FORM 2
THE PATENTS ACT, 1970
(39 of 1970)
&
THE PATENTS RULES, 2003
COMPLETE SPECIFICATION
[See section 10, Rule 13]
COMPRESSOR, REFRIGERATION CYCLE DEVICE, AND AIR
CONDITIONER;
MITSUBISHI ELECTRIC CORPORATION, A CORPORATION
ORGANISED AND EXISTING UNDER THE LAWS OF JAPAN, WHOSE
ADDRESS IS 7-3, MARUNOUCHI 2-CHOME, CHIYODA-KU, TOKYO
1008310, JAPAN
THE FOLLOWING SPECIFICATION PARTICULARLY DESCRIBES THE
INVENTION AND THE MANNER IN WHICH IT IS TO BE PERFORMED

2
DESCRIPTION
TECHNICAL FIELD
[0001]
5 The present disclosure relates to a compressor, a
refrigeration cycle device, and an air conditioner.
BACKGROUND ART
[0002]
10 A compressor including a compression mechanism that
compresses a refrigerant, an electric motor that drives
the compression mechanism, and a container containing the
compression mechanism, the electric motor, the
refrigerant, and lubricating oil has become widespread.
15 See, for example, Patent Literature 1. Patent Literature
1 describes that a rotor core of a rotor of an electric
motor includes a plurality of electromagnetic steel
sheets laminated with a gap in between, and the rotor
core has an opening (hereinafter referred to as an “air
20 opening”) serving as a flow channel in which a
refrigerant and lubricating oil flow.
PRIOR ART REFERENCE
PATENT REFERENCE
25 [0003]
Patent Reference 1: International Patent Publication
No. 2017/072967 (see, for example, paragraphs 0139, 0140,
and 0142, FIGS. 2 through 5, 8, 26, and 27)
30 SUMMARY OF THE INVENTION
PROBLEM TO BE SOLVED BY THE INVENTION
[0004]
However, in the case of increasing the flow rate of

3
a refrigerant flowing in the air opening in order to
increase the flow rate of the refrigerant discharged from
the compressor (hereinafter referred to as a “stroke
volume”), the flow velocity of the refrigerant in the air
5 opening increases. In this case, the refrigerant and
lubricating oil are not easily separated, and thus, the
lubricating oil does not easily flow in the gap between
the plurality of electromagnetic steel sheets and tends
to be discharged to the outside of the compressor.
10 Accordingly, there arises a problem of poor lubrication
due to a shortage of lubricating oil for lubricating a
compression mechanism in a compressor.
[0005]
It is therefore an object of the present disclosure
15 to prevent poor lubrication in a compressor.
MEANS OF SOLVING THE PROBLEM
[0006]
A compressor according to an aspect of the present
20 disclosure includes: a compression mechanism to compress
a refrigerant; an electric motor to drive the compression
mechanism; and a container to contain the compression
mechanism, the electric motor, the refrigerant, and
lubricating oil, wherein a rotor of the electric motor
25 includes: a rotor core including a plurality of steel
sheets laminated with a first gap in between; and a first
permanent magnet inserted in a magnet insertion hole of
the rotor core, the rotor core includes: a flow channel
which is located inward from the magnet insertion hole in
30 a radial direction of the rotor core and through which
the refrigerant and the lubricating oil flow; and a first
guide part to guide the lubricating oil flowing through
the flow channel to the first gap when the rotor rotates.
EFFECTS OF THE INVENTION

4
[0007]
According to the present disclosure, poor
lubrication in the compressor can be prevented.
5 BRIEF DESCRIPTION OF THE DRAWINGS
[0008]
FIG. 1 is a cross-sectional view illustrating a
configuration of a compressor according to a first
embodiment.
10 FIG. 2 is a cross-sectional view illustrating a
configuration of a compression mechanism shown in FIG. 1.
FIG. 3 is a cross-sectional view illustrating a
configuration of an electric motor shown in FIG. 1.
FIG. 4 is a cross-sectional view illustrating a
15 configuration of a rotor according to the first
embodiment.
FIG. 5 is a cross-sectional view illustrating a
portion of the configuration of the rotor shown in FIG. 3.
FIG. 6A is an enlarged cross-sectional view
20 illustrating a portion of the configuration of the rotor
shown in FIG. 5. FIG. 6B is a cross-sectional view of a
portion of the rotor shown in FIG. 6A taken along line
B6-B6.
FIG. 7A is a plan view illustrating a configuration
25 of an upper end plate shown in FIG. 1. FIG. 7B is a plan
view illustrating a configuration of a lower end plate
shown in FIG. 1.
FIG. 8 is a cross-sectional view illustrating a
configuration of a rotor of an electric motor of a
30 compressor according to a first variation of the first
embodiment.
FIG. 9 is a cross-sectional view illustrating a
configuration of a rotor of an electric motor of a
compressor according to a second variation of the first

5
embodiment.
FIG. 10 is a cross-sectional view illustrating a
configuration of a rotor of an electric motor of a
compressor according to a second embodiment.
5 FIG. 11 is a cross-sectional view illustrating a
configuration of a rotor of an electric motor of a
compressor according to a first variation of the second
embodiment.
FIG. 12 is a diagram illustrating a configuration of
10 a refrigerant circuit in cooling operation of an air
conditioner according to a third embodiment.
FIG. 13 is a diagram illustrating the configuration
of the refrigerant circuit in heating operation of the
air conditioner according to the third embodiment.
15
MODE FOR CARRYING OUT THE INVENTION
[0009]
A compressor, a refrigeration cycle device, and an
air conditioner according to an embodiment of the present
20 disclosure will be described with reference to the
drawings. The following embodiments are merely examples,
and the embodiments may be combined as appropriate and
each embodiment may be changed as appropriate.
[0010]
25 The type of “refrigerant” herein will be described
using a refrigerant number beginning with “R” specified
by the International Standard ISO 817.
[0011]
FIRST EMBODIMENT
30
FIG. 1 is a cross-sectional view illustrating a
configuration of a compressor 100 according to a first
embodiment. The compressor 100 is, for example, a rotary
compressor. The compressor 100 is not limited to a

6
rotary compressor, and may be another compressor such as
a low-pressure compressor or a scroll compressor.
[0012]
As illustrated in FIG. 1, the compressor 100
5 includes a compression mechanism 1, an electric motor 2,
a crankshaft 3 as a rotation shaft, and a sealed
container 4 as a container.
[0013]
The compression mechanism 1 sucks a refrigerant 110
10 from an accumulator 101 and compresses the refrigerant
110. The electric motor 2 drives the compression
mechanism 1. The electric motor 2 is disposed on a
downstream side with respect to the compression mechanism
1 in a direction in which the refrigerant 110 flows. In
15 the example illustrated in FIG. 1, the refrigerant 110
flows from a -z-axis side to a +z-axis side.
Specifically, a downstream side in the direction in which
the refrigerant 110 flows is the +z-axis side, and an
upstream side in the direction in which the refrigerant
20 110 flows is the -z-axis side.
[0014]
The refrigerant 110 includes ethylene-based
fluorocarbon having a double bond of carbon. That is,
the refrigerant 110 is a hydro fluoro olefin (HFO)
25 refrigerant. Accordingly, since the refrigerant 110
includes ethylene-based fluorocarbon, a working pressure
of the compressor 100 can be reduced. A global warming
potential (GWP) of the refrigerant 110 is lower than a
GWP of a hydro fluoro carbon (HFC) refrigerant. Thus,
30 the greenhouse effect of the refrigerant 110 is smaller
than the greenhouse effect of the HFC refrigerant. In
addition, since the refrigerant 110 includes ethylenebased fluorocarbon, disproportionation of the refrigerant
110 can be prevented.

