1
FORM 2
THE PATENTS ACT, 1970
(39 of 1970)
&
THE PATENTS RULES, 2003
COMPLETE SPECIFICATION
[See section 10, Rule 13]
ROTARY 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
INVENTION AND THE MANNER IN WHICH IT IS TO BE PERFORMED
2
DESCRIPTION
Technical Field
[0001]
The present disclosure relates to a rotary compressor and a refrigeration 5 cycle
apparatus that are used in an air-conditioning apparatus, a refrigerator, a refrigerating
machine, or other devices.
Background Art
[0002]
10 A rotary compressor includes an annular cylinder accommodated in a
hermetically sealed housing, a rolling piston that rotates eccentrically in the cylinder,
and a vane slidably disposed in a vane groove provided in the cylinder. The vane is
urged by a vane spring and constantly contacts with the rolling piston at the distal end
of the vane. The vane partitions the space inside the cylinder into a low-pressure
15 space and a high-pressure space. When the rolling piston eccentrically moves in the
cylinder, the low-pressure space reduces in volume into a high-pressure space, and
refrigerant sucked into the cylinder is compressed.
[0003]
In a hermetically sealed compressor of this type, the vane spring that urges the
20 vane is accommodated in a vane spring insertion hole formed in the cylinder and is
held in the cylinder. With the configuration in which the vane spring is held in the
cylinder in this way, the length of the vane spring is subjected to constraints on a
distance between a rear end-side end surface of the vane and an inner periphery of
the hermetically sealed housing and cannot be elongated any more. For this reason,
25 when the vane is positioned at the rearmost top dead center position of reciprocating
motion, there is a possibility that the overall length of the vane spring reaches a close
contact length that is obtained when the vane spring is fully compressed and a stress
that occurs in the vane spring increases to cause the vane spring to undergo a fatigue
failure.
30 [0004]
3
There is a technology for preventing a fatigue failure due to an excessive stress
on the vane spring by ensuring space for accommodating the vane spring outside the
hermetically sealed housing and eliminating constraints on the length of the vane
spring (see, for example, Patent Literature 1). Patent Literature 1 provides a
configuration in which a cylindrical spring guide in which 5 a vane spring is
accommodated is joined with a cylinder from outside a hermetically sealed housing.
The spring guide includes two slits at an end joined with the cylinder, has two
connecting pieces elastically displaceable in a radial direction, and has a retaining
piece that protrudes outward at the distal end of each of the two connecting pieces.
10 Then, the two connecting pieces of the spring guide are inserted into a spring
insertion hole provided in the cylinder by elastically deforming the two connecting
pieces radially inward, and the retaining pieces engage with a peripheral edge of the
spring insertion hole when passing through the spring insertion hole, thus fixing the
spring guide to the spring insertion hole.
15 Citation List
Patent Literature
[0005]
Patent Literature 1: Japanese Examined Utility Model Registration Application
Publication No. S51-030005
20 Summary of Invention
Technical Problem
[0006]
In the rotary compressor of Patent Literature 1, the spring guide is fixed by
using elastic deformation of the two connecting pieces of the spring guide, and, when
25 the retaining pieces pass through the spring insertion hole, the retaining pieces push
in a direction to expand the width of a vane groove, as a result, the width of the vane
groove may increase. As the width of the vane groove increases, the operation of
the vane may be instable.
[0007]
4
A force in a direction to draw the spring guide from the cylinder acts on the
spring guide by pressure and vibration during compressor operation, collision at the
time when the vane separates from the rolling piston at the time of, for example,
abnormal refrigerant compression or other operations in a compression unit and the
urging force of the vane spring at the time of expansion and contraction 5 when the
vane reciprocates. For this reason, it is desired to provide a configuration in which
the spring guide does not slip off from the cylinder.
[0008]
The present disclosure is contemplated in view of the above-described
10 situation and provides a rotary compressor and a refrigeration cycle apparatus
capable of suppressing deformation of a vane groove and capable of stopping a
spring guide from slipping off from a cylinder.
Solution to Problem
[0009]
15 A rotary compressor according to an embodiment of the present disclosure
includes a hermetically sealed housing; an annular cylinder accommodated in the
hermetically sealed housing; a rolling piston that rotates eccentrically along an inner
periphery of the cylinder; a vane that reciprocates in a vane groove provided in the
cylinder in a radial direction; a vane spring that urges the vane to bring a distal end of
20 the vane into contact with the rolling piston, and a spring guide that has a hollow
cylindrical portion in which the vane spring is fixed; and a fitting protrusion protruding
outward from an outer periphery of one end side of the hollow cylindrical portion.
The cylinder has a cylindrical fitting recess that is open at an outer periphery of the
cylinder and that communicates with the vane groove at its bottom surface. The
25 fitting recess has a retaining piece that retains the fitting protrusion of the spring
guide. The rotary compressor has a configuration in which the fitting protrusion is
engaged with the retaining piece to fix the spring guide to the cylinder by rotating the
spring guide in a state where one end of the spring guide on a side where the fitting
protrusion is formed is inserted and fitted in the fitting recess of the cylinder via an
30 opening formed in the hermetically sealed housing.
5
Advantageous Effects of Invention
[0010]
According to the embodiment of the present disclosure, since the spring guide
is fixed to the cylinder by fitting the fitting protrusion of the spring guide to the fitting
recess of the cylinder, no pressing force acts in a direction to widen 5 the vane groove.
Therefore, it is possible to suppress deformation of the vane groove. Since the
fitting protrusion is engaged with the retaining piece provided in the fitting recess, it is
possible to stop the spring guide from slipping off from the cylinder even when a force
acts in a direction to draw the spring guide from the cylinder.
10 Brief Description of Drawings
[0011]
[Fig. 1] Fig. 1 is a sectional view illustrating a schematic configuration of a
rotary compressor according to Embodiment 1.
[Fig. 2] Fig. 2 is an enlarged cross-sectional view illustrating a compression
15 structural unit in the rotary compressor according to Embodiment 1.
[Fig. 3] Fig. 3 is a perspective view of a spring guide in the rotary compressor
according to Embodiment 1.
[Fig. 4] Fig. 4 is an enlarged view illustrating a joint structure of the spring guide
and a cylinder in the rotary compressor according to Embodiment 1.
20 [Fig. 5] Fig. 5 is a schematic perspective view of the cylinder of the rotary
compressor according to Embodiment 1.
[Fig. 6] Fig. 6 is a view illustrating the cylinder of the rotary compressor
according to Embodiment 1.
[Fig. 7] Fig. 7 is a view illustrating an end surface part split by a vane groove
25 and a fitting recess in the cylinder of the rotary compressor according to Embodiment
1.
[Fig. 8] Fig. 8 is a view illustrating the spring guide of the rotary compressor
according to Embodiment 1.
[Fig. 9] Fig. 9 is a view illustrating Modification 1 of a stopper of the rotary
30 compressor according to Embodiment 1.
6
[Fig. 10] Fig. 10 is a perspective view of the cylinder of Fig. 9.
