1
FORM 2
THE PATENTS ACT, 1970
(39 of 1970)
&
THE PATENTS RULES, 2003
COMPLETE SPECIFICATION
[See section 10, Rule 13]
ROTARY COMPRESSOR
MITSUBISHI ELECTRIC CORPORATION, A CORPORATION ORGANISED AND
EXISTING UNDER THE LAWS OF JAPAN, WHOSE ADDRESS IS 7-3,
MARUNOUCHI 2-CHOME, CHIYODA-KU, TOKYO 100-8310, JAPAN
THE FOLLOWING SPECIFICATION PARTICULARLY DESCRIBES THE INVENTION
AND THE MANNER IN WHICH IT IS TO BE PERFORMED.
2
DESCRIPTION
Technical Field
5 [0001]
The present disclosure relates to a rotary compressor for use in a cooling and
heating apparatus such as an air-conditioning apparatus.
Background Art
[0002]
10 A rotary compressor is configured such that an electric motor unit and a
compression mechanism unit driven by the electric motor unit are provided in a
hermetic container (see, for example, Patent Literature 1). The compression
mechanism unit has a vane that is provided in a vane groove provided radially in a
cylinder and partitions a cylinder chamber of the cylinder into a suction chamber and
15 a compression chamber. Furthermore, the compression mechanism unit has a
rolling piston that is contained in the cylinder chamber and eccentrically rotates to
compress refrigerant and a vane spring that is contained in a vane spring containing
hole of the cylinder and urges the vane so that a front end of the vane is pressed
against an outer circumferential surface of the rolling piston.
20 Citation List
Patent Literature
[0003]
Patent Literature 1: Japanese Unexamined Patent Application Publication No.
H11-022675
25 Summary of Invention
Technical Problem
[0004]
To improve reliability of a rotary compressor, it is typically effective to elongate
a length of a vane groove so that a sliding area for sliding of a vane along the vane
30 groove is increased and the vane stably slides along the vane groove. However, a
3
vane spring containing hole needs to have a sufficient length that allows a vane
spring contained therein to bias the vane so that the vane follows movement of a
rolling piston. Accordingly, the increase in length of the vane groove invites an
increase in size of a hermetic container. This undesirably increases a size of the
whole 5 rotary compressor.
[0005]
The present disclosure was accomplished to overcome the above problem, and
the rotary compressor of the present disclosure aims to provide a rotary compressor
that is increased in sliding area for sliding of a vane along a vane groove without an
10 increase in size of a hermetic container and is thus improved in reliability.
Solution to Problem
[0006]
A rotary compressor according to an embodiment of the present disclosure
includes an electric motor unit; and a compression mechanism unit that compresses
15 refrigerant by using driving force transmitted from the electric motor unit, wherein the
electric motor unit and the compression mechanism unit are provided in a hermetic
container, the compression mechanism unit includes: a crankshaft that has an
eccentric shaft part and is driven to rotate by the electric motor unit, a cylinder that is
fixed to the hermetic container and has a cylinder chamber, shaft bearings that are
20 provided at top and bottom ends of the cylinder and close the cylinder chamber, a
rolling piston that is contained in the cylinder chamber so as to be fitted with the
eccentric shaft part and eccentrically rotates together with the eccentric shaft part to
compress refrigerant, a vane that is provided in a vane groove provided radially in the
cylinder and partitions the cylinder chamber into a suction chamber and a
25 compression chamber, and a vane spring that is contained in a vane spring
containing hole provided in the cylinder and urges the vane so that a front end of the
vane is pressed against an outer circumferential surface of the rolling piston, and the
cylinder has a vane spring groove that extends the vane spring containing hole, the
vane spring groove being provided around the vane groove so as to extend from the
30 vane spring containing hole toward the cylinder chamber.
4
Advantageous Effects of Invention
[0007]
According to the rotary compressor according to the embodiment of the present
disclosure, even in a case where a length of the vane spring containing hole is
shortened, the vane can be urged by the vane spring contained 5 in the vane spring
groove so that the vane follows movement of the rolling piston. The shortening of
the length of the vane spring containing hole allows the vane groove to be elongated
accordingly. This can increase a sliding area for sliding of the vane along the vane
groove, thereby improving reliability of the rotary compressor.
