
5 of the present invention.
DESCRIPTION OF EMBODIMENTS
Embodiment 1
[0032] FIG. 1 is a vertical sectional view of a structure of a
hermetic compressor according to Embodiment 1 of the present
invention. FIG. 2 is a horizontal sectional view of the structure
of the hermetic compressor according to Embodiment 1 of the present
invention (sectional view taken along the line A-A in FIG. 1).
Further, FIG. 3 is a perspective view of a rotary pressure
increasing mechanism that is arranged on an upper portion of a
rotator of the hermetic compressor according to Embodiment 1 of the
present invention. Note that, the solid arrow shown in FIG. 2
indicates a rotation direction of the rotary pressure increasing
mechanism. Further, the rotary pressure increasing mechanism
illustrated in FIG. 3 is viewed in a direction of the
three-dimensional arrow shown in FIG. 2.
[0033] First, with reference to FIGS. 1 to 3, a fundamental
structure and operation of a hermetic compressor 100 according to
Embodiment 1 is described.
[0034] <Fundamental structure and operation of hermetic
compressor 100>
[0035] 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.
[0036] 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.
[0037] 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.
[0038] 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.
[0039] 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.
[0040] 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.
[0041] 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.
[0042] 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).
[0043] 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 FIG. 1) in the hermetic container 1 through a discharge
port 18 of the fixed scroll 51.
[0044] 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 FIG. 1) in the hermetic container 1 through the discharge
port 18 of the fixed scroll 51 together with the refrigerant
compressed to have a high pressure in the compression chamber
4.
[0045] <Flow of Refrigerant in Hermetic Container>
[0046] 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 FIG. 1). Further, this
refrigerant flows downward into an electric motor stator subjacent
space ((3) in FIG. 1) in an electric motor subjacent space 5
through the stator outer peripheral passages 25 formed between the
core 7c of the stator 7 and the hermetic container 1, and reaches
the lower bearing member 12 including the sub bearing unit 54.
During this process, the refrigerant and the lubricating oil mixed
in an atomized form with the refrigerant are separated from each
other, and the separated lubricating oil is refluxed to the lower
oil reservoir 2 through an oil return hole 12a formed through the
lower bearing member 12.
[0047] 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
FIG. 1) in the electric motor subjacent space 5 through the rotator
vents 26 into a vane inner passage 46 of the centrifugal impeller
40 attached on an upper portion of the rotator 6 (passage on an
inner peripheral side of the inner peripheral flow guide 42, that
is, space represented by (5) in FIG. 1). Then, the refrigerant that
flows in the vane inner passage 46 is sucked into inter-vane
passages 47 formed between the vanes 41 of the centrifugal impeller
40, flows to the outer peripheral side while being increased in
pressure in accordance with a rotational speed of the centrifugal
impeller 40, and, on an outer peripheral side of the vanes 41,
flows up through a vane outer passage 48 formed in a region on an
inner peripheral side of the cylindrical lateral wall 37. Then,
this refrigerant is once released into the electric motor rotator
superjacent space 9b ((6) in FIG. 1) that is formed above the
circular vane superjacent disk 43 covering upper surfaces of the
vanes 41 of the centrifugal impeller 40 and on the inner peripheral
side of the cylindrical lateral wall 37. With this, static pressure
is increased. After that, the refrigerant that flows in the
electric motor rotator superjacent space 9b ((6) in FIG. 1) flows
into the discharge cover 56 through an opening portion 56a of the
discharge cover 56, and then is discharged into an external circuit
on an outside of the hermetic container 1 through a compressor
discharge pipe 22 that communicates to an inner space of the
discharge cover 56.
