1
FORM 2
THE PATENTS ACT, 1970
(39 of 1970)
&
THE PATENTS RULES, 2003
COMPLETE SPECIFICATION
[See section 10, Rule 13]
ROTARY COMPRESSOR, REFRIGERATION CYCLE APPARATUS, AND
MANUFACTURING METHOD FOR ROTARY COMPRESSOR;
MITSUBISHI ELECTRIC CORPORATION, A CORPORATION ORGANISED AND
EXISTING UNDER THE LAWS OF JAPAN, WHOSE ADDRESS IS 7-3,
MARUNOUCHI 2-CHOME, CHIYODA-KU, TOKYO 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 disclosure relates to a rotary compressor used in a refrigeration 5 cycle of an
air-conditioning device, a refrigerator, a refrigerating machine, or other devices, a
refrigeration cycle apparatus, and a manufacturing method for a rotary compressor.
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 is in contact with the rolling piston at the distal
end of the vane. The vane partitions the space inside the cylinder into a low15
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.
[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 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 Literature 1).
5 Citation List
Patent Literature
[0005]
Patent Literature 1: Japanese Unexamined Utility Model Application Publication
No. 56-017388
10 Summary of Invention
Technical Problem
[0006]
The vane spring repeats expansion and contraction while pressing the vane in
the hermetically sealed housing. For this reason, when there is a misalignment in
15 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
spring occurs. Therefore, it is desired to accurately assemble a vane spring to a
20 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 housing. An internal pressure generated by compressed refrigerant is
25 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 the hermetically sealed housing due to the
30 internal pressure, so it is not possible to accurately install the vane spring.
4
[0008]
The present disclosure is contemplated in view of the above-described
situation and provides a rotary compressor that allows accurate installation of a vane
spring to a cylinder, a refrigeration cycle apparatus, and a manufacturing method for a
5 rotary compressor.
Solution to Problem
[0009]
A rotary compressor according to an embodiment of the present disclosure
includes a hermetically sealed housing, an annular cylinder accommodated in the
10 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 cylindrical spring guide in which the
vane spring is fixed. The spring guide is provided to extend inside and outside the
15 hermetically sealed housing, and one end of the spring guide is fixed to the fixing
recess formed on an outer periphery of the cylinder.
Advantageous Effects of Invention
[0010]
According to the embodiment of the present disclosure, the spring guide in
20 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.
Brief Description of Drawings
[0011]
[Fig. 1] Fig. 1 is a sectional view showing a schematic configuration of a rotary
25 compressor according to Embodiment 1.
[Fig. 2] Fig. 2 is an enlarged cross-sectional view showing a compression
mechanism unit in the rotary compressor according to Embodiment 1.
[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.
30 [Fig. 4] Fig. 4 is a view showing a configuration example for increasing the
5
fixing strength of a fixing part of the cylinder with the spring guide in the rotary
compressor according to Embodiment 1.
[Fig. 5] Fig. 5 is a view showing an example in which axial grooves are
provided in the spring guide in the rotary compressor according to Embodiment 1.
[Fig. 6] Fig. 6 is a view showing an example in which circumferential 5 grooves
are provided in the spring guide in the rotary compressor according to Embodiment 1.
[Fig. 7] Fig. 7 is an enlarged view showing Modification of the joint structure of
the spring guide and the cylinder in the rotary compressor according to Embodiment 1.
[Fig. 8] Fig. 8 is an enlarged sectional view of the spring guide of the rotary
10 compressor according to Embodiment 1.
[Fig. 9] Fig. 9 is an enlarged sectional view of Modification of the spring guide
of the rotary compressor according to Embodiment 1.
[Fig. 10] Fig. 10 is a flowchart showing a manufacturing method for a relevant
part of the rotary compressor according to Embodiment 1.
15 [Fig. 11] Fig. 11 is a diagram showing a refrigerant circuit of a refrigeration cycle
apparatus according to Embodiment 2.
Description of Embodiments
[0012]
In Embodiments 1 and 2, a rotary compressor for use in an air-conditioning
20 apparatus, a refrigerator, a refrigerating machine, or other devices will be described
as an example.
[0013]
(Embodiment 1)
Fig. 1 is a sectional view showing a schematic configuration of a rotary
25 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
and a cylinder in the rotary compressor according to Embodiment 1. In the
specification, unless otherwise specified, the terms "radial direction", "circumferential
30 direction", and "axial direction" respectively mean the "radial direction",
6
"circumferential direction", and "axial direction" of the cylinder.