10 Brief Description of Drawings
[0008]
[Fig. 1] Fig. 1 is a longitudinal cross-sectional view schematically illustrating an
overall structure of a rotary compressor according to Embodiment 1 of the present
disclosure.
15 [Fig. 2] Fig. 2 is a transverse cross-sectional view illustrating a substantial part
of a compression mechanism unit of the rotary compressor according to Embodiment
1 of the present disclosure.
[Fig. 3] Fig. 3 is a transverse cross-sectional view illustrating a cylinder of the
rotary compressor according to Embodiment 1 of the present disclosure.
20 [Fig. 4] Fig. 4 is a cross-sectional view taken along line A-A illustrated in Fig. 3.
[Fig. 5] Fig. 5 is a transverse cross-sectional view illustrating a substantial part
of a compression mechanism unit in a modification of the rotary compressor
according to Embodiment 1 of the present disclosure.
[Fig. 6] Fig. 6 is a transverse cross-sectional view illustrating only a cylinder of
25 the compression mechanism unit illustrated in Fig. 5.
[Fig. 7] Fig. 7 is a transverse cross-sectional view illustrating a cylinder of a
rotary compressor according to Embodiment 2 of the present disclosure.
[Fig. 8] Fig. 8 is a transverse cross-sectional view illustrating a substantial part
of a compression mechanism unit of a rotary compressor according to Embodiment 3
30 of the present disclosure.
5
[Fig. 9] Fig. 9 is a transverse cross-sectional view illustrating only a cylinder of
the compression mechanism unit illustrated in Fig. 8.
Description of Embodiments
[0009]
Embodiments of the present disclosure are described below 5 with reference to
the drawings. In the drawings, identical or corresponding parts are given identical
reference signs, and repeated description thereof is omitted or simplified as
appropriate. Shapes, sizes, positions, and the like of elements in the drawings can
be changed as appropriate within the scope of the present disclosure.
10 [0010] Embodiment 1.
First, a rotary compressor according to Embodiment 1 of the present disclosure
is described with reference to Figs. 1 through 6. Fig. 1 is a longitudinal crosssectional
view schematically illustrating an overall structure of the rotary compressor
according to Embodiment 1 of the present disclosure. Fig. 2 is a transverse cross15
sectional view illustrating a substantial part of a compression mechanism unit of the
rotary compressor according to Embodiment 1 of the present disclosure. Fig. 3 is a
transverse cross-sectional view illustrating a cylinder of the rotary compressor
according to Embodiment 1 of the present disclosure. Fig. 4 is a cross-sectional
view taken along line A-A illustrated in Fig. 3.
20 [0011]
As illustrated in Fig. 1, a rotary compressor 100 according to Embodiment 1 is
configured such that an electric motor unit 2 and a compression mechanism unit 3
that compresses refrigerant by using driving force transmitted from the electric motor
unit 2 are provided in a hermetic container 1. The electric motor unit 2 and the
25 compression mechanism unit 3 are linked by a crankshaft 4. The refrigerant is, for
example, R410 refrigerant.
[0012]
The hermetic container 1 is connected to an accumulator 12 by a suction pipe
10, and refrigerant gas is taken into the hermetic container 1 from the accumulator
30 12. The accumulator 12 is provided to separate refrigerant into liquid refrigerant and
6
gas refrigerant so that liquid refrigerant sucked into the compression mechanism unit
3 is kept to a minimum. A discharge pipe 11 through which compressed refrigerant
is discharged is connected to an upper part of the hermetic container 1.
Refrigerating machine oil (not illustrated) is accumulated on a bottom of the hermetic
container 1. The refrigerating machine oil is mainly for lubricating 5 a sliding part of
the compression mechanism unit 3.
