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 100-8310, JAPAN
THE FOLLOWING SPECIFICATION PARTICULARLY DESCRIBES THE INVENTION
AND THE MANNER IN WHICH IT IS TO BE PERFORMED.
2
DESCRIPTION
5 Technical Field
[0001]
The present disclosure relates to a rotary compressor and a refrigeration cycle
apparatus that are used in an air-conditioning device, a refrigerator, a refrigerating
machine, or other devices.
10 Background Art
[0002]
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
15 urged by a vane spring and is constantly in contact with the rolling piston at the distal
end of the vane. The vane partitions the space inside the cylinder into a low-pressure
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 taken into the cylinder is compressed.
20 [0003]
In a hermetically sealed compressor of this type, the vane spring that urges the
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
25 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, 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
30 vane spring increases to cause the vane spring to undergo a fatigue failure.
3
[0004]
There is a technique 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 5 Literature 1).
Citation List
Patent Literature
[0005]
Patent Literature 1: Japanese Unexamined Utility Model Application Publication
10 No. 56-017388
Summary of Invention
Technical Problem
[0006]
The vane spring repeats expansion and contraction while pressing the vane in
15 the hermetically sealed housing. For this reason, when there is a misalignment in the
mounting location and mounting position of the vane spring, interference between the
vane spring and a peripheral part and bending or other deformation of the vane spring
occur during the expansion and contraction of the vane spring. As a result, an
inconvenience, such as a failure, a malfunction, and a decrease in life, of the vane
20 spring occurs. Therefore, it is desired to accurately assemble a vane spring to a rotary
compressor.
[0007]
In the rotary compressor of Patent Literature 1, the vane spring is configured to
be disposed in a spring guide fixed so as to protrude outward of the hermetically sealed
25 housing. An internal pressure generated by compressed refrigerant is applied to the
hermetically sealed housing, and the hermetically sealed housing changes its shape, for
example, the hermetically sealed housing bulges outward. For this reason, in the case
of a structure in which the spring guide is fixed to the hermetically sealed housing, the
vane spring is misaligned from a proper location under the influence of deformation of
4
the hermetically sealed housing due to the internal pressure, so it is not possible to
accurately install the vane spring.
[0008]
The present disclosure is contemplated in view of the above-described situation
and provides a rotary compressor that allows accurate installation of 5 a vane spring to a
cylinder, and a refrigeration cycle apparatus.
Solution to Problem
[0009]
A rotary compressor according to an embodiment of the present disclosure
10 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 is a coil spring that urges the vane to
bring a distal end of the vane into contact with the rolling piston and that has a small15
diameter portion and a large-diameter portion greater in diameter than the smalldiameter
portion, and a spring guide to which the vane spring is fixed by contact of the
large-diameter portion of the vane spring with an inner surface of the spring guide. The
spring guide has one end inserted in the hermetically sealed housing via an opening
formed in the hermetically sealed housing and fixed to the cylinder.
20 Advantageous Effects of Invention
[0010]
According to the embodiment of the present disclosure, the spring guide in which
the vane spring is fixed is directly fixed to the cylinder, so it is possible to accurately
install the vane spring to the cylinder.
25 Brief Description of Drawings
[0011]
[Fig. 1] Fig. 1 is a sectional view showing a schematic configuration of a rotary
compressor according to Embodiment 1.
[Fig. 2] Fig. 2 is an enlarged cross-sectional view showing a compression
30 mechanism unit in the rotary compressor according to Embodiment 1.
5
[Fig. 3] Fig. 3 is an enlarged view showing a joint structure of a spring guide and
a cylinder in the rotary compressor according to Embodiment 1.
[Fig. 4] Fig. 4 is a view illustrating a fixing structure of a vane spring with the
spring guide in the rotary compressor according to Embodiment 1.
[Fig. 5] Fig. 5 is a view showing Modification 1 of the spring guide 5 of the rotary
compressor according to Embodiment 1.
[Fig. 6] Fig. 6 is a view showing Modification 2 of the spring guide of the rotary
compressor according to Embodiment 1.
[Fig. 7] Fig. 7 is a view illustrating a fixing structure of a vane spring with a spring
10 guide in a rotary compressor according to Embodiment 2.
[Fig. 8] Fig. 8 is a view illustrating a fixing structure of a vane spring with a spring
guide in a rotary compressor according to Embodiment 3.
[Fig. 9] Fig. 9 is a view illustrating Modification of the fixing structure of the vane
spring with the spring guide in the rotary compressor according to Embodiment 3.
15 [Fig. 10] Fig. 10 is a view illustrating a fixing structure of a vane spring with a
spring guide in a rotary compressor according to Embodiment 4.
[Fig. 11] Fig. 11 is a diagram showing a refrigerant circuit of a refrigeration cycle
apparatus according to Embodiment 5.
Description of Embodiments
20 [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 as
an example.