[0014]
The rotary compressor 1 includes an electric element 25, a compression
element 10 that compresses refrigerant, and a rotary shaft 17 that transmits the
driving force of the electric element 25 to the compression mechanism 5 unit in a
hermetically sealed housing 5.
[0015]
As shown in Fig. 1, the hermetically sealed housing 5 is a schematically hollow
cylindrical, hermetically sealed housing. The hermetically sealed housing 5 is
10 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 reduce the influence of distortion of the hermetically sealed
housing 5 caused by heating on the compression element 10 at the time of mounting
15 the rotary compressor 1 to an apparatus, such as an air-conditioning apparatus and a
refrigerator, by, for example, 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
20 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 upper part of the hermetically sealed housing 5.
Refrigerating machine oil for lubricating the compression element 10 is stored at the
25 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]
The electric element 25 includes a hollow cylindrical stator 26 fixed to the inner
30 periphery of the hermetically sealed housing 5, and a solid cylindrical rotor 27
7
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 5 the magnetic poles
on the rotor 27 and magnetic fluxes generated by the stator 26.
[0018]
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
10 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) provided in the compression element 10. Therefore, the inside of the
hermetically sealed housing 5 is filled with high-temperature, high-pressure
15 compressed refrigerant gas.
[0019]
The compression element 10 includes the two compression mechanisms
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
20 10 is of a multi-cylinder type including two compression mechanisms. The rotary
compressor 1 is not limited to a multi-cylinder type including two or more compression
mechanisms and may be of a single cylinder type including one compression
mechanism.
[0020]
25 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 14, a vane spring 15, and a cylindrical spring guide 30 in which the vane spring
15 is fixed.
30 [0021]
8
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
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 5 periphery 11b of
the cylinder 11. The accumulator pipe 29 of the accumulator 28 is connected to the
suction port 20.
[0022]
As shown in Fig. 2, the rolling piston 13 is accommodated in the cylinder
10 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.
[0023]
The cylinder 11 has a vane groove 22 that communicates with the cylinder
15 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 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
20 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 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
25 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
chamber 11a is partitioned into a low-pressure space and a high-pressure space. As
30 the rolling piston 13 rotates eccentrically in the cylinder chamber 11a, the vane 14
9
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]
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 5 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
that does not expand or contract. The non-expansion and contraction portion 15b is
10 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]
The vane spring 15 is fixed in the cylindrical spring guide 30 at the non15
expansion 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 guide 30, and the
vane spring 15 is fixed in the spring guide 30 by restoring force for restoring the
20 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]
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
25 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
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
30 non-expansion and contraction portion 15b of the vane spring 15 is one, the following
10
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
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.
5 [0028]
The spring guide 30 is provided so as to extend through the hermetically
sealed housing 5. One end 30a of the spring guide 30 fixedly inserted in the fixing
recess 40 provided on the outer periphery 11c of the cylinder 11, and the other end
30b protrudes outward of the hermetically sealed housing 5 through an opening 8
10 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 hermetically sealed housing 5.
[0029]
15 Although described below, at the time of fixing the spring guide 30 to the
cylinder 11, pressure, frictional force, and other forces act on the spring guide 30.
For this reason, the material of the spring guide 30 is preferably a high-strength
material, such as an iron material. The spring guide 30 is not limited to a highstrength
material, such as an iron material, and may be made of a low-strength
20 material, such as a resin.
[0030]
Vane passage portions 31 are formed on the one end 30a of the spring guide
30. The vane passage portions 31 each are made up of a slit extending from an end
surface on the one end 30a of the spring guide 30 in the axial direction of the spring
25 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.
[0031]
30 Here, the dimensions of the spring guide 30 will be described. The diameter
11
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
portions 31 without being in contact with the vane passage 5 portions 31, and
reciprocates.
[0032]
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
15 by press-fitting the end of the protruded portion 6 to the opening 8 formed in the
hermetically sealed housing 5.
[0033]
A lid portion 7 is joined 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
20 5. 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 [0034]
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 rotates eccentrically in the cylinder chamber 11a. With the eccentric
30 rotation motion of the eccentric portion 17a, the rolling piston 13 rotates eccentrically
12
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 hole 21 to the internal space of the hermetically 5 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.
[0035]
10 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 rolling piston 13 is at a vane groove phase location), the vane 14 is
15 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 to approach the center of the cylinder 11, and is at a bottom
20 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 [0036]
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 vane passage portions 31 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
30 the intermediate position are as follows.