[0013]
The electric motor unit 2 includes a ring-shaped stator 20 that is fixedly
supported by an inner wall surface of the hermetic container 1, for example, by shrink
10 fitting and a rotor 21 that rotates within an inner side surface of the stator 20. The
crankshaft 4 penetrates the rotor 21. The electric motor unit 2 is driven by power
externally supplied via an airtight terminal (not illustrated).
[0014]
As illustrated in Figs. 1 and 2, the compression mechanism unit 3 includes a
15 crankshaft 4 that is driven to rotate by the electric motor unit 2, a cylinder 5 that has a
cylinder chamber 50, an upper shaft bearing 51 and a lower shaft bearing 52 that
close the cylinder chamber 50, a rolling piston 6, and a vane 7.
[0015]
The crankshaft 4 has a main shaft part 40 fixed to the rotor 21 of the electric
20 motor unit 2, a sub shaft part 41 provided opposite to the main shaft part 40 with the
cylinder 5 interposed therebetween, and an eccentric shaft part 42 provided between
the main shaft part 40 and the sub shaft part 41. The crankshaft 4 has an oil suction
hole in a shaft center part thereof. The crankshaft 4 has a spiral centrifugal pump in
the oil suction hole. With this configuration, the refrigerating machine oil
25 accumulated on the bottom of the hermetic container 1 can be pumped up and
supplied to the sliding part of the compression mechanism unit 3.
[0016]
An outer circumferential part of the cylinder 5 is fixed to the hermetic container
1, for example, with use of a bolt. As illustrated in Fig. 2, the cylinder 5 has a circular
30 outer circumference and has a cylinder chamber 50, which is a circular inner space.
7
The cylinder chamber 50 serves as a compression chamber that compresses
refrigerant during a driven state. As illustrated in Fig. 1, the cylinder chamber 50 is
opened at both ends thereof in an axial direction of the crankshaft 4, and these
openings are closed by the upper shaft bearing 51 provided on an upper surface of
the cylinder 5 and the lower shaft bearing 52 provided on a lower 5 surface of the
cylinder 5. Furthermore, the cylinder 5 has a suction port (not illustrated) through
which refrigerant gas flowing from the suction pipe 10 passes. The suction port
passes through the cylinder 5 from the outer circumferential surface of the cylinder 5
to the cylinder chamber 50.
10 [0017]
The upper shaft bearing 51 closes one end surface (on the electric motor unit 2
side) of the cylinder chamber 50 of the cylinder 5. The upper shaft bearing 51 and
the main shaft part 40 of the crankshaft 4 are fitted with each other so as to slide on
each other. The lower shaft bearing 52 closes the other end surface (the
15 refrigerating machine oil side) of the cylinder chamber 50. The lower shaft bearing
52 and the sub shaft part 41 of the crankshaft 4 are fitted with each other so as to
slide on each other. The upper shaft bearing 51 has a discharge hole (not
illustrated) through which refrigerant compressed in the compression chamber is
discharged. Furthermore, the upper shaft bearing 51 is provided with a discharge
20 muffler that covers the discharge hole.
[0018]
The rolling piston 6 has a ring shape, and the rolling piston 6 and the eccentric
shaft part 42 of the crankshaft 4 are fitted with each other so as to slide on each
other. The rolling piston 6 and the eccentric shaft part 42 are provided in the cylinder
25 chamber 50, and the rolling piston 6 and the eccentric shaft part 42 eccentrically
rotate to compress refrigerant.
[0019]
As illustrated in Fig. 2, the cylinder 5 has a vane groove 70 that communicates
with the cylinder chamber 50 and extends radially. In the vane groove 70, the vane
30 7 that partitions the cylinder chamber 50 into the suction chamber and the
8
compression chamber is fitted so as to slide. During a compression process, the
vane 7 slides back and forth in the vane groove 70 so as to follow eccentric rotation of
the rolling piston 6 while being in contact with an outer circumferential part of the
rolling piston 6 at a front end thereof. The cylinder chamber 50 is partitioned into the
suction chamber and the compression chamber since the front 5 end of the vane 7
makes contact with the outer circumferential part of the rolling piston 6. The vane 7
is, for example, made of a non-magnetic material.