[0013]
25 (Embodiment 1)
Fig. 1 is a sectional view showing a schematic configuration of a rotary
compressor according to Embodiment 1. Fig. 2 is an enlarged cross-sectional view
showing a compression mechanism unit in the rotary compressor according to
Embodiment 1. Fig. 3 is an enlarged view showing a joint structure of a spring guide
30 and a cylinder in the rotary compressor according to Embodiment 1. In the
6
specification, unless otherwise specified, the terms “radial direction”, “circumferential
direction”, and “axial direction” respectively mean the “radial direction”, “circumferential
direction”, and “axial direction” of the cylinder.
[0014]
The rotary compressor 1 includes an electric element 25, a compression 5 element
10 that compresses refrigerant, and a rotary shaft 17 that transmits the driving force of
the electric element 25 to the compression mechanism unit in a hermetically sealed
housing 5.
[0015]
10 As shown 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 not distorted
by internal pressure generated by refrigerant compressed in the compression element
10. By increasing the thickness of the hermetically sealed housing 5, it is possible to
15 reduce the influence of distortion of the hermetically sealed housing 5 caused by
heating on the compression element 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, arc-spot welding.
[0016]
20 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 mechanisms
(described later) that make up the compression element 10. A discharge pipe 16 that
discharges refrigerant compressed by the compression element 10 is connected to the
25 upper part of the hermetically sealed housing 5. Refrigerating machine oil for lubricating
the compression element 10 is stored at the bottom of the hermetically sealed housing
5. POE (polyor ester), PVE (polyvinyl ether), AB (alkylbenzene), or other materials,
which are synthetic oils, are used as the refrigerating machine oil.
[0017]
7
The electric element 25 includes a hollow cylindrical stator 26 fixed to the inner
periphery of the hermetically sealed housing 5, and a solid cylindrical rotor 27 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 5 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 on the rotor 27 and
magnetic fluxes generated by the stator 26.
[0018]
10 The electric element 25 and the compression element 10 are coupled by the
rotary shaft 17. The rotation of the electric element 25 is transmitted to the compression
element 10, and the compression element 10 compresses refrigerant by using the
transmitted rotational force. Refrigerant compressed by the compression element 10 is
released into the hermetically sealed housing 5 via a discharge hole 21 (see Fig. 2)
15 provided in the compression element 10. Therefore, the inside of the hermetically
sealed housing 5 is filled with high-temperature, high-pressure compressed refrigerant
gas.
[0019]
The compression element 10 includes the two compression mechanisms
20 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 element 10
is of a multi-cylinder type including two compression mechanisms. The rotary
compressor 1 is not limited to a multi-cylinder type including a plurality of compression
mechanisms and may be of a single cylinder type including one compression
25 mechanism.
[0020]
Since the compression mechanisms are similarly configured, only one of the
compression mechanisms will be described for the sake of convenience. As shown in
Fig. 2, the compression mechanism includes a cylinder 11, a rolling piston 13, a vane
8
14, a vane spring 15, and a hollow cylindrical 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 5 are closed by
the intermediate plate 12 and one of the upper bearing 18 and the lower bearing 19. As
shown 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
10 port 20.
[0022]
As shown 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
15 along the inner periphery 11b of the cylinder 11.
[0023]
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
20 direction. The vane spring 15 is disposed on the back 14b of the vane 14. An
accommodation recess in which one end of the vane spring 15 is accommodated is
formed at the back 14b of the vane 14. Fig. 2 shows a section at the accommodation
recess. One end of the vane spring 15 is fixed to the bottom surface of the
accommodation recess. The other end of the vane spring 15 is fixed to the inner
25 surface of the spring guide 30 (described later).
[0024]
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
30 contact with the rolling piston 13. Since the distal end 14a of the vane 14 is in contact
9
with the rolling piston 13 in this way, the inside of the cylinder 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
5 13.
[0025]
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 lowstrength
material, such as a resin. One end of the spring guide 30 is fixed to a fixing
10 recess 40 provided in the cylinder 11, and the other end of the spring guide 30
protrudes outward of the hermetically sealed housing 5 through an opening 8 provided
in the hermetically sealed housing 5. The inside diameter of the opening 8 of the
hermetically sealed housing 5 is greater than the outside diameter of the spring guide
30. The spring guide 30 is fixed to the cylinder 11 without being in contact with the
15 hermetically sealed housing 5. A method of fixing the spring guide 30 to the cylinder 11
is fixing with a method, such as fitting, press fitting, and screw fixing. Screw fixing is a
method of fixing by providing an external threaded portion on one of the outer periphery
of the spring guide 30 and the inner periphery of the fixing recess 40 of the cylinder 11
and an internal threaded portion on the other one of the outer periphery of the spring
20 guide 30 and the inner periphery of the fixing recess 40 of the cylinder 11 and screwfastening
the external threaded portion with the internal threaded portion.