[Fig. 11] Fig. 11 is a view illustrating Modification 2 of the stopper of the rotary
compressor according to Embodiment 1.
[Fig. 12] Fig. 12 is a diagram illustrating a refrigerant circuit of a refrigeration
cycle apparatus according 5 to Embodiment 2.
Description of Embodiments
[0012]
In Embodiments 1 and 2, a rotary compressor for use in an air-conditioning
apparatus, a refrigerator, a refrigerating machine, or other devices will be described
10 as an example.
[0013]
(Embodiment 1)
Fig. 1 is a sectional view illustrating a schematic configuration of a rotary
compressor according to Embodiment 1. Fig. 2 is an enlarged cross-sectional view
15 illustrating a compression mechanism unit in the rotary compressor according to
Embodiment 1. Fig. 3 is a perspective view of a spring guide in the rotary
compressor according to Embodiment 1. Fig. 4 is an enlarged view illustrating a
joint structure of the spring guide and a cylinder in the rotary compressor according to
Embodiment 1. In the specification, unless otherwise specified, the terms "radial
20 direction", "circumferential direction", and "axial direction" respectively mean the
"radial direction", "circumferential direction", and "axial direction" of the cylinder.
[0014]
A rotary compressor 1 includes an electric unit 25, a compression unit 10 that
compresses refrigerant, and a rotary shaft 17 that transmits the driving force of the
25 electric unit 25 to the compression unit 10 in a hermetically sealed housing 5.
[0015]
As illustrated in Fig. 1, the hermetically sealed housing 5 is a schematically
hollow cylindrical, hermetically sealed housing. The hermetically sealed housing 5 is
formed with a thickness to such an extent that the hermetically sealed housing 5 is
30 not distorted by internal pressure generated by refrigerant compressed in the
7
compression unit 10. By increasing the thickness of the hermetically sealed housing
5, it is possible to reduce the influence of distortion of the hermetically sealed housing
5 caused by heating on the compression unit 10 at the time of mounting the rotary
compressor 1 to an apparatus, such as an air-conditioning apparatus and a
refrigerator, by, for example, 5 arc-spot welding.
[0016]
An accumulator 28 for reducing refrigerant noise is provided adjacent to the
hermetically sealed housing 5 outside the hermetically sealed housing 5. The
accumulator 28 is connected via accumulator pipes 29 to two compression
10 mechanisms (described later) that make up the compression unit 10. A discharge
pipe 16 that discharges refrigerant compressed by the compression unit 10 is
connected to the upper part of the hermetically sealed housing 5. Refrigerating
machine oil for lubricating the compression unit 10 is stored at the bottom of the
hermetically sealed housing 5. POE (polyor ester), PVE (polyvinyl ether), AB
15 (alkylbenzene), or other materials, which are synthetic oils, are used as the
refrigerating machine oil.
[0017]
The electric unit 25 includes a hollow cylindrical stator 26 fixed to the inner
periphery of the hermetically sealed housing 5, and a solid cylindrical rotor 27
20 rotatably disposed on the inner side of the stator 26. The outside diameter of the
stator 26 is greater than the inside diameter of the hermetically sealed housing 5.
The stator 26 is fixed to the inner periphery of the hermetically sealed housing 5 by
shrink fitting. Magnetic poles are formed by permanent magnets on the rotor 27.
The rotor 27 rotates by the action of magnetic fluxes generated by the magnetic poles
25 on the rotor 27 and magnetic fluxes generated by the stator 26.
[0018]
The electric unit 25 and the compression unit 10 are coupled by the rotary shaft
17. The rotation of the electric unit 25 is transmitted to the compression unit 10, and
the compression unit 10 compresses refrigerant by using the transmitted rotational
30 force. Refrigerant compressed by the compression unit 10 is released into the
8
hermetically sealed housing 5 via a discharge hole 21 (see Fig. 2) provided in the
compression unit 10. Therefore, the inside of the hermetically sealed housing 5 is
filled with high-temperature and high-pressure compressed refrigerant gas.
[0019]
The compression unit 10 includes the two compression mechanisms 5 arranged
in the axial direction of the rotary shaft 17, an upper bearing 18, a lower bearing 19,
and an intermediate plate 12. In other words, the compression unit 10 is of a multicylinder
type including two compression mechanisms. The rotary compressor 1 is
not limited to a multi-cylinder type including a plurality of compression mechanisms
10 and may be of a single cylinder type including one compression mechanism.
[0020]
Since the compression mechanisms are similarly configured, only one of the
compression mechanisms will be described for the sake of convenience. As
illustrated in Fig. 2, the compression mechanism includes a cylinder 11, a rolling
15 piston 13, a vane 14, a vane spring 15, and a spring guide 30 in which the vane
spring 15 is fixed.
[0021]
The cylinder 11 is made up of an annular plate. A cylinder chamber 11a in the
cylinder 11 is open at both ends in the axial direction, and the openings are closed by
20 the intermediate plate 12 and one of the upper bearing 18 and the lower bearing 19.
As illustrated in Figs. 2 and 4, the cylinder 11 has a suction port 20 that extends
through in the radial direction, and a discharge hole 21 formed on an inner periphery
11b of the cylinder 11. The accumulator pipe 29 of the accumulator 28 is connected
to the suction port 20.
25 [0022]
As illustrated in Fig. 2, the rolling piston 13 is accommodated in the cylinder
chamber 11a of the cylinder 11 in a state where the rolling piston 13 is rotatably fitted
to an eccentric portion 17a of the rotary shaft 17. The rolling piston 13 rotates
eccentrically along the inner periphery 11b of the cylinder 11.
30 [0023]
9
The cylinder 11 has a vane groove 22 that communicates with the cylinder
chamber 11a and that extends in the radial direction. The vane 14 is disposed in the
vane groove 22 such that the vane 14 is able to advance and retract in the radial
direction. The vane spring 15 is disposed on the back 14b of the vane 14. An
accommodation recess in which an end of the vane spring 15 5 is accommodated is
formed at the back 14b of the vane 14. Fig. 2 shows a section at the
accommodation recess. An end of the vane spring 15 is fixed to the bottom surface
of the accommodation recess.
[0024]
10 The vane spring 15 urges the vane 14 to bring the distal end 14a of the vane
14 into contact with the rolling piston 13. The vane 14 is pressed radially inward by
the urging force of the vane spring 15, so the distal end 14a of the vane 14 is
constantly in contact with the rolling piston 13. Since the distal end 14a of the vane
14 is in contact with the rolling piston 13 in this way, the inside of the cylinder
15 chamber 11a is partitioned into a low-pressure space and a high-pressure space. As
the rolling piston 13 rotates eccentrically in the cylinder chamber 11a, the vane 14
reciprocates in the vane groove 22 while the distal end 14a is in contact with the outer
periphery 13c of the rolling piston 13.
[0025]
20 The vane spring 15 is a coil spring formed by winding a wire rod made of a
metal or other materials in a coil shape. The vane spring 15 has an expansion and
contraction portion 15a that expands and contracts following the motion of the vane
14, and a non-expansion and contraction portion 15b that is provided at an end of the
expansion and contraction portion 15a in an expansion and contraction direction and
25 that does not expand or contract. The non-expansion and contraction portion 15b is
made up of a wire rod wound so as to be greater in diameter than the expansion and
contraction portion 15a and does not expand or contract by the close contact of the
wire rods.