[0020]
As illustrated in Fig. 2, the cylinder 5 has a vane spring containing hole 80
10 behind the vane groove 70. An inner diameter of the vane spring containing hole 80
is larger than an inner diameter of the vane groove 70. In the vane spring containing
hole 80, a vane spring 8 that is disposed in series with the vane 7 is contained. The
vane spring 8 urges the vane 7 so that the front end of the vane 7 is pressed against
the outer circumferential surface of the rolling piston 6. The vane spring 8 is, for
15 example, a coil spring.
[0021]
Next, operation of the rotary compressor 100 according to Embodiment 1 is
described. In the rotary compressor 100, refrigerant in the accumulator 12 is
introduced into the compression chamber of the cylinder chamber 50 through the
20 suction pipe 10 and the suction port, and then the electric motor unit 2 is driven.
When the electric motor unit 2 is driven in the rotary compressor 100, the rolling
piston 6 fitted with the eccentric shaft part 42 of the crankshaft 4 eccentrically rotates.
This compresses the refrigerant in the cylinder chamber 50. The refrigerant
compressed in the cylinder chamber 50 is discharged from the discharge hole of the
25 upper shaft bearing 51 into a space in the discharge muffler and is then discharged
from a discharge hole of the discharge muffler within the hermetic container 1. The
discharged refrigerant is emitted out from the discharge pipe 11.
[0022]
To improve reliability of the rotary compressor 100, it is effective to elongate a
30 length of the vane groove 70 so that a sliding area for sliding of the vane 7 along the
9
vane groove 70 is increased and the vane 7 stably slides in the vane groove 70.
Meanwhile, the vane spring containing hole 80 needs to have a sufficient length that
allows the vane spring 8 to bias the vane 7 so that the vane 7 follows movement of
the rolling piston 6. Accordingly, the increase in length of the vane groove 70 invites
an increase in size of the hermetic container 1. This results in 5 an increase in the
whole rotary compressor 100.
[0023]
In view of this, as illustrated in Figs. 2 and 3, the cylinder 5 according to
Embodiment 1 has a vane spring groove 9 that extends the vane spring containing
10 hole 80. The vane spring groove 9 is provided around the vane groove 70 so as to
extend from the vane spring containing hole 80 toward the cylinder chamber 50.
That is, the vane spring 8 is contained in the vane spring containing hole 80 and the
vane spring groove 9 and moves back and forth in the vane spring containing hole 80
and the vane spring groove 9. Note that a length of the vane spring groove 9 is
15 changed as appropriate depending on a structure of the compressor or the kind of
refrigerant.
[0024]
As illustrated in Fig. 4, the vane spring groove 9 has a ring shape
corresponding to a shape of the vane spring 8 and partially intersects with the vane
20 groove 70, which has an elongated shape. This is to extend the vane spring
containing hole 80 and to bias the vane 7 by using the vane spring 8 so that the front
end of the vane 7 is pressed against the outer circumferential surface of the rolling
piston 6. The vane spring groove 9 has an outer diameter larger than an outer
diameter of the vane spring 8 and an inner diameter smaller than an inner diameter of
25 the vane spring 8 because the vane spring 8 needs to pass through the vane spring
groove 9.
[0025]
Note that the size and shape of the vane spring groove 9 are not limited to the
illustrated ones. The vane spring groove 9 can have any form, provided that the
30 vane spring groove 9 can extend the vane spring containing hole 80 and the vane
10
spring 8 contained in the vane spring groove 9 can bias the vane 7 so that the front
end of the vane 7 is pressed against the outer circumferential surface of the rolling
piston 6.
[0026]
As described above, according to the rotary compressor 5 100 according to
Embodiment 1, the vane 7 can be urged by the vane spring 8 contained in the vane
spring groove 9 so as to follow movement of the rolling piston 6 even in a case where
the length of the vane spring containing hole 80 is shortened. According to the
rotary compressor 100, the shortening of the length of the vane spring containing hole
10 80 allows the vane groove 70 to be elongated accordingly. This can increase a
sliding area for sliding of the vane 7 along the vane groove 70, thereby improving
reliability of the rotary compressor 100.
