FORM 2
THE PATENTS ACT, 1970
(39 of 1970)
&
THE PATENTS RULES, 2003
COMPLETE SPECIFICATION
[See section 10, Rule 13]
COMPRESSOR AND REFRIGERATION CYCLE APPARATUS;
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,

2
DESCRIPTION
Technical Field
[0001]
The present disclosure relates to a compressor that compresses and
5 discharges refrigerant, and a refrigeration cycle apparatus including the compressor,
and particularly to a suction mechanism that forms a refrigerant passage to a
compression chamber.
Background Art
[0002]
10 An existing rotary compressor includes a compression mechanism portion that
includes a rotation shaft having an eccentric portion, a cylinder provided on an outer
circumferential side of the eccentric portion and having a cylindrical shape, a piston
that rotates as the eccentric portion rotates and forms a compression chamber
between the piston and the cylinder, and upper and lower bearings that support both
15 ends of the cylinder (see, for example, Patent Literature 1). Furthermore, in recent
years, as one of countermeasures against global warming, low global warming
potential (GWP) refrigerant has been used for a refrigeration cycle apparatus
including a compressor such as a rotary compressor. However, the low GWP
refrigerant, such as R32, R1234yf, and R290, has a lower refrigeration capacity per
20 volume than refrigerant that has been used in the past, such as R410A.
Consequently, the flow rate of the low GWP refrigerant that flows in the refrigeration
cycle apparatus is increased to achieve a desired refrigeration capacity. Thus, in
order to improve the efficiency of the compressor, it is particularly effective to increase
the flow passage area of a suction hole in the cylinder that is a refrigerant suction
25 passage to the compression mechanism portion, and reduce a pressure loss in the
refrigerant suction passage.
Citation List
Patent Literature
[0003]
30 Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2013-

3
139726
Summary of Invention
Technical Problem
[0004]
5 In the rotary compressor, as the diameter of the suction hole in the cylinder is
increased, the suction refrigerant pressure loss is decreased. However, in general,
screw holes and a spring hole are formed around the suction hole in the cylinder of
the rotary compressor. The screw holes are holes in which screws for fastening
components of the compression mechanism portion to each other are set. The
10 spring hole is a hole in which a spring configured to move a vane is set. The vane
partitions the inside of the compression mechanism portion into a high-pressure
chamber and a low-pressure chamber. Interference between the suction hole and
the screw hole, or interference between the suction hole and the spring hole limits the
increase in the diameter of the suction hole, as a result of which it is not possible to
15 ensure a sufficient flow passage area of the suction hole. Therefore, under an
operating condition that refrigerant flows at a high rate, the efficiency of the
compressor may be reduced.
[0005]
The present disclosure is applied to solve the above problems, and relaters to
20 a compressor and a refrigeration cycle apparatus that prevent reduction in the
efficiency of the compressor even under an operating condition that refrigerant flows
at a high flow rate.
Solution to Problem
[0006]
25 A compressor according to one embodiment of the present disclosure includes:
an electric motor portion; a rotation shaft to be rotationally driven by the electric motor
portion and having an eccentric shaft portion; and a compression mechanism portion
configured to compress refrigerant with a driving force transmitted from the electric
motor portion through the rotation shaft, the electric motor portion, the rotation shaft,
30 and the compression mechanism portion being provided in a hermetic container.

4
The compression mechanism portion includes: a cylinder having a cylindrical shape,
fixed to the hermetic container, and having a hollow portion in which a cylinder
chamber is provided; a rolling piston accommodated in the cylinder chamber such
that the rolling piston is fitted to the eccentric shaft portion, and configured to
5 eccentrically rotate together with the eccentric shaft portion to compress the
refrigerant; a vane provided in a vane groove to partition the cylinder chamber into a
suction chamber and a compression chamber, the vane groove being formed to
extend in a radial direction of the cylinder; and bearings provided on respective end
faces of the cylinder to close the cylinder chamber. In the cylinder, a suction hole is
10 formed to extend in the radial direction of the cylinder and allow the refrigerant to be
sucked into the cylinder chamber through the suction hole. The suction hole has: a
suction-hole outer-diameter connection portion defining a space located on an outer
circumferential side of the cylinder in the radial direction of the cylinder; and a suctionhole inner-diameter connection portion defining a space located on an inner
15 circumferential side of the cylinder in the radial direction of the cylinder. In a cross
section perpendicular to the radial direction of the cylinder, the suction-hole outerdiameter connection portion is formed to have a larger sectional area than a sectional
area of the suction-hole inner-diameter connection portion. In the section
perpendicular to the radial direction of the cylinder, the suction-hole inner-diameter
20 connection portion has a sectional shape such that an opening width of the suctionhole inner diameter connection portion in a circumferential direction of the cylinder is
smaller than an opening width of the suction-hole inner diameter connection portion in
a thickness direction of the cylinder.
[0007]
25 A refrigeration cycle apparatus according to another embodiment of the present
disclosure includes: the compressor according to one embodiment of the present
disclosure; an outdoor heat exchanger configured to cause heat exchange to be
performed between outdoor air and refrigerant that flows in the outdoor heat
exchanger; an indoor heat exchanger configured to cause heat exchange to be
30 performed between indoor air and refrigerant that flows in the indoor heat exchanger;

5
and a pressure-reducing device configured to reduce a pressure of refrigerant that
flows into the outdoor heat exchanger or the indoor heat exchanger.
Advantageous Effects of Invention
[0008]
5 In the compressor and the refrigeration cycle apparatus according to the
embodiments of the present disclosure, the suction-hole outer-diameter connection
portion is formed to have a sectional area larger than the sectional area of the
suction-hole inner-diameter connection portion. Thus, in the compressor, it is
possible to increase the refrigerant flow passage area of the suction hole as a whole
10 without enlarging a radially inner circumferential side the suction hole in the
circumferential direction of the cylinder, and can also reduce a pressure loss in the
flow of the refrigerant. Furthermore, the suction-hole inner-diameter connection
portion has such a sectional shape that an opening width of the suction-hole innerdiameter connection portion in the circumferential direction of the cylinder is smaller
15 than an opening width of the suction-hole inner-diameter connection portion in the
thickness direction of the cylinder. Therefore, as compared with a compressor not
having such a suction hole as described above, the angle of the rolling piston can
reach an angle at an earlier timing from the start of rotation, at which the rolling piston
completely closes the suction hole, whereby the compressor can improve its
20 volumetric efficiency, as compared with the compressor not having the above suction
hole. In the compressor, since the suction hole having the above configuration is
provided, it is possible to prevent reduction of the efficiency of the compressor even
under an operating condition that the refrigerant flows at a high flow rate.
Brief Description of Drawings
25 [0009]
[1] Fig. 1 is a vertical sectional view of a compressor according to Embodiment
1.
[2] Fig. 2 is a cross-sectional view schematically illustrating a compression
mechanism portion of the compressor according to Embodiment 1.
30 [3] Fig. 3 is a configuration diagram schematically illustrating a configuration of

6
a cylinder in the compression mechanism portion of the compressor according to
Embodiment 1.
[4] Fig. 4 is a conceptual diagram of a vane groove and a spring hole when
viewed from a circumferential direction of the cylinder in the compression mechanism
5 portion according to Embodiment 1.
[5] Fig. 5 conceptually illustrates the vane groove and the spring hole as
viewed in a radial direction of the cylinder in the compression mechanism portion
according to Embodiment 1.
[6] Fig. 6 is a side view schematically illustrating a configuration of a suction
10 hole in the compression mechanism portion of the compressor according to
Embodiment 1.
[7] Fig. 7 is a vertical sectional view schematically illustrating the configuration
of the suction hole and the surroundings thereof in compression mechanism portion
of the compressor according to Embodiment 1.
15 [8] Fig. 8 is a partial sectional view schematically illustrating configurations of
the suction hole, a screw hole, and the spring hole in the cylinder of the compressor
according to Embodiment 1.
[9] Fig. 9 is a configuration diagram of a refrigeration cycle apparatus including
the compressor according to Embodiment 1.
20 [10] Fig. 10 is a configuration diagram schematically illustrating a configuration
of a cylinder in a compression mechanism portion of a compressor according to
Embodiment 2.
[11] Fig. 11 is a partial sectional view schematically illustrating configurations of
a suction hole, a screw hole, and a spring hole in the cylinder of the compressor
25 according to Embodiment 2.
[12] Fig. 12 is a vertical sectional view schematically illustrating a configuration
of a suction hole and the surroundings thereof in a compression mechanism portion
of a compressor according to Embodiment 3.
[13] Fig. 13 is a vertical sectional view schematically illustrating a configuration
30 of the suction hole and the surroundings thereof in a compression mechanism portion

7
of a compressor according to Embodiment 4.
Description of Embodiments
[0010]
A compressor and a refrigeration cycle apparatus according to embodiments
5 will be described with reference to the drawings, etc. It should be noted that in
figures including Fig. 1 which will be referred to, for example, relative relationships in
size between components and the shapes of the components may be different from
actual ones. Furthermore, in each of the figures, components that are the same as
those in a previous figure or previous figures are denoted by the same reference
10 signs, and the same is true of the entire text of the specification. In addition, in order
that the embodiments be more easily understood, terms related to directions (for
example, "up," "down," "right," "left," "front," and "rear") may be used as appropriate.
These terms are merely used as a matter of convenience for explanation, and are not
intended to limit locations or orientations of devices or components.
15 [0011]
Embodiment 1
Configuration of Compressor 100
Fig. 1 is a vertical sectional view of a compressor 100 according to
Embodiment 1. With reference to Fig. 1, the entire configuration of the compressor
20 100 will be described below. The compressor 100 is a fluid machine, and sucks lowtemperature and low-pressure refrigerant into the compressor 100, compresses the
refrigerant sucked into the compressor 100 to change it into high-temperature and
high-pressure refrigerant, and discharges the high-temperature and high-pressure
refrigerant to the outside of the compressor 100.
25 [0012]
The compressor 100 is, for example, a single-cylinder type rotary compressor
having a single cylinder 23 as illustrated in Fig. 1, that is, a single rotary compressor.
It should be noted that the compressor 100 is not limited to the single rotary
compressor, but may be a rotary compressor having a plurality of cylinders 23. The
30 compressor 100 may be, for example, a twin rotary compressor having two cylinders

8
23 or another type of compressor 100 having another configuration. In particular, it
should be noted that a compressor in which refrigerant flows at a high flow rate needs
to effectively reduce a pressure loss in a suction passage for refrigerant. In view of
this, for example, a twin rotary compressor required to have a high capacity and to
5 cause refrigerant to flow at a high flow rate may be used as the compressor 100.
[0013]
Hermetic Container 10
The compressor 100 is a hermetic compressor having a hermetic space
provided in a hermetic container 10. The hermetic container 10 is made up of an
10 upper container 11 and a lower container 12, and forms an outer shell of the
compressor 100. It should be noted that the hermetic container 10 is not limited to a
container made up of two constituent parts that are the upper container 11 and the
lower container 12, but may be made up of three or more constituent parts.
[0014]
15 On an outer side of the hermetic container 10, a suction muffler 101 is provided
in order to reduce direct suction of liquid refrigerant into a cylinder chamber 23a of the
cylinder 23. The suction muffler 101 is coupled to the cylinder 23 in a compression
mechanism portion 20 by a refrigerant suction pipe 107. The hermetic container 10
is connected to the suction muffler 101 by the refrigerant suction pipe 107, whereby
20 gas refrigerant is drawn into the hermetic container 10 from the suction muffler 101.
The suction muffler 101 operates as an accumulator configured to store liquid
refrigerant. In general, low-pressure gas refrigerant and liquid refrigerant may be
sent in a mixed state to the compressor from an external refrigerant circuit connected
to the compressor. In the case where the liquid refrigerant flows into a cylinder of a
25 compression mechanism portion and is compressed in the compression mechanism
portion, this causes occurrence of a failure in the compression mechanism portion.
[0015]
The suction muffler 101 is provided beside the hermetic container 10 to divide
the refrigerant into liquid refrigerant and gas refrigerant in order to reduce suction of
30 liquid refrigerant into the compression mechanism portion 20 as much as possible,

9
that is, this is intended to send only the gas refrigerant to the cylinder chamber 23a.
The suction muffler 101 is connected to the cylinder 23 by the refrigerant suction pipe
107 and through a suction hole 40 (see Fig. 3) in the cylinder 23. Low-pressure gas
refrigerant sent from the suction muffler 101 is sucked into the cylinder chamber 23a
5 through the refrigerant suction pipe 107. The suction muffler 101 also operates as a
silencer configured to reduce or remove noise made by inflow of the refrigerant.
[0016]
To an upper portion of the hermetic container 10, a discharge pipe 102 is
connected to allow compressed refrigerant to be discharged. The discharge pipe
10 102 is a refrigerant pipe through which high-pressure gas refrigerant is discharged to
the outside of the hermetic container 10. The discharge pipe 102 is provided to
penetrate the upper container 11 included in the hermetic container 10 and is fixed to
the upper container 11. The discharge pipe 102 and the upper container 11 are
joined together at their fixed portion by, for example, brazing or resistance welding.
15 [0017]
The compressor 100 includes, in the hermetic container 10, an electric motor
portion 30, a rotation shaft 21, and the compression mechanism portion 20. The
rotation shaft 21 has an eccentric shaft portion 21b and is rotationally driven by the
electric motor portion 30. The compression mechanism portion 20 compresses the
20 refrigerant with eccentric rotation of the eccentric shaft portion that is made by a
driving force transmitted from the electric motor portion 30 through the rotation shaft
21. In the hermetic container 10, the electric motor portion 30 is provided in an
upper portion of the hermetic container 10 and the compression mechanism portion
20 is provided in a lower portion of the hermetic container 10.
25 [0018]
The electric motor portion 30 and the compression mechanism portion 20 are
coupled together by the rotation shaft 21. The rotation shaft 21 transmits rotary
movement of the electric motor portion 30 to the compression mechanism portion 20.
In the compression mechanism portion 20, gas refrigerant is compressed by a
30 rotational force transmitted through the rotation shaft 21, and the compressed gas

10
refrigerant is discharged to the interior of the hermetic container 10.
[0019]
The interior of the hermetic container 10 is filled with high-temperature and
high-pressure gas refrigerant obtained by compression by the compression
5 mechanism portion 20. In the lower portion of the hermetic container 10, that is, at
the bottom portion thereof, refrigerating machine oil for use in lubrication of the
compression mechanism portion 20 is stored. The refrigerating machine oil is used
mainly to lubricate sliding parts of the compression mechanism portion 20. At a
lower portion of the rotation shaft 21, an oil pump (not illustrated) is provided. The oil
10 pump pumps up the refrigerating machine oil stored at the bottom portion of the
hermetic container 10 as the rotation shaft 21 rotates, and supplies the refrigerating
machine oil to the sliding parts of the compression mechanism portion 20. In the
compression mechanism portion 20, because the oil is supplied to the sliding parts, a
mechanical lubricating action is ensured.
15 [0020]
Electric Motor Portion 30
The electric motor portion 30 is an electric motor located in the hermetic
container 10 and is used to actuate the compression mechanism portion 20. The
electric motor portion 30 is a motor that causes the rotation shaft 21 to rotate and
20 produce a rotational driving force, with electric power supplied from an external power
supply, and transmits the rotational driving force to the compression mechanism
portion 20 through the rotation shaft 21. For example, a brushless DC motor is used
as the electric motor portion 30.
[0021]
25 The electric motor portion 30 includes a stator 31 that has a hollow cylindrical
appearance as viewed from above and a rotor 32 that has a cylindrical shape, is
rotatably located inward of an inner surface of the stator 31, and is rotated by a
magnetic action. In the electric motor portion 30, a wound coil included in the stator
31 is supplied with electric power from the external power supply, through a lead wire
30 33, whereby the rotor 32 is rotated in a region located inward of the stator 31.