13
[0037]
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 5 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 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.
10 [0038]
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
15 14 is moved radially outward beyond the top dead center position and stops at a
location 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
20 vane passage portions 31 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 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
25 11a rapidly increases. The close contact length of the vane spring 15 is a length in a
state where the vane spring 15 fully contracts and the wire rods closely contact with
each other.
[0039]
The rotary compressor 1 of Embodiment 1 has a structure in which the
30 protruded portion 6 is mounted so as to protrude outward of the hermetically sealed
14
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
the overall length of the vane spring 15 can be freely set. The 5 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
10 against a stress that repeatedly 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.
[0040]
15 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.
20 [0041]
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
25 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.
[0042]
In Embodiment 1, it is possible to freely set the distance between the lid portion
30 7 and the spring guide 30 by adjusting the length of the protruded portion 6, and the
15
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 characteristics of the vane spring 15 deteriorate. In contrast, in 5 Embodiment 1, it
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.
10 [0043]
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
15 internal 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
20 influence of deformation of 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.
[0044]
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
25 the cylinder 11. Therefore, it is possible to accurately install the vane spring 15, so it
is possible to stably operate the vane spring 15.
[0045]
Next, a structure of fixing of the spring guide 30 to the cylinder 11 will be
described. The hollow cylindrical fixing recess 40 in which one end 30a of the spring
30 guide 30 is fitted is provided on the outer periphery 11c of the cylinder 11. The fixing
16
recess 40 is formed so as to extend radially inward from the outer periphery 11c of the
cylinder 11 and communicates with the vane groove 22 at the bottom surface of the
fixing recess 40. The inside diameter of the fixing recess 40 is less than the outside
diameter of the spring guide 30, and one end 30a of the spring guide 30 is inserted
and press-fitted to the opening end of the 5 fixing recess 40.
[0046]
The outside diameter of the spring guide 30 is less than or equal to, for
example, 85% of the inside diameter of the protruded portion 6. This is because of
the following reason. The cylinder 11 is ideally fixed in the hermetically sealed
10 housing 5 such that the central axis of the cylinder 11 coincides with the central axis
of the hermetically sealed housing 5. However, there is a case where the cylinder 11
is installed such that the central axis of the cylinder 11 is inclined with respect to the
central axis of the hermetically sealed housing 5. When the central axis of the
cylinder 11 is inclined with respect to the central axis of the hermetically sealed
15 housing 5, the fixing recess 40 is also inclined.
[0047]
The spring guide 30 is inserted from the opening end of the protruded portion 6
into the protruded portion 6 fixed to the hermetically sealed housing 5 and fixed to the
cylinder 11. For this reason, when the fixing recess 40 is inclined, the spring guide
20 30 also needs to be passed into the protruded portion 6 in an inclined position at the
time when the spring guide 30 is inserted through the protruded portion 6 during
manufacturing. Here, when the outside diameter of the spring guide 30 is greater
than, for example, 85% of the inside diameter of the protruded portion 6, there is a
possibility that the clearance between the spring guide 30 and the protruded portion 6
25 is too small and, as a result, the spring guide 30 cannot be inserted in an inclined
position. Therefore, the outside diameter of the spring guide 30 is less than or equal
to, for example, 85% of the inside diameter of the protruded portion 6.
[0048]
The depth L2 of the fixing recess 40 of the cylinder 11 is preferably shorter
30 because of the following reason. As the depth L2 of the fixing recess 40 extends,
17
the length L3 of the vane groove 22 in the same direction, that is, the length L3 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 fixing recess 40 is preferably shorter and
is preferably less than or equal to 10% of the outside diameter D2 of 5 the cylinder 11.
[0049]
During compressor operation, a force in a direction to draw the spring guide 30
from the cylinder 11 at the fixing part of the fixing recess 40 of the cylinder 11 with one
end 30a of the spring guide 30 at the time when the vane 14 collides with the bottom
10 surfaces 31a of the vane passage portions 31 of the spring guide 30. For this
reason, a sufficient fixing strength is needed at the fixing part of the fixing recess 40 of
the cylinder 11 with one end 30a of the spring guide 30. Therefore, to increase the
fixing strength at the fixing part of the cylinder 11 with the spring guide 30, one or
some or all of the following methods (1) to (3) may be adopted.
15 [0050]
(1) The fixing strength may be increased by increasing the surface roughness
of the outer periphery of one end 30a of the spring guide 30 as compared to the inner
periphery of the spring guide 30 by applying treatment to the outer periphery of the
one end 30a with a chemical agent or other substances to thereby increase the
20 friction with the inner periphery of the fixing recess 40 of the cylinder 11.