[0026]
Vane passage portions 31 are formed on one end of the spring guide 30. The
vane passage portions 31 each are made up of a slit extending from an end surface on
25 the one end of the spring guide 30 in the axial direction of the spring guide 30. The two
vane passage portions 31 are formed symmetrically with respect to the central axis of
the spring guide 30. The vane passage portions 31 are located in an extension line of
the vane groove 22 in the radial direction in a state where the spring guide 30 is fixed to
the cylinder 11 as shown in Fig. 3.
30 [0027]
10
Here, the dimensions of the spring guide 30 will be described. The diameter D1
of the spring guide 30 is less than the axial length (the length in a direction orthogonal to
the drawing sheet of Fig. 3) of the vane 14. The radial width W1 of the vane passage
portion 31 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 5 portions 31
without being in contact with the vane passage portions 31, and reciprocates.
[0028]
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
10 housing 5. The protruded portion 6 is a cylindrical member of which the sectional shape
is a circular, rectangular, or oblong shape. As shown 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
15 end of the protruded portion 6 to the opening 8 formed in the hermetically sealed
housing 5.
[0029]
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.
20 The lid portion 7 is a lid that closes the outer-side end of the protruded 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.
25 [0030]
(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 element 25, the rotary shaft 17 is rotated
by the electric element 25. As the rotary shaft 17 rotates, the eccentric portion 17a
30 rotates eccentrically in the cylinder chamber 11a. With the eccentric rotation motion of
11
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 compressed. When the
gaseous refrigerant compressed in the cylinder chamber 11a reaches a predetermined
pressure, the gaseous refrigerant is discharged through the discharge 5 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 sealed housing 5.
10 [0031]
Here, the vane 14 reciprocates in the vane groove 22 with the rotation of the
rolling piston 13. As shown 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 coincides in
phase with the disposition location of the vane 14 (hereinafter, referred to as when the
15 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 degrees from the
disposition location of the vane 14, the vane 14 is moved forward, that is, in a direction
20 to 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 an intermediate position between the top dead
center position and the bottom dead center position.
25 [0032]
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
with respect to 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
30 follows.
12
[0033]
When the vane 14 is at the top dead center position shown in Fig. 2, the back 14b
of the vane 14 is located in the vane passage portions 31 of the spring 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 31 of the spring guide 30. When 5 the vane 14 is at
the intermediate position, the back 14b of the vane 14 is not located in the vane
passage portions 31 of the spring guide 30. The reason for the above configuration is
due to convenience during manufacturing, and this point will be described later.
[0034]
10 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 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
15 where the back 14b of the vane 14 is in contact with the bottom surfaces 31a of the
vane passage portions 31 of the spring guide 30. In other words, the bottom surfaces
31a of the vane passage portions 31 function as a stopper for the vane 14 in the event
of backflow of liquid. The radial locations of the bottom surfaces 31a of the vane
passage portions 31 are set such that the length of the vane spring 15 does not become
20 a close contact length in a state where the back 14b of the vane 14 is in contact with the
bottom surfaces 31a of the vane passage portions 31. For this 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.
[0035]
25 The rotary compressor 1 of Embodiment 1 has a structure in which the 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
30 and the inner periphery of the hermetically sealed housing 5, and the overall length of
13
the vane spring 15 can be freely set. The length of the vane 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 5 acts in the vane
spring 15 can be sufficiently 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.
[0036]
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 [0037]
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.
[0038]
In Embodiment 1, it is possible to freely set the distance between the lid portion 7
25 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, the
30 characteristics of the vane spring 15 deteriorate. In contrast, in Embodiment 1, it is
14
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 [0039]
Incidentally, an existing rotary compressor has a structure in which a vane spring
is disposed in a cylindrical spring guide provided so as to protrude outward from a
hermetically sealed housing. The spring guide is a part that makes up part of the shell
of the rotary compressor together with the hermetically sealed housing, and internal
10 pressure generated by refrigerant discharged from a compression element 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, with a structure in which the
spring guide is fixed to the shell parts, the spring guide and, by extension, a vane
spring, cannot be disposed at an intended location under the influence of deformation of
15 the shell parts due to the internal pressure. The intended location is a location along a
direction orthogonal to the central axis of the cylinder 11.
[0040]
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 directly fixed to the
20 cylinder 11. Therefore, it is possible to accurately install the vane spring 15, so it is
possible to stably operate the vane spring 15.
[0041]
Next, a structure of fixing the vane spring 15 to the spring guide 30 will be
described. The rotary compressors 1 of Embodiment 1 and Embodiments 2 to 4
25 (described later) each have a structure in which the vane spring 15 is fixed to the spring
guide 30 by bringing a large-diameter portion 15b (see Fig. 4) of the vane spring 15 into
contact with the inner surface of the spring guide 30, as a common structure.
Embodiment 1 relates to a structure of fixing the vane spring 15 to the spring guide 30
by press fitting.