[0026]
10
The vane spring 15 is fixed in the cylindrical spring guide 30 at the nonexpansion
and contraction portion 15b. The outside diameter of the non-expansion
and contraction portion 15b is greater than the inside diameter of the spring guide 30.
The diameter of the non-expansion and contraction portion 15b is reduced by pressfitting
the non-expansion and contraction portion 15b into the spring 5 guide 30, and the
vane spring 15 is fixed in the spring guide 30 by restoring force for restoring the
diameter. Fixing of the vane spring 15 to the spring guide 30 is not limited to this
fixing method and may be the following method.
[0027]
10 The vane spring 15 may be fixed to the spring guide 30 by providing a
circumferential groove on the inner periphery of the spring guide 30 and fitting the
non-expansion and contraction portion 15b into the circumferential groove.
Alternatively, the vane spring 15 may be fixed to the spring guide 30 by providing a
spiral groove that matches the wire diameter of the vane spring 15 on the inner
15 periphery of the spring guide 30 and fitting the non-expansion and contraction portion
15b of the vane spring 15 into the spiral groove. When the number of turns of the
non-expansion and contraction portion 15b of the vane spring 15 is one, the following
manner may be adopted. The vane spring 15 is fixed to the spring guide 30 by
providing one-turn groove that matches the wire diameter of the vane spring 15 on
20 the inner periphery of the spring guide 30 and fitting the non-expansion and
contraction portion 15b of the vane spring 15 into the one-turn groove.
[0028]
The spring guide 30 is made of an iron material. The spring guide 30 is not
limited to a high-strength material, such as an iron material, and may be made of a
25 low-strength material, such as a resin. One end 30a of the spring guide 30 is fitted
to the cylinder 11, and the other end 30b of the spring guide 30 protrudes outward of
the hermetically sealed housing 5 through an opening 8 provided in the hermetically
sealed housing 5.
[0029]
11
The spring guide 30 includes a hollow cylindrical portion 31 and fitting
protrusions 32 protruding outward from the outer periphery of one end side of the
hollow cylindrical portion 31, as illustrated in Fig. 3. The vane spring 15 is fixed in
the hollow cylindrical portion 31. The fitting protrusions 32 each are a circular arc
protrusion along the outer periphery of the hollow cylindrical portion 5 31. The two
fitting protrusions 32 are formed symmetrically with respect to the central axis of the
spring guide 30. The fitting protrusions 32 are used to be fitted to a fitting recess 40
(described later) provided in the cylinder 11. The spring guide 30 has one end 30a
side inserted in the hermetically sealed housing 5 via the opening 8 provided in the
10 hermetically sealed housing 5, and has the fitting protrusions 32 inserted and fitted to
the fitting recess 40 provided in the cylinder 11. The details of a structure of fitting
the spring guide 30 to the cylinder 11 will be described later.
[0030]
Vane passage portions 31a are formed at one end side of the hollow cylindrical
15 portion 31. The vane passage portions 31a each are a slit extending from one end
of the hollow cylindrical portion 31 in the axial direction of the hollow cylindrical
portion 31, and the two vane passage portions 31a are formed symmetrically with
respect to the central axis of the hollow cylindrical portion 31. The vane passage
portions 31a are located in an extension line of the vane groove 22 in the radial
20 direction in a state where the spring guide 30 is fixed to the cylinder 11 as illustrated
in Fig. 4, and the vane 14 reciprocates in the vane passage portions 31a.
[0031]
Here, the dimensions of the spring guide 30 will be described. The diameter
D1 of the hollow cylindrical portion 31 is less than the axial length (the length in a
25 direction orthogonal to the drawing sheet of Fig. 4) of the vane 14. The width W1 of
each of the vane passage portions 31a in the radial direction is greater than the width
of the vane 14 in the same direction. Thus, the vane 14 passes through the vane
groove 22, then enters the vane passage portions 31a without contacting with the
vane passage portions 31a, and reciprocates.
30 [0032]
12
The amount of projection L1 of the spring guide 30 from the outer periphery 11c
of the cylinder 11 is set within the following range. The amount of projection L1 is set
so as to be greater than a first length and less than or equal to a second length. The
first length is a length obtained by adding up "the distance between the back 14b of
the vane 14 and the outer periphery 11c of the cylinder 11 when the 5 vane 14 is moved
rearward to the top dead center position" and "the close contact length of the vane
spring 15". The second length is a length obtained by adding up "the overall length
of the vane 14" and "the overall length of the vane spring 15 in a natural state". The
close contact length of the vane spring 15 is a length in a state where the vane spring
10 15 fully contracts and the wire rods closely contact with each other.
[0033]
The spring guide 30 to which the vane spring 15 is fixed is disposed in a
protruded portion 6 provided so as to protrude outward of the hermetically sealed
housing 5. The protruded portion 6 is a cylindrical member of which the sectional
15 shape is a circular, rectangular, or oblong shape. As illustrated in Fig. 2, the
protruded portion 6 is mounted in the opening 8 formed in the hermetically sealed
housing 5 such that the central axis of the protruded portion 6 is orthogonal to the
central axis of the cylinder 11. The protruded portion 6 is fixed to the hermetically
sealed housing 5 by press-fitting the end of the protruded portion 6 to the opening 8
20 formed in the hermetically sealed housing 5.
[0034]
A lid portion 7 is attached to an end (hereinafter, referred to as outer-side end)
of the protruded portion 6 across from the side fixed to the hermetically sealed
housing 5. The lid portion 7 is a lid that closes the outer-side end of the protruded
25 portion 6. The lid portion 7 is joined with the outer-side end of the protruded portion
6 by, for example, welding, brazing, or other methods. When the outer-side end of
the protruded portion 6 is closed by the lid portion 7, the protruded portion 6 is
hermetically sealed, and the hermetically sealed housing 5 is hermetically sealed.
[0035]
13
In Embodiment 1, the vane spring 15 is fixed to the spring guide 30 and then
fixed to the cylinder 11. The outside diameter of the hollow cylindrical portion 31 of
the spring guide 30 is less than the inside diameter of the opening 8 of the
hermetically sealed housing 5, and the spring guide 30 is fixed to the cylinder 11
without contacting with the hermetically sealed housing 5. Here, if 5 the spring guide
30 is not provided and the end of the vane spring 15 is fixed to the lid portion 7, it is
not possible to accurately install the vane spring 15. The shell of the rotary
compressor 1 is made up of the hermetically sealed housing 5, the protruded portion
6, and the lid portion 7, and internal pressure generated by refrigerant discharged
10 from the compression unit 10 is applied to these shell parts. The shell parts change
their shapes, such as bulging outward under the influence of the internal pressure.
For this reason, in the case of a structure in which the vane spring 15 is fixed to the
shell parts, the vane spring 15 is not able to be disposed at an intended location, that
is, a location along a direction orthogonal to the central axis of the cylinder 11, under
15 the influence of deformation of the shell parts due to the internal pressure.