7
[0015]
In the first embodiment, the refrigerant 110 is a
refrigerant mixture in which ethylene-based fluorocarbon
is mixed with another refrigerant. The refrigerant 110
5 includes R1123 (i.e., 1,1,2-trifluoroethylene) as
ethylene-based fluorocarbon. The proportion of R1123 in
the refrigerant 110 is preferably within the range from
40wt% to 60wt%, for example.
[0016]
10 The refrigerant 110 includes R32 (difluoromethane)
as another refrigerant, for example. That is, in the
first embodiment, the refrigerant 110 is a refrigerant
mixture in which R1123 and R32 are mixed. R1123 is not
limited to R32, and R1123 may be mixed with one or more
15 refrigerants of R1234yf (i.e., 2,3,3,3-
tetrafluoropropene), R1234ze(E) (i.e., trans-1,3,3,3-
tetrafluoropropene), R1234ze(Z) (i.e., sis-1,3,3,3-
tetrafluoropropene), R125 (1,1,1,2-pentafluoroethane),
and R134a (i.e., 1,1,1,2-tetrafluoroethane).
20 [0017]
The refrigerant 110 may include two or more types of
ethylene-based fluorocarbon. For example, the
refrigerant 110 may include R1123 and another ethylenebased fluorocarbon. For example, the refrigerant 110 may
25 include one or more types of ethylene-based fluorocarbon
of R1141 (i.e., fluoroethylene), R1132a (i.e., 1,1-
diuoroethylene), R1132(E) (i.e., trans-1,2-
difluoroethylene), and R1132(Z) (i.e., sis-1,2-
difluoroethylene), as another ethylene-based fluorocarbon.
30 The refrigerant 110 may include R290 (i.e., propane)
composed of hydrocarbon, as well as ethylene-based
fluorocarbon. That is, the refrigerant 110 may be a
hydro carbon (HC) refrigerant.
[0018]

8
The crankshaft 3 couples the compression mechanism 1
and the electric motor 2 to each other. The crankshaft 3
includes a shaft body part 3a fixed to a rotor 10 of the
electric motor 2 and an eccentric shaft part 3b fixed to
5 a rolling piston 32 of the compression mechanism 1.
[0019]
In the following description, a direction along a
circumference of a circle about the crankshaft 3 will be
referred to as a “circumferential direction,” a direction
10 in which an axis (axis C shown in FIG. 2 described later)
as a rotation center of the crankshaft 3 will be referred
to as an “axial direction,” and a direction in which a
line orthogonal to the axial direction and passing
through the crankshaft 3 will be referred to as a “radial
15 direction.” In some drawings, an xyz orthogonal
coordinate system is shown in order to facilitate
understanding of relationship among the drawings. The z
axis is a coordinate axis parallel to the axis of the
crankshaft 3. The y axis is a coordinate axis orthogonal
20 to the z axis. The x axis is a coordinate axis
orthogonal to both the y axis and the z axis.
[0020]
The sealed container 4 is a substantially
cylindrical container, and contains the compression
25 mechanism 1, the electric motor 2, the refrigerant 110,
and refrigerating machine oil 40. The refrigerating
machine oil 40 is lubricating oil for lubricating the
compression mechanism 1, and is stored in a bottom
portion 4a of the sealed container 4. That is, the
30 bottom portion 4a of the sealed container 4 is an oil
sump in which the refrigerating machine oil 40 is stored.
The refrigerating machine oil 40 lubricates a sliding
part of the compression mechanism 1 (e.g., a fitting part
between the rolling piston 32 and the eccentric shaft

9
part 3b of the crankshaft 3 shown in FIG. 2 described
later). The refrigerating machine oil 40 flows through
an oil supply passage (not shown) formed in the
crankshaft 3 and lubricates the sliding part of the
5 compression mechanism 1.
[0021]
The compressor 100 further includes a discharge pipe
41 and a terminal 42 attached to an upper portion of the
sealed container 4. The discharge pipe 41 is connected
10 to a refrigerant flow channel of the refrigeration cycle
device. The discharge pipe 41 discharges the refrigerant
110 compressed by the compression mechanism 1 to the
outside of the sealed container 4. The terminal 42 is
connected to a driving device (not shown) disposed
15 outside the compressor 100. The terminal 42 supplies a
driving current to a coil 22 of a stator 20 of the
electric motor 2 through a lead wire 44. Accordingly,
magnetic flux flows in the coil 22 and consequently the
rotor 10 rotates.
20 [0022]

FIG. 2 is a cross-sectional view illustrating a
configuration of the compression mechanism 1 shown in FIG.
1. As illustrated in FIGS. 1 and 2, the compression
25 mechanism 1 includes a cylinder 31, the rolling piston 32,
a vane 33, an upper bearing 34, and a lower bearing 35.
The cylinder 31 includes a suction port 31a, a cylinder
chamber 31b, and a vane groove 31c.
[0023]
30 The suction port 31a is connected to the accumulator
101 through a suction pipe 43. The suction port 31a is a
passage in which the refrigerant 110 sucked from the
accumulator 101 flows, and communicates with the cylinder
chamber 31b.

10
[0024]
The cylinder chamber 31b is cylindrical space about
the axis C. The cylinder chamber 31b houses the
eccentric shaft part 3b of the crankshaft 3, the rolling
5 piston 32, and the vane 33. The rolling piston 32 has a
ring shape. The rolling piston 32 is fixed to the
eccentric shaft part 3b of the crankshaft 3.
[0025]
The vane groove 31c communicates with the cylinder
10 chamber 31b. The vane 33 is attached to the vane groove
31c. A back-pressure chamber 31d is provided in an end
portion of the vane groove 31c. The vane 33 is pressed
by a spring (not shown) disposed in the back-pressure
chamber 31d toward the axis C to be thereby brought into
15 contact with an outer peripheral surface of the rolling
piston 32. Accordingly, the vane 33 divides space 36
surrounded by an inner peripheral surface of the cylinder
chamber 31b, the outer peripheral surface of the rolling
piston 32, the upper bearing 34, and the lower bearing 35
20 into a suction-side working chamber (hereinafter referred
to as a “suction chamber”) 36a and a compression-side
working chamber (hereinafter referred to as a
“compression chamber”) 36b. The suction chamber 36a
communicates with the suction port 31a.
25 [0026]
While the rolling piston 32 eccentrically rotates,
the vane 33 reciprocates in the y-axis direction in the
vane groove 31c. The vane 33 has a plate shape, for
example. In the example illustrated in FIG. 2, the
30 rolling piston 32 and the vane 33 are separate components,
but the rolling piston 32 may be integrated with the vane
33.
[0027]
As illustrated in FIG. 1, the upper bearing 34

11
closes an end portion of the cylinder chamber 31b on the
+z-axis side. The lower bearing 35 closes an end portion
of the cylinder chamber 31b on the -z-axis side. The
upper bearing 34 and the lower bearing 35 are fixed to
5 the cylinder 31 by fastening members (e.g., bolts).
[0028]
Each of the upper bearing 34 and the lower bearing
35 has a discharge port from which the compressed
refrigerant 110 (see FIG. 1) is discharged to the outside
10 of the cylinder chamber 31b. The discharge port of each
of the upper bearing 34 and the lower bearing 35
communicates with the compression chamber 36b of the
cylinder chamber 31b. The discharge port is provided
with a discharge valve (not shown). When the pressure of
15 the refrigerant 110 compressed in the compression chamber
36b increases to a predetermined pressure or more, the
discharge valve opens and allows the high-temperature and
high-pressure refrigerant 110 to be discharged to inner
space of the sealed container 4. The lower bearing 35
20 may not have a discharge port.
[0029]
An upper discharge muffler 37 is attached to the
upper bearing 34 with a fastening member (e.g., a bolt).
A muffler chamber 37a is disposed between the upper
25 bearing 34 and the upper discharge muffler 37.
Accordingly, the refrigerant 110 discharged from the
discharge port of the upper bearing 34 is diffused in the
muffler chamber 37a, and thus, occurrence of discharge
noise of the refrigerant 110 discharged from the
30 discharge port of the upper bearing 34 can be suppressed.
[0030]
A lower discharge muffler 38 is attached to the
lower bearing 35 with a fastening member (e.g., a bolt).
A muffler chamber 38a is disposed between the lower

12
bearing 35 and the lower discharge muffler 38.
Accordingly, the refrigerant 110 discharged from the
discharge port of the lower bearing 35 is diffused in the
muffler chamber 38a, and thus, occurrence of discharge
5 noise of the refrigerant 110 discharged from the lower
bearing 35 can be suppressed. In a case where only one
of the upper bearing 34 or the lower bearing 35 has a
discharge port, a discharge muffler may be attached to
the bearing having the discharge port.
10 [0031]

Next, operation of the compressor 100 will be
described with reference to FIGS. 1 and 2. A driving
current is supplied from the terminal 42 to the electric
15 motor 2 and consequently the rotor 10 of the electric
motor 2 rotates. With the rotation of the rotor 10, the
crankshaft 3 rotates accordingly. While the crankshaft 3
rotates, the rolling piston 32 and the eccentric shaft
part 3b rotate about an axis eccentric from the axis C in
20 a direction indicated by arrow A in FIG. 2. Accordingly,
the low-pressure refrigerant 110 is sucked into the
suction chamber 36a.
[0032]
The refrigerant 110 sucked in the suction chamber
25 36a is compressed by rotation of the rolling piston 32.
Specifically, while the rolling piston 32 eccentrically
rotates, the vane 33 reciprocates in the vane groove 31c
to cause the refrigerant 110 sucked in the suction
chamber 36a to move to the compression chamber 36b to be
30 compressed. The refrigerant 110 compressed in the
compression chamber 36b changes to a high-temperature and
high-pressure refrigerant gas and is discharged from one
of the upper discharge muffler 37 or the lower discharge
muffler 38.