30 [0042]
15
Fig. 4 is a view illustrating a fixing structure of the vane spring with the spring
guide in the rotary compressor according to Embodiment 1.
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 a small-diameter portion 15a
and the large-diameter portion 15b greater in diameter than the small-5 diameter portion
15a. The small-diameter portion 15a has a non-expansion and contraction portion 15aa
and an expansion and contraction portion 15ab that expands and contracts following the
motion of the vane 14. The non-expansion and contraction portion 15aa of the smalldiameter
portion 15a and the large-diameter portion 15b do not expand or contract by
10 the close contact of wire rods.
[0043]
The vane spring 15 is fixed in the cylindrical spring guide 30 at the large-diameter
portion 15b. In other words, the diameter of the large-diameter portion 15b reduces by
press-fitting the large-diameter portion 15b of the vane spring 15 into the spring guide
15 30, and the vane spring 15 is fixed in the spring guide 30 by restoring force for restoring
the diameter.
[0044]
The spring guide 30 shown in Fig. 4 and other drawings has a hollow cylindrical
shape with a uniform inside diameter. Alternatively, the spring guide 30 may be as
20 shown in Fig. 5 or Fig. 6 below.
[0045]
Fig. 5 is a view showing Modification 1 of the spring guide of the rotary
compressor according to Embodiment 1. Fig. 6 is a view showing Modification 2 of the
spring guide of the rotary compressor according to Embodiment 1.
25 [0046]
The spring guides 30 of Figs. 5 and 6 each are configured such that the inside
diameter D2 of a part (hereinafter, referred to as non-fixing portion) 32b other than a
part (hereinafter, referred to as fixing portion) 32a to which the large-diameter portion
15b of the vane spring 15 is fixed is wider than the inside diameter D3 of the fixing
30 portion 32a. With this configuration, the clearance between the outer periphery of the
16
small-diameter portion 15a of the vane spring 15 and the inner periphery of the nonfixing
portion 32b of the spring guide 30 is ensured so as to be wider than that in the
configuration of Fig. 4. For this reason, it is possible to ease the accuracy of alignment
between the vane spring 15 and the spring guide 30, which is needed at the time of
press-fitting. In other words, if the clearance is narrow, the vane 5 spring 15 can be
difficult to be inserted or cannot be inserted by getting caught by the inner periphery of
the spring guide 30 unless the vane spring 15 is inserted in the spring guide 30 while
the alignment is ensured between the vane spring 15 and the spring guide 30.
[0047]
10 In contrast, with the configurations of Figs. 5 and 6, the vane spring 15 is easily
inserted in the spring guide 30 because the wide clearance is ensured between the
outer periphery of the small-diameter portion 15a of the vane spring 15 and the inner
periphery of the non-fixing portion 32b of the spring guide 30, so it is possible to ease
the accuracy of alignment between the vane spring 15 and the spring guide 30.
15 [0048]
As shown in Fig. 6, the inner periphery of the spring guide 30 may have an
inclined surface 33 that smoothly connects the inner periphery of the fixing portion 32a
to the inner periphery of the non-fixing portion 32b. With this configuration, the stiffness
of the spring guide 30 is improved. Since the stiffness of the spring guide 30 is
20 improved, it is possible to reduce deformation of the spring guide 30 from load at the
time when the large-diameter portion 15b of the vane spring 15 is press-fitted into the
spring guide 30.
[0049]
Next, a procedure of assembling a relevant part of the rotary compressor 1 will be
25 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 fixed to the
hermetically sealed housing 5 in position in which the vane groove 22 faces the opening
30 8 of the hermetically sealed housing 5. Then, the vane 14 is inserted into the vane
17
groove 22 of one of the two cylinders 11 fixed to the hermetically sealed housing 5.
Subsequently, the spring guide 30 is joined with the cylinder 11, and the vane spring 15
is inserted in the spring guide 30 and fixed. 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 5 portion 6.
[0050]
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
10 then the spring guide 30 may be mounted to the cylinder 11.
[0051]
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
15 to join the lid portion 7 with the protruded portion 6 while pressing and 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.
20 [0052]
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
25 can be installed in a state where the length of the vane spring 15 is long, that is, a state
where a spring force that acts on the vane spring 15 is small, so assembly is easy.
[0053]
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. For this reason,
30 when the rolling piston 13 in one of the cylinders 11 is at the vane groove phase
18
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 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 5 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 phase by 180 degrees
from the vane groove phase location, the vane 14 is positioned at the bottom dead
10 center position, and then the vane spring 15 is inserted.
[0054]
When the spring guide 30 is fixed to the cylinder 11 by screw fixing, the spring
guide 30 is rotated in a state where one end 30a of the spring guide 30 is inserted in the
fixing recess 40. For this reason, at the time when the spring guide 30 is rotated, if the
15 back 14b of the vane 14 is placed in the vane passage portions 31 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 31, operation to rotate the spring guide 30 is performed. Specifically, for
example, the vane 14 is positioned at the bottom dead center position or the above20
described intermediate position. The reason why the back 14b of the vane 14 is not
located in the vane passage portions 31 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 guide 30 is fixed by screw fixing in this
way.
