FORM 2
THE PATENTS ACT, 1970
(39 of 1970)
&
THE PATENTS RULES, 2003
COMPLETE SPECIFICATION
[See section 10, Rule 13]
COMPRESSOR AND REFRIGERATION CYCLE APPARATUS;
MITSUBISHI ELECTRIC CORPORATION, A CORPORATION ORGANISED AND
EXISTING UNDER THE LAWS OF JAPAN, WHOSE ADDRESS IS 7-3, MARUNOUCHI
2-CHOME, CHIYODA-KU, TOKYO 100-8310, JAPAN
THE FOLLOWING SPECIFICATION PARTICULARLY DESCRIBES THE INVENTION
AND THE MANNER IN WHICH IT IS TO BE PERFORMED.
2
DESCRIPTION
Title of Invention
COMPRESSOR AND REFRIGERATION CYCLE APPARATUS
Technical Field5
[0001]
The present disclosure relates to a compressor and a refrigeration cycle
apparatus, and in particular, to the configuration of a refrigerant flow passage in the
compressor.
Background Art10
[0002]
For example, a scroll compressor includes a hermetic container, a compression
mechanism unit that includes a fixed scroll and an orbiting scroll, and an electric motor
that drives the orbiting scroll of the compression mechanism unit to rotate the orbiting
scroll. When a high-pressure refrigerant gas obtained by compression by the15
compression mechanism unit and discharged from a discharge port of the fixed scroll is
discharged to the outside of the hermetic container as it is, a refrigeration machine oil
that lubricates a bearing portion of a drive unit is also discharged along with the
refrigerant gas to the outside of the hermetic container, since the refrigeration machine
oil is contained in the refrigerant gas. Therefore, the amount of the refrigeration20
machine oil stored in a bottom portion of the hermetic container is reduced, and for
example, seizure occurs in a bearing portion of a rotation shaft that rotates the orbiting
scroll, due to oil shortage, thus causing a failure in the scroll compressor.
[0003]
In order to solve the above problem, scroll compressors configured to reduce the25
amount of a refrigeration machine oil that flows out to the outside of a hermetic
container have been proposed (see, for example, Patent Literature 1). A scroll
compressor disclosed in Patent Literature 1 includes a compression mechanism unit, an
electric motor that drives the compression mechanism unit, and balance weights for
counteracting an imbalance between a moment and a centrifugal force generated by the30
3
compression mechanism unit. The balance weights are fixed to an upper end and a
lower end of a rotor. Furthermore, cups are provided to surround the balance weights.
The cups prevent the refrigerant and the refrigeration machine oil in the hermetic
container from being mixed by the balance weights.
[0004]5
A gas mixture of the refrigerant gas and the refrigeration machine oil discharged
from the compression mechanism unit is guided to a lower portion of the hermetic
container through a refrigerant flow passage. The gas mixture that has reached the
lower portion of the hermetic container is discharged toward the compression
mechanism unit via through-passages in the rotor, and flows into a discharge cover10
attached to an end face of the compression mechanism. In the process in which the
gas mixture passes through the refrigerant flow passage and the through-passages, the
refrigeration machine oil contained in the gas mixture is separated therefrom, thereby
reducing the amount of the refrigeration machine oil contained in the gas mixture.
Citation List15
Patent Literature
[0005]
Patent Literature 1: Japanese Unexamined Patent Application Publication No.
2014-109194
Summary of Invention20
Technical Problem
[0006]
In the scroll compressor disclosed in Patent Literature 1, the balance weight is
fixed to counteract an imbalance in force that is caused by an orbital motion of an
orbiting scroll. The refrigeration machine oil and the refrigerant gas discharged25
through the through-passages from below the rotor are mixed by rotation of the balance
weight that is performed as in blades of a fan. Thus, the refrigerant and the
refrigeration machine oil discharged through the through-passages in the rotor are re-
mixed by the balance weight, thus reducing the amount of refrigeration machine oil that
4
is separated from the refrigerant. As a result, it is not possible to sufficiently prevent
outflow of the refrigerant machine oil.
