Technical Field
[0001] The present invention relates to a compressor that is applied to an air conditioner
and the like, and that compresses refrigerant and discharges the compressed refrigerant.
Background Art
[0002] A compression portion of a compressor used in an air conditioner and the like is
driven by an electromagnetic motor. The electromagnetic motor is constituted of a
rotor and a stator, and the rotor and the compression portion are connected to each
other via a drive shaft (a shaft). The rotor of the motor rotates, which rotates the
compression portion.
[0003] The compression portion includes a rotary compression mechanism that includes a cylinder
main body, and an upper bearing and a lower bearing that each support a rotating shaft.
Refrigerant taken into a cylinder chamber formed in the cylinder main body is compressed
by the rotation of a roller in the cylinder chamber, and then discharged into a muffler
(a discharge chamber) via discharge ports and discharge valves. After that, the refrigerant
discharged to the muffler is delivered toward the motor in a sealed container (a housing)
of the compressor.
[0004] The muffler is, as described in Patent Document 1 below, almost in a bowl shape,
for example, and installed on the upper bearing so as to cover the discharge valves.
Patent Document 1 discloses the configuration in which a rib is integrally formed
with the upper bearing serving as a frame, which increases the rigidity of the frame.
Citation List
Patent Document
[0005] Patent Document 1: Japanese Patent Publication No.
3301837 JP 2013-238132 discloses a compressor.
WO 2013/073182 discloses a compressor according to the preamble of claim 1.
Summary of Invention
Technical Problems
[0006] In the above-described rotary compression mechanism, the refrigerant discharged
into the muffler is compressed in the cylinder chamber and thus has a high temperature,
which heats structural bodies such as the muffler and the upper bearing while the
compressor is in operation. As a result, the refrigerant taken into the cylinder chamber,
which has a relatively low temperature, is heated by the upper bearing and the like.
Therefore, the rotary compression mechanism takes in and compresses refrigerant having
an increased temperature, which deteriorates efficiency.
[0007] Unlike Patent Document 1, an upper bearing having no rib formed thereon has low rigidity,
which causes resonance at an eigenvalue (about 1 kHz) in a low frequency region of
the upper bearing, for example. As a result, the bearing and the drive shaft (the
shaft) suffer from elastic deformation and thus noise increases.
[0008] In light of the foregoing, an object of the present invention is to provide a compressor
capable of increasing the rigidity of a bearing and suppressing transmission of heat
to a cylinder main body.
Solution to Problems
[0009] A compressor of the present invention is defined by claim 1 and employs the following
solutions to solve the problems described above.
[0010] The compressor according to the present invention includes a cylinder main body of
a rotary compression mechanism, a bearing provided on one surface side of the cylinder
main body and supporting a drive shaft, and a plate portion disposed on one surface
side of the bearing. The bearing includes a wall portion formed rising from the one
surface of the bearing and extending along the radial direction of the bearing, a
refrigerant circulation section surrounded by the wall portion and the plate portion,
the refrigerant circulation section allowing refrigerant discharged from the cylinder
main body to circulate thereto, and a heat-blocking section surrounded by the wall
portion and the plate portion and separated from the refrigerant circulation section
by the wall portion and the plate portion to prevent the refrigerant from circulating
thereto.
[0011] According to this configuration, the heat-blocking section to which the refrigerant
does not circulate is formed separated from the refrigerant circulation section to
which the refrigerant circulates. The heat-blocking section is separated from the
refrigerant circulation section by the wall portion formed along the radial direction
of the bearing and the plate portion disposed on one surface side of the bearing.
As a result, the heat-blocking section serves as a heat-blocking space to which heat
of the refrigerant is hardly transmitted. Therefore, temperature rise of the cylinder
main body is suppressed, which can reduce temperature rise of the refrigerant flowing
on the intake side of the cylinder main body. The refrigerant circulation section
receives the refrigerant discharged from the cylinder main body, and thus provides
silencing effect.
[0012] In addition, the wall portion is formed rising from one surface of the bearing and
extending along the radial direction of the bearing, which increases the rigidity
of the bearing.
[0013] In order to separate the refrigerant circulation section and the heat-blocking section
from each other, two wall portions, for example, are provided extending in different
two directions from the center of the bearing. The angle between the two wall portions
or the angle between the wall portion and a first rib is preferably less than 180
degrees. Therefore, the rigidity of the bearing can be further increased.
[0014] The bearing further includes the first rib that is formed rising from the one surface
of the bearing and extending along the radial direction of the bearing in the heat-blocking
section.
[0015] According to this configuration, not only the wall portion but also the first rib
is formed, on one surface of the bearing, extending along the radial direction of
the bearing. Therefore, the rigidity of the bearing can be increased.
[0016] In the above-described invention, another configuration may be employed in which
the number of the cylinder main body provided is at least two, and the bearing further
includes a second rib that is formed rising from the one surface of the bearing and
extending along the radial direction of the bearing in the refrigerant circulation
section, the refrigerant circulation section is divided into at least two separated
spaces by the second rib, and one of the separated spaces allows refrigerant to be
discharged thereto from one of the cylinder main bodies and the other separated space
allows refrigerant to be discharged thereto from the other cylinder main body.