25 [0055]
As described above, the rotary compressor 1 of Embodiment 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 11b of the cylinder 11, and the vane 14 that reciprocates in the vane
30 groove 22 provided in the cylinder 11 in the radial direction. The rotary compressor 1
19
further includes the vane spring 15 that is a coil spring that urges the vane 14 to bring
the distal end 14a of the vane 14 into contact with the rolling piston 13 and that has the
small-diameter portion 15a and the large-diameter portion 15b greater in diameter than
the small-diameter portion 15a, and the spring guide 30 to which the vane spring 15 is
fixed by contact of the large-diameter portion 15b of the vane spring 5 15 with the inner
surface of the spring guide 30. The spring guide 30 has one end inserted in the
hermetically sealed housing 5 via the opening 8 formed in the hermetically sealed
housing 5 and fixed to the cylinder 11.
[0056]
10 In this way, since the spring guide 30 in which the vane spring 15 is fixed is
directly fixed to the cylinder 11, it is possible to accurately install the vane spring 15 to
the cylinder 11. Thus, it is possible to stably operate the vane spring 15.
[0057]
The inside diameter of the opening 8 of the hermetically sealed housing 5 is
15 greater than the outside diameter of the spring guide 30. The spring guide 30 is fixed to
the cylinder 11 without being in contact with the hermetically sealed housing 5.
[0058]
Thus, since the spring guide 30 is able to be fixed to the cylinder without
receiving the influence of deformation of the hermetically sealed housing 5, it is possible
20 to further accurately install the vane spring 15 to the cylinder 11.
[0059]
The vane spring 15 is fixed such that the large-diameter portion 15b is pressfitted
in the spring guide 30.
[0060]
25 In this way, fixing of the vane spring 15 to the spring guide 30 can be performed
by press-fitting the large-diameter portion 15b.
[0061]
The spring guide 30 is configured such that the inside diameter of the non-fixing
portion 32b is greater than the inside diameter of the fixing portion 32a.
30 [0062]
20
Thus, the wide clearance is ensured between the outer periphery of the smalldiameter
portion 15a of the vane spring 15 and the inner periphery of the non-fixing
portion 32b of the spring guide 30, so it is possible to ease the accuracy of alignment
between the vane spring 15 and the spring guide 30.
5 [0063]
(Embodiment 2)
The rotary compressor 1 of Embodiment 2 differs from that of Embodiment 1 in a
method of fixing the vane spring 15 to a spring guide 30A. In Embodiment 1, press
fitting is adopted; whereas, in Embodiment 2, screw fixing is adopted. Hereinafter, the
10 difference between Embodiment 2 and Embodiment 1 will be mainly described, and the
components not described in Embodiment 2 are similar to those of Embodiment 1.
[0064]
Fig. 7 is a view illustrating a fixing structure of the vane spring with the spring
guide in the rotary compressor according to Embodiment 2.
15 In Embodiment 2, screw fixing is used to fix the vane spring 15 to the spring
guide 30A. The hollow cylindrical spring guide 30A of Embodiment 2 has a thread
groove 34 on the inner periphery at a rear end in a screw insertion direction. The thread
groove 34 is a spiral groove.
[0065]
20 In Embodiment 2, the vane spring 15 is fixed in the spring guide 30A by screwing
the large-diameter portion 15b of the vane spring 15 into the thread groove 34.
[0066]
With such screw fixing, the large-diameter portion 15b of the vane spring 15 is
mounted so as to be guided along the thread groove 34 of the spring guide 30A. For
25 this reason, the accuracy of mounting location and position of the vane spring 15 is
improved.
[0067]
During operation of the rotary compressor 1, the spring force of the vane spring
15 that expands and contracts following the motion of the vane 14, the inertia force of
30 the vane spring 15, and a force caused by the vibration of the rotary compressor 1 act
21
on the vane spring 15. When the operation is continued, the vane spring 15 can be
misaligned from the original fixed location by these forces. For this reason, the thread
groove 34 of the spring guide 30A and the large-diameter portion 15b of the vane spring
15 need to be designed to shapes and dimensions that ensure a retaining force by
which the vane spring 15 is not misaligned. Specifically, the sectional 5 shape of the
thread groove 34 is set to a semicircle formed along the wire rod of the vane spring 15,
and the diameter of the semicircle is set to a diameter that matches the wire diameter of
the vane spring 15. The diameter that matches the wire diameter of the vane spring 15
includes a diameter that coincides with the wire diameter of the vane spring 15 or that is
10 slightly smaller than the wire diameter of the vane spring 15.
[0068]
As described above, the spring guide 30A of the rotary compressor 1 of
Embodiment 2 has the thread groove 34 on its inner periphery. The vane spring 15 is
fixed to the spring guide by screwing the large-diameter portion 15b of the spring guide
15 30A into the thread groove 34.