[0036]
In contrast, in Embodiment 1, the vane spring 15 is fixed to the spring guide 30
that is a part different from the shell parts, and the spring guide 30 is fixed to the
cylinder 11. Therefore, it is possible to accurately install the vane spring 15, so it is
20 possible to stably operate the vane spring 15.
[0037]
(Operation of Rotary Compressor)
Next, the operation of the rotary compressor of Embodiment 1 will be
described. When electric power is supplied to the electric unit 25, the rotary shaft 17
25 is rotated by the electric unit 25. As the rotary shaft 17 rotates, the eccentric portion
17a rotates eccentrically in the cylinder chamber 11a. With the eccentric rotation
motion of the eccentric portion 17a, the rolling piston 13 rotates eccentrically in the
cylinder chamber 11a, and low-pressure gaseous refrigerant introduced from the
accumulator pipe 29 of the accumulator 28 into the cylinder chamber 11a is
30 compressed. When the gaseous refrigerant compressed in the cylinder chamber
14
11a reaches a predetermined pressure, the gaseous refrigerant is discharged through
the discharge hole 21 to the internal space of the hermetically sealed housing 5.
Then, the high-pressure gaseous refrigerant discharged to the internal space of the
hermetically sealed housing 5 is discharged outside the hermetically sealed housing 5
through the discharge pipe 16 provided in the hermetically 5 sealed housing 5.
[0038]
Here, the vane 14 reciprocates in the vane groove 22 with the rotation of the
rolling piston 13. As illustrated in Fig. 2, when the contact location of the outer
periphery 13c of the rolling piston 13 with the inner periphery 11b of the cylinder 11
10 coincides in phase with the disposition location of the vane 14 (hereinafter, referred to
as when the rolling piston 13 is at a vane groove phase location), the vane 14 is
moved rearward, that is, in a direction away from the cylinder 11, and is at a top dead
center position. When the contact location of the outer periphery 13c of the rolling
piston 13 with the inner periphery 11b of the cylinder 11 is different in phase by 180
15 degrees from the disposition location of the vane 14, the vane 14 is moved forward,
that is, in a direction to approach the center of the cylinder 11, and is at a bottom
dead center position. In this way, the vane 14 reciprocates between the top dead
center position and the bottom dead center position. When the rolling piston 13 is at
a location rotated in phase by 90 degrees from the location of Fig. 2, the vane 14 is at
20 an intermediate position between the top dead center position and the bottom dead
center position.
[0039]
In this way, the range of reciprocation of the vane 14 is between the top dead
center position and the bottom dead center position, and the positions of the vane 14
25 with respect to the vane passage portions 31a of the spring guide 30 at the time when
the vane 14 is at the top dead center position, the bottom dead center position, and
the intermediate position are as follows.
[0040]
When the vane 14 is at the top dead center position illustrated in Fig. 2, the
30 back 14b of the vane 14 is located in the vane passage portions 31a of the spring
15
guide 30. When the vane 14 is at the bottom dead center position, the back 14b of
the vane 14 is not located in the vane passage portions 31a of the spring guide 30.
When the vane 14 is at the intermediate position, the back 14b of the vane 14 is not
located in the vane passage portions 31a of the spring guide 30. The reason for the
above configuration is due to convenience during manufacturing, and 5 this point will be
described later.
[0041]
During the operation of the rotary compressor 1, a so-called backflow of liquid,
that is, liquid refrigerant flows into the hermetically sealed housing 5, can occur. In
10 the event of backflow of liquid, the internal pressure of the cylinder chamber 11a
rapidly increases, so the vane 14 is pushed radially outward. In this case, the vane
14 is moved radially outward beyond the top dead center position and stops at a
location where the back 14b of the vane 14 contacts with the bottom surfaces 31ab of
the vane passage portions 31a of the spring guide 30. In other words, the bottom
15 surfaces 31ab of the vane passage portions 31a function as a stopper for the vane 14
in the event of backflow of liquid. The radial locations of the bottom surfaces 31ab of
the vane passage portions 31a are set such that the length of the vane spring 15
does not become a close contact length in a state where the back 14b of the vane 14
contacts with the bottom surfaces 31ab of the vane passage portions 31a. For this
20 reason, in the event of backflow of liquid or other events, no excessive pressure acts
on the vane spring 15 at the time when the internal pressure of the cylinder chamber
11a rapidly increases.
[0042]
The rotary compressor 1 of Embodiment 1 has a structure in which the
25 protruded portion 6 is mounted so as to protrude outward of the hermetically sealed
housing 5. For this reason, in a sense, the structure is such that the shell of the
rotary compressor 1 is enlarged in the radial direction for an installation part of the
vane spring 15. Therefore, there are no constraint on the distance between the back
14b of the vane 14 and the inner periphery of the hermetically sealed housing 5, and
30 the overall length of the vane spring 15 can be freely set. The length of the vane
16
spring 15 can be freely set by adjusting the length of the protruded portion 6. For
this reason, the rate of expansion and contraction of the vane spring 15 can be
reduced by extending the overall length of the vane spring 15. Since the rate of
expansion and contraction of the vane spring 15 can be reduced, a fatigue strength
against a stress that repeatedly acts in the vane spring 15 can be sufficiently 5 ensured
as compared to when a spring with a high rate of expansion and contraction is used.
Thus, it is possible to increase an urging force to press the vane 14 against the rolling
piston 13 while ensuring a fatigue strength.
[0043]
10 Here, if the urging force of the vane spring 15 cannot be increased and a force
pressing the vane 14 against the rolling piston 13 is not sufficient, the vane 14 is not
able to follow the motion of the rolling piston 13 when the vane 14 is at the bottom
dead center position. In other words, the distal end 14a of the vane 14 separates
from the rolling piston 13. In this case, noise and vibration occur.
15 [0044]
In contrast, in Embodiment 1, since the overall length of the vane spring 15 can
be freely set as described above, a sufficient fatigue strength can be ensured by
extending the overall length of the vane spring 15 to thereby reduce the rate of
expansion and contraction of the vane spring 15. Therefore, it is possible to obtain a
20 necessary urging force to constantly press the vane 14 against the rolling piston 13
while ensuring a sufficient fatigue strength, so it is possible to suppress noise and
vibration that occur when the vane 14 separates from the rolling piston 13.
[0045]
In Embodiment 1, it is possible to freely set the distance between the lid portion
25 7 and the spring guide 30 by adjusting the length of the protruded portion 6, and the
following advantageous effects are obtained. When the distance between the lid
portion 7 and the spring guide 30 is short, there is a possibility that heat generated at
the time of joining the lid portion 7 to the protruded portion 6 by welding, brazing, or
other methods is conducted to the vane spring 15 via the lid portion 7 and, as a result,
30 the characteristics of the vane spring 15 deteriorate. In contrast, in Embodiment 1, it
17
is possible to freely set the distance between the lid portion 7 and the spring guide 30,
so it is possible to prevent deterioration of the characteristics of the vane spring 15
due to heat conducted to the vane spring 15 during joining by sufficiently ensuring the
distance.