11
[0022]
A refrigerant flow passage 34 provided in an iron core of the rotor 32 is used to
guide gas refrigerant discharged from the compression mechanism portion 20 to the
upper portion of the hermetic container 10, and to cause refrigerating machine oil,
5 which is guided to the upper portion of the hermetic container 10 along with the gas
refrigerant, to drop to the lower portion of the hermetic container 10.
[0023]
At a central portion of the rotor 32, the rotation shaft 21 penetrates the rotor 32
in the axial direction and is fixed to the rotor 32. A rotational driving force of the rotor
10 32 is transmitted through the rotation shaft 21 to the compression mechanism portion
20. The iron core included in the rotor 32 has an inner diameter that is smaller than
an outer diameter of the rotation shaft 21. The iron core of the rotor 32 is fixed to a
main shaft portion 21a of the rotation shaft 21.
[0024]
15 Rotation Shaft 21
The rotation shaft 21 has the main shaft portion 21a fixed to the rotor 32 of the
electric motor portion 30, a sub-shaft portion 21c provided opposite to the main shaft
portion 21a with reference to the cylinder 23, and the eccentric shaft portion 21b
provided between the main shaft portion 21a and the sub-shaft portion 21c. In the
20 axial direction of the rotation shaft 21, the main shaft portion 21a, the eccentric shaft
portion 21b, and the sub-shaft portion 21c are provided in this order from an upper
side of the hermetic container 10 to a lower side thereof. The rotor 32 of the electric
motor portion 30 is fixed to the main shaft portion 21a by shrink fit or press fit. A
cylindrical rolling piston 22 is slidably fitted to the eccentric shaft portion 21b.
25 [0025]
The eccentric shaft portion 21b of the rotation shaft 21 is located at a position
corresponding to the position of the cylinder 23 in the compression mechanism
portion 20. At an outer circumference of the eccentric shaft portion 21b, a
substantially-cylindrical rolling piston 22 is provided such that the rolling piston can be
30 rotated along an outer circumferential surface of the eccentric shaft portion 21b.

12
When the rotation shaft 21 is rotated by the electric motor portion 30, the rolling piston
22 is rotated in the cylinder 23 along an inner circumferential wall 23e thereof (see Fig.
2).
[0026]
5 Compression Mechanism Portion 20
Fig. 2 is a cross-sectional view schematically illustrating the compression
mechanism portion 20 of the compressor 100 according to Embodiment 1. Fig. 2 is
a cross-sectional view of the compression mechanism portion 20 that is taken along
line A-A in Fig. 1 as viewed from the above. It should be noted that in Fig. 2,
10 illustrations of a suction hole 40, screw holes 50, a spring hole 60, etc., which will be
described below, are omitted for explanation of only a basic configuration of the
compression mechanism portion 20. With reference to Fig. 2, the basic
configuration of the compression mechanism portion 20 will be described below.
[0027]
15 The compression mechanism portion 20 is driven by the electric motor portion
30 and compresses gas refrigerant sucked from the outside. To be more specific,
the compression mechanism portion 20 is caused by a rotational driving force
supplied from the electric motor portion 30 to compress low-pressure gas refrigerant
that is sucked from the refrigerant suction pipe 107 into a low-pressure space of the
20 hermetic container 10, to change the low-pressure gas refrigerant into high-pressure
gas refrigerant, and discharges the high-pressure gas refrigerant to an upper side
located above the compression mechanism portion 20.
[0028]
As illustrated in Figs. 1 and 2, the compression mechanism portion 20 includes
25 the cylinder 23, the rolling piston 22, a vane 26, an upper bearing 24, and a lower
bearing 25.
[0029]
An outer circumferential portion of the cylinder 23 is fixed to the hermetic
container 10 by bolts or other fixing members, whereby the cylinder 23 is fixed in the
30 hermetic container 10. The cylinder 23 is formed in a hollow cylindrical shape.

13
Both ends of the cylinder 23 in the axial direction of the rotation shaft 21 are open,
and the cylinder 23 has a hollow portion in which a cylinder chamber 23a is provided.
Openings formed in the both ends of the cylinder 23 in the axial direction of the
rotation shaft 21 are closed by the upper bearing 24 and the lower bearing 25. The
5 upper bearing 24 is provided on an upper side of the cylinder 23, and the lower
bearing 25 is provided on a lower side of the cylinder 23. The cylinder chamber 23a
is a space formed in the shape of a circular column and surrounded by an inner
circumferential surface of the cylinder 23, an inner wall surface of the upper bearing
24, and an inner wall surface of the lower bearing 25.
10 [0030]
In the cylinder chamber 23a, the eccentric shaft portion 21b of the rotation shaft
21 and the rolling piston 22 are accommodated. The eccentric shaft portion 21b
performs eccentric motion in the cylinder chamber 23a. The rolling piston 22 is fitted
to the eccentric shaft portion 21b. In addition, in the cylinder chamber 23a, the vane
15 26 is accommodated to partition a space defined by the inner circumferential wall 23e
that forms the cylinder chamber 23a and by the outer circumferential wall 22a of the
rolling piston 22.
[0031]
In the compression mechanism portion 20, the vane 26 is provided to make a
20 reciprocating movement in a radial direction in a groove provided in the cylinder 23.
The vane 26 partitions the cylinder chamber 23a into a high-pressure space and a
low-pressure space such that one end of the vane 26 is in contact with the outer
circumferential wall 22a of the rolling piston 22. In the compression mechanism
portion 20, the space surrounded by the rolling piston 22, the cylinder 23, the vane 26,
25 the upper bearing 24, and the lower bearing 25 forms a compression chamber
configured to compress low-pressure gas refrigerant sucked from the refrigerant
suction pipe 107.
[0032]
The cylinder 23 has the suction hole 40 (see Fig. 3) that allows gas refrigerant
30 to pass therethrough and to be sucked into the cylinder chamber 23a from the outside

14
of the hermetic container 10. To be more specific, in the cylinder 23, the suction hole
40 is formed to allow gas refrigerant supplied from the refrigerant suction pipe 107 to
pass through the suction hole 40. The suction hole 40 extends through the cylinder
23 from an outer circumferential surface of the cylinder 23 to an inner circumferential
5 surface thereof, and is provided such that a pipe passage of the refrigerant suction
pipe 107 communicates with the cylinder chamber 23a. The cylinder 23 has a back
pressure chamber 23b and an opening 23d. A detailed configuration of the cylinder
23 including the back pressure chamber 23b and opening 23d will be described later.
[0033]
10 The rolling piston 22 is accommodated along with the eccentric shaft portion
21b in the cylinder chamber 23a. The rolling piston 22 is eccentrically rotated by the
eccentric shaft portion 21b in the cylinder chamber 23a to compress gas refrigerant.
The rolling piston 22 is formed in a hollow cylindrical shape, and the eccentric shaft
portion 21b of the rotation shaft 21 is accommodated in the rolling piston 22. An
15 inner portion of the rolling piston 22 is slidably fitted to the eccentric shaft portion 21b
of the rotation shaft 21.
[0034]
The vane 26 is provided in a vane groove 23c that is formed to extend in the
radial direction of the cylinder 23 and partitions the cylinder chamber 23a into a
20 suction chamber and a compression chamber. The vane 26 is formed in a
substantially cuboid shape. When the vane 26 is set in the vane groove 23c, the
thickness of the vane 26 in a circumferential direction of the cylinder 23 is smaller
than the length of the vane 26 in the radial direction of the cylinder 23 and is smaller
than a length of the vane 26 in an axial direction of the cylinder 23.
25 [0035]
The upper bearing 24 is fitted to the main shaft portion 21a of the rotation shaft
21 and supports the main shaft portion 21a such that the main shaft portion 21a is
rotatable. The upper bearing 24 is provided on one of end faces of the cylinder 23
that faces the electric motor portion 30 and closes an opening 23m (see Fig. 7) of the
30 cylinder chamber 23a that is one of openings thereof in the axial direction. Similarly,

15
the lower bearing 25 is fitted to the sub-shaft portion 21c of the rotation shaft 21 and
supports the sub-shaft portion 21c such that the sub-shaft portion 21c is rotatable.
The lower bearing 25 is provided on the other end face of the cylinder 23 that is
located on the opposite side of the above former end face facing the electric motor
5 portion 30, and closes another opening 23n (see Fig. 7) of the cylinder chamber 23a
in the axial direction.
[0036]
The upper bearing 24 is substantially inverted T-shaped as viewed side-on, and
the lower bearing 25 is substantially T-shaped as viewed side-on. The upper bearing
10 24 has a discharge port (not illustrated) through which gas refrigerant compressed in
the compression chamber is discharged to the outside of the cylinder chamber 23a.
[0037]
At the discharge port of the upper bearing 24, a discharge valve (not illustrated)
is provided. The discharge valve controls the timing of discharging the high15 temperature and high-pressure gas refrigerant from the cylinder 23 through the
discharge port. The discharge valve is kept closed until the pressure of gas
refrigerant compressed in the cylinder chamber 23a of the cylinder 23 reaches a
predetermined pressure. When the pressure of the gas refrigerant reaches the
predetermined pressure or higher, the discharge valve is opened, whereby the high20 temperature and high-pressure gas refrigerant is discharged to the outside of the
cylinder chamber 23a.
[0038]
In the cylinder chamber 23a, an operation cycle to suck the refrigerant,
compress the refrigerant, and discharge the refrigerant is repeated, and the gas
25 refrigerant is thus intermittently discharged from the discharge port. Consequently,
noise such as pulsing sound may be made from the cylinder 23. In order to reduce
such noise, a discharge muffler 27 is attached to an outer side of the upper bearing
24 that faces the electric motor portion 30, such that the discharge muffler 27 covers
the upper bearing 24.
30 [0039]

16
The discharge muffler 27 has a discharge hole (not illustrated) through which a
space defined by the discharge muffler 27 and the upper bearing 24 communicates
with the interior of the hermetic container 10. Gas refrigerant discharged from the
cylinder 23 through the discharge port is once discharged to the space defined by the
5 discharge muffler 27 and the upper bearing 24, and is thereafter discharged from the
discharge hole to the interior of the hermetic container 10.
[0040]
Detailed Configuration of Cylinder 23
Fig. 3 is a configuration diagram schematically illustrating an internal
10 configuration of the cylinder 23 in the compression mechanism portion 20 of the
compressor 100 according to Embodiment 1. Fig. 3 conceptually illustrates the
internal configuration of the cylinder 23. Fig. 4 is a conceptual diagram illustrating
the vane groove 23c and the spring hole 60 as viewed in the circumferential direction
of the cylinder 23 in the compression mechanism portion 20 according to
15 Embodiment 1. Fig. 4 is a schematic sectional view of the cylinder 23 as viewed in
the circumferential direction, which is taken along line H-H in Fig. 5. Fig. 5 is a
conceptual diagram illustrating the vane groove 23c and the spring hole 60 as the
cylinder 23 in the compression mechanism portion 20 according to Embodiment 1 is
viewed in the radial direction. Fig. 5 is a schematic sectional view of the cylinder 23
20 as viewed in the radial direction, which is taken along line G-G in Fig. 4. It should be
noted that in Figs. 3 to 5, illustration of the vane 26 is omitted for explanation of
configurations of the vane groove 23c and the spring hole 60. With reference to Figs.
2 to 4, the configuration of the cylinder 23 will be described below in more detail.
[0041]
25 In the cylinder 23, the vane groove 23c is formed to communicate with the
cylinder chamber 23a and extend in the radial direction of the cylinder 23 with
reference to the rotation shaft 21. The vane groove 23c has the opening 23d formed
at one end portion of the vane groove 23c that is located on an inner circumferential
side of the cylinder 23, and also has the back pressure chamber 23b formed at the
30 other end portion of the vane groove 23c that is located on an outer circumferential

17
side of the cylinder 23. The opening 23d is provided in the inner circumferential wall
23e of the cylinder 23 and is open to the cylinder chamber 23a.
[0042]
The vane groove 23c extends through part of the cylinder 23 that adjoins an
5 inner diameter portion of the cylinder 23 to communicate with the cylinder chamber
23a, and does not extend through part of the cylinder 23 that adjoins an outer
diameter portion of the cylinder 23. As the cylinder 23 is viewed from the front, that
is, in a direction in which the cylinder 23 is viewed such that the outer shape of the
cylinder 23 is circular, the vane groove 23c extends through the cylinder 23 from the
10 near side to the far side. In other words, the vane groove 23c extends through the
cylinder 23 in the axial direction of the cylinder 23.
[0043]
The vane groove 23c is a space in which the vane 26 makes a reciprocating
movement. The vane 26 that partitions the cylinder chamber 23a into a suction
15 chamber and a compression chamber is fitted in the vane groove 23c. The vane 26
is slidably accommodated in the vane groove 23c. The vane 26 is slid back and
forth in the vane groove 23c in the radial direction of the cylinder 23 in accordance
with eccentric rotation of the rolling piston 22, while a distal end portion of the vane 26
is kept in contact with the outer circumferential wall 22a of the rolling piston 22 during
20 a compression stroke. The cylinder chamber 23a is partitioned into the suction
chamber and the compression chamber by the vane 26 when the distal end portion of
the vane 26 is brought into contact with the outer circumferential wall 22a of the
rolling piston 22.
[0044]
25 The back pressure chamber 23b of the vane groove 23c is also referred to as a
"blind hole." The back pressure chamber 23b is a portion that limits the motion of
the vane 26 by stopping movement of the vane 26 toward the outer diameter portion
of the cylinder 23 to prevent the vane 26 from being moved toward the outer diameter
portion of the cylinder 23. The back pressure chamber 23b also has a function of
30 introducing high-pressure refrigerant into the back pressure chamber itself.