[0051]
(2) The fixing strength may be increased by the supplemental fixation with a
metal adhesive shown in Fig. 4.
Fig. 4 is a view showing a configuration example for increasing the fixing
25 strength of the fixing part of the cylinder with the spring guide in the rotary compressor
according to Embodiment 1.
As shown in Fig. 4, supplemental fixation may be performed by applying the
metal adhesive 34 to an appropriate location. Fig. 4 shows an example in which the
metal adhesive 34 is applied to a connecting corner of the spring guide 30 with the
30 cylinder 11; however, the configuration is not limited thereto. The metal adhesive 34
18
may be applied to one or some or all of the outer periphery of one end 30a of the
spring guide 30, the inner periphery of the fixing recess 40 of the cylinder 11, and the
connecting corner of the spring guide 30 with the cylinder 11.
[0052]
(3) Supplemental fixation may be performed by providing grooves 5 or machining
marks on the inner periphery of the fixing recess 40 of the cylinder 11 and the outer
periphery of one end 30a of the spring guide 30 in mutually different directions to
thereby increase the frictional force at the time of press-fitting the spring guide 30 into
the cylinder 11. Fig. 5 and Fig. 6 show examples in which grooves are provided in
10 the spring guide 30.
[0053]
Fig. 5 is a view showing an example in which axial grooves are provided in the
spring guide in the rotary compressor according to Embodiment 1. Fig. 6 is a view
showing an example in which circumferential grooves are provided in the spring guide
15 in the rotary compressor according to Embodiment 1. In Figs. 5 and 6, (a) is a
sectional view of the spring guide 30, and (b) is a plan view of the spring guide 30.
[0054]
When the frictional force at the time of press-fitting the spring guide 30 into the
cylinder 11 is increased by using grooves or machining marks, grooves or machining
20 marks are provided on the inner periphery of the fixing recess 40 of the cylinder 11 in
the circumferential direction, and the grooves 30c or machining marks are provided
on the outer periphery of one end 30a of the spring guide 30 in the axial direction as
shown in Fig. 5. By interchanging the directions in which grooves or machining
marks are provided, grooves or machining marks may be provided on the inner
25 periphery of the fixing recess 40 of the cylinder 11 in the axial direction, and the
grooves 30c or machining marks may be provided on the outer periphery of one end
30a of the spring guide 30 in the circumferential direction as shown in Fig. 6.
Alternatively, grooves or machining marks may be provided at an angle on the inner
periphery of the fixing recess 40 of the cylinder 11, and grooves or machining marks
30 may be provided at an opposite angle on the outer periphery of one end 30a of the
19
spring guide 30. Here, machining marks are areas where the surface is roughened
by machining.
[0055]
In the above-description, the method of joining the spring guide 30 with the
cylinder 11 is press fitting; however, the method is not limited thereto. 5 Screw fixing
shown in Fig. 7 may be adopted.
[0056]
Fig. 7 is an enlarged view showing Modification of the joint structure of the
spring guide and the cylinder in the rotary compressor according to Embodiment 1.
10 An internal threaded portion 41 is formed on the inner periphery of the fixing
recess 40 of the cylinder 11. An external threaded portion 32 is formed on the outer
periphery of one end 30a of the spring guide 30. The length of the external threaded
portion 32 in the central axis direction of the spring guide 30 is greater than or equal
to the length of a part screwed into the fixing recess 40.
15 [0057]
With this configuration, the spring guide 30 is fixed to the cylinder 11 by screw
fastening of the external threaded portion 32 of the spring guide 30 with the internal
threaded portion 41 of the cylinder 11.
[0058]
20 With such screw fastening, at the time of screwing the external threaded
portion 32 of the spring guide 30 into the internal threaded portion 41 of the cylinder
11, there is a possibility that a force acts on the vane groove 22 of the cylinder 11 and
deforms the vane groove 22 to thereby interfere with the reciprocation of the vane 14.
For this reason, to suppress deformation of the vane groove 22 during screw
25 fastening, the shape of the external threaded portion 32 of the spring guide 30 may
be an asymmetric screw shown in Fig. 8.
[0059]
Fig. 8 is an enlarged sectional view of the spring guide of the rotary
compressor according to Embodiment 1.