[0027]
The vane spring groove 9 has a ring shape corresponding to the coil-shaped
15 vane spring 8. With this configuration, the vane spring 8 can be smoothly contained
in the vane spring groove 9. This allows the rotary compressor 100 according to
Embodiment 1 to improve the function of biasing the vane 7 by using the vane spring
8 so that the vane 7 follows movement of the rolling piston 6.
[0028]
20 Effects of the rotary compressor according to Embodiment 1 are described
below by using specific values. For example, it is assumed that dimensions of the
rotary compressor 100 are set as follows: an outer diameter of the cylinder 5 is
approximately 150 mm, an inner diameter of the cylinder 5 is approximately 70 mm,
an outer diameter of the rolling piston 6 is approximately 45 mm, the length of the
25 vane groove 70 is approximately 35 mm, a height of the vane 7 is approximately 20
mm, and the vane spring groove 9 is approximately 10 mm. Typical conditions
during heating operation of the rotary compressor 100 are as follows: a suction
pressure and a discharge pressure, which are operating pressures, are approximately
0.2 MPaG and approximately 4.2 MPaG, respectively and an operating frequency is
30 approximately 120 rps.
11
[0029]
In general, strictness of conditions of sliding of the vane 7 along the vane
groove 70 is expressed by a PV value, which is the product of a pressure P for
supporting the vane 7 and an operating speed V of the vane 7. The pressure P is a
value obtained by dividing a difference between the suction 5 pressure and the
discharge pressure by the sliding area for sliding of the vane 7 along the vane groove
70. In a case where the PV value is 9.00 W/mm2 or more, the sliding conditions on
which the vane 7 slides in the vane groove 70 are strict, and a compressor
malfunction occurs due to a large difference between the suction pressure and the
10 discharge pressure. This makes it necessary to perform surface treatment such as
manganese treatment on the vane groove 70.
[0030]
According to the rotary compressor 100 according to Embodiment 1, the sliding
area for sliding of the vane 7 along the vane groove 70 is increased due to the
15 presence of the vane spring groove 9, and as a result, the PV value is 7.00 W/mm2.
It is therefore unnecessary to perform surface treatment on the vane groove 70.
Meanwhile, according to a conventional rotary compressor, a length of a vane groove
is 30 mm at most, and as a result, the PV value is 9.00 W/mm2. It is therefore
necessary to perform surface treatment on the vane groove.
20 [0031]
Next, operating refrigerant of the rotary compressor 100 is described. The
operating refrigerant of the rotary compressor 100 may be HC refrigerant such as
propane or R1234yf or HFO refrigerant instead of the R410A refrigerant. The HC
refrigerant and the HFO refrigerant are small in pressure for supporting the vane 7
25 due to a small difference between a suction pressure and a discharge pressure and
therefore require stronger base spring force than the R410A refrigerant. For
example, the dimensions of the rotary compressor 100 are set as follows: the outer
diameter of the cylinder 5 is approximately 160 mm, the inner diameter of the cylinder
5 is approximately 70 mm, the outer diameter of the rolling piston 6 is approximately
30 45 mm, the length of the vane groove 70 is approximately 40 mm, the height of the
12
vane 7 is approximately 20 mm, and the vane spring groove 9 is approximately 20
mm. In a case where propane is used as the operating refrigerant, typical conditions
during heating operation of a rotary compressor are as follows: a suction pressure
and a discharge pressure, which are operating pressures, are approximately 0.2
MPaG and approximately 2.0 MPaG, respectively and an operating 5 frequency is
approximately 120 rps.