[0048] <Flow in Short Circuit Passage 23 and Short-Circuit
Prevention>
[0049] 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 FIG. 1) to the electric
motor rotator superjacent space 9b ((6) in FIG. 1), the refrigerant
may flow from the electric motor stator superjacent space 9a ((2)
in FIG. 1) directly into the electric motor rotator superjacent
space 9b ((6) in FIG. 1) without flowing through the electric motor
stator subjacent space ((3) in FIG. 1). As a result, a large number
of droplets of unseparated oil may flow out from the hermetic
container 1 to the external circuit, which may cause degradation in
performance and reliability of the hermetic compressor 100, and
degradation in performance of the vapor compression-type
refrigeration cycle device (in particular, of the heat
exchanger).
[0050] 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.
[0051] (1) Set a passage resistance of the short circuit passage 23
to the electric motor rotator superjacent space 9b ((6) in FIG. 1)
to be sufficiently high.
[0052] (2) Increase a pressure in the electric motor rotator
superjacent space 9b ((6) in FIG. 1) to be close to or higher than
a pressure in the electric motor stator superjacent space 9a.
[0053] 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.
[0054] 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 FIG. 1) through radial passages 28 in
the electric motor upper coil-interconnecting portions 7a. As a
result, the pressure in the electric motor rotator superjacent
space 9b ((6) in FIG. 1) can be increased.
[0055] 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
FIG. 1) to the electric motor superjacent space 9 ((2) or (5) in
FIG. 1), and the pressure increasing effect by the centrifugal
impeller 40 cannot be exerted to the refrigerant gas that flows
through the stator inner peripheral passage 27. Therefore, a
greater pressure increasing effect can be obtained by the
centrifugal impeller 40 when the stator inner peripheral passage 27
is closed as much as possible. Thus, in Embodiment 1, to slightly
increase an outer diameter of the balancer fixing bottom plate 38
(for example, approximately 1 mm), the stator inner peripheral
passage closing portion 38b is arranged to the outer peripheral
portion of the disk portion 38a so that the upper part of the
stator inner peripheral passage 27 is closed. With this, an amount
of the refrigerant gas that flows through the stator inner
peripheral passage 27 can be suppressed, and thus the pressure in
the electric motor rotator superjacent space 9b ((6) in FIG. 1) can
be further increased.
[0056] <Design of Centrifugal Impeller>
[0057] To increase the pressure in the electric motor rotator
superjacent space 9b ((6) in FIG. 1) with the centrifugal impeller
40 such that approximately 100% of the refrigerant flows from the
electric motor stator superjacent space 9a ((2) in FIG. 1) to the
electric motor stator subjacent space ((3) in FIG. 1), the shape of
the vanes and the passages of the centrifugal impeller 40 need to
be designed such that a pressure (P.sub.6) in the electric motor
rotator superjacent space 9b ((6) in FIG. 1) is higher than a
pressure (P.sub.2) in the electric motor stator superjacent space
9a ((2) in FIG. 1). Further, to increase a pressure in the
centrifugal impeller 40, input to the compressor (electric power
consumption thereof) is increased. Thus, it is also important to
design a highly-efficient centrifugal impeller 40.
[0058] 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 .beta.1b 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.
[0059] The rotator vents 26 are arranged on an inner side with
respect to the inner peripheral flow guide 42 in plan view. [0060]
The vane superjacent disk 43 and the vane subjacent disk 44 for
covering the upper and lower sides of the vanes 41 are configured
to cover all over the inner peripheral side to the outer peripheral
side of the plurality of vanes 41.
[0061] 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 FIG. 1) can be
further increased.
[0062] <Effects>
[0063] In the hermetic compressor 100 configured as in Embodiment
1, the pressure in the electric motor rotator superjacent space 9b
((6) in FIG. 1) can be increased by using rotation of the rotator 6
in the hermetic container 1. Specifically, when the hermetic
compressor 100 that is configured to output three horsepower and
operated at a constant speed (50 rps), is operated by using a
refrigerant R22 under the condition of Ashrae standard, an effect
of increasing the pressure in the electric motor rotator
superjacent space 9b ((6) in FIG. 1) in units of several kPa can be
obtained. As a result, the refrigerant is less liable to flow from
the electric motor stator superjacent space 9a ((2) in FIG. 1)
directly into the electric motor rotator superjacent space 9b ((6)
in FIG. 1) through the short circuit passage 23, and the large
number of droplets of the unseparated oil are less liable to flow
out from the hermetic container 1 to the external circuit. Further,
to effectively use the sealed lubricating oil, an effect of
suppressing the degradation in performance of the hermetic
compressor 100, and an effect of suppressing the degradation in
reliability thereof due to insufficient lubrication that may be
caused by a decrease in amount of the oil stored in the hermetic
container 1 can be obtained.