13
[0033]
The refrigerating machine oil 40 is dissolved in the
refrigerant 110 compressed by the compression mechanism 1.
The refrigerating machine oil 40 flows in flow channel 15
5 (see FIG. 1) as an air opening formed in the rotor 10 of
the electric motor 2, through the oil supply passage (not
shown) formed in the crankshaft 3. At this time, the
refrigerant 110 and the refrigerating machine oil 40 are
separated in the flow channel 15 by a centrifugal force
10 exerted during rotation of the rotor 10. Specifically,
the refrigerating machine oil 40 having a larger specific
gravity than the refrigerant 110 flows at the outer side
in the radial direction in the flow channel 15, and the
refrigerant 110 flows at the inner side in the radial
15 direction in the flow channel 15 and consequently the
refrigerant 110 and the refrigerating machine oil 40 are
separated. The refrigerating machine oil 40 separated
from the refrigerant 110 cools the rotor core 11 and a
permanent magnet 12 of the rotor 10. On the other hand,
20 the refrigerant 110 is discharged to the outside of the
sealed container 4 through the discharge pipe 41, and
flows in a refrigerant flow channel (e.g., refrigerant
flow channel 310 shown in FIGS. 12 and 13 described
later) of the refrigeration cycle device.
25 [0034]

A configuration of the electric motor 2 according to
the first embodiment will now be described. FIG. 3 is a
cross-sectional view illustrating the configuration of
30 the electric motor 2 according to the first embodiment.
As illustrated in FIG. 3, the electric motor 2 includes
the rotor 10 and the stator 20. The rotor 10 is disposed
at the inner side of the stator 20. That is, the
electric motor 2 according to the first embodiment is an

14
inner-rotor electric motor. An air gap E is present
between the rotor 10 and the stator 20. The air gap E is
a gap defined within the range from 0.3 mm to 1.0 mm, for
example.
5 [0035]

A configuration of the stator 20 will now be
described. As illustrated in FIG. 3, the stator 20
includes a stator core 21 and the coil 22 wound around
10 the stator core 21. The stator core 21 is fixed to the
sealed container 4 illustrated in FIG. 1. The stator
core 21 is fixed to the inner wall of the sealed
container 4 by a method such as press fitting, shrink
fitting, or welding, for example. The coil 22 is wound
15 around the stator core 21 with an insulator 23 interposed
therebetween.
[0036]

A configuration of the rotor 10 will now be
20 described with reference to FIGS. 4 and 5. FIG. 4 is a
cross-sectional view illustrating a configuration of the
rotor 10 shown in FIG. 1. FIG. 5 is a cross-sectional
view illustrating a portion of the configuration of the
rotor 10 shown in FIG. 3. As illustrated in FIGS. 4 and
25 5, the rotor 10 includes a rotor core 11, a permanent
magnet 12a as a first permanent magnet, and a permanent
magnet 12b as a second permanent magnet. The permanent
magnets 12a and 12b are inserted in magnet insertion
holes 11b of the rotor core 11. In the following
30 description, in a case where it is unnecessary to
distinguish the permanent magnet 12a and the permanent
magnet 12b, the permanent magnet 12a and the permanent
magnet 12b will be collectively referred to as “permanent
magnets 12.” The permanent magnets 12 are omitted from

15
FIG. 4.
[0037]
As illustrated in FIG. 4, the rotor core 11 includes
a plurality of electromagnetic steel sheets 13 as a
5 plurality of steel sheets laminated in a z-axis direction.
The plurality of electromagnetic steel sheets 13 are
laminated with a gap D as a first gap in between. The
rotor core 11 includes non-oriented electromagnetic steel
sheets as the electromagnetic steel sheets 13. A
10 thickness t1 of each of the electromagnetic steel sheet 13
is a predetermined thickness within the range from 0.2 mm
to 0.7 mm, for example. In the first embodiment, the
thickness t1 of each electromagnetic steel sheet 13 is,
for example, 0.35 mm. The rotor core 11 may include
15 other magnetic steel sheets, instead of the
electromagnetic steel sheets 13.
[0038]
The plurality of electromagnetic steel sheets 13 are
fixed to one another by swaging, and thus the rotor core
20 11 is formed. Thus, the rotor core 11 includes a swaging
portion 14. The swaging portion 14 includes a swaging
projection 14a and a swaging recess 14b. The swaging
projection 14a is a projection projecting toward another
adjacent electromagnetic steel sheet 13. The swaging
25 recess 14b is a recess in which the swaging projection
14a is fitted. The swaging projection 14a is fitted in
the swaging recess 14b of another adjacent
electromagnetic steel sheet 13 and consequently two
adjacent electromagnetic steel sheets 13 are fastened.
30 In the first embodiment, the swaging projection 14a is a
V-shaped projection. Accordingly, as compared to a
configuration in which the swaging projection is a
cylindrical projection, a fastening force for fastening
two adjacent electromagnetic steel sheets 13 is enhanced.

16
The length of the swaging projection 14a in the z-axis
direction is larger than the thickness t1 of each
electromagnetic steel sheet 13.
[0039]
5 A spacing t2 of the gap D is smaller than the
thickness t1 of each electromagnetic steel sheet 13. The
spacing t2 is, for example, equal to or less than 1/10 of
the thickness t1 of each electromagnetic steel sheet 13.
In the first embodiment, the spacing t2 is 10 μm or less.
10 Specifically, the spacing t2 has a predetermined dimension
within the range from 1 μm to 5 μm. In the first
embodiment, since the swaging projection 14a has the Vshaped projection as described above, dimensional
accuracy of the spacing t2 is sufficiently obtained as
15 compared to the configuration in which the swaging
projection is a cylindrical projection.
[0040]
As illustrated in FIG. 5, the rotor core 11 includes
a shaft insertion hole 11a as a shaft insertion hole and
20 the plurality of magnet insertion holes 11b. The
crankshaft 3 (see FIG. 4) is fixed to the shaft insertion
hole 11a. The crankshaft 3 is fixed to the shaft
insertion hole 11a by a method such as press fitting,
shrink fitting, or welding, for example.
25 [0041]
The plurality of magnet insertion holes 11b are
spaced from one another in a circumferential direction R
with a spacing. The shape of each magnet insertion hole
11b when seen in the z-axis direction is a V shape
30 projecting radially inward. The shape of each magnet
insertion hole 11b when seen in the z-axis direction may
be an arc shape projecting radially inward or outward or
a bathtub shape projecting radially outward. The shape
of each magnet insertion hole 11b when seen in the z-axis

17
direction may be a rectangle.
[0042]
The permanent magnet 12a and the permanent magnet
12b are embedded in the magnet insertion holes 11b. Thus,
5 the structure of the rotor 10 is an interior permanent
magnet (IPM) structure. The permanent magnet 12a and the
permanent magnet 12b are disposed with a gap S1 as a
second gap in between in the magnet insertion holes 11b.
In the first embodiment, the rotor core 11 has six magnet
10 insertion holes 11b, for example. Accordingly, in the
first embodiment, the number of poles of the electric
motor 2 is six. The number of poles of the electric
motor 2 is not limited to six, and only needs to be two
or more.
15 [0043]
In the first embodiment, the permanent magnet 12 is,
for example, a plate-shaped magnet. The shape of the
permanent magnet 12 when seen in the z-axis direction is
a rectangle. The permanent magnet 12 is not limited to a
20 plate-shaped magnet, and may be a magnet having a
semicylindrical curved surface. The thickness of the
permanent magnet 12 in the lateral direction is smaller
than the thickness of each magnet insertion hole 11b in
the lateral direction. Thus, a gap S2 as a third gap is
25 present between the permanent magnet 12 and the magnet
insertion hole 11b. The gap S2 has a predetermined
dimension within the range from 0.1 mm to 0.2 mm, for
example.
[0044]
30 In the example illustrated in FIG. 5, the gap S2 is
present between the magnet insertion hole 11b and a
radially outward surface 12c of the permanent magnet 12a
and between the magnet insertion hole 11b and a radially
outward surface 12d of the permanent magnet 12b. That is,