5 [0046]
Incidentally, when retaining pieces provided on the spring guide pass through a
spring insertion hole provided in a cylinder, a spring guide of an existing rotary
compressor can deform in a direction in which the width of a vane groove increases
by being pressed in a direction to increase the width of the vane groove by elastic
10 force.
[0047]
Therefore, in the rotary compressor 1 of Embodiment 1, deformation to
increase the width of the vane groove 22 is stopped by fixing the spring guide 30 to
the cylinder 11 with a fitting method that will be described below. Hereinafter, a
15 structure of fitting the spring guide 30 to the cylinder 11 will be described.
[0048]
Fig. 5 is a schematic perspective view of the cylinder of the rotary compressor
according to Embodiment 1. Fig. 6 is a view illustrating the cylinder of the rotary
compressor according to Embodiment 1, in which (a) is a front view, and (b) is a
20 sectional view taken along the line A-A in (a). Fig. 7 is a view illustrating an end
surface part split by the vane groove and the fitting recess in the cylinder of the rotary
compressor according to Embodiment 1. Fig. 8 is a view illustrating the spring guide
of the rotary compressor according to Embodiment 1, in which (a) is a front view of an
end of the spring guide on an insertion side, and (b) is a sectional view of the spring
25 guide, taken along a plane including the central axis of the spring guide.
[0049]
The cylinder 11 has the cylindrical fitting recess 40 that is open at the outer
periphery 11c and to which the spring guide 30 is fitted as illustrated in Fig. 5. The
fitting recess 40 is formed so as to extend radially inward from the outer periphery 11c
30 of the cylinder 11 and communicates with the vane groove 22 at the bottom surface
18
44 of the fitting recess 40. The fitting recess 40 has a vane extension groove 45
extended radially outward from the vane groove 22 and is split into two split recesses
40a by the vane extension groove 45.
[0050]
A circular arc retaining piece 41 protruding inward of the fitting 5 recess 40 is
formed at the radially outer end of each of the split recesses 40a of the fitting recess
40. The retaining pieces 41 are formed symmetrically with respect to the central axis
of the fitting recess 40. A part where the retaining piece 41 is not formed in the
radially outer end of the fitting recess 40 is a passage portion 42 through which the
10 fitting protrusion 32 of the spring guide 30 passes when the spring guide 30 is fitted to
the fitting recess 40.
[0051]
A stopper 43 that contacts with the fitting protrusion 32 of the spring guide 30 to
stop rotation of the spring guide 30 is provided radially inward (hereinafter, referred to
15 as deep side in the insertion direction) of the retaining piece 41 of each of the split
recesses 40a of the fitting recess 40. The stopper 43 is to prevent rotation of the
spring guide 30 due to vibration or pressure generated during operation or impact
force in the event of a collision of the vane 14 with the spring guide 30. The stopper
43 also plays a role in positioning the spring guide 30. The stopper 43 is made up of
20 a protrusion that protrudes from the inner periphery of the split recess 40a.
[0052]
In the above configuration, at the time of fitting the spring guide 30 to the
cylinder 11, one end 30a of the spring guide 30 is inserted from outside the
hermetically sealed housing 5 into the fitting recess 40 via the opening 8. At this
25 time, one end 30a of the spring guide 30 is inserted such that the fitting protrusions
32 pass through the passage portions 42 formed at the fitting recess 40. Then, the
spring guide 30 is rotated in a counterclockwise direction in a state where one end
30a of the spring guide 30 is brought into contact with the bottom surface 44 of the
fitting recess 40. Thus, the fitting protrusions 32 are engaged with the retaining
30 pieces 41. In other words, the fitting protrusions 32 enter the deep side beyond the
19
retaining pieces 41 in the insertion direction and are engaged. Then, in this state,
the spring guide 30 is rotated until the fitting protrusions 32 contact with the stoppers
43. As a result, the spring guide 30 is fitted to the cylinder 11.
[0053]
Here, "the outside diameter 1 of the hollow cylindrical portion 5 31 of the spring
guide 30 and the inside diameter 2 of a circle passing through the circular arc inner
periphery of each retaining piece 41" or "the outside diameter 3 of a circle passing
through the outer periphery of each of the fitting protrusions 32 of the spring guide 30
and the inside diameter 4 of the fitting recess 40 of the cylinder 11" are configured to
10 substantially coincide with each other. Thus, the spring guide 30 is lightly pressfitted
to the cylinder 11, and the spring guide 30 is positioned.
[0054]
In a state where the spring guide 30 is fitted to the cylinder 11, the fitting
protrusions 32 are engaged with the retaining pieces 41. For this reason, when a
15 force acts in a direction to draw the spring guide 30 from the cylinder 11, the spring
guide 30 gets caught by the retaining pieces 41, so it is possible to prevent the spring
guide 30 from slipping off from the cylinder 11.
[0055]
The spring guide 30 needs to be attached to the cylinder 11 such that the vane
20 passage portions 31a and the vane groove 22 are in the same phase to not interfere
with reciprocation of the vane 14. In other words, the vane passage portions 31a
need to be positioned so as to be in the extension line of the vane groove 22. In
Embodiment 1, a positional relationship among the portions is set such that the
above-described positioning is performed by rotating the spring guide 30 until the
25 fitting protrusions 32 contact with the stoppers 43. Thus, at the time of fitting the
spring guide 30, it is possible to prevent the spring guide 30 from being excessively
rotated to cause the fitting protrusions 32 of the spring guide 30 to enter the vane
groove 22 and to interfere with reciprocation of the vane 14.
[0056]
20
The above-described fitting and fixing structure is a joining method that does
not use elastic force unlike the existing art, so it is possible to reduce the amount of
deformation of the vane groove 22 as compared to the existing art.
[0057]
Here, the dimensions in the structure of fixing the spring 5 guide 30 to the
cylinder 11 will be further described in detail.
[0058]
The depth L2 (see Fig. 7) of the fitting recess 40 of the cylinder 11 is shorter the
better because of the following reason. As the depth L2 of the fitting recess 40
10 extends, the length of the vane groove 22 in the same direction, that is, the length of
a part that is in sliding contact with the vane 14, shortens by that amount, and seizure
more easily occurs at the time when the vane 14 slides in the vane groove 22 at high
speed. For this reason, the depth L2 of the fitting recess 40 is shorter the better and
may be less than or equal to about a quarter of the radial width L3 (see Fig. 5) of the
15 cylinder 11.
[0059]
The radial length L4 (see Fig. 7) of the stopper 43 of the cylinder 11 may be
equal to or shorter than the length L5 from the end surface 41a of the retaining piece
41 on the deep side in the insertion direction to the bottom surface 44 of the fitting
20 recess 40.