Embodiment 2
[0064] FIG. 4 is a vertical sectional view of a structure of a
hermetic compressor according to Embodiment 2 of the present
invention. FIG. 5 is a horizontal sectional view of the structure
of the hermetic compressor according to Embodiment 2 of the present
invention (sectional view taken along the line A-A in FIG. 4).
Further, FIG. 6 is a perspective view of a rotary pressure
increasing mechanism that is arranged on an upper portion of a
rotator of the hermetic compressor according to Embodiment 2 of the
present invention. Note that, the solid arrow shown in FIG. 5
indicates a rotation direction of the rotary pressure increasing
mechanism. Further, the rotary pressure increasing mechanism
illustrated in FIG. 6 is viewed in a direction of the
three-dimensional arrow shown in FIG. 5.
[0065] Now, with reference to FIGS. 4 to 6, the hermetic compressor
100 according to Embodiment 2 is described. Note that, the
fundamental structure and the operation of the hermetic compressor
100 according to Embodiment 2 are the same as those in Embodiment
1, and hence description thereof is omitted.
[0066] (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.
[0067] 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.
[0068] (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.
[0069] 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.
[0070] (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. [0071] In
the hermetic compressor 100 according to Embodiment 2, the lower
end portion of the discharge cover 56 is not subjected to a bending
process, and hence the short circuit passage 23 has a simple shape.
Thus, in the hermetic compressor 100 according to Embodiment 2, the
passage resistance in the short circuit passage 23 is determined
based on a size of a smallest gap that is formed between the
discharge cover 56 and the cylindrical lateral wall 36a. [0072]
Further, the hermetic compressor 100 according to Embodiment 2 does
not include the closing member for closing the stator inner
peripheral passage 27 (counterpart of the stator inner peripheral
passage closing portion 38b in Embodiment 1).
Embodiment 3
[0073] FIG. 7 is a vertical sectional view of a structure of a
hermetic compressor according to Embodiment 3 of the present
invention. FIG. 8 is a horizontal sectional view of the structure
of the hermetic compressor according to Embodiment 3 of the present
invention (sectional view taken along the line A-A in FIG. 7). Note
that, the solid arrow shown in FIG. 8 indicates a rotation
direction of the rotary pressure increasing mechanism.
[0074] Now, with reference to FIGS. 7 and 8, the hermetic
compressor 100 according to Embodiment 3 is described. Note that,
the fundamental structure and the operation of the hermetic
compressor 100 according to Embodiment 3 are the same as those in
Embodiment 1, and hence description thereof is omitted.
[0075] (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.
[0076] (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.
[0077] 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.
Embodiment 4
[0078] FIG. 9 is a vertical sectional view of a structure of a
hermetic compressor according to Embodiment 4 of the present
invention. FIG. 10 is a horizontal sectional view of the structure
of the hermetic compressor according to Embodiment 4 of the present
invention (sectional view taken along the line A-A in FIG. 9).
Further, FIG. 11 is a perspective view of a rotary pressure
increasing mechanism that is arranged on an upper portion of a
rotator of the hermetic compressor according to Embodiment 4 of the
present invention. Note that, the solid arrow shown in FIG. 10
indicates a rotation direction of the rotary pressure increasing
mechanism. Further, the rotary pressure increasing mechanism
illustrated in FIG. 11 is viewed in a direction of the
three-dimensional arrow shown in FIG. 10.