18
the gap S2 is located radially outward of the permanent
magnets 12a and 12b. The gap S2 may be located radially
inward of the permanent magnets 12a and 12b.
[0045]
5 The permanent magnet 12 is, for example, a rare
earth magnet. Specifically, the permanent magnet 12 is a
rare earth magnet including neodymium (Nd), iron (Fe),
and boron (B). In the first embodiment, the permanent
magnet 12 may include none of dysprosium (Dy) and terbium
10 (Tr). Dy and Tr are rare earth metals, and thus,
expensive. In the first embodiment, the Dy content and
the Tr content in the permanent magnets 12 are 0 wt.%,
and thus, costs for the permanent magnets 12 can be
reduced. The permanent magnets 12 may include less than
15 1.0 wt.% of Dy or less than 1.0 wt.% of Tr. The
permanent magnets 12 may include both less than 1.0 wt.%
of Dy and less than 1.0 wt.% of Tr. The permanent magnet
12 is not limited to a rare earth magnet, and may be
another permanent magnet such as a ferrite magnet.
20 [0046]
A flux barrier 11c is present between the magnet
insertion hole 11b and the end portion of the permanent
magnet 12 in the circumferential direction R. Since a
portion between the flux barrier 11c and an outer
25 periphery 11j of the rotor core 11 is a thin portion,
leakage flux between adjacent magnetic poles are
suppressed. The flux barrier 11c communicates with the
gap S2. The refrigerant 110 and the refrigerating
machine oil 40 (see FIG. 1) flow in the flux barrier 11c.
30 [0047]
The rotor core 11 further includes the plurality of
flow channels 15. The refrigerant 110 compressed by the
compression mechanism 1 and the refrigerating machine oil
40 dissolved in the refrigerant 110 flow in each of the

19
flow channels 15 of the plurality of flow channels 15.
In the first embodiment, the rotor core 11 includes, for
example, six flow channels 15. That is, in the first
embodiment, the number of the flow channels 15 is equal
5 to the number of the magnet insertion holes 11b. The
number of the flow channels 15 may be different from the
number of the magnet insertion holes 11b.
[0048]
The flow channels 15 are formed radially inward of
10 the magnet insertion holes 11b. In the first embodiment,
the flow channels 15 are through holes penetrating the
rotor core 11 in the z-axis direction. The opening of
the flow channel 15 is, for example, circular. The
opening of the flow channel 15 is not limited to a
15 circular shape, and may have another shape such as an
oval, or may have any shape formed by combining a curve
and a straight line.
[0049]
FIG. 6A is an enlarged cross-sectional view
20 illustrating a portion of the configuration of the rotor
10 shown in FIG. 5. FIG. 6B is a cross-sectional view of
a portion of the configuration of the rotor 10 shown in
FIG. 6A taken along line B6-B6. As illustrated in FIGS.
6A and 6B, the rotor core 11 includes a guide part 16 as
25 an oil introduction part for guiding the refrigerating
machine oil 40 (see FIG. 1) to the gap D. Specifically,
the guide part 16 has a guide structure for guiding the
refrigerating machine oil 40 flowing in the flow channels
15 together with the refrigerant 110 to the gap D when
30 the rotor 10 rotates.
[0050]
For example, while the rotor 10 rotates, the
refrigerating machine oil 40 flows along a path indicated
by arrows in FIG. 6B. The refrigerating machine oil 40

20
guided in the gap D flows from the inside to the outside
in the radial direction in the gap D under the influence
of a centrifugal force. Accordingly, the refrigerating
machine oil 40 flows in the gap S1 (see FIG. 5) in the
5 magnet insertion hole 11b. The refrigerating machine oil
40 flows in the gap D and then flows toward the bottom
portion 4a of the sealed container 4 (see FIG. 1) under
the influence of the gravity.
[0051]
10 In the manner described above, the refrigerating
machine oil 40 flowing in the flow channels 15 is guided
by the guide part 16 to the gap D and consequently the
refrigerating machine oil 40 flows in the gap D and
passes through the gap S1, and accordingly, the permanent
15 magnets 12 are easily cooled. In addition, the
refrigerating machine oil 40 that has flowed in the flow
channels 15 can easily return to the bottom portion 4a of
the sealed container 4 (see FIG. 1) through the gap D.
Accordingly, the compression mechanism 1 is easily
20 lubricated by the refrigerating machine oil 40, and thus
poor lubrication in the compressor 100 can be prevented.
[0052]
In a case where the refrigerant 110 is a refrigerant
including ethylene-based fluorocarbon (R1123 in the first
25 embodiment) described above, although a working pressure
of the compressor 100 can be reduced, the flow rate of
the refrigerant 110 discharged from the compressor 100
decreases disadvantageously. In this case, it is
necessary to increase the flow rate of the refrigerant
30 110 flowing in the flow channels 15 by increasing the
number of rotations of the rotor 10. However, in the
case where the flow rate of the refrigerant 110 flowing
in the flow channels 15 increases, the flow velocity of
the refrigerant 110 increases, and thus, the

21
refrigerating machine oil 40 is not easily separated from
the refrigerant 110. In the first embodiment, since the
rotor core 11 includes the guide part 16, even in the
case where the refrigerant 110 includes ethylene-based
5 fluorocarbon, the guide part 16 easily guides the
refrigerating machine oil 40 to the gap D. Accordingly,
the refrigerating machine oil 40 flowing in the flow
channels 15 is easily separated from the refrigerant 110.
[0053]
10 As illustrated in FIG. 6B, the guide part 16 is
provided in the flow channel 15. The guide part 16 has a
radially inward surface 17 defining the flow channel 15.
The radially inward surface 17 includes a vertical
portion 171 and a slope portion 172 as a first slope
15 portion. The vertical portion 171 is a plane of the
radially inward surface 17 extending in parallel with the
z-axis direction.
[0054]
The slope portion 172 is closer to the +z-axis side
20 than the vertical portion 171. The slope portion 172 is
a slope that inclines in a direction away from the axis C
(see FIG. 4) of the rotor 10 as approaching an end
surface 13d at the +z-axis side that is an end surface of
the electromagnetic steel sheets 13 in the z-axis
25 direction. The refrigerating machine oil 40 flows along
the vertical portion 171 and the slope portion 172 in the
flow channel 15 to be thereby guided to a portion of the
gap D radially outside the flow channel 15 (i.e., in a
direction toward the magnet insertion hole 11b). In the
30 example illustrated in FIG. 6B, the slope portion 172 is
a flat surface, but may be a curved surface.
[0055]
Since the specific gravity of the refrigerating
machine oil 40 is heavier than the specific gravity of

22
the refrigerant 110, the refrigerating machine oil 40
easily flows at a radially outer side in the flow channel
15 by a centrifugal force exerted during rotation of the
rotor 10. In the first embodiment, the guide part 16
5 includes the slope portion 172 in the radially inward
surface 17 defining the flow channel 15. Thus, the
refrigerating machine oil 40 flowing in the flow channel
15 is easily guided to the gap D through the slope
portion 172.
10 [0056]
The gap S1 faces the guide part 16 in the radial
direction. Accordingly, the refrigerating machine oil 40
guided to the gap D by the guide part 16 easily flows in
the gap S1. Thus, the permanent magnets 12a and 12b are
15 easily cooled by the refrigerating machine oil 40.
[0057]
Supposing the area of the opening of the flow
channel 15 is A1 and the area of the gap S1 when seen in
the z-axis direction is A2, the area A1 is larger than
20 the area A2. In the first embodiment, the area A1 is,
for example, equal to or larger than 10 times as large as
the area A2. Since the guide part 16 is provided in the
flow channel 15, as the area A1 is larger than the area
A2, the length of the guide part 16 in the
25 circumferential direction R increases. Accordingly, the
refrigerating machine oil 40 is easily separated from the
refrigerant 110 flowing in the flow channels 15.
[0058]
As illustrated in FIG. 5, supposing the spacing of
30 the gap S2 is t3, the spacing t3 is larger than the
spacing t2 (see FIG. 4) of the gap D. That is, the
spacing t3 and the spacing t2 satisfy Equation (1):
t3 > t2 (1)
Accordingly, the refrigerating machine oil 40 guided

23
from the flow channel 15 to the gap D easily flows in the
gap S2. Thus, the refrigerating machine oil 40 flows
along the radially outward surfaces 12c and 12d of the
permanent magnets 12a and 12b and consequently the
5 permanent magnets 12a and 12b can be more easily cooled.
[0059]
As illustrated in FIG. 6A, the flow channel 15 is
formed between the magnet insertion hole 11b and the
shaft insertion hole 11a in the rotor core 11.
10 Specifically, the flow channel 15 is disposed closer to
the magnet insertion hole 11b than the shaft insertion
hole 11a. Accordingly, a thin portion 11g is formed
between the magnet insertion hole 11b and the flow
channel 15. The thin portion 11g extends in the
15 circumferential direction R. Supposing the thickness of
the thin portion 11g is W1, the thickness W1 is uniform in
the circumferential direction R. The thickness W1 is
equal to or larger than the thickness t1 of each
electromagnetic steel sheet 13. Accordingly, a
20 sufficient strength of the thin portion 11g is obtained.
[0060]
Supposing the thickness of an iron core portion
(hereinafter referred to as a “bridge portion 11h”)
between the flow channel 15 and the shaft insertion hole
25 11a is W2, the thickness W2 is larger than the thickness
W1. That is, the thickness W1 and the thickness W2
satisfy Equation (2):
W1 < W2 (2)
Accordingly, the length of a portion of the gap D
30 between the shaft insertion hole 11a and the flow channel
15 increases, and thus, a passage in which the
refrigerant 110 flows in the gap D can be sufficiently
obtained. In addition, since a sufficient thickness of
the bridge portion 11h as an iron core portion around the