[0060]
The circumferential length (see Fig. 6) of the stopper 43 is up to a length
obtained by subtracting the circumferential length L6 (see Fig. 8) of the fitting
protrusion 32 of the spring guide 30 from the circumferential length of the split recess
25 40a. This is because, when the circumferential length of the stopper 43 is longer
than that length, the fitting protrusions 32 are located in the vane extension groove 45
and interfere with reciprocation of the vane 14 in a state where the spring guide 30 is
fitted to the fitting recess 40. Similarly, the circumferential length L6 (see Fig. 8) of
the fitting protrusion 32 of the spring guide 30 is up to a length obtained by
21
subtracting the circumferential length of the stopper 43 from the circumferential length
of the inner periphery 40b of the split recess 40a.
[0061]
When the circumferential length L6 of the fitting protrusion 32 is set to the
maximum length, the length of fitting of the fitting protrusions 32 to 5 the fitting recess
40 extends, so it is possible to increase the effect of suppressing rotation from friction
between the fitting protrusions 32 and the fitting recess 40 and the stiffness of the
fitting protrusions 32. On the other hand, when the circumferential length L6 of the
fitting protrusion 32 is too short, it is not possible to ensure the effect of suppressing
10 rotation or sufficient stiffness of the fitting protrusions 32. For this reason, the
circumferential length L6 of the fitting protrusion 32 is desirably about a half of the
circumferential length of the inner periphery of the split recess 40a. Similarly, for the
retaining pieces 41, the circumferential length of the retaining piece 41 is desirably
about a half of the circumferential length of the inner periphery of the split recess 40a.
15 [0062]
The length L8 (see Fig. 8) of the fitting protrusion 32 of the spring guide 30 in
the insertion direction and the length L9 (see Fig. 7) of the retaining piece 41 in the
insertion direction each are desirably about a half of the depth L2 of the fitting recess
40 of the cylinder 11 to ensure the stiffness.
20 [0063]
The outside diameter 3 of a circle passing through the outer peripheries of the
fitting protrusions 32 of the spring guide 30 is less than or equal to the axial length L7
(see Fig. 5) of the cylinder 11.
[0064]
25 Next, a procedure of assembling a relevant part of the rotary compressor 1 will
be described. Initially, a unit product that is a combination of the upper bearing 18,
the two cylinders 11, the intermediate plate 12, the lower bearing 19, and the rotary
shaft 17 that includes the two rolling pistons 13 is fixed in the hermetically sealed
housing 5 with which the protruded portion 6 is joined. Each of the cylinders 11 is
30 fixed to the hermetically sealed housing 5 in position in which the fitting recess 40
22
faces the opening 8 of the hermetically sealed housing 5. Then, the vane 14 is
inserted from the opening end of the protruded portion 6 into the vane groove 22 of
one of the two cylinders 11 fixed to the hermetically sealed housing 5. Subsequently,
the spring guide 30 is inserted from the opening end of the protruded portion 6, and
one end 30a is fitted to the fitting recess 40 of the cylinder 11 as 5 described above.
Then, the vane spring 15 is inserted and fixed in the spring guide 30. For the other
one of the cylinders 11, the vane 14, the spring guide 30, and the vane spring 15 are
similarly fixed. Then, the lid portion 7 is joined with the protruded portion 6.
[0065]
10 In the assembling procedure, the spring guide 30 is mounted to the cylinder 11
and then the vane spring 15 is fixed to the spring guide 30; however, the order may
be reversed. In other words, the vane spring 15 may be fixed to the spring guide 30
and then the spring guide 30 to which the vane spring 15 is fixed may be mounted to
the cylinder 11.
15 [0066]
Here, if the spring guide 30 is not provided and one end of the vane spring 15
is fixed to the back 14b of the vane 14 and the other end is brought into contact with
the lid portion 7 to thereby hold the vane spring 15 in the protruded portion 6, it is
necessary to join the lid portion 7 with the protruded portion 6 while pressing and
20 holding the other end of the vane spring 15. In contrast, in Embodiment 1, at the
time when the lid portion 7 is joined with the protruded portion 6, the vane spring 15 is
fixed to the spring guide 30 joined with the cylinder 11, so it is not necessary to press
and hold the vane spring 15. Therefore, assembly is easy.
[0067]
25 At the time when the vane spring 15 is fixed to the spring guide 30, the rolling
piston 13 is positioned at the vane groove phase location by rotating the rotary shaft
17, and the vane 14 is positioned at the bottom dead center position. Thus, as
compared to, for example, when the vane 14 is at the top dead center position, the
vane spring 15 can be installed in a state where the length of the vane spring 15 is
23
long, that is, a state where a spring force that acts on the vane spring 15 is small, so
assembly is easy.
[0068]
The rolling piston 13 in one of the cylinders 11 and the rolling piston 13 in the
other one of the cylinders 11 are shifted in phase by 180 degrees. 5 For this reason,
when the rolling piston 13 in one of the cylinders 11 is at the vane groove phase
location, the rolling piston 13 in the other one of the cylinders 11 is at a location
shifted in phase by 180 degrees from the vane groove phase location. Therefore, at
the time when the vane spring 15 is inserted in one of the cylinders 11, initially, the
10 rolling piston 13 is positioned at a location shifted in phase by 180 degrees from the
vane groove phase location, the vane 14 is positioned at the bottom dead center
position, and then the vane spring 15 is inserted. Then, at the time when the vane
spring 15 is inserted in the other one of the cylinders 11, the rotary shaft 17 is rotated
by 180 degrees, the rolling piston 13 is similarly positioned at a location shifted in
15 phase by 180 degrees from the vane groove phase location, the vane 14 is positioned
at the bottom dead center position, and then the vane spring 15 is inserted.
[0069]
When the spring guide 30 is fixed to the cylinder 11, the spring guide 30 is
rotated in a state where one end 30a of the spring guide 30 is inserted in the fitting
20 recess 40, as described above. For this reason, at the time when the spring guide
30 is rotated, if the back 14b of the vane 14 is located in the vane passage portions
31a of the spring guide 30, the spring guide 30 cannot be rotated. For this reason, in
a state where the vane 14 is positioned such that the back 14b of the vane 14 is not
located in the vane passage portions 31a, operation to rotate the spring guide 30 is
25 performed. Specifically, for example, the vane 14 is positioned at the bottom dead
center position or the above-described intermediate position. The reason why the
back 14b of the vane 14 is not located in the vane passage portions 31a at the time
when the vane 14 is at the bottom dead center position or the intermediate position is
to not interfere with the rotation of the spring guide 30 at the time when the spring
30 guide 30 is fixed by screw fixing in this way.
24
[0070]
In the above description, the spring guide 30 is fixed to the cylinder 11 by fitting.
Alternatively, to obtain further strong fixation, an adhesive agent may be further used
for fixing or the cylinder 11 and the spring guide 30 may be welded. Any one of the
methods is performed on the assumption that the vane groove 5 22 does not deform
due to application of excessive stress load on the vane groove 22 of the cylinder 11.
[0071]
The rotary compressor 1 of Embodiment 1 is not limited to the above structure
and may be modified without departing from the scope of the present disclosure.
10 For example, it is applicable as long as the stoppers 43 are capable of stopping
rotation of the spring guide 30 by contacting with the fitting protrusions 32 of the
spring guide 30, and the following Modifications 1 to 3 may be adopted.