[0079] Now, with reference to FIGS. 9 to 11, the hermetic
compressor 100 according to Embodiment 4 is described. Note that,
the fundamental structure and the operation of the hermetic
compressor 100 according to Embodiment 4 are the same as those in
Embodiment 1, and hence description thereof is omitted.
[0080] (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 FIG. 9) through a cup
inner passage 36d formed on an inner peripheral side of the oil
separating cup 36. In the rotary pressure increasing mechanism 49
according to Embodiment 4, although the great pressure increasing
effect (for example, in units of several kPa) by the centrifugal
impeller cannot be obtained, a pressure increasing effect (for
example, 1 kPa or less) can be obtained by rotations of the rotary
disk 30b of the balancer cover 30, the oil separating rotary disk
35, and the cylindrical lateral wall 36a of the oil separating cup
36.
[0081] 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.
[0082] 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.
Embodiment 5
[0083] 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.
[0084] FIG. 12 is a configuration diagram of a vapor
compression-type refrigeration cycle device 101 according to
Embodiment 5. The vapor compression-type refrigeration cycle device
101 includes the hermetic compressor 100 described in any one of
Embodiments 1 to 4, a radiator 102 for transferring heat of the
refrigerant compressed by the hermetic compressor 100, an expansion
mechanism 103 for expanding the refrigerant that flows out from the
radiator 102, and an evaporator 104 for causing the refrigerant
that flows out from the expansion mechanism 103 to receive heat.
When the hermetic compressor 100 according to any one of
Embodiments 1 to 4 is used in the vapor compression-type
refrigeration cycle device 101, the vapor compression-type
refrigeration cycle device 101 can be improved in energy saving
efficiency, reduced in vibration and noise, and increased in
reliability.
REFERENCE SIGNS LIST
[0085] 1 hermetic container 2 lower oil reservoir 3 drive shaft 3a
hollow hole 3b oil supply hole 4 compression chamber 5 electric
motor subjacent space 6 rotator 7 stator 7a electric motor upper
coil-interconnecting portion 7b electric motor lower
coil-interconnecting portion 7c core 8 electric motor 9 electric
motor superjacent space 9a electric motor stator superjacent space
9b electric motor rotator superjacent space 10 discharge space 11
upper bearing member 12 lower bearing member 12a oil return hole 18
discharge port 21 compressor suction pipe 22 compressor discharge
pipe 23 short circuit passage 25 stator outer peripheral passage 26
rotator vent 27 stator inner peripheral passage 27a air gap 27b
core inner peripheral portion cut-out passage 28 radial passage 29
closing cover [0086] 29a cylindrical portion 29b projecting portion
for closing stator inner peripheral passage 29c smallest gap 30
balancer cover 30a inner passage 30b rotary disk 30c inner
peripheral flow guide 31 upper balance weight 31a rotation
direction leading end portion 31b rotation direction trailing end
portion 32 lower balance weight 33 rotator upper end fixing
substrate 34 rotator lower end fixing substrate 35 oil separating
rotary disk (single member) 36 oil separating cup 36a cylindrical
lateral wall [0087] 36b bottom plate 36c oil drain hole 36d cup
inner passage 37 cylindrical lateral wall (single member) 38
balancer fixing bottom plate 38a disk portion 38b stator inner
peripheral passage closing portion 39 oil drain hole 40 centrifugal
impeller 41 vane 42 inner peripheral flow guide 43 vane superjacent
disk 44 vane subjacent disk 46 vane inner passage 47 inter-vane
passage 48 vane outer passage 49 rotary pressure increasing
mechanism 50 compression mechanism casing 51 fixed scroll 52
orbiting scroll 54 sub bearing unit 55 main bearing unit 56
discharge cover [0088] 56a opening portion 57 refrigerant passage
60 compression mechanism 100 hermetic compressor 101 vapor
compression-type refrigeration cycle device 102 radiator 103
expansion mechanism 104 evaporator
* * * * *