24
shaft insertion hole 11a is obtained, when the crankshaft
3 is fixed to the shaft insertion hole 11a, a sufficient
strength of the rotor core 11 is obtained.
[0061]
5
A configuration of an end plate of the rotor 10 will
now be described with reference to FIGS. 4, 7A, and 7B.
As illustrated in FIG. 4, the rotor 10 includes an upper
end plate 51 as a first end plate and a lower end plate
10 52 as a second end plate. The upper end plate 51 is
disposed on an end surface 11m at the +z-axis side as a
first end surface of the rotor core 11. The lower end
plate 52 is disposed on an end surface 11n at the -z-axis
side as a second end surface of the rotor core 11. The
15 rotor 10 may be implemented when the rotor 10 includes
only one of the upper end plate 51 and the lower end
plate 52.
[0062]
FIG. 7A is a plan view illustrating a configuration
20 of the upper end plate 51. As illustrated in FIGS. 4 and
7A, the upper end plate 51 is an annular plate about the
axis C. The upper end plate 51 includes a shaft
insertion hole 51a in which the crankshaft 3 is inserted
and through holes 51b as first through holes
25 communicating with the flow channels 15 of the rotor core
11. The refrigerant 110 that has passed through the flow
channels 15 flows in the through holes 51b. Accordingly,
the refrigerant 110 that has flowed in the flow channels
15 is easily guided to the discharge pipe 41 through the
30 through holes 51b.
[0063]
As illustrated in FIG. 4, the upper end plate 51
covers the magnet insertion holes 11b. In other words,
the upper end plate 51 closes the magnet insertion holes

25
11b. Accordingly, it is possible to prevent the
refrigerating machine oil 40 that has flowed in the
magnet insertion holes 11b from flowing to the outside of
the compressor 100 through the discharge pipe 41.
5 [0064]
FIG. 7B is a plan view illustrating a configuration
of the lower end plate 52. As illustrated in FIGS. 4 and
7B, the lower end plate 52 is an annular plate about the
axis C. The lower end plate 52 includes a shaft
10 insertion hole 52a in which the crankshaft 3 is inserted
and through holes 52b as second through holes
communicating with the flow channels 15.
[0065]
The lower end plate 52 further includes a slits 52c
15 as first slits communicating with the gaps S1 of the
rotor core 11 and slits 52d as second slits communicating
with the flux barriers 11c. The refrigerating machine
oil 40 flows in the through holes 52b and the slits 52c
and 52d. Since the oil sump (i.e., the bottom portion 4a
20 of the sealed container 4) is provided at the -z-axis
side of the lower end plate 52, the refrigerating machine
oil 40 flows in the through holes 52b and the slits 52c
and 52d to be thereby returned to the oil sump.
[0066]
25
In the compressor 100 according to the first
embodiment described above, the rotor core 11 of the
electric motor 2 that drives the compression mechanism 1
includes the guide part 16 that guides the refrigerating
30 machine oil 40 flowing in the flow channels 15 to the gap
D when the rotor 10 rotates. Accordingly, the
refrigerating machine oil 40 easily flows in the gap D
between the plurality of electromagnetic steel sheets 13
constituting the rotor core 11, and thus the permanent

26
magnets 12 can be easily cooled. In addition, since the
refrigerating machine oil 40 easily flows in the gap D,
the refrigerating machine oil 40 can easily return to the
bottom portion 4a of the sealed container 4 as the oil
5 sump. Accordingly, the compression mechanism 1 is easily
lubricated by the refrigerating machine oil 40 and
consequently poor lubrication in the compressor 100 can
be prevented.
[0067]
10 In a case where the refrigerant 110 is a refrigerant
including ethylene-based fluorocarbon (R1123 in the first
embodiment), the stroke volume of the compressor 100
decreases disadvantageously, and thus, the flow rate of
the refrigerant 110 flowing in the flow channels 15 needs
15 to be increased. However, when the flow rate of the
refrigerant 110 flowing in the refrigerant 110 increases,
the flow velocity of the refrigerant 110 increases, and
thus, the refrigerant 110 and the refrigerating machine
oil 40 are not easily separated from each other. In the
20 first embodiment, since the rotor core 11 includes the
guide part 16 described above, even if the refrigerant
110 is a refrigerant including ethylene-based
fluorocarbon, the guide part 16 makes it easier to
separate the refrigerating machine oil 40 from the
25 refrigerant 110 and to guide to the gap D.
[0068]
In the compressor 100 according to the first
embodiment, the guide part 16 has the radially inward
surface 17 defining the flow channel 15, and the radially
30 inward surface 17 includes the slope portion 172 that
inclines in a direction away from the axis C as
approaching the end surface 13d of the electromagnetic
steel sheets 13 at the +z-axis side. Accordingly, the
refrigerating machine oil 40 flowing in the flow channels

27
15 can be easily guided to the gap D through the slope
portion 172 when the rotor 10 rotates.
[0069]
In the compressor 100 according to the first
5 embodiment, the spacing t3 of the gap S2 between the
magnet insertion hole 11b and the surfaces 12c and 12d of
the permanent magnet 12 facing in the radial direction is
larger than the spacing t2 of the gap D. Accordingly, the
refrigerating machine oil 40 guided from the flow
10 channels 15 to the gap D easily flows in the gap S2.
Consequently, the permanent magnet 12 can be easily
cooled by the refrigerating machine oil 40.
[0070]
In the compressor 100 according to the first
15 embodiment, the gap S2 is located radially outward from
the permanent magnet 12. Since the refrigerating machine
oil 40 guided to the gap D is subjected to the effect of
a centrifugal force when the rotor 10 rotates, the
refrigerating machine oil 40 easily flows in the gap D in
20 a direction away from the axis C, that is, from the
inside to the outside of the rotor core 11 in the radial
direction. Thus, the gap S2 is present radially outward
from the permanent magnets 12 and consequently the
refrigerating machine oil 40 can easily flow to the gap
25 S2 through the gap D. Accordingly, the permanent magnets
12 can be easily cooled by the refrigerating machine oil
40.
[0071]
In the compressor 100 according to the first
30 embodiment, the rotor 10 further includes the upper end
plate 51 disposed at the end surface 11m of the rotor
core 11 on a downstream side in the direction in which
the refrigerant 110 flows, and the upper end plate 51
covers the magnet insertion holes 11b. Accordingly, it

28
is possible to prevent the refrigerating machine oil 40
guided to the gap D by the guide part 16 from flowing to
the outside of the compressor 100 through the discharge
pipe 41 after having flowed from the magnet insertion
5 holes 11b.
[0072]
In the compressor 100 according to the first
embodiment, the upper end plate 51 has the through hole
51b which communicates with the flow channels 15 and
10 through which the refrigerant 110 flows. Accordingly,
the refrigerant 110 that has flowed in the flow channels
15 easily flows to the outside of the compressor 100
through the discharge pipe 41 after having flowed from
the through hole 51b.
15 [0073]
In addition, in the compressor 100 according to the
first embodiment, the rotor 10 further includes the lower
end plate 52 disposed at the end surface 11n of the rotor
core 11 at the upstream side in the direction in which
20 the refrigerant 110 flows. The lower end plate 52 has
the through hole 52b which communicates with the flow
channels 15 and through which the refrigerating machine
oil 40 flows. Accordingly, when the refrigerating
machine oil 40 flowing in the flow channels 15 is
25 subjected to the effect of the gravity, the refrigerating
machine oil 40 easily returns to the bottom portion 4a of
the sealed container 4 through the through hole 52b.
Thus, the compression mechanism 1 is easily lubricated by
the refrigerating machine oil 40 and consequently poor
30 lubrication in the compressor 100 can be prevented.
[0074]
In the compressor 100 according to the first
embodiment, the lower end plate 52 further includes the
slit 52c which communicates with the gap S1 and in which