30 The external threaded portion 32 of the spring guide 30 is an asymmetric screw
20
of which the center of a thread 33 is inclined to one side. Specifically, an angle 
that one side of the thread 33 makes with a plane orthogonal to the central axis of the
spring guide 30 is different from an angle  that the opposite side of the thread 33
makes with the plane orthogonal to the central axis of the spring guide 30. In this
example,  > ; however, it is applicable 5 that  < .
[0060]
In this way, by using an asymmetric screw for the external threaded portion 32
of the spring guide 30, it is possible to reduce a force at the time of screwing the
external threaded portion 32 of the spring guide 30 into the internal threaded portion
10 41 of the cylinder 11, so it is possible to suppress deformation of the vane groove 22.
[0061]
In Fig. 8, the inclined direction of each thread 33 is the same over the entire
external threaded portion 32. Alternatively, the configuration shown in Fig. 9 is also
applicable.
15 [0062]
Fig. 9 is an enlarged sectional view of Modification of the spring guide of the
rotary compressor according to Embodiment 1.
In Modification, part of the external threaded portion 32 of the spring guide 30
is inclined toward the distal end in the insertion direction (left-hand side in Fig. 9), and
20 another part is inclined toward the rear end in the insertion direction. In this example,
an example in which the threads of the external threaded portion 32 on the distal end
side in the insertion direction are inclined toward the distal end in the insertion
direction and the threads on the rear end side in the insertion direction are inclined
toward the rear end in the insertion direction is shown; however, it is only illustrative,
25 and the configuration is not limited to the illustrated example.
[0063]
With this configuration, it is possible to further reduce a force at the time of
screwing the external threaded portion 32 of the spring guide 30 into the internal
threaded portion 41 of the cylinder 11 as compared to Fig. 8, so it is possible to
30 further suppress deformation of the vane groove 22.
21
[0064]
Here, the external threaded portion is provided on the spring guide 30, and the
internal threaded portion is provided on the cylinder 11. Alternatively, an internal
threaded portion may be provided on the spring guide 30, and an external threaded
portion may be provided on 5 the cylinder 11.
[0065]
Next, a manufacturing method for a relevant part of the rotary compressor 1 will
be described.
[0066]
10 Fig. 10 is a flowchart showing a manufacturing method for a relevant part of the
rotary compressor 1 according to Embodiment 1.
Initially, a process of fixing the cylinder 11 in the hermetically sealed housing 5
with which the protruded portion 6 is joined, and inserting the rolling piston 13 in the
cylinder 11 is performed (step S1). Here, since the compression element 10
15 includes the plurality of compression mechanisms, 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. Each of the cylinders 11 is fixed to the
hermetically sealed housing 5 in position in which the fixing recess 40 faces the
20 opening 8 of the hermetically sealed housing 5.
[0067]
Then, a step of inserting the vane 14 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 is performed (step S2). Subsequently, one end 30a of
25 the spring guide 30 is inserted from outside the hermetically sealed housing 5 through
the opening 8 of the hermetically sealed housing 5 and is fixed to the fixing recess 40
of the cylinder 11 (step S3). Specifically, the spring guide 30 is inserted from the
opening end of the protruded portion 6, and one end 30a is fixed to the fixing recess
40 of the cylinder 11 as described above. Then, the vane spring 15 is inserted in the
30 spring guide 30 and fixed (step S4). For the other one of the cylinders 11, the vane
22
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 (step S5).
[0068]
In the manufacturing method, 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 to which the vane spring 15 is fixed may be mounted to
the cylinder 11.
[0069]
10 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
holding the other end of the vane spring 15. In contrast, in Embodiment 1, at the
15 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.
[0070]
At the time when the vane spring 15 is fixed to the spring guide 30, the rolling
20 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
long, that is, a state where a spring force that acts on the vane spring 15 is small, so
25 assembly is easy.
[0071]
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,
when the rolling piston 13 in one of the cylinders 11 is at the vane groove phase
30 location, the rolling piston 13 in the other one of the cylinders 11 is at a location
23
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
position, and then the vane spring 15 is inserted. Then, at the 5 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 center position, and then the vane spring 15 is inserted.
10 [0072]
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 back 14b of the vane 14 is placed in the vane passage portions 31 of the spring
15 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 above-described intermediate position. The reason why the back 14b of the
20 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.
[0073]
25 When the back 14b of the vane 14 is not located in the vane passage portions
31 at the time when the rolling piston 13 is at a location rotated by 90 degrees from
the vane groove phase location, simplification of a manufacturing process is possible.