[0069]
In this way, since the vane spring 15 is fixed to the spring guide 30A by screwing
the large-diameter portion 15b of the spring guide 30A into the thread groove 34, the
accuracy of mounting location and position of the vane spring 15 is improved.
20 [0070]
The sectional shape of the thread groove 34 is a shape of a semicircle, and the
diameter of the semicircle matches the wire diameter of the vane spring 15.
[0071]
Thus, it is possible to suppress a misalignment of the vane spring 15 from the
25 original fixed location.
[0072]
(Embodiment 3)
The rotary compressor 1 of Embodiment 3 differs from that of Embodiment 1 in a
method of fixing the vane spring 15 to a spring guide 30B. The fixing method of
30 Embodiment 3 is groove fixing. Hereinafter, the difference between Embodiment 3 and
22
Embodiment 1 will be mainly described, and the components not described in
Embodiment 3 are similar to those of Embodiment 1.
[0073]
Fig. 8 is a view illustrating a fixing structure of the vane spring with the spring
guide in the rotary compressor according 5 to Embodiment 3.
In Embodiment 3, groove fixing is used to fix the vane spring 15 to the spring
guide 30B. The hollow cylindrical spring guide 30B of Embodiment 3 has a
circumferential groove 35 with a rectangular shape in cross section on its inner
periphery. The vane spring 15 is fixed in the spring guide 30B by press-fitting the large10
diameter portion 15b of the vane spring 15 into the groove 35. The sectional shape is
not limited to the rectangular shape and may be a selected shape.
[0074]
During operation of the rotary compressor 1, the spring force of the vane spring
15 that expands and contracts following the motion of the vane 14, the inertia force of
15 the vane spring 15, and a force caused by the vibration of the rotary compressor 1 act
on the vane spring 15. In addition to these forces, a frictional force caused by the
contact with the inner periphery of the spring guide 30B acts on the vane spring 15. A
resultant force obtained by taking the directions of these forces into consideration acts
in a direction to cause the vane spring 15 to be misaligned. For this reason, when the
20 operation is continued, the vane spring 15 can be misaligned from the original fixed
position.
[0075]
Therefore, the vane spring 15 is fixed to the spring guide 30B with a retaining
force by which the fixed location is not misaligned. In fixing the vane spring 15 to the
25 spring guide 30B, when a press fit interference of the large-diameter portion 15b with
the groove 35 is too large, it is not possible to insert the vane spring 15 into the spring
guide 30B. On the other hand, when a press fit interference is small, there is a problem
that the vane spring 15 is easily misaligned. For this reason, to prevent a misalignment
of the vane spring 15, a press fit interference of the large-diameter portion 15b with the
30 groove 35 is set as follows.
23
[0076]
The press fit interference is greater than or equal to a press fit interference by
which the large-diameter portion 15b of the vane spring 15 slides in the groove 35
radially outward by the spring force of the vane spring 15 when the rolling piston 13 is at
the vane groove phase location, that is, when the vane 14 is at the 5 top dead center
position. The press fit interference is less than or equal to a press fit interference by
which the large-diameter portion 15b does not slide in the groove 35 by the inertia force
of the vane spring 15 itself when the rolling piston 13 is at a location shifted in phase by
180 degrees from the vane groove phase location, that is, when the vane 14 is at the
10 bottom dead center position.
[0077]
Fig. 8 shows the configuration in which the vane spring 15 is fixed in the spring
guide 30B by press-fitting the large-diameter portion 15b of the vane spring 15into the
groove 35; however, a configuration as shown in Fig. 9 may be adopted.
15 [0078]
Fig. 9 is a view illustrating Modification of the fixing structure of the vane spring
with the spring guide in the rotary compressor according to Embodiment 3.
In Modification, an intermediate-diameter portion 15c greater in diameter than the
small-diameter portion 15a and less in diameter than the large-diameter portion 15b is
20 provided between the small-diameter portion 15a and the large-diameter portion 15b.
The intermediate-diameter portion 15c is press-fitted to the inner periphery of the spring
guide 30B. With this configuration, since the vane spring 15 is fixed in the spring guide
30B by both the large-diameter portion 15b and the intermediate-diameter portion 15c, it
is possible to further increase a retaining force, so it is possible to increase the effect of
25 preventing a misalignment. The configuration of Fig. 9 may be regarded as a
configuration in which a positioning portion made up of a further large-diameter nonexpansion
and contraction portion is provided further radially outward of the largediameter
portion 15b of the vane spring 15 shown in Fig. 4 and the positioning portion is
fitted into the groove 35.
30 [0079]
24
The spring guide 30B of the rotary compressor 1 of Embodiment 3 has the
circumferential groove 35 on its inner periphery, and the vane spring 15 is fixed to the
spring guide by fitting the large-diameter portion 15b of the vane spring 15 into the
groove 35.