29
the refrigerating machine oil 40 flows. Accordingly,
when the refrigerating machine oil 40 flowing in the gap
S1 is subjected to the effect of the gravity, the
refrigerating machine oil 40 easily returns to the bottom
5 portion 4a of the sealed container 4 through the slit 52c.
Thus, the compression mechanism 1 is easily lubricated by
the refrigerating machine oil 40 and consequently poor
lubrication in the compressor 100 can be prevented.
[0075]
10 In the compressor 100 according to the first
embodiment, the rotor core 11 further includes the flux
barrier 11c present between the magnet insertion hole 11b
and the end portion of the permanent magnet 12 in the
circumferential direction. The lower end plate 52
15 further includes the slit 52d which communicates with the
flux barrier 11c and in which the refrigerating machine
oil 40 flows. Accordingly, when the refrigerating
machine oil 40 flowing in the flux barrier 11c is
subjected to the effect of the gravity, the refrigerating
20 machine oil 40 can easily return to the bottom portion 4a
of the sealed container 4 through the slit 52d. Thus,
the compression mechanism 1 is easily lubricated by the
refrigerating machine oil 40 and consequently poor
lubrication in the compressor 100 can be prevented.
25 [0076]
In the compressor 100 according to the first
embodiment, the rotor core 11 includes the shaft
insertion hole 11a in which the crankshaft 3 is inserted.
The thickness W1 of the thin portion 11g as an iron core
30 portion between the magnet insertion hole 11b and the
flow channel 15 in the rotor core 11 is smaller than the
thickness W2 of the bridge portion 11h as an iron core
portion between the flow channel 15 and the shaft
insertion hole 11a in the rotor core 11. Accordingly,

30
the length of a portion of the gap D between the shaft
insertion hole 11a and the flow channel 15 is large, and
thus, a sufficient passage in which the refrigerant 110
flows in the gap D can be obtained. In addition, since a
5 sufficient thickness of the bridge portion 11h is
obtained, strength of the rotor 10 can be sufficiently
ensured when the crankshaft 3 is fixed to the shaft
insertion hole 11a.
[0077]
10
FIG. 8 is a cross-sectional view illustrating a
configuration of a rotor 10a of an electric motor of a
compressor according to a first variation of the first
embodiment. In FIG. 8, the same reference characters as
15 those in FIG. 4 designate the same or corresponding
components as those illustrated in FIG. 4. The
compressor according to the first variation of the first
embodiment is different from the compressor 100 according
to the first embodiment in the configuration of a guide
20 part 16a. In other respects, the compressor according to
the first variation of the first embodiment is the same
as the compressor 100 according to the first embodiment.
Thus, the following description will be made with
reference to FIG. 1.
25 [0078]
As illustrated in FIG. 8, the rotor 10a includes a
rotor core 111. The rotor core 111 includes a plurality
of electromagnetic steel sheets 13a laminated in the zaxis direction with a gap D in between. The rotor core
30 111 includes a flow channel 15 and a guide part 16a. The
guide part 16a guides refrigerating machine oil 40 (see
FIG. 1) flowing in the flow channels 15 to a gap D when
the rotor 10a rotates.
[0079]

31
The guide part 16a includes a radially inward
surface 17a defining the flow channel 15. The radially
inward surface 17a includes a vertical portion 171 and a
slope portion 173 as a second slope portion. The slope
5 portion 173 is disposed closer to the -z-axis side than
the vertical portion 171. The slope portion 173 is a
slope that inclines in a direction away from an axis C as
approaching an end surface 13e at the -z-axis side as
another end surface of the electromagnetic steel sheets
10 13a in the z-axis direction.
[0080]
The refrigerating machine oil 40 flowing in the flow
channels 15 is guided to the gap D through the slope
portion 173. Accordingly, the refrigerating machine oil
15 40 easily flows in the gap D, and thus, the permanent
magnet 12 is easily cooled. Since the refrigerating
machine oil 40 easily flows in the gap D, the
refrigerating machine oil 40 can easily return to a
bottom portion 4a of a sealed container 4 (see FIG. 1).
20 Thus, a compression mechanism 1 is easily lubricated by
the refrigerating machine oil 40 and consequently poor
lubrication in the compressor 100 can be prevented.
[0081]

25 In the compressor according to the first variation
of the first embodiment described above, the radially
inward surface 17a defining the flow channel 15 in the
guide part 16a includes the slope portion 173 that
inclines in the direction away from the axis C as
30 approaching the end surface 13e of the electromagnetic
steel sheets 13a at the -z-axis side. Accordingly, the
refrigerating machine oil 40 easily flows in the gap D
between the plurality of electromagnetic steel sheets 13a
constituting the rotor core 111 and consequently the

32
permanent magnets 12 can be easily cooled. Since the
refrigerating machine oil 40 easily flows in the gap D,
the refrigerating machine oil 40 can easily return to the
bottom portion 4a of the sealed container 4. Thus, the
5 compression mechanism 1 is easily lubricated by the
refrigerating machine oil 40 and consequently poor
lubrication in the compressor can be prevented.
[0082]

10 FIG. 9 is a cross-sectional view illustrating a
configuration of a rotor 10b of an electric motor of a
compressor according to a second variation of the first
embodiment. In FIG. 9, the same reference characters as
those in FIGS. 4 and 8 designate the same or
15 corresponding components as those illustrated in FIGS. 4
and 8. The compressor according to the second variation
of the first embodiment is different from the compressor
100 according to the first embodiment in the
configuration of a guide part 16b. In other respects,
20 the compressor according to the second variation of the
first embodiment is the same as the compressor 100
according to the first embodiment. Thus, the following
description will be made with reference to FIG. 1.
[0083]
25 As illustrated in FIG. 9, the rotor 10b includes a
rotor core 112. The rotor core 112 includes a plurality
of electromagnetic steel sheets 13b laminated in the zaxis direction with a gap D in between. The rotor core
112 includes a flow channel 15 and a guide part 16b. The
30 guide part 16b guides the refrigerating machine oil 40
flowing in the flow channels 15 to a gap D when the rotor
10b rotates.
[0084]
The guide part 16b includes a radially inward

33
surface 17b defining the flow channel 15. The radially
inward surface 17b includes a slope portion 172 as a
first slope portion, a slope portion 173 as a second
slope portion, and a coupling portion 174 coupling the
5 slope portion 172 and the slope portion 173 to each other.
That is, in the second variation of the first embodiment,
the guide part 16b includes two slope portions 172 and
173. Accordingly, refrigerating machine oil 40 flowing
in the flow channels 15 is guided to the gap D through
10 the slope portions 172 and 173. Accordingly, the
refrigerating machine oil 40 more easily flows in the gap
D, and thus, the permanent magnets 12 are more easily
cooled. Since the refrigerating machine oil 40 is guided
to the gap D through the slope portions 172 and 173, the
15 refrigerating machine oil 40 can easily return to the
bottom portion 4a of the sealed container 4. Thus, the
compression mechanism 1 is easily lubricated by the
refrigerating machine oil 40 and consequently poor
lubrication in the compressor can be prevented.
20 [0085]

In the compressor according to the second variation
of the first embodiment described above, the radially
inward surface 17b defining the flow channel 15 in the
25 guide part 16b includes the slope portion 172 and the
slope portion 173. The slope portion 172 inclines in a
direction away from the axis C as approaching the end
surface 13d of the electromagnetic steel sheets 13b at
the +z-axis side. The slope portion 173 inclines in a
30 direction away from the axis C as approaching the end
surface 13e of the electromagnetic steel sheets 13b at
the -z-axis side. Accordingly, the refrigerating machine
oil 40 more easily flows in the gap D between the
plurality of electromagnetic steel sheets 13b

34
constituting the rotor core 112 and consequently the
permanent magnets 12 can be easily cooled. In addition,
since the refrigerating machine oil 40 easily flows in
the gap D, the refrigerating machine oil 40 can easily
5 return to the bottom portion 4a of the sealed container 4
as an oil sump. Thus, the compression mechanism 1 is
easily lubricated by the refrigerating machine oil 40 and
consequently poor lubrication in the compressor can be
prevented.
10 [0086]
SECOND EMBODIMENT
FIG. 10 is a cross-sectional view illustrating a
configuration of a rotor 210 of an electric motor of a
compressor according to a second embodiment. In FIG. 10,
15 the same reference characters as those in FIG. 4
designate the same or corresponding components as those
illustrated in FIG. 4. The compressor according to the
second embodiment is different from the compressor 100
according to the first embodiment in the configuration of
20 a guide part 216. In other respects, the compressor
according to the second embodiment is the same as the
compressor 100 according to the first embodiment. Thus,
the following description will be made with reference to
FIG. 1.
25 [0087]
As illustrated in FIG. 10, the rotor 210 includes a
rotor core 211. The rotor core 211 includes a plurality
of electromagnetic steel sheets 213 laminated in the zaxis direction with a gap D in between. The rotor core
30 211 includes flow channel 15 and the guide part 216.
[0088]
The guide part 216 guides refrigerating machine oil
40 flowing in the flow channels 15 to the gap D when the
rotor 210 rotates. The guide part 216 includes a