18
[0045]
In the back pressure chamber 23b of the vane groove 23c, a vane spring 62 is
provided. The vane spring 62 is fixed to an inner portion of the spring hole 60. The
vane spring 62 and the cylinder 23 are fixed together at a spring fixing portion 63. In
5 the spring fixing portion 63, an end-turn portion 62a of the vane spring 62 is pressfitted into the spring hole 60 and is thus brought into contact with the inner wall of the
cylinder 23, whereby the vane spring 62 is fixed to the cylinder 23. It should be
noted that fixation of the vane spring 62 to the cylinder 23 that is achieved by pressfitting the end-turn portion 62a is merely an example of the method of fixing the vane
10 spring 62 to the cylinder 23. The method of fixing the vane spring 62 to the cylinder
23 is not limited.
[0046]
The vane spring 62 is brought into contact with a back portion of the vane 26
(the outer diameter portion) to press the vane 26 toward the center of the cylinder 23.
15 In the compression mechanism portion 20, high-pressure gas refrigerant in the
hermetic container 10 flows into the back pressure chamber 23b, and a force to move
the vane 26 toward the center of the cylinder chamber 23a in the radial direction of
the cylinder chamber 23a is produced by a differential pressure between the pressure
of gas refrigerant in the back pressure chamber 23b and the pressure of gas
20 refrigerant in the cylinder chamber 23a. The vane 26 is moved in the radial direction
toward the center of the cylinder chamber 23a by the force which is produced by the
differential pressure between the back pressure chamber 23b and the cylinder
chamber 23a and by the force of the vane spring 62 that presses the vane 26 in the
radial direction.
25 [0047]
The force to move the vane 26 in the radial direction brings one end of the
vane 26, that is, an end portion of the vane 26 that adjoins the cylinder chamber 23a,
into contact with the outer circumferential wall 22a of the rolling piston 22 formed in a
cylindrical shape. As a result, the vane 26 can partitions the space defined by the
30 inner circumferential wall 23e of the cylinder 23 and the outer circumferential wall 22a

19
of the rolling piston 22 into the suction chamber and the compression chamber as
described above.
[0048]
A differential pressure between the pressure of gas refrigerant in the hermetic
5 container 10, that is, the pressure of gas refrigerant in the back pressure chamber
23b, and the pressure of gas refrigerant in the cylinder chamber 23a, may be
insufficient to press the vane 26 against the outer circumferential wall 22a of the
rolling piston 22. Even in such a case, the compression mechanism portion 20 can
be moved by the force of the vane spring 62 to press one end of the vane 26 against
10 the outer circumferential wall 22a of the rolling piston 22, whereby the one end of the
vane 26 can be in contact with the outer circumferential wall 22a of the rolling piston
22 at all times.
[0049]
Suction Hole 40
15 Fig. 6 is a side view schematically illustrating a configuration of the suction hole
40 in the compression mechanism portion 20 of the compressor 100 according to
Embodiment 1. Fig. 7 is a vertical sectional view schematically illustrating a
configuration of the suction hole 40 and the surroundings thereof in the compression
mechanism portion 20 of the compressor 100 according to Embodiment 1. Fig. 8 is
20 a partial sectional view schematically illustrating the configurations of the suction hole
40, the screw holes 50, and the spring hole 60 in the cylinder 23 of the compressor
100 according to Embodiment 1. It should be noted that Fig. 6 is a view of the
cylinder 23 that is taken in a direction indicated by an arrow C in Fig. 3 and that
illustrates the cylinder 23 as viewed from the lateral side of the cylinder 23 in the
25 direction indicated by the arrow C in Fig. 3. Fig. 8 is a sectional view taken along
line D-D in Fig. 3. It should be noted that in Fig. 7, an illustration of an internal
illustration of the cylinder chamber 23a is omitted for explanation of the configurations
of the cylinder 23, the upper bearing 24, and the lower bearing 25. Next, the shape
of the suction passage for the refrigerant that is provided in the compression
30 mechanism portion 20 will be described with reference to Figs. 3 to 8.

20
[0050]
As illustrated in Figs. 3 and 6, in the cylinder 23, the suction hole 40 is formed
as a hole through which the refrigerant is sucked into the cylinder chamber 23a is
formed, such that the suction hole 40 extends in the radial direction of the cylinder 23.
5 The suction hole 40 extends through a wall that forms the cylinder 23. To be more
specific, the suction hole 40 extends between an outer circumferential wall 23f and
the inner circumferential wall 23e. The suction hole 40 extends through the cylinder
23 in the radial direction, but does not extend though the cylinder 23 in a thickness
direction of the cylinder 23. It should be noted that the thickness direction of the
10 cylinder 23 is the axial direction of the rotation shaft 21, and corresponds to an updown direction in Fig. 6.
[0051]
The suction hole 40 has a suction-hole outer-diameter connection portion 40a
formed on a radially outer circumferential side of the cylinder 23 and a suction-hole
15 inner-diameter connection portion 40b formed on a radially inner circumferential side
of the cylinder 23. In the cylinder 23, the suction-hole outer-diameter connection
portion 40a defines a space S1 located on the radially outer circumferential side of
the cylinder 23. In the cylinder 23, the suction-hole inner-diameter connection
portion 40b defines a space S2 located on the radially inner circumferential side of the
20 cylinder 23.
[0052]
As illustrated in Fig. 7, a sectional area SA1 of a hole of the suction-hole outerdiameter connection portion 40a in a section perpendicular to the radial direction of
the cylinder 23 is larger than a sectional area SA2 of a hole of the suction-hole inner25 diameter connection portion 40b in the section perpendicular to the radial direction of
the cylinder 23.
[0053]
The suction-hole outer-diameter connection portion 40a has an opening formed
in the outer circumferential wall 23f of the cylinder 23. The refrigerant suction pipe
30 107 is inserted into and connected to the suction-hole outer-diameter connection

21
portion 40a. The suction-hole inner-diameter connection portion 40b has an opening
formed in the inner circumferential wall 23e of the cylinder 23, and communicates with
the cylinder chamber 23a through the opening. In the circumferential direction of the
cylinder 23, the suction-hole inner-diameter connection portion 40b is formed
5 adjacent to one of the screw holes 50 which is the closest to the suction hole 40.
[0054]
As illustrated in Fig. 6, in the section perpendicular to an axial direction of the
suction hole 40, the suction-hole outer-diameter connection portion 40a has a circular
sectional shape, and the suction-hole inner-diameter connection portion 40b has an
10 oval sectional shape. It should be noted that the axial direction of the suction hole
40 is also the radial direction of the cylinder 23. As illustrated in Fig. 8, in the section
perpendicular to the radial direction of the cylinder 23, the suction-hole inner-diameter
connection portion 40b is formed to have such a section that an opening width W2 of
the section in the thickness direction of the cylinder 23 is greater than an opening
15 width W1 of the section in the circumferential direction of the cylinder 23. It should
be noted that the thickness direction of the cylinder 23 is also the axial direction of the
rotation shaft 21.
[0055]
In other words, the sectional shape of the suction-hole inner-diameter
20 connection portion 40b in the section perpendicular to the radial direction of the
cylinder 23 is the shape of an oval such that the length of the oval in the thickness
direction of the cylinder 23 is greater than the length of the oval in the circumferential
direction of the cylinder 23. In the cylinder 23, the suction-hole outer-diameter
connection portion 40a has a circular sectional shape in the section perpendicular to
25 the radial direction of the cylinder 23, and the suction-hole inner-diameter connection
portion 40b has a non-circular sectional shape in the section perpendicular to the
radial direction of the cylinder 23.
[0056]
It should be noted that the sectional shape of the suction-hole inner-diameter
30 connection portion 40b is not limited to the oval shape. It suffices that the suction-

22
hole inner-diameter connection portion 40b has a section that is shaped such that the
dimension of the section in a given direction is greater than the dimension of the
section in another direction as in an ellipse or a rectangle. It should be noted that
the dimension of the section in the given direction is the dimension of the section in
5 the axial direction of the cylinder 23, that is, the dimension of the section in the
thickness direction of the cylinder 23; and the dimension of the section in the above
another direction is the dimension of the section in the circumferential direction of the
cylinder 23. For example, in the case where the suction-hole inner-diameter
connection portion 40b has an oval shape, a major-axis direction of the suction-hole
10 inner-diameter connection portion 40b coincides with the thickness direction of the
cylinder 23.
[0057]
The sectional shape of the suction-hole outer-diameter connection portion 40a
is not limited to the circular shape. The suction-hole outer-diameter connection
15 portion 40a may have a section that is shaped such that the dimension of the section
in a given direction is greater than that of the section in another direction such as in
an ellipse or a rectangle, like the shape of a suction-hole outer-diameter connection
portion 40a2 as illustrated in Fig. 6. It should be noted that the dimension of the
section in the given direction is the dimension of the section in the circumferential
20 direction of the cylinder 23, and the dimension of the section in the above another
direction is the dimension of the section in the axial direction of the cylinder 23, that is,
the thickness direction of the cylinder 23. For example, in the case where the
suction-hole outer-diameter connection portion 40a has an oval shape, the majordiameter direction of the suction-hole outer-diameter connection portion 40a
25 coincides with the circumferential direction of the cylinder 23. That is, in the cylinder
23, the suction-hole outer-diameter connection portion 40a2 may have a non-circular
shape in the section perpendicular to the radial direction of the cylinder 23, and the
suction-hole inner-diameter connection portion 40b may have a non-circular shape in
the-section perpendicular to the radial direction of the cylinder 23.
30 [0058]

23
In the compression mechanism portion 20, the major-diameter direction in the
section of the suction-hole inner-diameter connection portion 40b coincides with the
thickness direction of the cylinder 23, whereby the rolling piston 22 completely closes
the suction hole 40 at an earlier timing than in the case where the suction-hole inner5 diameter connection portion 40b has an exactly circular sectional shape. That is, the
opening width in the circumferential direction of the cylinder 23 is smaller than the
opening width in the thickness direction of the cylinder 23, whereby the rolling piston
22 completely closes the suction hole 40 at an earlier timing than in the case where
the suction-hole inner-diameter connection portion 40b has an exactly circular
10 sectional shape. Thus, the compression mechanism portion 20 can ensure a large
volume of a formed compression chamber, and ensure a large delivery capacity in a
compression process per rotation of the rotation shaft 21 and the rolling piston 22. It
should be noted that as described above, the suction hole 40 is completely closed at
an earlier timing than in the case where the section is exactly circular; however, this is
15 true in the case where the exactly circular section has a diameter that is equal to the
diameter of the major axis of the suction-hole inner-diameter connection portion 40b
of the suction hole 40.
[0059]
An example of the configuration of the cylinder 23 according to Embodiment 1
20 will be described. Dimensions of the cylinder 23 that will be described below are
each merely an example, and the descriptions concerning the dimensions of the
cylinder 23 are not liming. For example, the cylinder 23 has a thickness of 23 mm.
The suction-hole outer-diameter connection portion 40a formed to have a circular
shape in the section perpendicular to the radial direction of the cylinder 23 has a
25 diameter of 19 mm.
[0060]
The suction-hole inner-diameter connection portion 40b formed to have an oval
shape in the section perpendicular to the radial direction of the cylinder 23 has a
major axis having 18 mm and a minor axis having 15 mm. The cylinder 23 having
30 the above dimensions has a first thin portion 23g that has a thickness t1 of 2 mm.