[0017] According to this configuration, the refrigerant circulation section to which the
refrigerant circulates is divided into two separate spaces by the second rib. One
of the separated spaces allows the refrigerant to be discharged thereto from one of
the cylinder main bodies. The other separated space allows the refrigerant to be discharged
thereto from the other cylinder main body. Therefore, the refrigerant discharged from
one of the cylinder main bodies and the refrigerant discharged from the other cylinder
main body both circulate in the respective separated spaces of the refrigerant circulation
section and are silenced.
[0018] In the above-described invention, another configuration may be employed in which
the at least two separated spaces allow refrigerant to circulate therein, from one
to another, and the plate portion has only one discharge port formed thereon, the
discharge port causing refrigerant to be discharged therethrough from the separated
spaces.
[0019] According to this configuration, the refrigerant discharged from the one of the cylinder
main bodies and the refrigerant discharged from the other cylinder main body join
each other in the separated spaces of the refrigerant circulation section. The joined
refrigerant is discharged from the separated spaces via the discharge port formed
on the plate portion. Therefore, providing the one of the cylinder main bodies and
the other cylinder main body eliminates the need to provide an additional part for
joining the refrigerant outside of the compression mechanism.
[0020] In the above-described invention, another configuration may be employed in which
the second rib has a notch portion formed thereon to allow the refrigerant to circulate
in the at least two separated spaces, from one to another, the notch portion being
formed by partially cutting the bearing in the radial direction.
[0021] According to this configuration, the refrigerant circulates via the notch portion
of the second rib, that is, the refrigerant circulates between the at least two separated
spaces without lowering the height of the second rib other than the notch portion.
Therefore, the rigidity of the bearing can be increased in comparison with the configuration
in which the height of the second rib is uniformly lowered along the radial direction
of the bearing to circulate the refrigerant in the separated spaces, from one to another.
[0022] In the above-described invention, another configuration may be employed in which
the plate portion has a groove portion formed thereon to allow the refrigerant to
circulate in the at least two separated spaces, from one to another, the groove portion
being formed at a position corresponding to the second rib.
[0023] According to this configuration, the refrigerant circulates via the groove portion
formed on the plate portion, that is, the refrigerant circulates between the at least
two separated spaces without lowering the height of the second rib. Therefore, the
rigidity can be increased in comparison with the configuration in which, to circulate
the refrigerant in the separated spaces from one to another, the height of the second
rib is uniformly lowered along the radial direction of the bearing or the notch portion
is partially formed on the second rib.
Advantageous Effects of Invention
[0024] According to the present invention, the rigidity of the bearing can be increased
by the wall portion and transmission of heat to the cylinder main body can be reduced.
Therefore, temperature rise of the cylinder main body is suppressed, which can reduce
temperature rise of refrigerant flowing on the intake side of the cylinder main body.
Brief Description of Drawings
[0025]
FIG. 1 is a vertical cross-sectional view of a compressor according to a first embodiment
of the present invention.
FIG. 2 is a horizontal cross-sectional view of a cylinder main body of the compressor
according to the first embodiment of the present invention.
FIG. 3 is a plan view of an upper bearing and a muffler plate of the compressor according
to the first embodiment of the present invention.
FIG. 4 is a plan view of the upper bearing of the compressor according to the first
embodiment of the present invention.
FIG. 5 is a vertical cross-sectional view taken along line V-V in FIG. 3.
FIG. 6 is a vertical cross-sectional view taken along line VI-VI in FIG. 4.
FIG. 7 is an outline vertical cross-sectional view of the upper bearing and the muffler
plate of the compressor according to the first embodiment of the present invention.
FIG. 8 is a plan view of an upper bearing and a muffler plate of a compressor according
to a second embodiment of the present invention.
FIG. 9 is a plan view of the upper bearing of the compressor according to the second
embodiment of the present invention.
FIG. 10 is an outline vertical cross-sectional view of the upper bearing and the muffler
plate of the compressor according to the second embodiment of the present invention.
FIG. 11 is an outline vertical cross-sectional view of an upper bearing and a muffler
plate of a compressor according to a first modification of the second embodiment of
the present invention.
FIG. 12 is an outline vertical cross-sectional view of an upper bearing and a muffler
plate of a compressor according to a second modification of the second embodiment
of the present invention.
FIG. 13 is an outline vertical cross-sectional view of an upper bearing and a muffler
plate of a compressor according to a third modification of the second embodiment of
the present invention.
FIG. 14 is a plan view of an upper bearing and a muffler plate of a compressor according
to a fourth modification of the second embodiment of the present invention.
Description of Embodiments
First Embodiment
[0026] A compressor 1 according to a first embodiment of the present invention will be described
below with reference to the drawings. As illustrated in FIG. 1, the multi-cylinder
rotary compressor 1 according to the present embodiment is provided with a cylindrical
sealed container 2 whose upper and lower portions are respectively sealed by an upper
cover 3 and a lower cover 4. A motor 5 is installed in the upper part of the interior
of the sealed container 2, and a rotary compression mechanism 6 driven by the motor
5 is installed in the lower part of the sealed container 2.