35
radially inward surface 17 defining the flow channel 15
and a radially outward surface 18 defining the flow
channel 15.
[0089]
5 The radially outward surface 18 of the guide part
216 includes a vertical portion 181 and a slope portion
182 as a third slope portion. The vertical portion 181
is a flat surface extending in parallel with the z-axis
direction in the radially outward surface 18. The slope
10 portion 182 is closer to the +z-axis side than the
vertical portion 181. The slope portion 182 is a slope
that inclines in a direction toward an axis C as
approaching an end surface 13d of the electromagnetic
steel sheets 213 at the +z-axis side. The slope portion
15 182 may be disposed closer to the -z-axis side than the
vertical portion 181. In this case, the slope portion of
the radially outward surface 18 may be a slope that
inclines in a direction toward the axis C as approaching
the end surface 13e of the electromagnetic steel sheets
20 213 at the -z-axis side. The radially outward surface 18
may include a plurality of slope portions at both sides
of the vertical portion 181 in the z-axis direction. In
the example illustrated in FIG. 10, the slope portion 182
is a flat surface, but may be a curved surface.
25 [0090]
In the second embodiment, the refrigerating machine
oil 40 flowing in the flow channels 15 is guided to the
gap D through the slope portion 182 as well as the slope
portion 172, when the rotor 210 rotates. Accordingly,
30 the refrigerating machine oil 40 flowing in the flow
channels 15 easily flows in the gap D. Thus, the
permanent magnets 12 are easily cooled. In addition, the
refrigerating machine oil 40 is easily guided to the gap
D through the slope portions 172 and 182 and consequently

36
the refrigerating machine oil 40 can easily return to the
bottom portion 4a of the sealed container 4. Thus, the
compression mechanism 1 is easily lubricated by the
refrigerating machine oil 40 and consequently poor
5 lubrication in the compressor can be prevented.
[0091]

In the compressor according to the second embodiment
described above, the guide part 216 further includes the
10 radially outward surface 18 defining the flow channel 15.
The radially outward surface 18 includes the slope
portion 182 that inclines in the direction toward the
axis C as approaching the end surface 13d of the
electromagnetic steel sheets 213. Accordingly, the
15 refrigerating machine oil 40 easily flows in the gaps D
between the plurality of electromagnetic steel sheets 213
constituting the rotor core 211 and consequently the
permanent magnets 12 can be easily cooled. In addition,
since the refrigerating machine oil 40 easily flows in
20 the gaps D, the refrigerating machine oil 40 can easily
return to the bottom portion 4a of the sealed container 4
as an oil sump. Thus, the compression mechanism 1 is
easily lubricated by the refrigerating machine oil 40 and
consequently poor lubrication in the compressor can be
25 prevented.
[0092]

FIG. 11 is a cross-sectional view illustrating a
configuration of a rotor 210a of an electric motor of a
30 compressor according to a first variation of the second
embodiment. In FIG. 11, the same reference characters as
those in FIG. 10 designate the same or corresponding
components as those illustrated in FIG. 10. The
compressor according to the first variation of the second

37
embodiment is different from the compressor according to
the second embodiment in that the rotor 210a further
includes the guide part 216a as a second guide part. In
other respects, the compressor according to the first
5 variation of the second embodiment is the same as the
compressor according to the second embodiment.
[0093]
As illustrated in FIG. 11, the rotor 210a includes a
rotor core 211a. The rotor core 211a includes a
10 plurality of electromagnetic steel sheets 213a laminated
in the z-axis direction with a gap D in between. The
rotor core 211a includes flow channel 15, a guide part
216 as a first guide part, and a guide part 216a as a
second guide part.
15 [0094]
The guide part 216a is included in the magnet
insertion hole 11b. In this manner, in the first
variation of the second embodiment, the guide part that
guides the refrigerating machine oil 40 to the gap D when
20 the rotor 210a rotates is included in the flow channel 15
and the magnet insertion hole 11b. Specifically, the
guide part 216a guides the refrigerating machine oil 40
flowing in the magnet insertion holes 11b to the gap D
when the rotor 210a rotates. Accordingly, the
25 refrigerating machine oil 40 that has flowed in the
magnet insertion holes 11b is guided to a portion of the
gap D radially outward from the magnet insertion holes
11b, and thus, easily returns to the bottom portion 4a of
the sealed container 4. Thus, the compression mechanism
30 1 is easily lubricated by the refrigerating machine oil
40 and consequently poor lubrication in the compressor
can be prevented.
[0095]
The guide part 216a includes the radially inward

38
surface 216b defining the magnet insertion hole 11b. The
radially inward surface 216b includes a vertical portion
191 and a slope portion 192. The vertical portion 191 is
a plane extending in parallel with the z-axis direction
5 in the radially inward surface 216b. The slope portion
192 is disposed closer to the +z-axis side than the
vertical portion 191. The slope portion 192 is a slope
that inclines in a direction away from an axis C (see FIG.
4) of the rotor 10 as approaching an end surface 13d of
10 the electromagnetic steel sheets 213 at the +z-axis side.
Accordingly, the refrigerating machine oil 40 flowing in
the magnet insertion holes 11b is easily guided to the
gap D through the slope portion 192. The slope portion
192 may be disposed closer to the -z-axis side than the
15 vertical portion 191. In the example illustrated in FIG.
11, the slope portion 192 is a flat surface, but may be a
curved surface.
[0096]

20 In the compressor according to the first variation
of the second embodiment, the rotor 210a of the electric
motor includes the guide part 216a that guides the
refrigerating machine oil 40 flowing in the magnet
insertion holes 11b to the gap D during rotation.
25 Accordingly, the refrigerating machine oil 40 that has
flowed in the magnet insertion holes 11b is guided to a
portion radially outward from the magnet insertion hole
11b in the gaps D between the plurality of
electromagnetic steel sheets 13 constituting the rotor
30 core 11, and thus, easily returns to the bottom portion
4a of the sealed container 4. Thus, the compression
mechanism 1 is easily lubricated by the refrigerating
machine oil 40 and consequently poor lubrication in the
compressor can be prevented.

39
[0097]
THIRD EMBODIMENT
A configuration of an air conditioner 300 according
to a third embodiment will now be described. The third
5 embodiment will be directed to an example of a case where
a refrigeration cycle device is applied to the air
conditioner 300. The refrigeration cycle device may be
applied to another device such as a refrigerator or a
heat pump cycle device.
10 [0098]
FIG. 12 is a diagram illustrating a configuration of
a refrigerant circuit in cooling operation of the air
conditioner 300 according to the third embodiment. FIG.
13 is a diagram illustrating the configuration of the
15 refrigerant circuit in heating operation of the air
conditioner 300 according to the third embodiment. As
illustrated in FIGS. 12 and 13, the air conditioner 300
includes the compressor 100, and a refrigerant flow
channel 310 in which a refrigerant 110 compressed by the
20 compressor 100 flows.
[0099]
The refrigerant flow channel 310 includes an
accumulator 101, a four-way valve 311 for switching
between cooling operation and heating operation, an
25 outdoor heat exchanger 312, an expansion valve 313 as a
decompressor, an indoor heat exchanger 314, and a pipe
(e.g., copper pipe) 315. The compressor 100, the
accumulator 101, the outdoor heat exchanger 312, the
expansion valve 313, and the indoor heat exchanger 314
30 are connected to one another by the pipe 315. In the
manner described above, the compressor 100, the outdoor
heat exchanger 312, the expansion valve 313, and the
indoor heat exchanger 314 constitute the refrigerant
circuit.