24
The first thin portion 23g is a wall portion of the cylinder 23 that forms part of the
suction-hole outer-diameter connection portion 40a, and also a portion that forms part
of a wall of the cylinder 23 that is located between the suction-hole outer-diameter
connection portion 40a and an end face 23h of the cylinder 23 in the thickness
5 direction thereof. The thickness t1 mm of the first thin portion 23g is the distance
between the suction-hole outer-diameter connection portion 40a and the end face 23h
of the cylinder 23 in the axial direction of the cylinder 23, that is, in the thickness
direction of the cylinder 23.
[0061]
10 The first thin portion 23g is part of the cylinder 23 at which the distance
between the suction hole 40 and the end face 23h of the cylinder 23 in the thickness
direction of the cylinder 23 is the minimum. The end face 23h of the cylinder 23 is
an end face of the cylinder 23 in the axial direction, on which the upper bearing 24 or
the lower bearing 25 is located.
15 [0062]
In the interior of the suction hole 40, the diameter of the suction-hole outerdiameter connection portion 40a is different from that of the suction-hole innerdiameter connection portion 40b. Thus, a step portion 41 is formed in the cylinder
23 at a boundary portion between the suction-hole outer-diameter connection portion
20 40a and the suction-hole inner-diameter connection portion 40b. In the interior of the
suction hole 40, the step portion 41 faces the outer circumferential side of the cylinder
23, and forms a step portion between an inner circumferential wall 40a1 of the
suction-hole outer-diameter connection portion 40a and an inner circumferential wall
40b1 of the suction-hole inner-diameter connection portion 40b.
25 [0063]
In the suction hole 40 of the cylinder 23, a typical dimension of the suction-hole
outer-diameter connection portion 40a is larger than that of the suction-hole innerdiameter connection portion 40b. Therefore, at the time of forming the suction hole
40 in the cylinder 23, a worker or a processing machine can perform processing on
30 the suction hole 40 only from a side where the suction-hole outer-diameter connection

25
portion 40a is located, in the radial direction of the cylinder 23. That is, at the time of
forming the suction hole 40 in the cylinder 23, the worker or the processing machine
does not need to greatly change a processing position of the cylinder 23. Therefore,
at the time of manufacturing the cylinder 23 of the compression mechanism portion
5 20, the suction hole 40 can be simply and easily processed, thereby reducing the
manufacturing cost.
[0064]
It should be noted that in the cylinder 23 in Embodiment 1, the typical
dimension of the suction-hole outer-diameter connection portion 40a is larger than
10 that of the suction-hole inner-diameter connection portion 40b. However, in the case
where processing can be performed on the cylinder 23 from the inner diameter side
thereof by using an appropriate processing tool, the cylinder 23 may have the suctionhole inner-diameter connection portion 40b whose typical dimension is larger than
that of the suction-hole outer-diameter connection portion 40a. For example, the
15 suction-hole outer-diameter connection portion 40a formed to have a circular shape
may have a diameter of 19 mm, and the suction-hole inner-diameter connection
portion 40b formed to have an oval shape may have a major axis having a diameter
of 19.5 mm and a minor axis having a diameter of 15 mm. That is, the major axis of
the suction-hole inner-diameter connection portion 40b formed to have an oval shape
20 may be set greater than the diameter of the suction-hole outer-diameter connection
portion 40a formed to have a circular shape.
[0065]
It should be noted that the suction-hole outer-diameter connection portion 40a
is formed to have a constant diameter in the radial direction from the inner
25 circumferential side to the outer circumferential side. The suction-hole innerdiameter connection portion 40b is also formed to have a constant diameter in the
radial direction from the inner circumferential side to the outer circumferential side.
That is, the suction-hole outer-diameter connection portion 40a and the suction-hole
inner-diameter connection portion 40b are formed such that their diameters are
30 constant in the radial direction from the inner circumferential side to the outer

26
circumferential side. The suction-hole outer-diameter connection portion 40a has
the space S1 formed in the shape of a circular column, and the suction-hole innerdiameter connection portion 40b has the space S2 formed in the shape of a column.
The space S1 is located outward of the space S2 in the radial direction of the cylinder
5 23.
[0066]
However, although it is described above that in the cylinder 23, the suction-hole
outer-diameter connection portion 40a and the suction-hole inner-diameter
connection portion 40b are formed such that their diameters are constant in the radial
10 direction from the inner circumferential side to the outer circumferential side, such a
description is not limiting. The suction-hole outer-diameter connection portion 40a
may have a diameter that varies in the radial direction from the inner circumferential
side to the outer circumferential side, as long as the cylinder 23 has the step portion
41 in the suction hole 40. The suction-hole inner-diameter connection portion 40b
15 may have a diameter that varies in the radial direction from the inner circumferential
side to the outer circumferential side, as long as the cylinder 23 has the step portion
41 in the suction hole 40.
[0067]
In the axial direction of the rotation shaft 21, the center of the suction-hole
20 outer-diameter connection portion 40a coincides with the center of the cylinder 23 in
the thickness direction thereof. This, however, is not limiting. In some cases, for
example, in the case where the compressor 100 is a twin rotary compressor, the
center of the suction-hole outer-diameter connection portion 40a in the axial direction
of the rotation shaft 21 does not need to coincide with the center of the cylinder 23 in
25 its thickness direction. That is, whether those centers are set to coincide with each
other depends on the configuration of the compressor 100.
[0068]
The cylinder 23 is interposed between the upper bearing 24 and the lower
bearing 25, and is fastened to the upper bearing 24 and the lower bearing 25 by
30 screws 80 (see Fig. 1). In the compression mechanism portion 20, the cylinder 23

27
forms a lateral side of the compression chamber and the two bearings form the end
faces of the compression chamber, thereby forming a columnar cylinder chamber 23a.
Furthermore, in the cylinder chamber 23a in the compression mechanism portion 20,
a compression chamber surrounded by the rolling piston 22, the cylinder 23, the vane
5 26, the upper bearing 24, and the lower bearing 25 is provided.
[0069]
Screw Hole 50
Next, the screw holes 50 will be described with reference to Figs. 3 and 8.
The compression mechanism portion 20 has a plurality of screws 80 (see Fig. 1) to
10 fasten the upper bearing 24 and the lower bearing 25 to the cylinder 23. In the
cylinder 23, the screw holes 50 are formed to extend through the cylinder 23 in the
thickness direction thereof. The plurality of screws 80 are set in the respective
screw holes 50.
[0070]
15 As described above, in the cylinder 23, the screw holes 50 are formed in which
the screws 80 are set and into which the screws 80 are inserted to fasten the upper
bearing 24 and the lower bearing 25 to the cylinder 23. As illustrated in Fig. 8, each
of the screw holes 50 is formed parallel to the axial direction of the cylinder 23, that is,
the thickness direction of the cylinder 23. The screw hole 50 extends through the
20 cylinder 23 in the axial direction, that is, in the thickness direction, from one of end
faces of the cylinder 23 to the other end face.
[0071]
As illustrated in Fig. 3, the screw holes 50 are arranged along the
circumferential direction of the cylinder 23. In the cylinder 23 according to
25 Embodiment 1, the screw holes 50 are formed at six positions in the circumferential
direction. The cylinder 23, the upper bearing 24, and the lower bearing 25 are
fastened together by six screws 80. It should be noted that the number of positions
where the screw holes 50 are formed is not limited to six, but may be five or less, or
seven or more, as long as it is possible to fasten the cylinder 23 and the upper
30 bearing 24 to each other, and fasten the cylinder 23 and the lower bearing 25 to each

28
other.
[0072]
In many cases, the screws 80 to fasten the upper bearing 24 and the lower
bearing 25 to the cylinder 23 in a rotary compressor are spaced apart from each other
5 by substantially the same distance in the circumferential direction of the cylinder 23.
That is, in the case where the cylinder 23 is formed in the shape of a circle having
360° about a center AX of the cylinder 23 in the circumferential direction thereof, the
screw holes 50 are formed and the screws 80 are set at positions at which the circle
is substantially equally divided in angle.
10 [0073]
With reference to Fig. 3, the positions at which the screw holes 50 are formed
as the cylinder 23 is viewed in the axial direction will be described below in more
detail. In the case where a center axis CS of the vane groove 23c is set at 0° that is
a reference, about the center AX of the cylinder 23, the screw hole 50 at the first
15 position in the counterclockwise direction is formed close to the suction hole 40 at a
position of approximately 30° relative to the center axis CS.
[0074]
That is, when the center axis CS of the vane groove 23c is set at 0° that is the
reference, the first screw 80 is located close to the suction hole 40 at a position of
20 approximately 30° relative to the center axis CS in the counterclockwise direction.
The first screw 80 is located near the suction hole 40 at a position of approximately
30° relative to the center axis CS for the reason that many operating components are
located around the vane groove 23c, and it is therefore impossible to provide the
screws 80 around the vane groove 23c.
25 [0075]
In the cylinder 23 in Embodiment 1, the suction hole 40 is formed in such a
manner that in the case where the center axis CS of the vane groove 23c is set as the
reference, a center axis CL of the suction hole 40 is located at a rotation angle of 26°
from the center axis CS of the vane groove 23c in the counterclockwise direction.
30 That is, the vane groove 23c and the suction hole 40 are formed in the cylinder 23

29
such that the angle between the center axis CS of the vane groove 23c and the
center axis CL of the suction hole 40 in the circumferential direction of the cylinder 23
is 26°.
[0076]
5 In the cylinder 23 in Embodiment 1, an interference margin distance between
the suction hole 40 and the screw hole 50 is 1.3 mm. The screw 80 has a nominal
diameter of M6. The screw hole 50 through which the screw 80 is inserted has a
diameter Φ7.4, that is, 7.4 mm. The screw 80 has a screw head portion having a
diameter of Φ14, that is, 14 mm. As the cylinder 23 is viewed from its end face,
10 when the screw hole 50, the screw head of the screw 80, and the suction hole 40 are
projected onto the lower end face of the cylinder 23, then the screw hole 50 and the
suction hole 40 do not interfered with each other, while the screw head of the screw
80 and the suction hole 40 may interfere with each other.
[0077]
15 As illustrated in Fig. 3, at least one of the screw holes 50 that is the closest to
the suction hole 40 a is formed closer to the inner circumferential side than the
suction-hole outer-diameter connection portion 40a in the radial direction of the
cylinder 23. The above screw hole 50 which is the closest to the suction hole 40 is
not formed adjacent to the suction-hole outer-diameter connection portion 40a in the
20 circumferential direction, but is formed adjacent to the suction-hole inner-diameter
connection portion 40b.
[0078]
With reference to Figs. 3 and 8, a relationship between the first thin portion 23g
and a second thin portion 23j of the cylinder 23 will be described. As described
25 above, at the first thin portion 23g, the distance between the suction hole 40 and the
end face 23h of the cylinder 23 in the thickness direction of the cylinder 23 is the
minimum. The second thin portion 23j is part of the wall forming the cylinder 23 at
which the distance between one of the screw holes 50 and the suction-hole innerdiameter connection portion 40b of the suction hole 40 is the minimum in the
30 circumferential direction of the cylinder 23, the above one of the screw holes 50 being

30
located closest to the suction-hole inner-diameter connection portion 40b.
[0079]
As described above, the thickness t1 [mm] of the first thin portion 23g is the
distance between the suction-hole outer-diameter connection portion 40a and the end
5 face 23h of the cylinder 23 in the axial direction of the cylinder 23, that is, in the
thickness direction of the cylinder 23. A thickness t2 [mm] of the second thin portion
23j is represented as the distance between the suction-hole inner-diameter
connection portion 40b of the suction hole 40 and one of the screw holes 50 that is
the closest to the suction-hole inner-diameter connection portion 40b in the
10 circumferential direction of the cylinder 23. That is, the thickness t2 [mm] of the
second thin portion 23j is the thickness of part of the cylinder 23 at which the distance
between the suction-hole inner-diameter connection portion 40b and one of the screw
holes 50 that is the closest to the suction-hole inner-diameter connection portion 40b
is the minimum in the circumferential direction of the cylinder 23.
15 [0080]
The cylinder 23 is formed such that the thickness t1 mm of the first thin portion
23g is greater than the thickness t2 mm of the second thin portion 23j (thickness t1 >
thickness t2).
[0081]
20 The refrigerant suction pipe 107 made of copper or ion is press-fitted into the
suction-hole outer-diameter connection portion 40a of the suction hole 40, thereby
forming a refrigerant flow passage. Therefore, a large external force is applied to the
first thin portion 23g in the process of connecting the refrigerant suction pipe 107.
[0082]
25 In contrast, the suction-hole inner-diameter connection portion 40b of the
suction hole 40 may be affected by screwing from the screw hole 50 through which
the screw 80 is inserted to fasten the cylinder 23 and other parts together. However,
the second thin portion 23j does not easily receive a large external force, as
compared with the first thin portion 23g. Therefore, the first thin portion 23g receives
30 a greater force at the time of assembling the compression mechanism portion 20, as

31
compared to the second thin portion 23j, and thus, the cylinder 23 is easily distorted.
Accordingly, the thickness t1 of the first thin portion 23g is set greater than the
thickness t2 of the second thin portion 23j, whereby the compression mechanism
portion 20 can reduce distortion of the cylinder 23 at the time of manufacturing.
5 [0083]
The section of the suction-hole outer-diameter connection portion 40a is
circular as described above. Thus, the refrigerant suction pipe 107 made of copper
or iron can also be made to have a circular section. As a result, pipes can be
molded in units of one pipe at low cost, and in addition, each of the pipes can be
10 simply and easily driven into the cylinder 23.
[0084]
However, the above does not intend to limit the sectional shape of the suctionhole outer-diameter connection portion 40a to a circular shape. For example, the
suction-hole outer-diameter connection portion 40a may have an oval sectional shape
15 as well as the suction-hole inner-diameter connection portion 40b, or may have an
elliptical sectional shape. Furthermore, for example, while the suction-hole innerdiameter connection portion 40b has an oval section that is vertically long in the axial
direction of the cylinder 23, the suction-hole outer-diameter connection portion 40a
may have an oval section that is horizontally long in the circumferential direction of
20 the cylinder 23.
[0085]
In Embodiment 1, part of the cylinder 23 that forms the second thin portion 23j
is located between the screw hole 50 and part of the suction hole 40 that is formed to
have an oval sectional shape. That is, the screw hole 50 is formed close to part of
25 the suction hole 40 where the suction-hole inner-diameter connection portion 40b is
formed to have an oval sectional shape. The screw hole 50 is formed close to the
suction-hole inner-diameter connection portion 40b having an oval sectional shape,
whereby it is possible for the suction-hole outer-diameter connection portion 40a to
increase the diameter thereof without interfering with the screw hole 50. Accordingly,
30 the compressor 100 can reduce a pressure loss at the time of sucking the refrigerant,