[0072]
(Modification 1)
15 Fig. 9 is a view illustrating Modification 1 of the stopper of the rotary
compressor according to Embodiment 1 and is a front view of a state where the
spring guide is fixed to the cylinder. To easily distinguish the spring guide 30 and the
cylinder 11 from each other in Fig. 9, the spring guide 30 is hatched by dots. Fig. 10
is a perspective view of the cylinder of Fig. 9.
20 [0073]
A stopper 43A of Modification 1 is made up of a rod-shaped pin 50. The pin
50 is inserted in a pin insertion hole 51 formed in the cylinder 11, and a distal end 50a
contacts with the side of the fitting protrusion 32. In this way, the pin 50 contacts with
the side of the fitting protrusion 32 to stop rotation of the spring guide 30. In this
25 example, it is possible to stop rotation of the spring guide 30 in a counterclockwise
direction.
[0074]
The configuration of the stopper 43 illustrated in Figs. 9 and 10 may be
combined with the configuration of Modification 1. In other words, a configuration in
30 which a protrusion that makes up the stopper 43 is provided on one of the split
25
recesses 40a of the fitting recess 40, different from the one on which the pin 50 is
inserted, may be provided in addition to the configuration illustrated in Figs. 9 and 10.
[0075]
(Modification 2)
Fig. 11 is a view illustrating Modification 2 of the stopper 5 of the rotary
compressor according to Embodiment 1. Fig. 11 shows an end surface part split by
the vane groove 22 and the fitting recess 40 in the cylinder 11.
A stopper 43B of Modification 2 is made up of a sheet-shaped elastic body 60.
The elastic body 60 is used by being inserted in a gap formed on the front and rear
10 sides of the fitting protrusion 32 in the insertion direction in a state where the fitting
protrusion 32 of the spring guide 30 is fitted to the fitting recess 40 of the cylinder 11.
The elastic body 60 can be bonded to the surface of the retaining piece 41 on the
deep side in the insertion direction or the bottom surface 44 of the fitting recess 40.
Fig. 11 shows an example in which the elastic body 60 is bonded to the surface of the
15 retaining piece 41 on the deep side in the insertion direction.
[0076]
The elastic body 60 is disposed in the gap between the front surface of the
fitting protrusion 32 of the spring guide 30 in the insertion direction and the bottom
surface 44 of the fitting recess 40 of the cylinder 11 or the gap between the rear
20 surface of the fitting protrusion 32 of the spring guide 30 in the insertion direction and
the retaining piece 41 of the cylinder 11. The elastic body 60 is thicker than the gap.
[0077]
When the elastic body 60 is inserted so as to fill the gap formed on the front
side of the fitting protrusion 32 in the insertion direction, the fitting protrusion 32 is
25 pushed by the retaining piece 41, so it is possible to stop rotation of the spring guide
30. When the elastic body 60 is inserted so as to fill the gap formed on the rear side
of the fitting protrusion 32 in the insertion direction, the fitting protrusion 32 is pushed
by the bottom surface 44 of the fitting recess 40, so it is possible to stop rotation of
the spring guide 30.
30 [0078]
26
(Modification 3)
The stopper may be made up of a combination of the stopper illustrated in Fig.
5 and other drawings and the stoppers illustrated in Modifications 1 and 2 as needed.
[0079]
As described above, the rotary compressor 1 of Embodiment 5 1 includes the
hermetically sealed housing 5, the annular cylinder 11 accommodated in the
hermetically sealed housing 5, the rolling piston 13 that rotates eccentrically along the
inner periphery of the cylinder 11, and the vane 14 that reciprocates in the vane
groove 22 provided in the cylinder 11 in the radial direction. The rotary compressor 1
10 further includes the vane spring 15 that urges the vane 14 to bring the distal end 14a
of the vane 14 into contact with the rolling piston 13. The rotary compressor 1
further includes the spring guide 30 that has the hollow cylindrical portion 31 in which
the vane spring 15 is fixed, and the fitting protrusions 32 protruding outward from the
outer periphery of one end side of the hollow cylindrical portion 31. The cylinder 11
15 has the cylindrical fitting recess 40 that is open at the outer periphery 11c of the
cylinder 11 and that communicates with the vane groove 22 at its bottom surface 44.
The fitting recess 40 has the retaining pieces 41 that retain the fitting protrusions of
the spring guide 30. The fitting protrusions 32 are engaged with the retaining pieces
and the spring guide 30 is fixed to the cylinder 11 so as not to slip off from the fitting
20 recess 40 by rotating the spring guide 30 in a state where one end of the spring guide
30 on the side where the fitting protrusions 32 are formed is inserted and fitted to the
fitting recess 40 of the cylinder 11 via the opening formed in the hermetically sealed
housing 5.
[0080]
25 In this way, since the spring guide 30 is fixed to the cylinder 11 by fitting the
fitting protrusions 32 of the spring guide 30 to the fitting recess 40 of the cylinder 11,
no pressing force in a direction to widen the vane groove 22 is applied unlike the
existing fixing structure using elastic deformation. For this reason, it is possible to
suppress deformation of the vane groove 22, so it is possible to stably operate the
30 vane 14. Since the fitting protrusions 32 are engaged with the retaining pieces 41
27
provided in the fitting recess 40, it is possible to stop the spring guide 30 from slipping
off from the cylinder 11 even when a force acts in a direction to draw the spring guide
30 from the cylinder 11 during operation.
[0081]
The retaining piece 41 has a shape protruding inward from the 5 outer end, in the
radial direction, of the fitting recess 40 of the spring guide 30.
[0082]
In this way, the retaining piece 41 has a shape protruding inward from the outer
end, in the radial direction, of the fitting recess 40 of the spring guide 30.
10 [0083]
The two fitting protrusions 32 of the spring guide 30 are formed symmetrically
with respect to the central axis of the spring guide 30, and the two retaining pieces 41
are provided in correspondence with the two fitting protrusions 32.
[0084]
15 By providing the two fitting protrusions 32 and the two retaining pieces 41 in
this way, it is possible to reliably stop the spring guide 30 from slipping off from the
cylinder 11.
[0085]
The rotary compressor 1 of Embodiment 1 includes the stoppers 43 that stop
20 rotation of the spring guide 30 by contacting with the fitting protrusions 32 of the
spring guide 30.
[0086]
Thus, it is possible to prevent the spring guide 30 from rotating during
operation.
25 [0087]
The stopper 43 may be made up of a protrusion protruding from the inner
periphery 40b of the fitting recess 40 or may be made up of the pin 50 that is inserted
in the pin insertion hole 51 formed in the cylinder 11 and of which the distal end 50a
contacts with the fitting protrusion 32. The stopper 43 may be made up of the sheet30
shaped elastic body 60 that is inserted to fill the gap formed on the front and rear
28
sides of the fitting protrusion 32 in the insertion direction in a state where the fitting
protrusion 32 of the spring guide 30 is fitted to the fitting recess 40 of the cylinder 11
and that is thicker than the gap.