[0027] A mounting leg 7 is provided on the outer circumference of the lower portion of the
sealed container 2. Further, a discharge piping 8 that penetrates through the upper
cover 3 is provided in the upper portion of the sealed container 2. The discharge
piping 8 discharges a high-pressure refrigerant gas compressed by the multi-cylinder
rotary compressor 1 toward a refrigeration cycle. Furthermore, an accumulator 9 is
installed on an outer circumferential portion of the sealed container 2. The accumulator
9 separates a liquid portion, such as oil and liquid refrigerant, contained in a low-pressure
refrigerant gas returned from the refrigerating cycle side, and causes only a gas
portion to be taken in by the compression mechanism 6 via intake piping 10 and 11.
[0028] The motor 5 is provided with a stator 12 and a rotor 13. The stator 12 is fixedly
installed on the inner circumferential surface of the sealed container 2 by press
fitting and the like. The rotor 13 is connected to and integrally provided with a
drive shaft 14. This configuration allows a rotational driving force of the rotor
13 to be transmitted to the compression mechanism 6 via the drive shaft 14. Further,
in the lower part of the drive shaft 14, a first eccentric pin 15 and a second eccentric
pin 16 are provided respectively corresponding to a first roller 24 and a second roller
25 of the rotary compression mechanism 6 described below.
[0029] In the present embodiment, the rotary compression mechanism 6 is of a two-cylinder
type, and a first cylinder chamber 17 and a second cylinder chamber 18 are respectively
formed in first and second compression mechanisms 6A and 6B of the compression mechanism
6. The compression mechanism 6 is further provided with a first cylinder main body
19, a second cylinder main body 20, a partition plate (a separator plate) 21, an upper
bearing 22, a lower bearing 23, and the like.
[0030] The first cylinder main body 19 and the second cylinder main body 20 are fixedly
installed inside the sealed container 2 respectively corresponding to the first eccentric
pin 15 and the second eccentric pin 16 of the drive shaft 14. The partition plate
21 is interposed between the first cylinder main body 19 and the second cylinder main
body 20, defining the first cylinder chamber 17 and the second cylinder chamber 18.
The upper bearing 22 is provided on the upper surface of the first cylinder main body
19, defining the first cylinder chamber 17 and supporting the drive shaft 14. The
lower bearing 23 is provided on the lower surface of the second cylinder main body
20, defining the second cylinder chamber 18 and supporting the drive shaft 14.
[0031] The first and second compression mechanisms 6A and 6B are respectively provided with
the first roller 24 and the second roller 25 and with blades 28 and 29.
[0032] The first roller 24 and the second roller 25 are respectively rotatably fitted with
the first eccentric pin 15 and the second eccentric pin 16, and rotate inside the
first cylinder chamber 17 and the second cylinder chamber 18. The first eccentric
pin 15 and the second eccentric pin 16 are connected to the drive shaft 14 and rotate
together with the drive shaft 14. The center of gravity of the second roller 25 fitted
with the second eccentric pin 16 is positioned, with respect to an axis of the drive
shaft 14, remote from the center of gravity of the first roller 24 fitted with the
first eccentric pin 15.
[0033] As illustrated in FIG. 2, the blades 28 and 29 are slidably fitted into blade grooves
26 and 27 provided in the first cylinder main body 19 and the second cylinder main
body 20, and partition the interior of each of the first cylinder chamber 17 and the
second cylinder chamber 18 into an intake chamber side and a discharge chamber side.
[0034] The low-pressure refrigerant gas is taken into the first cylinder chamber 17 and
the second cylinder chamber 18 of the first and second compression mechanisms 6A and
6B, from the intake piping 10 and 11 via intake ports 30 and 31.
[0035] The refrigerant gas taken into the first cylinder chamber 17 is compressed by the
rotation of the first roller 24, and then discharged into a later-described refrigerant
circulation section 38 of the upper bearing 22 via discharge ports and discharge valves
(not illustrated). After that, the refrigerant gas is discharged into a muffler 32.
The muffler 32 is almost in a bowl shape, for example, and installed on the upper
bearing 22 so as to cover the discharge ports and the discharge valves (not illustrated).
The refrigerant gas taken into the second cylinder chamber 18 is compressed by the
rotation of the second roller 25, and then discharged into the muffler 32 via discharge
ports and discharge valves. The refrigerant gas discharged into the muffler 32 is
discharged into the sealed container 2, and then delivered to the refrigeration cycle
via the discharge piping 8.
[0036] The first cylinder main body 19, the second cylinder main body 20, the partition
plate 21, the upper bearing 22, and the lower bearing 23, which constitute the compression
mechanism 6, are integrally tightened and fixed by bolts. Further, a bottom portion
of the interior of the sealed container 2 is filled with refrigeration oil 34, such
as PAG oil or POE oil. The refrigeration oil 34 can be supplied to lubrication parts
inside the compression mechanism 6 via oil supply holes and the like provided in the
drive shaft 14. An appropriate amount of an extreme-pressure agent suitable for each
type of oil is added to the refrigeration oil 34. Note that, because an oil supply
mechanism for the compression mechanism 6 has a typical configuration, a detailed
description thereof is omitted herein.