32
as compared with a compressor having a cylinder in which the screw hole 50 is
formed close to the suction-hole outer-diameter connection portion 40a and
consequently the diameter of the suction-hole outer-diameter connection portion 40a
cannot be increased.
5 [0086]
Spring Hole 60
The cylinder 23 includes therein the vane spring 62 that moves the vane 26.
The vane spring 62 urges the vane 26 to press a distal end portion of the vane 26
against the outer circumferential wall 22a of the rolling piston 22. The vane 26 is a
10 partition plate that partitions the cylinder chamber 23a into a high-pressure chamber
and a low-pressure chamber. In the cylinder 23, the spring hole 60 is formed as a
space to accommodate the vane spring 62 in such a manner as to allow this vane
spring 62 to move therein. The spring hole 60 is a space where the vane spring 62
is provided, the vane spring 62 being configured to provide a force to cause the vane
15 26 to move back and forth.
[0087]
In the cylinder 23, the spring hole 60 in which the vane spring 62 is provided is
formed in such a manner as to extend in the radial direction of the cylinder 23. As
illustrated in Fig. 4, the spring hole 60 does not extend through the cylinder 23 on an
20 inner diameter side of the cylinder chamber 23a as the cylinder 23 is viewed in the
circumferential direction, that is, in a direction in which the cylinder 23 is viewed such
that the cylinder 23 has a rectangular outer shape. The spring hole 60 extends
through the cylinder 23 on an outer diameter side of the cylinder 23, but does not
extend through the cylinder 23 on the inner diameter side. The spring hole 60 has
25 an exactly circular section in the section perpendicular to the radial direction of the
cylinder 23, that is, the direction in which the spring hole 60 extends. In Embodiment
1, the spring hole 60 has a diameter of Φ14, that is, 14 mm. Although the depth of
the spring hole 60 depends on the shape of the vane spring 62 which is to be moved,
or depends on the shape of the cylinder 23, it is assumed that the depth of the spring
30 hole 60 is 30 mm. The depth of the spring hole 60 is the length of the spring hole 60

33
in the radial direction of the cylinder 23 from the outer circumferential wall 23f toward
the inner circumferential wall 23e of the cylinder 23.
[0088]
It is assumed that the outer diameter of the cylinder 23 is 130 mm, and the
5 inner diameter of the cylinder 23 is 60 mm. The difference in radius between the
inner diameter and the outer diameter of the cylinder 23 is 35 mm. The depth of the
spring hole 60 accounts for 85% of the difference in radius.
[0089]
In a rotary compressor, in many cases, the depth of the spring hole 60
10 accounts for approximately 50 to 99% of the difference in radius in the cylinder 23,
and by increasing the depth of the spring hole 60, it is possible to increase the design
margin of the vane spring 62 that moves in the spring hole 60. At the bottom of the
spring hole 60, a spring-hole conical portion 61 is formed by a distal end of a drill.
The spring-hole conical portion 61 is a space portion formed in a conical shape in the
15 cylinder 23. It should be noted that it is allowable that the spring-hole conical portion
61 is not formed in the cylinder 23. The interference margin distance between the
spring hole 60 and the suction hole 40 is 1.2 mm. It should be noted that the
dimensions of the cylinder 23 as described above are each an example, and the
above descriptions concerning the dimensions of the cylinder 23 are not limiting.
20 [0090]
If the spring hole 60 is not sufficiently deep, a force to press the vane 26 is
decreased, and the movement of the vane 26 to follow the rolling piston 22 that orbits
in the compression chamber is reduced. Consequently, a force which causes the
vane 26 to separate from the rolling piston 22 may be reduced particularly in a low
25 rotation region of the compressor 100, more specifically, at less than 20 rps. If the
vane 26 separates from the rolling piston 22, high-pressure refrigerant leaks to the
low-pressure refrigerant side, and the performance of the compressor is thus
degraded. In addition, if the vane 26 separates from the rolling piston 22, the vane
26 or the rolling piston 22 is shaved or deformed by a stress that acts when the vane
30 26 collides with the rolling piston 22, and the reliability is thus reduced.

34
[0091]
With reference to Figs. 6 and 8, a relationship between the first thin portion 23g
and a third thin portion 23k of the cylinder 23 will be described. The third thin portion
23k is part of the cylinder 23 at which the distance between the suction hole 40 and
5 the spring hole 60 is the minimum in the circumferential direction of the cylinder 23.
More specifically, the third thin portion 23k is part of the wall forming the cylinder 23 at
which the distance between the spring hole 60 and the suction-hole inner-diameter
connection portion 40b of the suction hole 40 is the minimum in the circumferential
direction of the cylinder 23.
10 [0092]
A thickness t3 [mm] of the third thin portion 23k is represented as the distance
between the spring hole 60 and the suction-hole inner-diameter connection portion
40b in the circumferential direction of the cylinder 23. That is, the thickness t3 [mm]
of the third thin portion 23k is the thickness of part of the cylinder 23 at which the
15 distance between the spring hole 60 and the suction-hole inner-diameter connection
portion 40b of the suction hole 40 is the minimum in the circumferential direction of
the cylinder 23.
[0093]
The cylinder 23 is formed such that the thickness t1 [mm] of the first thin
20 portion 23g is greater than the thickness t3 [mm] of the third thin portion 23k
(thickness t1 > thickness t3).
[0094]
As described above, the refrigerant suction pipe 107 made of copper or ion is
driven into the suction-hole outer-diameter connection portion 40a of the suction hole
25 40, thereby forming a refrigerant flow passage. Therefore, a large external force is
applied to the first thin portion 23g in the process of connecting the refrigerant suction
pipe 107.
[0095]
In contrast, the third thin portion 23k is not easily given a large external force,
30 though the vane spring 62 may be lightly press-fitted into the spring hole 60 in order

35
that the vane spring 62 be fixed to the spring hole 60. Therefore, the first thin portion
23g receives a greater force at the time of assembling the compression mechanism
portion 20 than the third thin portion 23k, and the cylinder 23 is easily distorted.
Therefore, the thickness t1 of the first thin portion 23g is set greater than the
5 thickness t3 of the third thin portion 23k, whereby the compression mechanism
portion 20 can reduce distortion of the cylinder 23 at the time of manufacturing.
[0096]
The suction-hole outer-diameter connection portion 40a has a circular section
as described above. Since the suction-hole outer-diameter connection portion 40a
10 has the circular section, the refrigerant suction pipe 107 made of copper or iron can
also be made to have a circular section. Since the refrigerant suction pipe 107 can
also be made to have a circular section, pipes can be molded in units of one pipe at
low cost, and each of the pipes can be simply and easily driven into the cylinder 23.
[0097]
15 In Embodiment 1, part of the cylinder 23 that forms the third thin portion 23k is
located between the spring hole 60 and part of the suction hole 40 that is formed to
have an oval sectional shape. That is, part of the spring hole 60 that is the closest to
the suction hole 40 is located close to part of the suction hole 40 where the suctionhole inner-diameter connection portion 40b is formed to have an oval sectional shape.
20 Thus, the suction-hole outer-diameter connection portion 40a can be made to have a
larger diameter without interfering with the spring hole 60. The compressor 100 can
reduce a pressure loss at the time of suctioning refrigerant, as compared with a
compressor having a cylinder in which the screw hole 50 is formed close to the
suction-hole outer-diameter connection portion 40a and consequently the diameter of
25 the suction-hole outer-diameter connection portion 40a cannot be increased.
[0098]
Operation of Compressor 100
In the compressor 100, by the rotational motion of the rotation shaft 21, the
eccentric shaft portion 21b of the rotation shaft 21 is rotated in the cylinder chamber
30 23a of the cylinder 23. As the rotation shaft 21 rotates, the volume of the suction

36
chamber that is partitioned off by the inner circumferential wall 23e defining the
cylinder chamber 23a, the outer circumferential wall 22a of the rolling piston 22 fitted
to the eccentric shaft portion 21b, and the vane 26 increases, and the volume of the
compression chamber decreases.
5 [0099]
In the compressor 100, first, this suction chamber and the suction hole 40
communicate with each other, and low-pressure gas refrigerant is sucked into the
cylinder chamber 23a. Next, the communication of the suction hole 40 with the
compression chamber in which gas refrigerant is compressed is blocked by the rolling
10 piston 22, and as the volume of the compression chamber decreases, the gas
refrigerant in the compression chamber is compressed. Finally, the compression
chamber communicates with the discharge port (not illustrated). After the pressure
of the gas refrigerant in the compression chamber reaches a predetermined pressure,
the discharge valve provided at the discharge port is opened, and the compressed
15 high-pressure high-temperature gas refrigerant is discharged to the outside of the
compression chamber, that is, to the outside of the cylinder chamber 23a.
[0100]
The high-pressure high-temperature gas refrigerant discharged from the
cylinder chamber 23a through the discharge muffler 27 into the hermetic container 10
20 passes through the electric motor portion 30, then flows up in the hermetic container
10, and is discharged to the outside of the hermetic container 10 from the discharge
pipe 102 provided at the upper portion of the hermetic container 10. A refrigeration
circuit 201 (see Fig. 9) in which refrigerant flows is formed outside the hermetic
container 10. The discharged refrigerant circulates in the refrigeration circuit 201
25 and flows back to the suction muffler 101.
[0101]
Advantages of Compressor 100
In the compressor 100, the suction-hole outer-diameter connection portion 40a
is formed to have the sectional area SA1 larger than the sectional area SA2 of the
30 suction-hole inner-diameter connection portion 40b. Therefore, in the compressor

37
100, it is possible to increase the refrigerant flow passage area of the suction hole 40
as a whole without enlarging the suction hole 40 on a radially inner circumferential
side thereof in the circumferential direction of the cylinder 23, and to reduce the
pressure loss of the flow of the refrigerant. The suction-hole inner-diameter
5 connection portion 40b has a section that is formed such that an opening width W2 in
the thickness direction of the cylinder 23 is greater than an opening width W1 in the
circumferential direction of the cylinder 23. That is, the section of the suction-hole
inner-diameter connection portion 40b is formed such that the opening width W1 in
the circumferential direction of the cylinder 23 is smaller than the opening width W2 in
10 the thickness direction of the cylinder 23. Thus, in the compressor 100, the angle of
the rolling piston 22 can reach, at an earlier timing from the start of rotation, an angle
at which the rolling piston completely closes the suction hole, than in a compressor
not having this suction hole 40. Since the angle of the rolling piston 22 can reach
the angle at which the rolling piston 22 completely closes the suction hole 40, at an
15 earlier timing from the start of rotation, the compressor 100 can thus improve its
volumetric efficiency, as compared with the compressor not having this suction hole
40. The compressor 100 has the suction hole 40 having the above configuration,
and can thus ensure an adequate flow passage area of the refrigerant suction
passage, while avoiding interference of the suction hole 40 with the screw hole 50 or
20 the spring hole 60. Accordingly, even under the operating condition that the
refrigerant flows at a high flow rate, it is possible to prevent reduction of the efficiency
of the compressor 100, and improve the performance and capacity of the compressor
100.
[0102]
25 The cylinder 23 is formed such that the thickness t1 [mm] of the first thin
portion 23g is greater than the thickness t2 [mm] of the second thin portion 23j. It
should be noted that since the refrigerant suction pipe 107 is driven into the suctionhole outer-diameter connection portion 40a of the cylinder 23, a great force is applied
to the first thin portion 23g at the time of assembling the compressor 100. In the
30 compressor 100, the thickness t1 of the first thin portion 23g is greater than the

38
thickness t2 of the second thin portion 23j, whereby it is possible to ensure an
adequate distortion resistance for the first thin portion 23g at the time of assembling
the compressor 100, and reduce distortion of the cylinder 23 at the time of
manufacturing the compressor 100. When the refrigerant suction pipe 107 is driven,
5 a stronger force acts on the cylinder 23 than in screwing using the screws 80. It is
therefore preferable that the thickness t1 of the first thin portion 23g be greater than
the thickness t2 of the second thin portion 23j.
[0103]
The cylinder 23 is formed such that the thickness t1 [mm] of the first thin
10 portion 23g is greater than the thickness t3 [mm] of the third thin portion 23k. As
described above, the refrigerant suction pipe 107 is driven into the suction-hole outerdiameter connection portion 40a of the cylinder 23. Accordingly, a great force is
applied to the first thin portion 23g at the time of assembling the compressor 100. In
the compressor 100, since the thickness t1 of the first thin portion 23g is greater than
15 the thickness t3 of the third thin portion 23k, it is possible to ensure an adequate
distortion resistance for the first thin portion 23g that is required at the time of
assembling the compressor 100, and can reduce distortion of the cylinder 23 at the
time of manufacturing the compressor 100. When the refrigerant suction pipe 107 is
driven, a greater force is applied to the cylinder 23 than at the time of inserting the
20 vane spring 62 into the spring hole 60. Therefore, it is preferable that the thickness
t1 of the first thin portion 23g is greater than the thickness t3 of the third thin portion
23k.
[0104]
In the cylinder 23, the suction-hole outer-diameter connection portion 40a has a
25 circular shape in the section perpendicular to the radial direction of the cylinder 23,
while the suction-hole inner-diameter connection portion 40b has a non-circular shape
in the section perpendicular to the radial direction of the cylinder 23. In many cases,
since the section of a suction pipe such as the refrigerant suction pipe 107 is formed
in a circular shape, it is preferable that the suction-hole outer-diameter connection
30 portion 40a into which the refrigerant suction pipe 107 is driven have a circular