[0032]
The PV value based on the above values is 7.08 W/mm2. Therefore, surface
treatment of the vane groove 70 is not needed in the rotary compressor 100
10 according to Embodiment 1. Meanwhile, in a conventional rotary compressor, a
length of a vane groove is approximately 10 mm at most, and as a result, the PV
value is 14.17 W/mm2. It is therefore necessary to perform surface treatment on the
vane groove. As described above, reliability of the rotary compressor 100 according
to Embodiment 1 can be improved even in a case where the HC refrigerant or the
15 HFO refrigerant is used as the operating refrigerant.
[0033]
Next, a modification of the rotary compressor according to Embodiment 1 is
described with reference to Figs. 5 and 6. Fig. 5 is a transverse cross-sectional view
illustrating a substantial part of a compression mechanism unit in the modification of
20 the rotary compressor according to Embodiment 1 of the present disclosure. Fig. 6
is a transverse cross-sectional view illustrating only a cylinder of the compression
mechanism unit illustrated in Fig. 5.
[0034]
In the rotary compressor illustrated in Figs. 5 and 6, the vane spring groove 9
25 for extending the vane spring containing hole 80 is provided around the vane groove
70 from a position close to the outer circumferential surface of the cylinder 5 toward
the cylinder chamber 50. The vane spring containing hole 80 is provided to fix an
end turn of the vane spring 8. That is, the rotary compressor illustrated in Figs. 5
and 6 is configured such that the length of the vane spring containing hole 80 is made
13
as short as possible. This can make the vane groove 70 longer, thereby increasing
a sliding area for sliding of the vane 7 along the vane groove 70.
[0035] Embodiment 2.
Next, a rotary compressor according to Embodiment 2 of the present disclosure
is described with reference to Fig. 7. Fig. 7 is a transverse cross-5 sectional view
illustrating a cylinder of the rotary compressor according to Embodiment 2 of the
present disclosure. Elements identical to those of the rotary compressor described
in Embodiment 1 are given identical reference signs, and repeated description thereof
is omitted as appropriate.
10 [0036]
The rotary compressor according to Embodiment 2 is configured such that a
vane spring containing hole 80 has an inclined part 81 connecting a side wall of the
vane spring containing hole 80 and a side wall of a vane groove 70 and a vane spring
groove 9 is provided so as to extend from the inclined part 81 toward a cylinder
15 chamber 50. In a case where the vane spring containing hole 80 is formed by
drilling, an end of the vane spring containing hole 80 on a cylinder chamber 50 side
may often have a triangular shape that is substantially identical to a front end shape
of a drill. Even in such a case, the vane spring groove 9 can be formed so as to
extend from the inclined part 81 toward the cylinder chamber 50, and the vane spring
20 containing hole 80 can be extended accordingly.
[0037]
Effects of the rotary compressor according to Embodiment 2 are described
below by using specific values. For example, dimensions of the rotary compressor
are set as follows: an outer diameter a cylinder 5 is approximately 140 mm, an inner
25 diameter of the cylinder 5 is approximately 70 mm, an outer diameter of a rolling
piston 6 is approximately 45 mm, a length of the vane groove 70 is approximately 30
mm, a height of a vane 7 is approximately 20 mm, the vane spring groove 9 is
approximately 10 mm, and a length of the inclined part 81 is approximately 10 mm.
Typical conditions during cooling operation of the rotary compressor are as follows; a
30 suction pressure and a discharge pressure, which are operating pressures, are
14
approximately 1.0 MPaG and approximately 3.5 MPaG, respectively and an operating
frequency is approximately 120 rps.
[0038]
The PV value based on the above values is 6.56 W/mm2. Therefore, surface
treatment of the vane groove 70 is not needed in the rotary compressor 5 according to
Embodiment 2. Meanwhile, in a conventional rotary compressor, a length of a vane
groove is approximately 20 mm at most, and as a result, the PV value is 9.84 W/mm2.
It is therefore necessary to perform surface treatment on the vane groove.
[0039]
10 As described above, effects similar to those of the rotary compressor according
to Embodiment 1 can also be obtained in the rotary compressor according to
Embodiment 2 in which the vane spring containing hole 80 has the inclined part 81
that connects the side wall of the vane spring containing hole 80 and the side wall of
the vane groove 70 and the vane spring groove 9 is provided so as to extend from the
15 inclined part 81 toward the cylinder chamber 50.