40
[0100]
The air conditioner 300 further includes a control
part 316. The control part 316 controls, for example, a
pressure and a temperature in the compressor 100. The
5 control part 316 is, for example, a microcomputer. The
control part 316 may control other elements (e.g., fourway valve 311, etc.) constituting the refrigerant circuit.
[0101]
Operation of the air conditioner 300 in cooling
10 operation will now be described. As illustrated in FIG.
12, the compressor 100 compresses the refrigerant 110
sucked from the accumulator 101 and sends the refrigerant
110 as a high-temperature and high-pressure refrigerant
gas. The four-way valve 311 causes the high-temperature
15 and high-pressure refrigerant gas sent from the
compressor 100 to flow in the outdoor heat exchanger 312.
The outdoor heat exchanger 312 performs heat exchange
between the high-temperature and high-pressure
refrigerant gas and a medium (e.g., air) to thereby
20 condense the refrigerant gas and send the resulting gas
as a low-temperature and high-pressure liquid refrigerant.
That is, in the cooling operation, the outdoor heat
exchanger 312 functions as a condenser.
[0102]
25 The expansion valve 313 expands the liquid
refrigerant from the outdoor heat exchanger 312 and sends
the resulting refrigerant as a low-temperature and lowpressure liquid refrigerant. Specifically, the lowtemperature and high-pressure liquid refrigerant sent
30 from the outdoor heat exchanger 312 is decompressed by
the expansion valve 313 to thereby become a two-phase
state of a low-temperature and low-pressure refrigerant
gas and a low-temperature and low-pressure liquid
refrigerant. The indoor heat exchanger 314 performs heat

41
exchange between the refrigerant and in the two-phase
state sent from the expansion valve 313 and the medium
(e.g., air), evaporates the liquid refrigerant, and sends
the refrigerant gas. That is, in the cooling operation,
5 the indoor heat exchanger 314 functions as an evaporator.
The refrigerant gas sent from the indoor heat exchanger
314 returns to the compressor 100 through the accumulator
101. In the manner described above, in the cooling
operation, the refrigerant 110 circulates in the
10 refrigerant circuit along a path indicted by arrows in
FIG. 12. That is, in the cooling operation, the
refrigerant 110 circulates in the order of the compressor
100, the outdoor heat exchanger 312, the expansion valve
313, and the indoor heat exchanger 314.
15 [0103]
Switching between cooling operation and heating
operation is performed by switching a flow channel with
the four-way valve 311 illustrated in FIGS. 12 and 13.
That is, in the heating operation, the indoor heat
20 exchanger 314 functions as a condenser, and the outdoor
heat exchanger 312 functions as an evaporator. In the
heating operation, the refrigerant 110 circulates in the
refrigerant circuit along a path indicated by arrows in
FIG. 13.
25 [0104]
In the air conditioner 300 according to the third
embodiment described above, the air conditioner 300
includes the compressor 100 described in the first
embodiment. As described above, in the compressor 100,
30 poor lubrication in the compression mechanism 1 is
prevented, and cooling effect of the permanent magnets 12
is enhanced. Accordingly, performance of the compressor
100 can be enhanced. As a result, performance of the air
conditioner 300 can also be enhanced.

42
DESCRIPTION OF REFERENCE CHARACTERS
[0105]
1 compression mechanism, 2 electric motor, 3
5 crankshaft, 4 sealed container, 10, 210, 210a rotor, 11,
111, 112, 211, 211a rotor core, 11a shaft insertion hole,
11b magnet insertion hole, 11c flux barrier, 11g thin
portion, 11h bridge portion, 11m, 11n end surface, 12,
12a, 12b permanent magnet, 13, 13a, 13b, 213, 213a
10 electromagnetic steel sheet, 13d, 13e end surface, 15
flow channel, 16, 16a, 16b, 216, 216a guide part, 17, 17a,
17b, 216b radially inward surface, 12c, 12d, 18 radially
outward surface, 40 refrigerating machine oil, 51 upper
end plate, 51b, 52b through hole, 52 lower end plate, 52c,
15 52d slit, 100 compressor, 110 refrigerant, 172, 172a, 173,
182, 192 slope portion, 300 air conditioner, 312 outdoor
heat exchanger, 313 expansion valve, 314 indoor heat
exchanger, C axis, D, S1, S2 gap, t2, t3 spacing, W1, W2
thickness.

43
We Claim:
1. A compressor comprising:
5 a compression mechanism to compress a refrigerant;
an electric motor to drive the compression
mechanism; and
a container to contain the compression mechanism,
the electric motor, the refrigerant, and lubricating oil,
10 wherein
a rotor of the electric motor includes:
a rotor core including a plurality of steel sheets
laminated with a first gap in between; and a first
permanent magnet inserted in a magnet insertion hole of
15 the rotor core, and
the rotor core includes:
a flow channel which is located inward from the
magnet insertion hole in a radial direction of the rotor
core and through which the refrigerant and the
20 lubricating oil flow; and
a first guide part to guide the lubricating oil
flowing through the flow channel to the first gap when
the rotor rotates.
25 2. The compressor according to claim 1, wherein
the rotor further includes a second permanent magnet
inserted in the magnet insertion hole with a second gap
disposed between the first permanent magnet and the
second permanent magnet, and
30 the lubricating oil guided in the first gap by the
first guide part flows in the second gap.

44
3. The compressor according to claim 2, wherein
the first guide part faces the second gap in the
radial direction.
5 4. The compressor according to claim 2 or 3, wherein
a third gap communicating with the second gap is
present between the magnet insertion hole and a surface
of each of the first permanent magnet and the second
permanent magnet facing in the radial direction, and
10 the lubricating oil flows in the third gap.
5. The compressor according to claim 4, wherein
the third gap is present outward from the first
permanent magnet and the second permanent magnet in the
15 radial direction.
6. The compressor according to claim 4 or 5, wherein
a spacing of the third gap is larger than a spacing
of the first gap.
20
7. The compressor according to claim 5 or 6, wherein
the rotor core further includes a flux barrier
communicating with the third gap, the flux barrier being
a gap between the magnet insertion hole and an end of
25 each of the first permanent magnet and the second
permanent magnet in a circumferential direction of the
rotor, and
the lubricating oil flows in the flux barrier.
30 8. The compressor according to any one of claims 1 to 7,
wherein
the first guide part has a surface facing inward in
the radial direction and defining the flow channel, and

45
the surface facing inward in the radial direction
has a first slope portion inclining in a direction away
from a rotation axis of the rotor as approaching an end
surface of each of the plurality of steel sheets.
5
9. The compressor according to any one of claims 1 to 7,
wherein
the first guide part has a surface facing inward in
the radial direction and defining the flow channel, and
10 the surface facing inward in the radial direction
includes:
a first slope portion inclining in a direction away
from a rotation axis of the rotor as approaching one end
surface of each of the plurality of steel sheets; and
15 a second slope portion inclining in a direction away
from the rotation axis as approaching another end surface
of each of the plurality of steel sheets.
10. The compressor according to claim 8 or 9, wherein
20 the first guide part further includes a surface
facing outward in the radial direction and defining the
flow channel, and
the surface facing outward in the radial direction
includes a third slope portion inclining in a direction
25 toward the rotation axis as approaching the end surface
of each of the plurality of steel sheets.
11. The compressor according to any one of claims 1 to
10, wherein
30 the rotor core further includes a second guide part
to guide the lubricating oil flowing in the magnet
insertion hole to the first gap when the rotor rotates.

46
12. The compressor according to claim 1, wherein
the rotor further includes a first end plate located
at a first end surface of the rotor core on a downstream
side in a direction in which the refrigerant flows, and
5 the first end plate covers the magnet insertion hole.
13. The compressor according to claim 12, wherein
the first end plate has a first through hole which
communicates with the flow channel and through which the
10 refrigerant flows.
14. The compressor according to claim 7, wherein
the rotor further includes a second end plate
located at a second end surface of the rotor core on an
15 upstream side in a direction in which the refrigerant
flows, and
the second end plate has a second through hole which
communicates with the flow channel and through which the
lubricating oil flows.
20
15. The compressor according to claim 14, wherein
the second end plate further includes a first slit
which communicates with the second gap and through which
the lubricating oil flows.
25
16. The compressor according to claim 14 or 15, wherein
the second end plate further includes a second slit
which communicates with the flux barrier and through
which the lubricating oil flows.
30

47
17. The compressor according to any one of claims 1 to
16, wherein
the rotor core further has a shaft insertion hole in
which a rotation shaft of the rotor is inserted, and
5 W1 < W2
where W1 is a thickness of a portion of the rotor core
between the magnet insertion hole and the flow channel
and W2 is a thickness of a portion of the rotor core
between the flow channel and the shaft insertion hole.
10
18. The compressor according to any one of claims 1 to
17, wherein
the electric motor is located on a downstream side
with respect to the compression mechanism in a direction
15 in which the refrigerant flows.
19. The compressor according to any one of claims 1 to
18, wherein
the refrigerant contains ethylene-based fluorocarbon.
20
20. The compressor according to any one of claims 1 to
19, wherein
the refrigerant includes at least one of R1123 or
R1132(E).
25
21. A refrigeration cycle device comprising:
the compressor according to any one of claims 1 to
20;
a condenser to condense the refrigerant sent from
30 the compressor;
a decompressor to decompress the refrigerant
condensed by the condenser; and
an evaporator to evaporate the refrigerant
decompressed by the decompressor.

48
22. An air conditioner including the refrigeration cycle
device according to claim 21.