39
section. In the configuration of the compressor 100, a relatively sufficient space
remains on the outer diameter side of the cylinder 23. It is therefore unnecessary to
pay much attention to interference with, for example, the screw hole 50. Therefore,
it is unnecessary that the suction-hole outer-diameter connection portion 40a is
5 formed to have a non-circular section.
[0105]
In the cylinder 23, the suction-hole outer-diameter connection portion 40a2 may
have a non-circular shape in the section perpendicular to the radial direction of the
cylinder 23, and the suction-hole inner-diameter connection portion 40b may have a
10 non-circular shape in the section perpendicular to the radial direction of the cylinder
23. In this case, since the suction-hole outer-diameter connection portion 40a has
the non-circular sectional shape, it is less easy to drive the refrigerant suction pipe
107 into the suction-hole outer-diameter connection portion 40a; however, it is
possible to increase the refrigerant flow passage area and reduce the pressure loss.
15 The non-circular shape is, for example, an oval shape in which the major axis extends
in the circumferential direction of the cylinder 23. In the case where the non-circular
shape is applied, it is possible to increase the refrigerant flow passage area in the
suction-hole outer-diameter connection portion 40a without changing the thickness t1
of the first thin portion 23g. That is, the suction hole 40 may be formed in the
20 cylinder 23 such that the diameter of the oval section of the suction hole 40 in the
circumferential direction of the cylinder 23 is greater than that in the height direction of
the cylinder 23. The suction hole 40 easily interferes with the spring hole 60 or the
screw hole 50 on a side adjoining the suction-hole inner-diameter connection portion
40b of the suction hole 40. In contrast, a relatively sufficient space is provided
25 around the suction-hole outer-diameter connection portion 40a of the suction hole 40.
Therefore, in the suction-hole outer-diameter connection portion 40a of the suction
hole 40, it is possible to increase the flow passage area by extending the flow
passage section of the suction hole 40 in the circumferential direction of the cylinder
23.
30 [0106]

40
The suction-hole inner-diameter connection portion 40b has an oval shape in
the section perpendicular to the radial direction of the cylinder 23, in which the length
of the oval section in the thickness direction of the cylinder 23 is greater than that in
the circumferential direction of the cylinder 23. Since the compressor 100 has the
5 cylinder 23 having the above configuration, the rolling piston 22 can completely close
the suction hole 40 at an earlier timing than in an existing compressor having a
suction hole having a circular sectional shape as a whole, the compressor 100 can
improve the volumetric efficiency.
[0107]
10 Configuration of Refrigeration Cycle Apparatus 200
Fig. 9 is a configuration diagram of the refrigeration cycle apparatus 200
including the compressor 100 according to Embodiment 1. The refrigeration cycle
apparatus 200 includes the compressor 100, a flow switching device 103, an outdoor
heat exchanger 104, a pressure-reducing device 105, and an indoor heat exchanger
15 106. The refrigeration cycle apparatus 200 further includes a suction muffler 101.
The suction muffler 101 is connected to the suction side of the compressor 100. It
should be noted that in the refrigeration cycle apparatus 200 such as a refrigerating
and air-conditioning apparatus, in many cases, the indoor heat exchanger 106 is
provided in an apparatus installed indoors, and the compressor 100, the flow
20 switching device 103, the outdoor heat exchanger 104, the pressure-reducing device
105, etc., are provided in an apparatus installed outdoors.
[0108]
In the refrigeration cycle apparatus 200, the compressor 100, the flow switching
device 103, the outdoor heat exchanger 104, the pressure-reducing device 105, and
25 the indoor heat exchanger 106 are sequentially connected to each other by
refrigerant pipes, whereby the refrigeration circuit 201 in which refrigerant circulates is
provided. As refrigerant that flows in the refrigeration circuit 201, R407 refrigerant,
R410A refrigerant, R32 refrigerant, or other kinds of refrigerant is used. However, by
using, for example, low GWP refrigerant such as R1234yf refrigerant or R290
30 refrigerant, it is possible to improve the efficiency of the compressor.

41
[0109]
The flow switching device 103 is, for example, a four-way valve that switches
the flow direction of the refrigerant between a plurality of flow directions. The flow
switching device 103 is connected to the discharge side of the compressor 100. The
5 outdoor heat exchanger 104 causes heat exchange to be performed between outside
air and refrigerant that flows in the outdoor heat exchanger 104. The outdoor heat
exchanger 104 operates as a condenser or an evaporator. Whether the outdoor
heat exchanger 104 operates as a condenser or an evaporator depends on the flow
direction of the refrigerant. The pressure-reducing device 105 reduces the pressure
10 of refrigerant that flows out from the condenser, enters the pressure-reducing device
105, and flows in the pressure-reducing device 105.
[0110]
The pressure-reducing device 105 is, for example, an electronic expansion
valve whose opening degree can be adjusted. By adjusting the opening degree of
15 the pressure-reducing device 105, the pressure-reducing device 105 controls the
pressure of refrigerant that flows into the outdoor heat exchanger 104 or into the
indoor heat exchanger 106. The indoor heat exchanger 106 causes heat exchange
to be performed between indoor air and refrigerant that flows in the indoor heat
exchanger 106. The indoor heat exchanger 106 operates as an evaporator or a
20 condenser. Whether indoor heat exchanger 106 operates as an evaporator or a
condenser depends on the flow direction of the refrigerant. It should be noted that
the refrigeration cycle apparatus 200 may include an outdoor fan (not illustrated) that
sends outside air to the outdoor heat exchanger 104, and may include an outdoor fan
(not illustrated) configured to deliver indoor air to the indoor heat exchanger 106.
25 [0111]
Operation of Refrigeration Cycle Apparatus 200
Operation of the refrigeration cycle apparatus 200 in the case where the
refrigeration cycle apparatus 200 is an air-conditioning apparatus and the airconditioning apparatus performs a heating operation will be described below. When
30 the air-conditioning apparatus performs the heating operation, in the flow switching

42
device 103, a circuit is formed such that pipes are connected as indicated by solid
lines in Fig. 9.
[0112]
High-temperature and high-pressure refrigerant obtained through compression
5 by the compressor 100 flows into the indoor heat exchanger 106, and condenses and
liquefies in the indoor heat exchanger 106. After flowing out from the indoor heat
exchanger 106, the refrigerant flows into the pressure-reducing device 105, and is
reduced in pressure by the pressure-reducing device 105 to change into the lowtemperature and low-pressure two-phase gas-liquid refrigerant. The low10 temperature and low-pressure two-phase gas-liquid refrigerant flows into the outdoor
heat exchanger 104, and then evaporates and gasifies in the outdoor heat exchanger
104. After flowing out from the outdoor heat exchanger 104, the refrigerant passes
through the flow switching device 103 and flows back to the compressor 100.
[0113]
15 In the case where the refrigeration cycle apparatus 200 is an air-conditioning
apparatus and the air-conditioning apparatus performs the heating operation, the
refrigerant is circulated in the refrigeration circuit 201 as indicated by solid arrows in
Fig. 9. Because of this circulation of the refrigerant, outside air and the refrigerant
exchange heat with each other in the outdoor heat exchanger 104 that operates as an
20 evaporator, and the refrigerant sent to the outdoor heat exchanger 104 receives heat
from the outside air. The refrigerant having received heat is sent to the indoor heat
exchanger 106 that operates as a condenser to exchange heat with indoor air and
heat the indoor air.
[0114]
25 Operation of the refrigeration cycle apparatus 200 in the case where the
refrigeration cycle apparatus 200 is an air-conditioning apparatus and the airconditioning apparatus performs a cooling operation will be described below. When
the air-conditioning apparatus performs the cooling operation, in the flow switching
device 103, a circuit is formed such that the pipes are connected by broken lines in
30 Fig. 9.

43
[0115]
High-temperature and high-pressure refrigerant obtained through compression
by the compressor 100 flows into the outdoor heat exchanger 104, and condenses
and liquefies in the outdoor heat exchanger 104. After flowing out from the outdoor
5 heat exchanger 104, the refrigerant flows into the pressure-reducing device 105, and
is reduced in pressure by the pressure-reducing device 105 to change into lowtemperature and low-pressure two-phase gas-liquid refrigerant. The lowtemperature and low-pressure two-phase gas-liquid refrigerant flows into the indoor
heat exchanger 106, and then evaporates and gasifies in the indoor heat exchanger
10 106. After flowing out from the indoor heat exchanger 106, the refrigerant passes
through the flow switching device 103 and flows back to the compressor 100.
[0116]
When the operation of the refrigeration cycle apparatus 200 is changed from
the heating operation to the cooling operation, the indoor heat exchanger 106 that
15 operates as a condenser changes to operate as an evaporator, and the outdoor heat
exchanger 104 that operates as an evaporator changes to operate as a condenser.
In the case where the refrigeration cycle apparatus 200 is an air-conditioning
apparatus and the air-conditioning apparatus performs the cooling operation, the
refrigerant is circulated in the refrigeration circuit 201 as indicated by dashed arrows
20 in Fig. 2. Because of this circulation of the refrigerant, indoor air and the refrigerant
exchange with each other at the indoor heat exchanger 106 operating as an
evaporator, and the refrigerant receives heat from the indoor air, that is, cools the
indoor air. The refrigerant that has received heat is sent to the outdoor heat
exchanger 104 that operates as a condenser to exchange heat with outside air and
25 transfer heat to the outside air.
[0117]
Advantages of Refrigeration Cycle Apparatus 200
The refrigeration cycle apparatus 200 includes the compressor 100 according
to Embodiment 1. The refrigeration cycle apparatus 200 can thus obtain similar
30 advantages to those obtained by the compressor 100 according to Embodiment 1.

44
[0118]
Embodiment 2
Fig. 10 is a configuration diagram schematically illustrating a configuration of
the cylinder 23 in the compression mechanism portion 20 of the compressor 100
5 according to Embodiment 2. Fig. 11 is a partial sectional view schematically
illustrating configurations of the suction hole 40, the screw hole 50, and the spring
hole 60 in the cylinder 23 of the compressor 100 according to Embodiment 2. Fig.
11 is a sectional view taken along line E-E in Fig. 10. Regarding Embodiment 2,
constituent elements that have the same functions and the same advantages as
10 those of the stator 31 in Embodiment 1 will be denoted by the same reference signs,
and their descriptions will thus be omitted. The following description concerning
Embodiment 2 is made by referring mainly to the differences between Embodiments 1
and 2, and configurations in Embodiment 2 that will not be described are the same as
those in Embodiment 1. The cylinder 23 according to Embodiment 2 is different in
15 configuration of the suction hole 40 from the cylinder 23 according to Embodiment 1.
[0119]
In the cylinder 23 according to Embodiment 1, the suction hole 40 extends
through the cylinder 23 in the radial direction thereof, but does not extend through the
cylinder 23 in the thickness direction thereof. In the cylinder 23 according to
20 Embodiment 2, part of the suction hole 40 extends through the cylinder 23 in the
thickness direction as illustrated in Figs. 10 and 11.
[0120]
In the cylinder 23 according to Embodiment 2, suction grooves 42 are formed
in the suction-hole inner-diameter connection portion 40b of the suction hole 40.
25 More specifically, in the cylinder 23, a suction groove 42 is formed to extend in the
thickness direction, through a wall of the cylinder 23 that is located between the
suction-hole inner-diameter connection portion 40b and at least one of the end faces
of the cylinder 23 in the thickness direction.
[0121]
30 The suction grooves 42 are formed to extend through the cylinder 23 in the

45
thickness direction. Each of the suction grooves 42 is a through hole through which
the suction-hole inner-diameter connection portion 40b communicates with an
external region on the end-face side of the cylinder 23. Where the axial direction of
the rotation shaft 21 is an up-down direction, the suction grooves 42 are provided in
5 an upper portion and a lower portion of the suction-hole inner-diameter connection
portion 40b. In the cylinder 23 according to Embodiment 2, the suction hole 40
extends through the cylinder 23 in the thickness direction in such a manner as to pass
through the suction-hole inner-diameter connection portion 40b, through the suction
groove 42 provided in the upper portion of the suction-hole inner-diameter connection
10 portion 40b, and through the suction groove 42 provided in the lower portion of the
suction-hole inner-diameter connection portion 40b.
[0122]
The suction grooves 42 are formed to communicate with the cylinder chamber
23a, and are formed in part of the suction-hole inner-diameter connection portion 40b
15 in the radial direction of the cylinder 23. In the radial direction of the cylinder 23, the
suction grooves 42 are formed to extend from the inner circumferential wall 23e of the
cylinder 23 toward the outer circumferential wall 23f of the cylinder 23. It should be
noted that although it is described above that the suction grooves 42 are formed in
part of the suction-hole inner-diameter connection portion 40b in the radial direction of
20 the cylinder 23, it is not limiting. The suction grooves 42 may be formed in the entire
suction-hole inner-diameter connection portion 40b in the radial direction of the
cylinder 23. That is, the suction grooves 42 may be formed to extend from the inner
circumferential wall 23e of the cylinder 23 to the step portion 41 in the suction-hole
inner-diameter connection portion 40b.
25 [0123]
The suction groove 42 has a dimension of 10 mm in a width direction. That is,
the suction groove 42 has a dimension of 10 mm in the circumferential direction of the
cylinder 23. As illustrated in Figs. 10 and 11, the dimension of the suction groove 42
in the width direction is smaller than a minor axis of the suction-hole inner-diameter
30 connection portion 40b, that is, the width of the suction-hole inner-diameter

46
connection portion 40b in the circumferential direction of the cylinder 23. The
suction groove 42 has a dimension of 5 mm in a depth direction. That is, the suction
groove 42 has a dimension of 5 mm in the radial direction of the cylinder 23. The
depth of the suction groove 42 is the length of the suction groove 42 that extends in
5 the radial direction of the cylinder 23, from the inner circumferential wall 23e toward
the outer circumferential wall 23f of the cylinder 23. It should be noted that the
dimensions of the cylinder 23 as described above are each merely an example, and
the above descriptions concerning the dimensions of the cylinder 23 are not limiting.
[0124]
10 Opening portions that are defined by the suction grooves 42 and that penetrate
the cylinder 23 to extend the end faces of the cylinder 23 in the thickness direction
thereof are closed by the upper bearing 24 and the lower bearing 25. The cylinder
23 is interposed between the upper bearing 24 and the lower bearing 25. The
cylinder 23, the upper bearing 24, and the lower bearing 25 are fastened together by
15 the screws 80. Then, the opening portions of the suction grooves 42 formed in the
cylinder 23 are closed by end faces of the upper bearing 24 and the lower bearing 25
that adjoin the cylinder 23. Therefore, although the suction grooves 42 are formed in
the cylinder 23, the refrigerant is prevented from leaking from the compression
mechanism portion 20 to the outside thereof. That is, although the suction-hole
20 inner-diameter connection portion 40b of the suction hole 40 penetrates the cylinder
23 in the direction toward the end faces, leakage of the refrigerant does not occur,
since the suction-hole inner-diameter connection portion 40b is closed by the end
face of the upper bearing 24 or the end face of the lower bearing 25. The end face
of the upper bearing 24 or the end face of the lower bearing 25 forms part of the flow
25 passage wall of the suction hole 40.
[0125]
Advantages of Compressor 100
In the cylinder 23, the suction groove 42 is formed in such a manner as to
extend through a wall of the cylinder 23 in the thickness direction that is located
30 between the suction-hole inner-diameter connection portion 40b and at least one of