[0088]
The inside diameter of the opening 8 of the hermetically sealed 5 housing 5 is
greater than the outside diameter of the hollow cylindrical portion 31 of the spring
guide 30 and is fixed to the cylinder 11 such that the spring guide 30 does not contact
with the hermetically sealed housing 5.
[0089]
10 Thus, since the spring guide 30 is fixed to the cylinder 11 without contacting
with the hermetically sealed housing 5, it is possible to accurately install the vane
spring 15 from the following reason. The shell of the rotary compressor 1 is made up
of the hermetically sealed housing 5, the protruded portion 6, and the lid portion 7,
and internal pressure generated by refrigerant discharged from the compression unit
10 is applied to these shell parts. The shell parts change their shapes, such as
bulging outward under the influence of the internal pressure. For this reason, in the
case of a structure in which the vane spring 15 is fixed to the shell parts, the location
of the vane spring 15 is influenced by deformation of the shell parts due to the internal
pressure. In contrast, in Embodiment 1, since the spring guide 30 is fixed to the
20 cylinder 11 such that the spring guide 30 does not contact with the hermetically
sealed housing 5, it is possible to install the vane spring 15 without receiving the
influence of deformation of the shell parts. In other words, it is possible to install the
vane spring 15 with reference to the location of the cylinder 11, so it is possible to
accurately install the vane spring 15.
[0090]
(Embodiment 2)
Embodiment 2 relates to a refrigeration cycle apparatus that includes the rotary
compressor 1 of Embodiment 1.
[0091]
Fig. 12 is a view illustrating a refrigerant circuit of the refrigeration cycle
apparatus according to Embodiment 2.
A refrigeration cycle apparatus 70 includes the rotary compressor 1 of
Embodiment 1, a condenser 71, an expansion valve 72 serving as a pressure
reducing device, and an evaporator 73. Gas refrigerant discharged 5 from the rotary
compressor 1 flows into the condenser 71, exchanges heat with air passing through
the condenser 71, and flows out as high-pressure liquid refrigerant. The highpressure
liquid refrigerant flowing out from the condenser 71 is reduced in pressure
by the expansion valve 72 into low-pressure two-phase gas-liquid refrigerant, and
flows into the evaporator 73. The low-pressure two-phase gas-liquid refrigerant
flowing into the evaporator 73 exchanges heat with air passing through the
evaporator 73 into low-pressure gas refrigerant, and is introduced into the rotary
compressor 1 again.
[0092]
The thus configured refrigeration cycle apparatus 70 includes the rotary
compressor 1 of Embodiment 1, so the stable operation of the vane 14 and the vane
spring 15 is obtained. It is also possible to suppress falling off of the spring guide 30
from the cylinder 11. Thus, the refrigeration cycle apparatus 70 with high reliability
can be provided.
[0093]
The refrigeration cycle apparatus 70 is applicable to an air-conditioning
apparatus, a refrigerator, a refrigerating machine, or other devices.
Reference Signs List
[0094]
1: rotary compressor, 5: hermetically sealed housing, 6: protruded portion, 7: lid
portion, 8: opening, 10: compression unit, 11: cylinder, 11a: cylinder chamber, 11b:
inner periphery, 11c: outer periphery, 12: intermediate plate, 13: rolling piston, 13c:
outer periphery, 14: vane, 14a: distal end, 14b: back, 15: vane spring, 15a: expansion
and contraction portion, 15b: non-expansion and contraction portion, 16: discharge
30 pipe, 17: rotary shaft, 17a: eccentric portion, 18: upper bearing, 19: lower bearing, 20:
suction port, 21: discharge hole, 22: vane groove, 25: electric unit, 26: stator, 27:
rotor, 28: accumulator, 29: accumulator pipe, 30: spring guide, 30a: one end, 30b: the
other end, 31: hollow cylindrical portion, 31a: vane passage portion, 31ab: bottom
surface, 32: fitting protrusion, 40: fitting recess, 40a: split recess, 40b: inner periphery,
41: retaining piece, 41a: end surface, 42: passage portion, 43: stopper, 5 43A: stopper,
43B: stopper, 44: bottom surface, 45: vane extension groove, 50: pin, 50a: distal end,
51: pin insertion hole, 60: elastic body, 70: refrigeration cycle apparatus, 71:
condenser, 72: expansion valve, 73: evaporator
We Claim:
[Claim 1]
A rotary compressor comprising:
a hermetically 5 sealed housing;
an annular cylinder accommodated in the hermetically sealed housing;
a rolling piston that rotates eccentrically along an inner periphery of the
cylinder;
a vane that reciprocates in a vane groove provided in the cylinder in a radial
direction;
a vane spring that urges the vane to bring a distal end of the vane into contact
with the rolling piston; and
a spring guide that has a hollow cylindrical portion in which the vane spring is
fixed, and a fitting protrusion protruding outward from an outer periphery of one end
side of the hollow cylindrical portion, wherein
the cylinder has a cylindrical fitting recess that is open at an outer periphery of
the cylinder and that communicates with the vane groove at its bottom surface, and
the fitting recess has a retaining piece that retains the fitting protrusion of the spring
guide, and the rotary compressor has a configuration in which the fitting protrusion is
engaged with the retaining piece and the spring guide is fixed to the cylinder by
rotating the spring guide in a state where one end of the spring guide on a side where
the fitting protrusion is formed is inserted and fitted in the fitting recess of the cylinder
via an opening formed in the hermetically sealed housing.
[Claim 2]
The rotary compressor of claim 1, wherein the retaining piece has a shape
protruding inward from an outer end, in the radial direction, of the fitting recess of the
spring guide.
[Claim 3]
The rotary compressor of claim 1 or 2, wherein the two fitting protrusions of the
spring guide are formed symmetrically with respect to a central axis of the spring
guide, and the two retaining pieces are provided in correspondence with the two
fitting 5 protrusions.
[Claim 4]
The rotary compressor of any one of claims 1 to 3, further comprising a stopper
that stops rotation of the spring guide by contacting with the fitting protrusion of the
spring guide.
10 [Claim 5]
The rotary compressor of claim 4, wherein the stopper is a protrusion
protruding from an inner periphery of the fitting recess.
[Claim 6]
The rotary compressor of claim 4, wherein the stopper is a pin that is inserted
15 in a pin insertion hole formed in the cylinder and of which a distal end contacts with
the fitting protrusion.
[Claim 7]
The rotary compressor of claim 4, wherein the stopper is made up of a sheetshaped
elastic body that is inserted to fill a gap formed on front and rear sides of the
20 fitting protrusion in an insertion direction in a state where the fitting protrusion of the
spring guide is fitted to the fitting recess of the cylinder and that is thicker than the
gap.
[Claim 8]
The rotary compressor of any one of claims 1 to 7, wherein an inside diameter
25 of the opening of the hermetically sealed housing is greater than an outside diameter
of the hollow cylindrical portion of the spring guide, and the spring guide is fixed to the
cylinder so as not to contact with the hermetically sealed housing.
[Claim 9]
A refrigeration cycle apparatus comprising the rotary compressor of any one of
claims 1 to 8.