[0037] A first balance weight 35 is provided on the upper surface of the rotor 13, which
is one side of the drive shaft 14 in the axial direction thereof and is a surface
located remote from the compression mechanism 6. Further, the center of gravity of
the first balance weight 35 is positioned, with respect to the axis of the drive shaft
14, remote from the center of gravity of the first roller 24. A second balance weight
36 is provided on the lower surface of the rotor 13, which is the other side of the
drive shaft 14 in the axial direction thereof and is a surface located adjacent to
the compression mechanism 6. Further, the center of gravity of the second balance
weight 36 is positioned, with respect to the axis of the drive shaft 14, remote from
the center of gravity of the second roller 25.
[0038] As a result of the first balance weight 35 and the second balance weight 36 being
provided on the upper surface and the lower surface of the rotor 13, a centrifugal
force that acts on the first balance weight 35 and the second balance weight 36 can
be balanced against a centrifugal force that is generated by the rotation of the first
roller 24 and the second roller 25 and acts on the first roller 24 and the second
roller 25.
[0039] The rotor 13 is formed of a plurality of steel plates insulated from each other and
stacked on top of each other in the axial direction of the drive shaft 14. The steel
plate is an example of a magnetic metal plate, and may be another magnetic metal plate.
The steel plates stacked on top of each other suppress generation of an eddy current.
The steel plates are arranged such that the outer surface of the rotor 13 is on the
same plane. Therefore, a gap (also referred to as an air gap) formed between the stator
12 and the rotor 13 is constant in the circumferential direction. The size of the
air gap ranges, for example, from a hundred and several ten µm to several hundred
µm in a manner that depends on the size of the motor 5 and the like.
[0040] The following describes the upper bearing 22 according to the present embodiment
with reference to FIGS. 3 to 6.
[0041] The upper bearing 22 has a disc shape and includes, in the center thereof, a cylindrical
portion 37 through which the drive shaft 14 penetrates. The bottom surface of the
upper bearing 22 is provided in contact with the upper surface of the first cylinder
main body 19. The outer circumferential surface of the upper bearing 22 is fixed to
the sealed container 2.
[0042] The refrigerant circulation section 38 and a heat-blocking section 39 are formed
on the upper surface of the upper bearing 22 adjacent to the motor 5.
[0043] The refrigerant circulation section 38 is a space surrounded by a recessed portion
40 and a muffler plate 42. The recessed portion 40 is formed on the upper surface
side of the upper bearing 22 in a shape depressed toward the bottom surface thereof.
The muffler plate 42 is installed on the upper surface of the upper bearing 22.
[0044] The heat-blocking section 39 is a space surrounded by a recessed portion 41 and the
muffler plate 42. The recessed portion 41 is formed on the upper surface side of the
upper bearing 22 in a shape depressed toward the bottom surface thereof. The recessed
portion 41 is formed on a different portion from the recessed portion 40 included
in the refrigerant circulation section 38.
[0045] The muffler plate 42 has a disc shape and includes, in the center thereof, a through
hole 43 through which a cylindrical portion 37 of the upper bearing 22 penetrates.
[0046] The recessed portions 40 and 41 formed on the upper surface side of the upper bearing
22, are surrounded by an outer peripheral wall 44, a center wall 45, and partition
ribs 46. The outer peripheral wall 44 is almost parallel to the outer circumferential
surface of the upper bearing 22 and has a circular arc shape. The center wall 45 is
almost parallel to the outer circumferential surface of the cylindrical portion 37
and has a circular arc shape.
[0047] The partition ribs 46 are formed extending in two different directions from the center
side of the upper bearing 22 along the radial direction thereof. The partition ribs
46 are provided between the outer peripheral wall 44 and the center wall 45. The partition
ribs 46 are provided in a projecting manner with respect to the flat plate surface
of the upper bearing 22. This configuration allows the upper bearing 22 to have the
ribs formed on one surface side thereof along the radial direction, thereby increasing
the rigidity of the upper bearing 22 in comparison with the configuration in which
the upper bearing 22 has no ribs.
[0048] In the refrigerant circulation section 38, a discharge port 47 is formed on the upper
bearing 22. The discharge port 47 has a discharge valve (not illustrated) installed
therein. The refrigerant discharged from the first cylinder chamber 17 is supplied
to the refrigerant circulation section 38 via the discharge port 47. The refrigerant
is stored once inside of the refrigerant circulation section 38, and then discharged
from the refrigerant circulation section 38 toward the motor 5 in the sealed container
2 via a discharge port 48 formed on the muffler plate 42.
[0049] The heat-blocking section 39 is separated from the refrigerant circulation section
38 by the partition ribs 46, therefore, the refrigerant discharged from the first
cylinder chamber 17 or the second cylinder chamber 18 is not supplied to the heat-blocking
section 39, unlike the refrigerant circulation section 38. In addition, no refrigerant
is introduced from the refrigerant circulation section 38 into the heat-blocking section
39.