47
the end faces of the cylinder 23 in the thickness direction. The compression
mechanism portion 20 according to Embodiment 2 includes the suction groove 42 in
the suction-hole inner-diameter connection portion 40b of the cylinder 23, and thus
can further increase the area of the suction passage, as compared with the
5 compression mechanism portion 20 according to Embodiment 1. Therefore, the
compressor 100 according to Embodiment 2 can reduce the pressure loss and
improve the efficiency of the compressor, as compared with a compressor not having
the above configuration.
[0126]
10 Advantages of Refrigeration Cycle Apparatus 200
The refrigeration cycle apparatus 200 includes the compressor 100 according
to Embodiment 2. The refrigeration cycle apparatus 200 can thus obtain the same
advantages as the compressor 100 according to Embodiment 2.
[0127]
15 Embodiment 3
Fig. 12 is a vertical sectional view schematically illustrating a configuration of
the suction hole 40 and the surroundings thereof in the compression mechanism
portion 20 of the compressor 100 according to Embodiment 3. It should be noted
that because in Fig. 12, illustration of an internal configuration of the cylinder chamber
20 23a is omitted for explanation of the configurations of the cylinder 23, the upper
bearing 24, and the lower bearing 25. Regarding Embodiment 3, components that
have the same functions and the same advantages as those of the compression
mechanism portion 20 in Embodiments 1 and 2 will be denoted by the same
reference signs, and their descriptions will thus be omitted. The following description
25 concerning Embodiment 3 is made by referring mainly to the differences between
Embodiment 3 and Embodiments 1 and 2, and configurations in Embodiment 3 that
are the same as those in Embodiment 1 or 2 will not be described.
[0128]
The compression mechanism portion 20 according to Embodiment 3 is different
30 in configurations of the upper bearing 24 and the lower bearing 25 from the

48
compression mechanism portion 20 according to Embodiments 1 and 2. It should be
noted that in the compression mechanism portion 20 according to Embodiment 3, the
suction grooves 42 are formed in the cylinder 23 as in the compression mechanism
portion 20 according to Embodiment 2.
5 [0129]
In the above description concerning the compression mechanism portion 20
according to each of Embodiments 1 and 2, the shapes of the end faces of the upper
bearing 24 and the lower bearing 25, which adjoin the cylinder 23, are not specified.
In the compression mechanism portion 20 according to Embodiment 3, the upper
10 bearing 24 has an end-face groove 24a formed in an end face 24b of the upper
bearing 24 that adjoins the cylinder 23. In the compression mechanism portion 20
according to Embodiment 3, the lower bearing 25 has an end-face groove 25a formed
in an end face 25b of the lower bearing 25 that adjoins the cylinder 23.
[0130]
15 The end face 24b of the upper bearing 24 is an end face of an upper closing
portion 24c formed in a plate-like shape. The end face adjoins the cylinder 23. The
end face 24b of the upper bearing 24 covers one of the end faces of the cylinder 23 in
the axial direction of the rotation shaft 21, and closes one of openings 23m of the
cylinder 23. The end face 25b of the lower bearing 25 is an end face of a lower
20 closing portion 25c formed in a plate-like shape. The end face adjoins the cylinder
23. The end face 25b of the lower bearing 25 covers the other end face of the
cylinder 23 in the axial direction of the rotation shaft 21, and closes the other opening
23n of the cylinder 23.
[0131]
25 The end-face groove 24a is formed in the end face 24b of the upper closing
portion 24c and formed in a recessed groove shape. The end-face groove 24a is not
a through hole, and is open to face the cylinder 23 in the compression mechanism
portion 20. The end-face groove 24a is formed to communicate with at least part of
the suction groove 42 formed in the upper portion of the cylinder 23. The end-face
30 groove 24a and the suction groove 42 formed in the upper portion of the cylinder 23

49
form a single space. The end-face groove 24a is formed to extend in the radial
direction of the cylinder 23 along the suction groove 42 formed in the upper portion of
the cylinder 23.
[0132]
5 The end-face groove 25a is formed in the end face 25b of the lower closing
portion 25c and formed in a recessed groove shape. The end-face groove 25a is not
a through hole, and is open to face the cylinder 23 in the compression mechanism
portion 20. The end-face groove 25a is formed to communicate with at least part of
the suction groove 42 formed in the lower portion of the cylinder 23. The end-face
10 groove 25a and the suction groove 42 formed in the lower portion of the cylinder 23
form a single space. The end-face groove 25a is formed to extend in the radial
direction of the cylinder 23 along the suction groove 42 formed in the lower portion of
the cylinder 23.
[0133]
15 The end-face grooves 24a and 25a are formed at positions through which the
end faces of the rolling piston 22 in the axial direction do not pass when the rolling
piston 22 moves as the rotation shaft 21 rotates. It should be noted that either the
end-face groove 24a or the end-face groove 25a may be formed.
[0134]
20 The end-face groove 24a has a dimension of 10 mm in the width direction.
That is, the end-face groove 24a has a dimension of 10 mm in the circumferential
direction of the cylinder 23. Similarly, the end-face groove 25a has a dimension of
10 mm in the width direction. That is, the end-face groove 25a has a dimension of
10 mm in the circumferential direction of the cylinder 23.
25 [0135]
The end-face groove 24a has a dimension of 4 mm in the radial direction of the
cylinder 23. The end-face groove 24a has a depth dimension of 3 mm in the depth
direction thereof in the axial direction of the rotation shaft 21. Similarly, the end-face
groove 25a has a dimension of 4 mm in the radial direction thereof in the radial
30 direction of the cylinder 23. The end-face groove 25a has a dimension of 3 mm in

50
the depth direction thereof in the axial direction of the rotation shaft 21. It should be
noted that the dimensions of the cylinder 23 as described above are each merely an
example, and the above description concerning the dimensions of the cylinder 23 is
not limiting. For example, the dimension of the end-face groove 24a in the radial
5 direction in the radial direction of the cylinder 23 may be equal to the dimension of the
end-face groove 24a in the depth direction thereof in the axial direction of the rotation
shaft 21. Similarly, the dimension of the end-face groove 25a in the radial direction
in the radial direction of the cylinder 23 may be equal to the dimension of the end-face
groove 25a in the depth direction thereof in the axial direction of the rotation shaft 21.
10 [0136]
Advantages of Compressor 100
In the compression mechanism portion 20 according to Embodiment 3, the
end-face groove 24a is formed to communicate with at least part of the suction
groove 42 formed in the upper portion of the cylinder 23, and the end-face groove 25a
15 is formed to communicate with at least part of the suction groove 42 formed in the
lower portion of the cylinder 23. In the compression mechanism portion 20
according to Embodiment 3, because of provision of the above configuration, it is
possible to further increase the area of the flow passage through which the refrigerant
passes to flow into the cylinder chamber 23a, as compared with the compression
20 mechanism portion 20 according to Embodiment 2. Therefore, in the compressor
100 according to Embodiment 3, it is possible to reduce the pressure loss and
improve the efficiency of the compressor, as compared with a compressor not having
the above configuration.
[0137]
25 Advantages of Refrigeration Cycle Apparatus 200
The refrigeration cycle apparatus 200 includes the compressor 100 according
to Embodiment 3. Therefore, the refrigeration cycle apparatus 200 can obtain the
same advantages as those obtained by the compressor 100 according to
Embodiment 3.
30 [0138]

51
Embodiment 4
Fig. 13 is a vertical sectional view schematically illustrating a configuration of
the suction hole 40 and the surroundings thereof in in the compression mechanism
portion 20 of the compressor 100 according to Embodiment 4. It should be noted
5 that in Fig. 13, illustration of an internal configuration of the cylinder chamber 23a is
omitted for explanation of that configurations of the cylinder 23, the upper bearing 24,
and the lower bearing 25. Regarding Embodiment 4, components that have the
same functions and the same advantages as those of the compression mechanism
portion 20 will be denoted by the same reference signs, and their descriptions will
10 thus be omitted. The following description concerning Embodiment 4 is made by
referring mainly to the differences between Embodiment 4 and any of Embodiments 1
to 3, and configurations in Embodiment 3 that are the same as those in any of
Embodiments 1 to 3 are omitted.
[0139]
15 The above description concerning Embodiment 3 is made with respect to the
case where the compressor 100 is a single rotary compressor in which the
compression mechanism portion 20 includes a single cylinder 23. In contrast, the
following description concerning Embodiment 4 is made with respect to the case
where the compressor 100 is a twin rotary compressor which the compression
20 mechanism portion 20 has two cylinders 23. In the compression mechanism portion
20 according to Embodiment 4, the cylinders 23, the upper bearing 24, and the lower
bearing 25 have the same configurations as those in the compression mechanism
portion 20 according to Embodiment 3.
[0140]
25 In the compression mechanism portion 20 according to Embodiment 4, the
suction grooves 42 are formed in the cylinder 23 as in the compression mechanism
portion 20 according to Embodiment 3. Furthermore, in the compression
mechanism portion 20 according to Embodiment 4, the upper bearing 24 has the endface groove 24a formed in the end face 24b of the upper bearing 24, which adjoins
30 the cylinder 23. In the compression mechanism portion 20 according to Embodiment

52
4, the lower bearing 25 has the end-face groove 25a formed in the end face 25b of
the lower bearing 25, which adjoins the cylinder 23.
[0141]
The end face 24b of the upper bearing 24 covers one of the end faces of the
5 cylinder 23 in the axial direction of the rotation shaft 21, and closes the opening 23m
of the upper one of the two cylinders 23, the opening 23m being located to face the
upper bearing 24. The end face 25b of the lower bearing 25 covers one of the end
faces of the cylinder 23 in the axial direction of the rotation shaft 21, and closes the
opening 23n of the lower one of the two cylinders 23, the opening 23n being located
10 to face the lower bearing 25.
[0142]
The compression mechanism portion 20 according to Embodiment 4 includes
two cylinders 23. The compression mechanism portion 20 according to Embodiment
4 has an intermediate plate 28 that is provided between the two cylinders 23 and that
15 closes the cylinder chambers 23a. It should be noted that Fig. 13 illustrates the twin
rotary compressor in which the compression mechanism portion 20 has the two
cylinders 23, however, the number of the cylinders 23 included in the compression
mechanism portion 20 according to Embodiment 4 is not limited to two, but may be
three or more.
20 [0143]
The intermediate plate 28 is formed in a plate-like shape. A plate surface 28a
of the intermediate plate 28 covers the other end face of the cylinder 23 in the axial
direction of the rotation shaft 21, and closes the opening 23n of one of the cylinders
23 that is located above the intermediate plate 28, the opening 23n being located to
25 face the lower bearing 25. A plate surface 28b of the intermediate plate 28 covers
the other end face of the cylinder 23 in the axial direction of the rotation shaft 21, and
closes the opening 23m of one of the cylinders 23 that is located below the
intermediate plate 28, the opening 23m being located to face the upper bearing 24.
[0144]
30 The intermediate plate 28 has an intermediate plate groove 28a1 recessed and

53
formed in a groove shape in the plate surface 28a that adjoins the cylinder 23 located
above the intermediate plate 28, that is, in the plate surface 28a that faces the upper
bearing 24. The intermediate plate 28 has an intermediate plate groove 28b1
recessed and formed in a groove shape in the plate surface 28b that adjoins the
5 cylinder 23 located below the intermediate plate 28, that is, in the plate surface 28b
that faces the lower bearing 25.
[0145]
The intermediate plate groove 28a1 is formed in the plate surface 28a of the
intermediate plate 28 and formed in a recessed groove shape. The intermediate
10 plate groove 28a1 is not a through hole, and is open to face the upper bearing 24 in
the compression mechanism portion 20. The intermediate plate groove 28a1 is
formed to communicate with at least part of the suction groove 42 formed in the lower
portion of the cylinder 23 located above the intermediate plate 28. The intermediate
plate groove 28a1 forms a space integrated with the suction groove 42 formed in the
15 lower portion of the cylinder 23 located above the intermediate plate 28. The
intermediate plate groove 28a1 is formed to extend in the radial direction of the
cylinder 23 along the suction groove 42 formed in the lower portion of the cylinder 23
located above the intermediate plate 28.
[0146]
20 The intermediate plate groove 28b1 is formed in the plate surface 28b of the
intermediate plate 28 and formed in a recessed groove shape. The intermediate
plate groove 28b1 is not a through hole, and is open to face the lower bearing 25 in
the compression mechanism portion 20. The intermediate plate groove 28b1 is
formed to communicate with at least part of the suction groove 42 formed in the upper
25 portion of the cylinder 23 located below the intermediate plate 28. The intermediate
plate groove 28b1 and the suction groove 42 formed in the upper portion of the
cylinder 23 located below the intermediate plate 28 form a single space. The
intermediate plate groove 28b1 is formed to extend in the radial direction of the
cylinder 23 along the suction groove 42 formed in the upper portion of the cylinder 23
30 located below the intermediate plate 28.