In other words, in the above-described assembling procedure, the spring guide 30 is
fixed to one of the two cylinders 11 and then the spring guide 30 is fixed to the other
30 one of the cylinders 11, it is necessary to position the rolling piston 13 by rotating the
24
rotary shaft 17 by 180 degrees. However, when the back 14b of the vane 14 is not
located in the vane passage portions 31 at the time when the rolling piston 13 is at a
location rotated by 90 degrees from the vane groove phase location, rotation of the
rotary shaft 17 is not needed. In other words, while the rolling piston 13 is at a
location rotated by 90 degrees from the vane groove phase location, 5 the spring guide
30 can be fixed to one of the cylinders 11, and then the spring guide 30 can be fixed
to the other one of the cylinders 11.
[0074]
The rotary compressor 1 of Embodiment 1 includes the hermetically sealed
10 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, the vane 14 that reciprocates in the vane groove 22 provided in the
cylinder 11 in the radial direction, 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, and the
15 cylindrical spring guide 30 in which the vane spring 15 is fixed. The spring guide 30
is provided to extend inside and outside the hermetically sealed housing 5, and one
end 30a of the spring guide 30 is fixed to the fixing recess 40 formed on the outer
periphery of the cylinder 11.
[0075]
20 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.
[0076]
The inside diameter of the opening 8 of the hermetically sealed housing 5 is
25 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.
[0077]
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
30 possible to accurately install the vane spring 15 to the cylinder 11.
25
[0078]
The diameter of the fixing recess 40 is less than the outside diameter of one
end 30a of the spring guide 30, and the spring guide 30 is fixedly press-fitted to the
cylinder 11.
5 [0079]
In this way, fixing of the spring guide 30 to the cylinder 11 can be performed by
press fitting.
[0080]
The outer periphery of one end 30a of the spring guide 30 is higher in
10 roughness than the inner periphery of the spring guide 30. The metal adhesive is
provided at one or some or all of the outer periphery of one end 30a of the spring
guide 30, the inner periphery of the fixing recess 40 of the cylinder 11, and the
connecting corner of the spring guide 30 with the cylinder 11. Grooves or machining
marks are formed on the outer periphery of one end 30a of the spring guide 30 and
15 the inner periphery of the fixing recess 40 of the cylinder 11 in mutually different
directions.
[0081]
Thus, it is possible to increase the fixing strength at the fixing part of the spring
guide 30 with the cylinder 11.
20 [0082]
One of the outer periphery of one end 30a of the spring guide 30 and the inner
periphery of the fixing recess 40 of the cylinder 11 has the external threaded portion
32, the other one of the outer periphery of one end 30a of the spring guide 30 and the
inner periphery of the fixing recess 40 of the cylinder 11 has the internal threaded
25 portion 41, and the spring guide 30 is fixed to the cylinder 11 by screw fastening of
the external threaded portion 32 with the internal threaded portion 41
[0083]
In this way, fixing of the spring guide 30 to the cylinder 11 can be performed by
screw fastening.
30 [0084]
26
The external threaded portion 32 is an asymmetric screw of which the center of
each thread 33 is inclined to one side.
[0085]
In this way, by using an asymmetric screw, it is possible to reduce a force at the
time of screwing the external threaded portion 32 of the spring 5 guide 30 into the
internal threaded portion 41 of the cylinder 11, so it is possible to suppress
deformation of the vane groove 22.
[0086]
The threads 33 of the external threaded portion 32 are partially inclined radially
10 inward and partially inclined radially outward.
[0087]
Thus, it is possible to further suppress deformation of the vane groove 22.
[0088]
The spring guide 30 includes the vane passage portions 31 through which the
15 vane 14 passes at a location extended from the vane groove 22 in the radial direction.
[0089]
Thus, the stroke of the vane 14 is ensured.
[0090]
The vane passage portions 31 of the spring guide 30 each are a slit formed in
20 the axial direction of the spring guide 30 from one end 30a-side end surface of the
spring guide 30. In a state where the vane 14 is in contact with the bottom surfaces
31a of the vane passage portions 31, the location of each of the bottom surfaces 31a
of the vane passage portions 31 is set such that the length of the vane spring 15 does
not become a close contact length by which the wire rods that make up the vane
25 spring 15 closely contact with each other.
[0091]
Thus, at the time when the internal pressure of the cylinder chamber 11a
rapidly increases, such as in the event of backflow of liquid, it is possible to prevent
excessive pressure from being applied to the vane spring 15.