[0050] In the heat-blocking section 39, a rib (a first rib) 49 is provided extending along
the radial direction of the upper bearing 22. Therefore, on the upper surface of the
upper bearing 22, at least three rib-like portions including the two partition ribs
46 projecting and extending along the radial direction are formed in the circumferential
direction. This configuration reinforces the upper surface of the upper bearing 22
by not only the partition ribs 46 but also the rib 49 in the heat-blocking section
39, thereby increasing the rigidity of the upper bearing 22. As a result, a bending
mode hardly appears in a low frequency region, which makes resonance less likely to
occur than the configuration in which two rib-like portions are provided.
[0051] The rib 49 may have a height so as to extend from the bottom portion of the recessed
portion 41 to the bottom surface of the muffler plate 42. Alternatively, the rib 49
may have a height so as not to come into contact with the bottom surface of the muffler
plate 42. Larger height of the rib 49 can increase the rigidity of the upper bearing
22.
[0052] The angle between the rib 49 and each of the adjacent partition ribs 46, or the angle
between the partition ribs 46 adjacent to each other is preferably less than 180 degrees.
In this configuration, a bending mode hardly appears in a low frequency region, which
makes resonance less likely to occur than the configuration in which the angle is
180 degrees.
[0053] On the upper bearing 22, through holes 50 are formed on places other than the refrigerant
circulation section 38 and the heat-blocking section 39. Into the through holes 50,
the refrigerant flows from the second cylinder chamber 18. The refrigerant passed
through the through holes 50 is discharged into the muffler 32.
[0054] On the upper bearing 22, a plurality of bolt holes 51 are formed. The bolt holes
51 have bolts penetrating therethrough, the bolts passing through the muffler plate
42, the first cylinder main body 19 and the second cylinder main body 20, the partition
plate 21, the upper bearing 22 and the lower bearing 23. All these members are tightened
together by the bolts.
[0055] According to the present embodiment, as illustrated in FIG. 7, in the upper bearing
22, the heat-blocking section 39 in which the refrigerant does not circulate is formed
separated from the refrigerant circulation section 38 in which the refrigerant circulates.
The heat-blocking section 39 is separated from the refrigerant circulation section
38 by the partition ribs 46 formed along the radial direction of the upper bearing
22, the muffler plate 42 installed on the upper surface side of the upper bearing
22, and the like. In the heat-blocking section 39, air or refrigerant oil is present
having lower temperatures than the refrigerant discharged from the first cylinder
chamber 17. This configuration allows the heat-blocking section 39 to serve as a heat-blocking
space to which the heat of the refrigerant is hardly transmitted. FIG. 7 is an outline
vertical cross-sectional view of the upper bearing and the muffler plate of the compressor
according to the present embodiment.
[0056] The heat-blocking section 39 can therefore suppress the temperature rises of the
first and second compression mechanisms 6A and 6B caused by the refrigerant discharged
from the first cylinder chamber 17 or the refrigerant on the motor 5 side. Furthermore,
the heat-blocking section 39 can reduce the temperature rise of the refrigerant taken
into the first cylinder chamber 17 or the second cylinder chamber 18. The refrigerant
circulation section 38 temporarily stores therein the refrigerant discharged from
the first cylinder chamber 17, which reduces the noise generated when discharging
the refrigerant and thus provides silencing effect.
Second Embodiment
[0057] The following describes a compressor according to a second embodiment of the present
invention with reference to FIGS. 8 to 10. Because the structural members are the
same as those of the first embodiment, a detailed description thereof will be omitted.
[0058] In the above-described first embodiment, the configuration in which no rib is formed
in the refrigerant circulation section 38 has been described. But the present invention
is not limited to this configuration. In the present embodiment, a rib (a second rib)
52 is formed in the refrigerant circulation section 38.
[0059] Specifically, the rib 52 is formed in the refrigerant circulation section 38 along
the radial direction of the upper bearing 22. Therefore, on the upper surface of the
upper bearing 22, rib-like portions projecting and extending along the radial direction
of the upper bearing 22 including not only the partition ribs 46 and the rib 49 in
the heat-blocking section 39, but also the rib 52 in the refrigerant circulation section
38 are formed. Therefore, on the upper surface of the upper bearing 22, at least four
rib-like portions projecting and extending along the radial direction are formed in
the circumferential direction. This configuration increases the rigidity of the upper
bearing 22. As a result, a bending mode hardly appears at a low frequency, which makes
resonance less likely to occur than the configuration in which two or three rib-like
portions are provided.
[0060] The rib 52 formed in the refrigerant circulation section 38 has a height so as not
to come into contact with the muffler plate 42. This configuration allows the refrigerant
to circulate through the refrigerant circulation section 38, although the rib 52 is
formed therein.
[0061] The refrigerant circulation section 38 is divided into a first separated space 38A
and a second separated space 38B with the rib 52 interposed therebetween.