[0007]
The present disclosure is applied to solve the above problem, and relates to a
compressor and a refrigeration cycle apparatus that reduce mixture of refrigerant gas5
and refrigeration machine oil from which is caused by a balance weight and that are
improved in efficiency of separation of the refrigeration machine oil from the refrigerant.
Solution to Problem
[0008]
A compressor according to an embodiment of the present disclosure includes: a10
hermetic container including an oil reservoir configured to store a refrigeration machine
oil; a compression mechanism unit provided in the hermetic container and configured to
compress refrigerant; an electric motor provided in the hermetic container and
configured to generate a driving force; and a rotation shaft configured to transmit the
driving force generated by the electric motor to the compression mechanism unit. The15
electric motor includes; a rotor fixed to the rotation shaft; a stator fixed to the hermetic
container and including a refrigerant flow passage through which refrigerant gas
discharged from the compression mechanism unit is guided to a lower portion of the
hermetic container; a first balance weight fixed to an end face of the rotor that faces the
compression mechanism unit; and a first cup-shaped member having a side wall that20
surrounds an outer peripheral surface of the first balance weight. The first balance
weight includes a light weight portion having an arc shape and a heavy weight portion
having an arc shape, the light weight portion and the heavy weight portion being
connected to each other, and the first balance weight further includes a separation
portion that is a recessed portion formed at an end face of the first balance weight and25
that is open in the outer peripheral surface of the first balance weight, the end face of
the first balance weight facing the rotor. The separation portion is provided to face an
opening of a through-passage that is provided to extend through the rotor in an axial
direction. The side wall of the first cup-shaped member has an outlet portion that is
located outward of the separation portion in a radial direction.30
5
[0009]
A refrigeration cycle apparatus according to another embodiment of the present
disclosure includes the compressor.
Advantageous Effects of Invention
[0010]5
According to the embodiments of the present disclosure, the compressor causes
the refrigeration machine oil that passes together with the refrigerant through the
through-passage in the rotor together with the refrigerant to collide with the separation
portion provided at the end face of the first balance weight provided above the rotor, to
thereby discharge the refrigeration machine oil and the refrigerant to the outside of the10
first cup-shaped member through the outlet portion provided at the side wall of the first
cup-shaped member. Therefore, it is possible to reduce stirring of the refrigeration
machine oil that is caused by the first balance weight and to reduce the flow of the
refrigeration machine oil together with the refrigerant, into an opening of a discharge
cover that communicates with a discharge pipe. As a result, the compressor and the15
refrigeration cycle apparatus are improved in efficiency of separation the refrigeration
machine oil from the refrigerant.
Brief Description of Drawings
[0011]
[Fig. 1] Fig. 1 is a vertical sectional view of a scroll compressor 100 that is a20
compressor according to Embodiment 1.
[Fig. 2] Fig. 2 illustrates an example of a refrigeration cycle apparatus using the
scroll compressor 100 according to Embodiment 1.
[Fig. 3] Fig. 3 is a cross-sectional view illustrating first passages 4f provided at an
outer peripheral portion of a guide frame 4 as illustrated in Fig. 1.25
[Fig. 4] Fig. 4 includes sectional views of a rotor 5a of the scroll compressor 100
according to Embodiment 1.
[Fig. 5] Fig. 5 includes diagrams of a configuration of an upper portion of the rotor
5a of the scroll compressor 100 according to Embodiment 1.
6
[Fig. 6] Fig. 6 is an enlarged view of a surrounding structure of a first cup-shaped
member 17 of the scroll compressor 100 according to Embodiment 1.
[Fig. 7] Fig. 7 is a sectional view of a stator 5b of an electric motor 5 of the scroll
compressor 100 according to Embodiment 1.
[Fig. 8] Fig. 8 includes diagrams of a configuration of an upper portion of the rotor5
5a of the scroll compressor 100 according to Embodiment 2.
[Fig. 9] Fig. 9 includes diagrams of a configuration of an upper portion of the rotor
5a of the scroll compressor 100 according to Embodiment 3.