5 [0080]
In this way, the vane spring 15 can be fixed by fitting the large-diameter portion
15b of the vane spring 15 into the circumferential groove 35 formed on the inner
periphery of the spring guide 30B.
[0081]
10 The vane 14 reciprocates between the bottom dead center position on the front
side that is a direction to the center of the cylinder 11 and the top dead center position
on the rear side that is a direction away from the cylinder 11. The vane spring 15 is
press-fitted by fitting the large-diameter portion 15b into the groove 35. The press fit
interference of the large-diameter portion 15b with the groove 35 is set so as to be
15 greater than or equal to a press fit interference by which the large-diameter portion 15b
of the vane spring 15 slides in the groove 35 radially outward by the spring force of the
vane spring 15 when the rolling piston 13 is at the vane groove phase location and less
than or equal to a press fit interference by which the large-diameter portion 15b of the
vane spring 15 does not slide in the groove 35 by the inertia force of the vane spring
20 itself when the rolling piston 13 is at a location shifted in phase by 180 degrees from the
vane groove phase location.
[0082]
Thus, it is possible to prevent a misalignment of the vane spring 15.
[0083]
25 (Embodiment 4)
The rotary compressor 1 of Embodiment 4 differs from that of Embodiment 1 in a
method of fixing the vane spring 15 to a spring guide 30C. In Embodiment 1, press
fitting is adopted; whereas, in Embodiment 4, lid fixing is adopted. Hereinafter, the
difference between Embodiment 4 and Embodiment 1 will be mainly described, and the
30 components not described in Embodiment 4 are similar to those of Embodiment 1.
25
[0084]
Fig. 10 is a view illustrating a fixing structure of the vane spring with the spring
guide in the rotary compressor according to Embodiment 4.
In Embodiment 4, lid fixing is used to fix the vane spring 15 to the spring guide
30C. In Embodiment 1, the inside diameter of the spring guide 30 5 is less than the
outside diameter of the large-diameter portion 15b of the vane spring 15, and the largediameter
portion 15b is press-fitted and fixed in the spring guide 30. In Embodiment 4,
the inside diameter of the spring guide 30C is greater than the outside diameter of the
large-diameter portion 15b of the vane spring 15, and the entire vane spring 15
10 including the large-diameter portion 15b is not in contact with the spring guide 30C.
[0085]
The spring guide 30C of Embodiment 4 has a hollow cylindrical portion 36 and a
spring lid 37 that closes an end of the hollow cylindrical portion 36. The vane spring 15
is fixed between the vane 14 and the spring lid 37 in a state of being constantly
15 contracted as compared to a natural length. In this way, the vane spring 15 is disposed
in the spring guide 30C in a contracted state, and the vane spring 15 is fixed in the
spring guide 30C.
[0086]
Next, a procedure of assembling a relevant part of the rotary compressor 1 will be
20 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 fixed to the
hermetically sealed housing 5 in position in which the fixing recess 40 faces the opening
25 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 30C is
inserted from the opening end of the protruded portion 6, and the end of the spring
guide 30C is fixed to the fixing recess 40 of the cylinder 11. Then, the vane spring 15 is
30 inserted and fixed in the spring guide 30C. For the other one of the cylinders 11, the
26
vane 14, the spring guide 30C, and the vane spring 15 are similarly fixed. Then, the lid
portion 7 is joined with the protruded portion 6.
[0087]
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, 5 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 may be mounted to the cylinder 11.
[0088]
In the rotary compressor 1 of Embodiment 4, the spring guide 30 has the hollow
10 cylindrical portion 36 and the spring lid 37 that closes the end of the hollow cylindrical
portion 36. The vane spring 15 is fixed between the vane 14 and the spring lid 37 in a
state of being constantly contracted as compared to a natural length. In this way, the
vane spring 15 may be fixed in the spring guide 30.
[0089]
15 (Embodiment 5)
Embodiment 5 relates to a refrigeration cycle apparatus that includes the rotary
compressor 1 of any one of Embodiments 1 to 4.
[0090]
Fig. 11 is a diagram showing a refrigerant circuit of the refrigeration cycle
20 apparatus according to Embodiment 5.
A refrigeration cycle apparatus 50 includes the rotary compressor 1 of any one of
Embodiments 1 to 4, a condenser 51, an expansion valve 52 serving as a pressure
reducing device, and an evaporator 53. Gas refrigerant discharged from the rotary
compressor 1 flows into the condenser 51, exchanges heat with air passing through the
25 condenser 51, and flows out as high-pressure liquid refrigerant. The high-pressure
liquid refrigerant flowing out from the condenser 51 is reduced in pressure by the
expansion valve 52 into low-pressure two-phase gas-liquid refrigerant, and flows into
the evaporator 53. The low-pressure two-phase gas-liquid refrigerant flowing into the
evaporator 53 exchanges heat with air passing through the evaporator 53 into low30
pressure gas refrigerant, and is introduced into the rotary compressor 1 again.