[0040] Embodiment 3.
Next, a rotary compressor according to Embodiment 3 of the present disclosure
is described with reference to Figs. 8 and 9. Fig. 8 is a transverse cross-sectional
view illustrating a substantial part of a compression mechanism unit of the rotary
20 compressor according to Embodiment 3 of the present disclosure. Fig. 9 is a
transverse cross-sectional view illustrating only a cylinder of the compression
mechanism unit illustrated in Fig. 8. Elements identical to those of the rotary
compressor described in Embodiment 1 are given identical reference signs, and
repeated description thereof is omitted as appropriate.
25 [0041]
As illustrated in Figs. 8 and 9, the rotary compressor according to Embodiment
3 is configured such that a vane spring 8 that urges a vane 7 so that a front end of the
vane 7 is pressed against an outer circumferential surface of a rolling piston 6 is
contained in a vane spring groove 90 of a cylinder 5. The vane spring groove 90 is
15
provided around the vane groove 70 so as to extend from an outer circumferential
surface of the cylinder 5 toward a cylinder chamber 50.
[0042]
The cross section taken along line A-A illustrated in Fig. 9 is identical to the
shape of Fig. 4 described in Embodiment 1. That is, the vane spring 5 groove 90 of
the rotary compressor according to Embodiment 3 also has a ring shape
corresponding to a coil shape of the vane spring 8 and partially intersects with the
vane groove 70, which has an elongated shape. With this configuration, the vane
spring 8 can be smoothly contained in the vane spring groove 90. This allows the
10 rotary compressor to improve the function of biasing the vane 7 by using the vane
spring 8 so that the vane 7 follows movement of the rolling piston 6.
[0043]
Note that the vane spring groove 90 has an outer diameter larger than an outer
diameter of the vane spring 8 and an inner diameter smaller than an inner diameter of
15 the vane spring 8 since the vane spring 8 needs to pass through the vane spring
groove 90. The size and shape of the vane spring groove 90 are not limited to the
illustrated ones. The vane spring groove 90 can have any form, provided that the
vane spring 8 contained in the vane spring groove 90 can bias the vane 7 so that the
front end of the vane 7 is pressed against the outer circumferential surface of the
20 rolling piston 6.
[0044]
Therefore, according to the rotary compressor according to Embodiment 3, the
vane 7 can be urged by the vane spring 8 contained in the vane spring groove 90
having a sufficient length so that the vane 7 follows movement of the rolling piston 6.
25 Furthermore, according to this rotary compressor, the vane groove 70 can be
elongated in a radial direction of the cylinder 5 irrespective of a length of the vane
spring groove 90. This can increase a sliding area for sliding of the vane 7 along the
vane groove 70, thereby improving reliability of the rotary compressor.
[0045]
16
Effects of the rotary compressor according to Embodiment 3 are described
below by using specific values. For example, dimensions of the rotary compressor
are set as follows: an outer diameter of the cylinder 5 is approximately 160 mm, an
inner diameter of the cylinder 5 is approximately 70 mm, an outer diameter of the
rolling piston 6 is approximately 45 mm, a length of the 5 vane groove 70 is
approximately 40 mm, a height of the vane 7 is approximately 20 mm, and the vane
spring groove 90 is approximately 20 mm. Typical conditions during heating
operation of the rotary compressor are as follows; a suction pressure and a discharge
pressure, which are operating pressures, are approximately 0.2 MPaG and
10 approximately 4.7 MPaG, respectively and an operating frequency is approximately
120 rps.
[0046]
The PV value based on the above values is 8.85 W/mm2. Therefore, surface
treatment of the vane groove 70 is not needed in the rotary compressor according to
15 Embodiment 3. Meanwhile, in a conventional rotary compressor, a length of a vane
groove is, for example, approximately 20 mm at most, and as a result, the PV value is
17.71 W/mm2. It is therefore necessary to perform surface treatment on the vane
groove 70.