54
[0147]
The intermediate plate grooves 28a1 and 28b1 are formed at positions through
which the end faces of the rolling piston 22 in the axial direction do not pass when the
rolling piston 22 moves as the rotation shaft 21 rotates. It should be noted that either
5 the intermediate plate groove 28a1 or the intermediate plate groove 28b1 may be
formed.
[0148]
Advantages of Compressor 100
In the compression mechanism portion 20 according to Embodiment 4, the
10 intermediate plate groove 28a1 is formed to communicate with at least part of the
suction groove 42 formed in the lower portion of the cylinder 23 located above the
intermediate plate 28. Furthermore, in the compression mechanism portion 20
according to Embodiment 4, the intermediate plate groove 28b1 is also formed to
communicate with at least part of the suction groove 42 formed in the upper portion of
15 the cylinder 23 located below the intermediate plate 28. In the compression
mechanism portion 20 according to Embodiment 4, because of provision of the above
configuration, it is possible to further increase the area of the flow passage through
which the refrigerant passes to flow into the cylinder chamber 23a, as compared with
a compressor not having the above configuration. Therefore, the compressor 100
20 according to Embodiment 4 can reduce the pressure loss and improve the efficiency
of the compressor, as compared to a compressor not having the configuration
described above.
[0149]
Advantages of Refrigeration Cycle Apparatus 200
25 The refrigeration cycle apparatus 200 includes the compressor 100 according
to Embodiment 4. Therefore, the refrigeration cycle apparatus 200 can obtain the
same advantages as the compressor 100 according to Embodiment 4.
[0150]
The configurations described above regarding the above embodiments are
30 merely examples, and can thus be combined with another publicly known technique,

55
or partially omitted and modified without departing from the gist of the present
disclosure. Furthermore, in the configurations described regarding the embodiments,
a plurality of components disclosed regarding the embodiments may be appropriately
combined.
5 [0151]
For example, in Embodiments 1 to 3, in the axial direction of the rotation shaft
21, the center of the suction-hole outer-diameter connection portion 40a coincides
with the center of the cylinder 23 in the thickness direction thereof. However, as
described regarding the compressor 100 according to Embodiment 4, in the case
10 where the compressor 100 is the twin rotary compressor, if the distance between the
suction holes 40 in the two cylinders 23 is too short, the pressure resistance of the
hermetic container 10 is reduced. In view of this point, the centers of the suction
holes 40 in the two cylinders 23 may be located offset toward the respective bearings
that are in contact with the cylinders 23, that is, may be located offset in a direction in
15 which each of the suction holes 40 is moved away from the other suction hole 40.
Also, in this configuration, the compressor 100 can obtain the same advantages as
the compressors 100 according to Embodiments 1 to 3.
[0152]
In the compressors 100 according to Embodiments 1 to 4, it is necessary to
20 reduce distortion that would occur in an assembly process in which the refrigerant
suction pipe 107 is driven into the cylinder 23. In view of this point, in the
compressors 100 according to Embodiments 1 to 4, it is necessary to ensure a
specific thickness of the first thin portion 23g that forms the wall between the suction
hole 40 and the end face of the cylinder 23. Meanwhile, in the case where the
25 hermetic container 10 has a small plate thickness, it may be possible to ensure a
larger suction passage by locating the centers of the suction holes 40 such that the
suction holes 40 are offset, in consideration of limitations on the strength of the
hermetic container 10. In this case, for example, in the cylinder 23 according to
Embodiment 1, the suction holes 40 may be offset toward the bearings by 0.5 mm.
30 [0153]

56
In view of reduction in the efficiency of the compressor 100 that is caused by
the pressure loss of the flow of the refrigerant, in the case where the compressor 100
is a twin rotary compressor having two cylinders 23, it is preferable that the area of
the flow passage of each of suction holes 40 be increased as much as possible.
5 However, because of limitations on the structure of the compressor 100, it is
necessary to offset the suction holes 40 toward the respective bearings to increase
the areas of the flow passages of the suction holes 40 as much as possible while
avoiding the limitations.
[0154]
10 In the case where the compressor 100 is a twin rotary compressor, the distance
between the two suction holes 40 will be referred to as "the minimum distance CD"
(see Fig. 13). If the minimum distance CD is too short, the pressure resistance of
the hermetic container 10 (see Fig. 1) is reduced, and the hermetic container 10 thus
bursts. Therefore, the minimum distance CD needs to be adequately long. In the
15 case where the compressor 100 is a twin rotary compressor, the upper one of the two
cylinders 23 is offset toward the upper bearing 24, and the lower one of the two
cylinders 23 is offset toward the lower bearing 25, whereby the closest distance CD
between the two suction holes 40 can be increased. If the opening diameter of the
suction holes 40 is increased without offsetting the cylinders 23, the closest distance
20 CD does not satisfy the structural requirement for the thickness of the wall between
the suction holes 40; that is, it does not avoid the limitations on the thickness of the
wall. It is therefore impossible for the compressor 100 to sufficiently increase the
opening diameters of the suction holes 40.
[0155]
25 Therefore, in the case where the suction holes 40 are offset, it is preferable that
each of the cylinders 23 be formed such that the thickness t1 [mm] of the first thin
portion 23g is greater than the thickness t2 [mm] of the second thin portion 23j
(thickness t1 > thickness t2). In addition, in the case where the suction holes 40 are
offset, the cylinders 23 are formed such that the thickness t1 [mm] of the first thin
30 portion 23g is greater than the thickness t3 [mm] of the third thin portion 23k

57
(thickness t1 > thickness t3). It is appropriate that the suction holes 40 are offset
such that the largest possible suction-hole diameter can be ensured, while the
cylinders 23 satisfy inequalities "thickness t1 > thickness t2" and "thickness t1 >
thickness t3."
5 Reference Signs List
[0156]
10: hermetic container, 11: upper container, 12: lower container, 20:
compression mechanism portion, 21: rotation shaft, 21a: main shaft portion, 21b:
eccentric shaft portion, 21c: sub-shaft portion, 22: rolling piston, 22a: outer
10 circumferential wall, 23: cylinder, 23a: cylinder chamber, 23b: back pressure chamber,
23c: vane groove, 23d: opening, 23e: inner circumferential wall, 23f: outer
circumferential wall, 23g: first thin portion, 23h: end face, 23j: second thin portion,
23k: third thin portion, 23m: opening, 23n: opening, 24: upper bearing, 24a: end-face
groove, 24b: end face, 24c: upper closing portion, 25: lower bearing, 25a: end-face
15 groove, 25b: end face, 25c: lower closing portion, 26: vane, 27: discharge muffler, 28:
intermediate plate, 28a: plate surface, 28a1: intermediate plate groove, 28b: plate
surface, 28b1: intermediate plate groove, 30: electric motor portion, 31: stator, 32:
rotor, 33: lead wire, 34: refrigerant flow passage, 40: suction hole, 40a: suction-hole
outer-diameter connection portion, 40a1: inner circumferential wall, 40a2: suction20 hole outer-diameter connection portion, 40b: suction-hole inner-diameter connection
portion, 40b1: inner circumferential wall, 41: step portion, 42: suction groove, 50:
screw hole, 60: spring hole, 61: spring-hole conical portion, 62: vane spring, 62a: endturn portion, 62b: end-turn portion, 63: spring fixing portion, 80: screw, 100:
compressor, 101: suction muffler, 102: discharge pipe, 103: flow switching device,
25 104: outdoor heat exchanger, 105: pressure-reducing device, 106: indoor heat
exchanger, 107: refrigerant suction pipe, 200: refrigeration cycle apparatus, 201:
refrigeration circuit

We Claim:
[Claim 1]
A compressor comprising: an electric motor portion; a rotation shaft to be
5 rotationally driven by the electric motor portion and having an eccentric shaft portion;
and a compression mechanism portion configured to compress refrigerant with a
driving force transmitted from the electric motor portion through the rotation shaft, the
electric motor portion, the rotation shaft, and the compression mechanism portion
being provided in a hermetic container,
10 wherein the compression mechanism portion includes
a cylinder having a cylindrical shape, fixed to the hermetic container, and
having a hollow portion in which a cylinder chamber is provided,
a rolling piston accommodated in the cylinder chamber such that the
rolling piston is fitted to the eccentric shaft portion, and configured to eccentrically
15 rotate together with the eccentric shaft portion to compress the refrigerant,
a vane provided in a vane groove to partition the cylinder chamber into a
suction chamber and a compression chamber, the vane groove being formed to
extend in a radial direction of the cylinder, and
bearings provided on respective end faces of the cylinder to close the
20 cylinder chamber,
wherein in the cylinder, a suction hole is formed to extend in the radial direction
of the cylinder and allow the refrigerant to be sucked into the cylinder chamber
through the suction hole,
wherein the suction hole has
25 a suction-hole outer-diameter connection portion defining a space
located on an outer circumferential side of the cylinder in the radial direction of the
cylinder, and
a suction-hole inner-diameter connection portion defining a space
located on an inner circumferential side of the cylinder in the radial direction of the
30 cylinder,

59
wherein in a section perpendicular to the radial direction of the cylinder, the
suction-hole outer-diameter connection portion is formed to have a larger sectional
area than a sectional area of the suction-hole inner-diameter connection portion, and
wherein in the section perpendicular to the radial direction of the cylinder, the
5 suction-hole inner-diameter connection portion has a sectional shape such that an
opening width of the suction-hole inner diameter connection portion in a
circumferential direction of the cylinder is smaller than an opening width of the
suction-hole inner diameter connection portion in a thickness direction of the cylinder.
[Claim 2]
10 The compressor of claim 1, further comprising a plurality of screws to fasten
the bearings to the cylinder,
wherein in the cylinder, a plurality of screw holes are formed in each of which
an associated one of the plurality of screws is set, the plurality of screw holes
extending through the cylinder in the thickness direction of the cylinder,
15 wherein the cylinder has
a first thin portion forming part of a wall of the cylinder that is located
between the suction-hole outer-diameter connection portion and one of the end faces
of the cylinder that is located at an end thereof in the thickness direction thereof, and
a second thin portion that is part of a wall forming the cylinder, the
20 second thin portion being provided at a location where a distance between the
suction-hole inner-diameter connection portion and one of the plurality of screw holes
that is located closest to the suction-hole inner-diameter connection portion is the
minimum in the circumferential direction of the cylinder, and
wherein the first thin portion is formed to have a thickness t1 in the thickness
25 direction of the cylinder that is greater than a thickness t2 of the second thin portion in
the circumferential direction of the cylinder.
[Claim 3]
The compressor of claim 1, further comprising a spring configured to urge the
vane to press a distal end portion of the vane against an outer circumferential wall of
30 the rolling piston,

60
wherein in the cylinder, a spring hole is formed to extend in the radial direction
of the cylinder, the spring hole being provided as a hole in which the spring is
provided,
wherein the cylinder further has
5 a first thin portion forming part of a wall of the cylinder that is located
between the suction-hole outer-diameter connection portion and one of the end faces
of the cylinder that is located at an end thereof in the thickness direction thereof, and
a third thin portion that is part of a wall forming the cylinder, the third thin
portion being provided at a location where a distance between the suction-hole inner10 diameter connection portion and the spring hole is the minimum in the circumferential
direction of the cylinder, and
wherein the first thin portion is formed to have a thickness t1 in the thickness
direction of the cylinder that is greater than a thickness t3 of the third thin portion in
the circumferential direction of the cylinder.
15 [Claim 4]
The compressor of claim 2, further comprising a spring configured to urge the
vane to press a distal end portion of the vane against an outer circumferential wall of
the rolling piston,
wherein in the cylinder, a spring hole is formed to extend in the radial direction
20 of the cylinder, the spring hole being provided as a hole in which the spring is located,
wherein the cylinder further has a third thin portion that is part of a wall forming
the cylinder, the third thin portion being provided at a location where a distance
between the suction-hole inner-diameter connection portion and the spring hole is the
minimum in the circumferential direction of the cylinder, and
25 wherein the thickness t1 of the first thin portion is greater than a thickness t3 of
the third thin portion in the circumferential direction of the cylinder.
[Claim 5]
The compressor of any one of claims 1 to 4, wherein in the section
perpendicular to the radial direction of the cylinder, the suction-hole outer-diameter
30 connection portion has a circular shape, and the suction-hole inner-diameter

61
connection portion has a non-circular shape.
[Claim 6]
The compressor of any one of claims 1 to 5, wherein in the section
perpendicular to the radial direction of the cylinder, the suction-hole inner-diameter
5 connection portion has an oval sectional shape such that a length of the suction-hole
inner-diameter connection portion in the thickness direction is greater than a length of
the suction-hole inner-diameter connection portion in the circumferential direction of
the cylinder.
[Claim 7]
10 The compressor of any one of claims 1 to 6, wherein in the cylinder, a suction
groove is formed to extend through a wall of the cylinder in the thickness direction of
the cylinder, the wall being located between the suction-hole inner-diameter
connection portion and at least one of the end faces of the cylinder that is located at
an end thereof in the thickness direction thereof.
15 [Claim 8]
The compressor of claim 7, wherein
an end-face groove is formed in an end face of each of the bearings, the end
face adjoining the cylinder, and
the end-face groove is formed to communicate with at least part of the suction
20 groove formed in the cylinder, the end-face groove being located at a position through
which end faces of the rolling piston do not pass when the rolling piston moves as the
rotation shaft rotates.
[Claim 9]
The compressor of claim 7 or 8, comprising:
25 two cylinders including the cylinder:
an intermediate plate located between the two cylinders to close the cylinder
chambers, and
an intermediate plate groove formed in a plate surface of the intermediate plate
that adjoins the cylinder,
30 wherein the intermediate plate groove is formed to communicate with at least

62
part of the suction groove formed in the cylinder, the intermediate plate groove being
formed at a position through which end faces of the rolling piston do not pass when
the rolling piston moves as the rotation shaft rotates.
[Claim 10]
5 A refrigeration cycle apparatus comprising:
the compressor of any one of claims 1 to 9;
an outdoor heat exchanger configured to cause heat exchange to be performed
between outdoor air and refrigerant that flows in the outdoor heat exchanger;
an indoor heat exchanger configured to cause heat exchange to be performed
10 between indoor air and refrigerant that flows in the indoor heat exchanger; and
a pressure-reducing device configured to reduce a pressure of refrigerant that
flows into the outdoor heat exchanger or the indoor heat exchanger.