27
[0091]
The thus configured refrigeration cycle apparatus 50 includes the rotary
compressor 1 of any one of Embodiments 1 to 4, 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 from the cylinder 11. Thus, the refrigeration cycle apparatus 5 50 with high
reliability can be provided.
[0092]
The refrigeration cycle apparatus 50 is applicable to an air-conditioning
apparatus, a refrigerator, a refrigerating machine, or other devices.
10 Reference Signs List
[0093]
1: rotary compressor, 5: hermetically sealed housing, 6: protruded portion, 7: lid
portion, 8: opening, 10: compression element, 11: cylinder, 11a: cylinder chamber, 11b:
inner periphery, 11c: outer periphery, 12: intermediate plate, 13: rolling piston, 13c: outer
15 periphery, 14: vane, 14a: distal end, 14b: back, 15: vane spring, 15a: small-diameter
portion, 15aa: non-expansion and contraction portion, 15ab: expansion and contraction
portion, 15b: large-diameter portion, 15c: intermediate-diameter portion, 16: discharge
pipe, 17: rotary shaft, 17a: eccentric portion, 18: upper bearing, 19: lower bearing, 20:
suction port, 21: discharge hole, 22: vane groove, 25: electric element, 26: stator, 27:
20 rotor, 28: accumulator, 29: accumulator pipe, 30: spring guide, 30A: spring guide, 30B:
spring guide, 30C: spring guide, 30a: one end, 31: vane passage portion, 31a: bottom
surface, 32a: fixing portion, 32b: non-fixing portion, 33: inclined surface, 34: thread
groove, 35: groove, 36: hollow cylindrical portion, 37: spring lid, 40: fixing recess, 50:
refrigeration cycle apparatus, 51: condenser, 52: expansion valve, 53: evaporator
We Claim :
[Claim 1]
A rotary compressor comprising:
a hermetically sealed housing;
an annular cylinder accommodated in the hermetically 5 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 is a coil spring that urges the vane to bring a distal end of the
vane into contact with the rolling piston and that has a small-diameter portion and a
large-diameter portion greater in diameter than the small-diameter portion; and
a spring guide to which the vane spring is fixed by contact of the large-diameter
portion of the vane spring with an inner surface of the spring guide, wherein
the spring guide has one end inserted in the hermetically sealed housing via an
opening formed in the hermetically sealed housing and fixed to the cylinder.
[Claim 2]
The rotary compressor of claim 1, wherein an inside diameter of the opening of
the hermetically sealed housing is configured to be greater than an outside diameter of
the spring guide, and the spring guide is fixed to the cylinder without being in contact
with the hermetically sealed housing.
[Claim 3]
The rotary compressor of claim 1 or 2, wherein the vane spring is fixed such that
the large-diameter portion is press-fitted into the spring guide.
[Claim 4]
25 The rotary compressor of claim 3, wherein the spring guide is configured such
that an inside diameter of a part other than a part to which the large-diameter portion of
the vane spring is fixed is greater than an inside diameter of the part to which the largediameter
portion is fixed.
[Claim 5]
The rotary compressor of claim 3, wherein the spring guide has a thread groove
on its inner periphery, and the vane spring is fixed to the spring guide by screwing the
large-diameter portion of the spring guide into the thread groove.
[Claim 6]
The rotary compressor of claim 5, wherein a sectional shape of 5 the thread groove
is a shape of a semicircle, and a diameter of the semicircle matches a wire diameter of
the vane spring.
[Claim 7]
The rotary compressor of claim 3, wherein the spring guide has a circumferential
groove on its inner periphery, and the vane spring is fixed to the spring guide by fitting
the large-diameter portion of the vane spring to the groove.
[Claim 8]
The rotary compressor of claim 7, wherein
the vane is configured to reciprocate between a bottom dead center position on a
front side that is a direction to a center of the cylinder and a top dead center position on
a rear side that is a direction away from the cylinder,
the vane spring is press-fitted by fitting the large-diameter portion to the groove,
and
a press fit interference of the large-diameter portion with the groove is
20 set greater than or equal to a press fit interference by which the large-diameter
portion of the vane spring slides in the groove outward in the radial direction by a spring
force of the vane spring when the vane is at the top dead center position and less than
or equal to a press fit interference by which the large-diameter portion of the vane
spring does not slide in the groove by an inertia force of the vane spring caused by the
spring force of the vane spring when the vane is at the bottom dead center position.
[Claim 9]
The rotary compressor of any one of claims 1 to 8, wherein the spring guide has
a hollow cylindrical portion and a spring lid that closes an end of the hollow cylindrical
portion, and the vane spring is fixed between the vane and the spring lid in a state of
being constantly contracted as compared to a natural length.
[Claim 10]
A refrigeration cycle apparatus comprising the rotary compressor of any one of
claims 1 to 9.