[0062] On the upper bearing 22, a discharge port 53 is formed in the first separated space
38A and a discharge port 54 is formed in the second separated space 38B in the refrigerant
circulation section 38. The discharge port 53 formed in the first separated space
38A has a discharge valve (not illustrated) installed therein. Via the discharge port
53, the refrigerant discharged from the first cylinder chamber 17 is supplied to the
first separated space 38A. Via the discharge port 54, the refrigerant discharged from
the second cylinder chamber 18 is supplied to the second separated space 38B.
[0063] The muffler plate 42 has a discharge port 55 formed on the first separated space
38A side thereof.
[0064] The refrigerant is stored once in the first separated space 38A and second separated
space 38B of the refrigerant circulation section 38. The refrigerant stored in the
second separated space 38B flows into the first separated space 38A, and then joins
the refrigerant stored therein. Subsequently, the joined refrigerant is discharged
from the first separated space 38A toward the motor 5 in the sealed container 2 via
the discharge port 55 formed on the first separated space 38A side of the muffler
plate 42.
[0065] The discharge port 55, which is formed only one on the muffler plate 42, may be formed
on the side of the second separated space 38B rather than the side of the first separated
space 38A. In this configuration, the refrigerant flows from the first separated space
38A to the second separated space 38B.
[0066] According to the present embodiment, the refrigerant discharged from the first cylinder
chamber 17 and the refrigerant discharged from the second cylinder chamber 18 join
in the refrigerant circulation section 38, which eliminates the need to provide an
additional part for joining the refrigerant outside of the upper bearing 22.
[0067] According to the present embodiment, the refrigerant from the second cylinder chamber
18 is introduced to the second separated space 38B. This configuration increases the
number of steps of the muffler, unlike the first embodiment in which the refrigerant
passes through the through holes 50 on the upper bearing 22 as is and discharged to
the outside. Therefore, the compressor according to the present embodiment has an
increased silencing effect.
[0068] Furthermore, according to the present embodiment, as illustrated in FIG. 10, in the
upper bearing 22, the heat-blocking section 39 in which the refrigerant does not circulate
is formed separated from the refrigerant circulation section 38 in which the refrigerant
circulates. The heat-blocking section 39 is separated from the refrigerant circulation
section 38 by the partition ribs 46 formed along the radial direction of the upper
bearing 22, the muffler plate 42 installed on the upper surface side of the upper
bearing 22, and the like. In the heat-blocking section 39, air or refrigerant oil
is present having lower temperatures than the refrigerant discharged from the first
cylinder chamber 17 or the second cylinder chamber 18. This configuration allows the
heat-blocking section 39 to serve as a heat-blocking space to which the heat of the
refrigerant is hardly transmitted.
[0069] The heat-blocking section 39 can therefore suppress the temperature rises of the
first and second compression mechanisms 6A and 6B caused by the refrigerant discharged
from the first cylinder chamber 17 or the second cylinder chamber 18, and the refrigerant
on the motor 5 side. Furthermore, the heat-blocking section 39 can reduce the temperature
rise of the refrigerant taken into the first cylinder chamber 17 or the second cylinder
chamber 18.
[0070] In the above-described example, the configuration is employed in which the refrigerant
discharged from the second cylinder chamber 18 is supplied to the second separated
space 38B. But the present invention is not limited to this example. For example,
another configuration may be employed in which the refrigerant discharged from the
second cylinder chamber 18 is not supplied to the refrigerant circulation section
38; the upper bearing 22, as illustrated in FIG. 11, has a discharge port 56 formed
only at the second separated space 38B; via the discharge port 56, the refrigerant
discharged from the first cylinder chamber 17 is supplied to the second separated
space 38B.
[0071] The muffler plate 42 has a discharge port 57 formed on the first separated space
38A side thereof.
[0072] This configuration causes the refrigerant to be stored once in the second separated
space 38B of the refrigerant circulation section 38 and then flow to the first separated
space 38A. Subsequently, the refrigerant is discharged from the first separated space
38A toward the motor 5 in the sealed container 2 via the discharge port 57 formed
on the first separated space 38A side of the muffler plate 42.
[0073] The refrigerant from the second cylinder chamber 18 is, in the same manner as the
first embodiment, not stored in the refrigerant circulation section 38 and passes
through the through holes (not illustrated) on the upper bearing 22 as is, and discharged
to the motor 5 side in the sealed container 2.
[0074] In the above-described embodiment, the configuration is employed in which the rib
52 is provided along the radial direction of the upper bearing 22 and has a height
so as not to come into contact with the muffler plate 42. But the present invention
is not limited to this configuration. For example, another configuration may be employed
in which the rib 52, as illustrated in FIG. 12, has a notch portion 58 formed thereon,
the notch portion 58 being formed by cutting a part of the rib 52 in the radial direction
and the remaining part of the rib 52 having a height so as to come into contact with
the muffler plate 42. In this configuration, the refrigerant circulates between the
first separated space 38A and the second separated space 38B via the notch portion
58 formed on the rib 52.