30 [0092]
27
The manufacturing method for the rotary compressor 1 according to
Embodiment 1 includes a step of fixing the annular cylinder 11 in the hermetically
sealed housing 5 and inserting the rolling piston 13, which rotates eccentrically along
the inner periphery 11b of the cylinder 11, into the cylinder 11, and a step of inserting
the vane 14 in the vane groove 22 formed in the cylinder 11. 5 The manufacturing
method for the rotary compressor 1 further includes a step of inserting one end 30a of
the spring guide 30, in which 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 is fixed, from the
outside of the hermetically sealed housing 5 through the opening 8 formed in the
10 hermetically sealed housing 5 and fixing the one end 30a to the fixing recess 40
provided opposite to the opening 8 in the cylinder 11, and a step of fixing the vane
spring 15 in the spring guide 30.
[0093]
In this way, since the spring guide 30 in which the vane spring 15 is fixed is
15 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 obtain the rotary compressor 1 capable of
stably operating the vane spring 15.
[0094]
Where the cylinder 11, the rolling piston 13, the vane 14, the vane spring 15,
20 and the spring guide 30 are defined as a compression mechanism, the rotary
compressor 1 includes a plurality of the compression mechanisms. The vane spring
15 is fixed to the cylinder 11 of a corresponding one of compression elements 10
while the rolling piston 13 is positioned such that the contact location of the outer
periphery 13c of the rolling piston 13 with the inner periphery 11b of the cylinder 11 is
25 different in phase by 180 degrees from the disposition location of the vane 14.
[0095]
Thus, it is possible to install the vane spring 15 in a state where a spring force
that acts on the vane spring 15 is small, so assembly is easy.
[0096]
30 Where the cylinder 11, the rolling piston 13 disposed in the cylinder 11, the
28
vane 14, the vane spring 15, and the spring guide 30 are defined as a compression
mechanism, the rotary compressor 1 includes a plurality of the compression
mechanisms. The vane spring 15 is fixed to the cylinder 11 of a corresponding one
of compression elements 10 while the rolling piston 13 is positioned such that the
contact location of the outer periphery 13c of the rolling piston 5 13 with the inner
periphery 11b of the cylinder 11 is different in phase by 90 degrees from the
disposition location of the vane 14.
[0097]
Thus, even when the rolling piston 13 is not moved each time the vane spring
10 15 is installed in a corresponding one of the cylinders 11, it is possible to install the
vane spring 15 in a state where a spring force that acts on the vane spring 15 is small,
so assembly is easy. In other words, once the rolling piston 13 is positioned such
that 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 90 degrees from the
15 disposition location of the vane 14, it is possible to install the vane spring 15 in a state
where a spring force that acts on the vane spring 15 is small without positioning the
rolling piston 13 thereafter. As a result, simplification of a manufacturing process is
possible.
[0098]
20 (Embodiment 2)
Embodiment 2 relates to a refrigeration cycle apparatus that includes the rotary
compressor 1 of Embodiment 1.
[0099]
Fig. 11 is a view showing a refrigerant circuit of the refrigeration cycle
25 apparatus according to Embodiment 2.
The refrigeration cycle apparatus 50 includes the rotary compressor 1 of
Embodiment 1, 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
30 the condenser 51, and flows out as high-pressure liquid refrigerant. The high29
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 low-pressure gas refrigerant, and is introduced 5 into the rotary
compressor 1 again.
[0100]
The thus configured refrigeration cycle apparatus 50 includes the rotary
compressor 1 of Embodiment 1, so the stable operation of the vane 14 and the vane
10 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 50 with high reliability
can be provided.
[0101]
The refrigeration cycle apparatus 50 is applicable to an air-conditioning
15 apparatus, a refrigerator, a refrigerating machine, or other devices.
Reference Signs List
[0102]
1: rotary compressor, 5: hermetically sealed housing, 6: protruded portion, 7: lid
portion, 8: opening, 10: compression element, 11: cylinder, 11a: cylinder chamber,
20 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 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,
25 26: stator, 27: rotor, 28: accumulator, 29: accumulator pipe, 30: spring guide, 30a: one
end, 30b: the other end, 30c: groove, 31: vane passage portion, 31a: bottom surface,
32: external threaded portion, 33: thread, 34: metal adhesive, 40: fixing recess, 41:
internal threaded portion, 50: refrigeration cycle apparatus, 51: condenser, 52:
expansion valve, 53: evaporator
30
30
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
10 direction;
a vane spring that urges the vane to bring a distal end of the vane into contact
with the rolling piston; and
a cylindrical spring guide in which the vane spring is fixed, wherein
the spring guide is provided to extend inside and outside the hermetically
15 sealed housing, and one end of the spring guide is fixed to a fixing recess formed on
an outer periphery of the cylinder.