[0047]
20 The present disclosure has been described above based on Embodiments, but
the present disclosure is not limited to the configurations described in Embodiments.
For example, the illustrated internal configurations of the rotary compressor 100 are
merely examples. The internal configuration of the rotary compressor 100 is not
limited to ones described above, and the present disclosure is also applicable to a
25 rotary compressor including other constituent elements. Specifically, the present
disclosure is also applicable, for example, to a twin rotary compressor including two
compression chambers. In short, the present disclosure encompasses design
changes and variations made by a person skilled in the art within the technical idea of
the present disclosure.
30 Reference Signs List
17
[0048]
1 hermetic container 2 electric motor unit 3 compression mechanism
unit 4 crankshaft 5 cylinder 6 rolling piston 7 vane 8 vane spring 9
vane spring groove 10 suction pipe 11 discharge pipe 12 accumulator 20
stator 21 rotor 40 main shaft part 41 sub shaft part 42 5 eccentric shaft
part 50 cylinder chamber 51 upper shaft bearing 52 lower shaft bearing 70
vane groove 80 vane spring containing hole 81 inclined part 90 vane spring
groove 100 rotary compressor
18
We Claim :
[Claim 1]
A rotary compressor comprising:
an electric motor unit; and
a compression mechanism unit that compresses refrigerant 5 by using driving
force transmitted from the electric motor unit,
wherein
the electric motor unit and the compression mechanism unit are provided in a
hermetic container,
10 the compression mechanism unit includes:
a crankshaft that has an eccentric shaft part and is driven to rotate by the
electric motor unit,
a cylinder that is fixed to the hermetic container and has a cylinder
chamber,
15 shaft bearings that are provided at top and bottom ends of the cylinder
and close the cylinder chamber,
a rolling piston that is contained in the cylinder chamber so as to be fitted
with the eccentric shaft part and eccentrically rotates together with the
eccentric shaft part to compress refrigerant,
20 a vane that is provided in a vane groove provided radially in the cylinder
and partitions the cylinder chamber into a suction chamber and a compression
chamber, and
a vane spring that is contained in a vane spring containing hole provided
in the cylinder and urges the vane so that a front end of the vane is pressed
25 against an outer circumferential surface of the rolling piston, and
the cylinder has a vane spring groove that extends the vane spring containing
hole, the vane spring groove being provided around the vane groove so as to extend
from the vane spring containing hole toward the cylinder chamber.
[Claim 2]
30 The rotary compressor of claim 1, wherein
19
the vane spring containing hole has an inclined part that connects a side wall of
the vane spring containing hole and a side wall of the vane groove; and
the vane spring groove is provided so as to extend from the inclined part
toward the cylinder chamber.
5 [Claim 3]
A rotary compressor comprising:
an electric motor unit; and
a compression mechanism unit that compresses refrigerant by using driving
force transmitted from the electric motor unit,
10 wherein
the electric motor unit and the compression mechanism unit are provided in a
hermetic container,
the compression mechanism unit includes:
a crankshaft that has an eccentric shaft part and is driven to rotate by the
15 electric motor unit,
a cylinder that is fixed to the hermetic container and has a cylinder
chamber,
shaft bearings that are provided at top and bottom ends of the cylinder
and close the cylinder chamber,
20 a rolling piston that is contained in the cylinder chamber so as to be fitted
with the eccentric shaft part and eccentrically rotates together with the
eccentric shaft part to compress refrigerant,
a vane that is provided in a vane groove provided radially in the cylinder
and partitions the cylinder chamber into a suction chamber and a compression
25 chamber, and
a vane spring that is contained in a vane spring groove provided in the
cylinder and urges the vane so that a front end of the vane is pressed against
an outer circumferential surface of the rolling piston, and
the vane spring groove is provided around the vane groove so as to extend
30 from an outer circumferential surface of the cylinder toward the cylinder chamber.
[Claim 4]
The rotary compressor of any one of claims 1 through 3, wherein
the vane spring has a coil shape; and
the vane spring groove has a ring shape corresponding to the shape of the
5 vane spring.