[0075] According to this modification, the rigidity of the upper bearing 22 can be increased
in comparison with the configuration in which the height of the rib 52 is uniformly
lowered along the radial direction of the upper bearing 22. In addition, the muffler
plate 42 and the rib 52 come into contact with each other, which hardly causes deformation
in the muffler plate 42 formed in a planar shape, allowing a flow path area to be
constantly ensured for a long time and also increasing the reliability. Furthermore,
this configuration can readily reduce the area through which the refrigerant circulates
between the first separated space 38A and the second separated space 38B, thereby
increasing silencing effect.
[0076] In addition, in the above-described embodiment, the configuration in which the height
of the rib 52 is lowered or the notch portion 58 is partially formed on the rib 52
to circulate the refrigerant has been described. But the present invention is not
limited to this configuration. For example, another configuration, as illustrated
in FIG. 13, may be employed in which on a surface on the refrigerant circulation section
38 side of the muffler plate 42, a groove portion 59 is formed at the position corresponding
to the rib 52. The groove portion 59 and the rib 52 are separated from each other,
which allows the refrigerant to circulate between the groove portion 59 and the rib
52.
[0077] According to this modification, the refrigerant circulates between the first separated
space 38A and the second separated space 38B via the groove portion 59 formed on the
muffler plate 42, which eliminates the need to lower the height of the rib 52. Therefore,
the rigidity of the upper bearing 22 can be increased in comparison with the configuration
in which the height of the rib 52 is uniformly lowered along the radial direction
of the upper bearing 22 or the notch portion 58 is partially formed on the rib 52.
[0078] In addition, the groove portion 59 formed on the muffler plate 42 may be formed by
bending an area corresponding to the groove portion 59 of the muffler plate 42 that
is formed of a thin plate. In this configuration, the rigidity of the muffler plate
42 can be increased in comparison with the configuration in which the muffler plate
42 does not have the groove portion 59. In addition, the muffler plate 42 and the
upper bearing 22 are tightened together by bolts, which can also increase rigidity
of the combination of the muffler plate 42 and the upper bearing 22.
[0079] The groove portion formed on the muffler plate 42 may be formed with a method other
than bending. For example, the groove portion may be formed in a concave shape by
digging into the muffler plate 42 having a plate shape at the area corresponding to
the groove portion.
[0080] Furthermore, in the above-described embodiment, the configuration in which with the
first separated space 38A and the second separated space 38B provided in the refrigerant
circulation section 38, the refrigerant circulates between the first separated space
38A and the second separated space 38B has been described. But the present invention
is not limited to this configuration. The rib 52 may be provided in contact with the
muffler plate 42 throughout the radial direction of the upper bearing 22. That is,
the first separated space 38A and the second separated space 38B may be separated
from each other by the rib 52.
[0081] In this configuration, the upper bearing 22, as illustrated in FIG. 9, has the discharge
ports 53 and 54 formed in the first separated space 38A and the second separated space
38B, respectively, of the refrigerant circulation section 38. The discharge port 53,
which is formed in the first separated space 38A, has a discharge valve installed
therein.
[0082] In addition, the muffler plate 42, as illustrated in FIG. 14, has discharge ports
60 and 61 formed on the first separated space 38A side and the second separated space
38B side, respectively.
[0083] Via the discharge port 53, the refrigerant discharged from the first cylinder chamber
17 is supplied to the first separated space 38A of the refrigerant circulation section
38 and stored once therein. The refrigerant is then discharged from the first separated
space 38A toward the motor 5 in the sealed container 2 via the discharge port 60 formed
on the first separated space 38A side of the muffler plate 42. In addition, via the
discharge port 54, the refrigerant discharged from the second cylinder chamber 18
is supplied to the second separated space 38B of the refrigerant circulation section
38 and stored once therein. The refrigerant is then discharged from the second separated
space 38B toward the motor 5 in the sealed container 2 via the discharge port 61 formed
on the second separated space 38B side of the muffler plate 42.
[0084] On this occasion, the refrigerant does not circulate between the first separated
space 38A and the second separated space 38B. Also in this configuration, the refrigerant
is stored in the first separated space 38A and the second separated space 38B, thereby
providing silencing effect.
[0085] Note that although in the above-described embodiment, the configuration in which
the muffler 32 is installed has been described, the present invention is not limited
to this configuration, and a configuration in which the muffler 32 is not installed
can be employed. In addition, in the above-described embodiment, the configuration
in which the multi-cylinder rotary compressor has a plurality of compression mechanisms
has been described. But a configuration in which the multi-cylinder rotary compressor
has a single compression mechanism may be employed.