[Claim 2]
The rotary compressor of claim 1, wherein the hermetically sealed housing has
an opening through which the spring guide extend inside and outside of the
20 hermetically sealed housing, an inside diameter of the opening 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 a diameter of the fixing recess
25 is configured to be less than an outside diameter of the one end of the spring guide,
and the spring guide is fixedly press-fitted to the cylinder.
[Claim 4]
The rotary compressor of claim 3, wherein an outer periphery of the one end of
the spring guide is higher in roughness than an inner periphery of the spring guide.
30 [Claim 5]
31
The rotary compressor of any one of claims 1 to 4, wherein a metal adhesive is
provided on one or some or all of an outer periphery of the one end of the spring
guide, an inner periphery of the fixing recess of the cylinder, and a connecting corner
of the spring guide with the cylinder.
5 [Claim 6]
The rotary compressor of any one of claims 1 to 5, wherein grooves or
machining marks are formed on an outer periphery of the one end of the spring guide
and an inner periphery of the fixing recess of the cylinder in mutually different
directions.
10 [Claim 7]
The rotary compressor of claim 1 or 2, wherein one of an outer periphery of the
one end of the spring guide and an inner periphery of the fixing recess of the cylinder
has an external threaded portion, an other one of the outer periphery of the one end
of the spring guide and the inner periphery of the fixing recess of the cylinder has an
15 internal threaded portion, and the spring guide is fixed to the cylinder by screw
fastening of the external threaded portion with the internal threaded portion.
[Claim 8]
The rotary compressor of claim 7, wherein the external threaded portion is an
asymmetric screw of which a center of a thread is inclined to one side.
20 [Claim 9]
The rotary compressor of claim 8, wherein the thread of the external threaded
portion is partially inclined inward in the radial direction and partially inclined outward
in the radial direction.
[Claim 10]
25 The rotary compressor of any one of claims 1 to 9, wherein the spring guide
includes a vane passage portion through which the vane passes, at a location
extended from the vane groove in the radial direction.
[Claim 11]
The rotary compressor of claim 10, wherein the vane passage portion of the
30 spring guide is a slit formed in an axial direction of the spring guide from an end
32
surface of the spring guide at the one end, and a location of a bottom surface of the
vane passage portion is set such that, in a state where the vane is in contact with the
bottom surface of the vane passage portion, a length of the vane spring does not
become a close contact length by which wire rods that make up the vane spring do
not closely contact 5 with each other.
[Claim 12]
A refrigeration cycle apparatus comprising the rotary compressor of any one of
claims 1 to 11.
[Claim 13]
10 A manufacturing method for a rotary compressor, the manufacturing method
comprising:
a step of fixing an annular cylinder in a hermetically sealed housing and
inserting a rolling piston, which rotates eccentrically along an inner periphery of the
cylinder, into the cylinder;
15 a step of inserting a vane into a vane groove formed in the cylinder;
a step of inserting one end of a spring guide, at which a vane spring that urges
the vane to bring a distal end of the vane into contact with the rolling piston is fixed,
from outside of the hermetically sealed housing through an opening formed in the
hermetically sealed housing and fixing the one end to a fixing recess provided
20 opposite to the opening in the cylinder; and
a step of fixing the vane spring in the spring guide.
[Claim 14]
The manufacturing method for a rotary compressor of claim 13, wherein
where the cylinder, the rolling piston, the vane, the vane spring, and the spring
guide are defined as a compression mechanism, the compression mechanism
included in the rotary compressor includes a plurality of compression mechanisms,
and
the vane spring is fixed to the cylinder of a corresponding one of compression
elements while the rolling piston is positioned such that a contact location of an outer
30 periphery of the rolling piston with an inner periphery of the cylinder is different in
phase by 180 degrees from a disposition location of the vane.
[Claim 15]
The manufacturing method for a rotary compressor of claim 13, wherein
where the cylinder, the rolling piston, the vane, the vane spring, and the spring
guide are defined as a compression mechanism, the compression 5 mechanism
included in the rotary compressor includes a plurality of compression mechanisms,
and
the vane spring is fixed to the cylinder of a corresponding one of compression
elements while the rolling piston is positioned such that a contact location of an outer
periphery of the rolling piston with an inner periphery of the cylinder is different in
phase by 90 degrees from a disposition location of the vane.