Reference Signs List
[0086]
1 Compressor
2 Sealed container
5 Motor
6 Compression mechanism
6A First compression mechanism
6B Second compression mechanism
8 Discharge piping
9 Accumulator
10, 11 Intake piping
12 Stator
13 Rotor
14 Drive shaft
17 First cylinder chamber
18 Second cylinder chamber
19 First cylinder main body (Cylinder main body, One cylinder main body)
20 Second cylinder main body (Cylinder main body, Other cylinder main body)
21 Partition plate
22 Upper bearing (Bearing)
23 Lower bearing
30, 31 Intake port
32 Muffler
37 Cylindrical portion
38 Refrigerant circulation section
38A First separated space (Separated space, One separated space)
38B Second separated space (Separated space, Other separated space)
39 Heat-blocking section
40, 41 Recessed portion
42 Muffler plate (Plate portion)
43, 50 Through hole
44 Outer peripheral wall
45 Center wall
46 Partition rib (Wall portion)
47, 48 Discharge port
49 Rib (First rib)
51 Bolt hole
52 Rib (Second rib)
53, 54, 55, 56, 57 Discharge port
58 Notch portion
59 Groove portion
60, 61 Discharge port
1. Verdichter (1), der Folgendes umfasst:
einen Zylinderhauptkörper (19) eines Rotationsverdichtungsmechanismus (6);
ein Lager (22), das auf einer Flächenseite des Zylinderhauptkörpers (19) bereitgestellt
ist und eine Antriebswelle (14) stützt; und
einen Plattenabschnitt (42), der auf einer Flächenseite des Lagers (22) angeordnet
ist, wobei
das Lager (22) Folgendes beinhaltet:
einen Wandabschnitt (46), der gebildet ist, indem er von der einen Fläche des Lagers
(22) aufsteigt und sich in zwei verschiedene Richtungen von einer Mittenseite des
Lagers (22) entlang einer Radialrichtung davon erstreckt;
einen Kältemittelzirkulationsbereich (38), der vom Wandabschnitt (46), von einer Außenumfangswand
(44) des Lagers (22), von einer mittleren Wand (45) des Lagers (22) und vom Plattenabschnitt
(42) umgeben ist, wobei der Kältemittelzirkulationsbereich (38) dazu ausgelegt ist,
es zu erlauben, dass Kältemittel, das aus dem Zylinderhauptkörper (19) ausgegeben
wird, dorthin zirkuliert; und
einen ausgenommenen Abschnitt (41), der am Lager (22) von der Außenumfangswand (44)
des Lagers (22), von der mittleren Wand (45) des Lagers (22) und vom Wandabschnitt
(46) am Lager gebildet wird, und
einen Wärmeblockierbereich (39), der vom ausgenommenen Abschnitt und vom Plattenabschnitt
umgeben, und vom Kältemittelzirkulationsbereich (38) durch den Wandabschnitt (46)
und den Plattenabschnitt (42) getrennt ist, um zu verhindern, dass das Kältemittel
dorthin zirkuliert,
dadurch gekennzeichnet, dass das Lager (22) ferner eine erste Rippe (49) beinhaltet, die gebildet ist, indem sie
von der Fläche des Lagers (22) aufsteigt und sich von der mittleren Wand (45) zur
Außenumfangswand (44) entlang der Radialrichtung des Lagers (22) im Wärmeblockierbereich
(39) erstreckt.
2. Verdichter (1) nach Anspruch 1, wobei:
die Anzahl der bereitgestellten Zylinderhauptkörper (19, 20) mindestens zwei ist;
das Lager (22) ferner eine zweite Rippe (52) beinhaltet, die gebildet ist, indem sie
von der Fläche des Lagers (22) aufsteigt und sich entlang der Radialrichtung des Lagers
(22) im Kältemittelzirkulationsbereich (38) erstreckt;
der Kältemittelzirkulationsbereich (38) durch die zweite Rippe (52) in mindestens
zwei getrennte Räume (38A, 38B) geteilt ist; und
einer der getrennten Räume (38A) dazu ausgelegt ist, es zu erlauben, dass Kältemittel
von einem der Zylinderhauptkörper (19) dorthin ausgegeben wird, und der andere getrennte
Raum (38B) dazu ausgelegt ist, es zu erlauben, dass Kältemittel vom anderen Zylinderhauptkörper
(20) dorthin ausgegeben wird.
3. Verdichter (1) nach Anspruch 2, wobei:
die mindestens zwei getrennten Räume (38A, 38B) dazu ausgelegt sind, es zu erlauben,
dass Kältemittel darin von einem zu einem anderen zirkuliert; und
am Plattenabschnitt (42) nur ein Ausgabeanschluss (55) gebildet ist, wobei der Ausgabeanschluss
(55) dazu ausgelegt ist zu bewirken, dass Kältemittel von den getrennten Räumen (38A,
38B) dadurch ausgegeben wird.
4. Verdichter (1) nach Anspruch 2 oder 3, wobei an der zweiten Rippe (52) ein Rillenabschnitt
(58) gebildet ist, der es erlaubt, dass Kältemittel in den mindestens zwei getrennten
Räumen (38A, 38B) von einem zu einem anderen zirkuliert, wobei der Rillenabschnitt
(58) durch teilweises Einschneiden des Lagers (22) in der Radialrichtung gebildet
wird.
5. Verdichter (1) nach Anspruch 2 oder 3, wobei am Plattenabschnitt (42) ein Nutabschnitt
(59) gebildet ist, der es erlaubt, dass Kältemittel in den mindestens zwei getrennten
Räumen (38A, 38B) von einem zu einem anderen zirkuliert, wobei der Nutabschnitt (59)
in einer Position gebildet ist, die der zweiten Rippe (52) entspricht.