[Fig. 10] Fig. 10 includes diagrams of a configuration of an upper portion of the
rotor 5a of the scroll compressor 100 according to Embodiment 4.10
[Fig. 11] Fig. 11 includes diagrams of a configuration of an upper portion of the
rotor 5a of a modification of the scroll compressor 100 according to Embodiment 4.
[Fig. 12] Fig. 12 includes diagrams of a configuration of an upper portion of the
rotor 5a of another modification of the scroll compressor 100 according to Embodiment
4.15
[Fig. 13] Fig. 13 includes diagrams of a configuration of an upper portion of the
rotor 5a of still another modification of the scroll compressor 100 according to
Embodiment 4.
[Fig. 14] Fig. 14 includes diagrams of a configuration of an upper portion of the
rotor 5a of the scroll compressor 100 according to Embodiment 5.20
[Fig. 15] Fig. 15 includes diagrams of a configuration of an upper portion of the
rotor 5a of a modification of the scroll compressor 100 according to Embodiment 5.
[Fig. 16] Fig. 16 includes diagrams of a configuration of an upper portion of the
rotor 5a of the scroll compressor 100 according to Embodiment 6.
[Fig. 17] Fig. 17 includes diagrams of a configuration of an upper portion of the25
rotor 5a of a modification of the scroll compressor 100 according to Embodiment 6.
[Fig. 18] Fig. 18 includes diagrams of a configuration of an upper portion of the
rotor 5a of the scroll compressor 100 according to Embodiment 7.
[Fig. 19] Fig. 19 is a diagram of a configuration of an upper portion of the rotor 5a
of the scroll compressor 100 according to Embodiment 8.30
7
[Fig. 20] Fig. 20 is a diagram of a configuration of an upper portion of the rotor 5a
of the scroll compressor 100 according to Embodiment 9.
Description of Embodiments
[0012]
A compressor according to each of embodiments of the present disclosure will be5
described with reference to the drawings. As the compressor according to each
embodiment, a vertical scroll compressor will be described below by way of example,
but the compressor according to each embodiment may be a horizontal compressor or
a compressor including a compression mechanism unit that is not a scroll compression
mechanism unit. In addition, figures including Fig. 1 which will be referred to below are10
schematic, and relationships in size between components in the figures may differ from
those of actual ones.
[0013]
Embodiment 1
Fig. 1 is a vertical sectional view of a scroll compressor 100 that is a compressor15
according to Embodiment 1. Fig. 2 illustrates an example of a refrigeration cycle
apparatus using the scroll compressor 100 according to Embodiment 1. A refrigeration
cycle apparatus 200 is applicable to, for example, various industrial machines such as a
refrigerator, a freezer, an air-conditioning apparatus, a refrigeration apparatus, and a
water heater. The scroll compressor 100 is one of the components of the refrigeration20
cycle apparatus 200.
[0014]
Refrigeration Cycle Apparatus 200
The refrigeration cycle apparatus 200 includes the scroll compressor 100, a four-
way switching valve 103, an indoor heat exchanger 106, a pressure reducing device25
105, and an outdoor heat exchanger 104, which are sequentially connected by pipes.
A suction muffler 101 is connected to a suction side of the scroll compressor 100 and to
the four-way switching valve 103. The four-way switching valve 103 is also connected
to a discharge side of the scroll compressor 100, and switches the flow direction of
8
refrigerant that flows from the scroll compressor 100 and switches the flow direction of
refrigerant that flows in a circuit of the refrigeration cycle apparatus 200.
[0015]
In Embodiment 1, the refrigeration cycle apparatus 200 is, for example, an air-
conditioning apparatus. The refrigeration cycle apparatus 200 causes the four-way5
switching valve 103 to perform the above switching operation to switch an operation to
be performed, between a cooling operation and a heating operation. In general, in air-
conditioning apparatuses, the indoor heat exchanger 106 is provided in an indoor unit,
and the scroll compressor 100, the four-way switching valve 103, the outdoor heat
exchanger 104, and the pressure reducing device 105 are provided in an outdoor unit.10
[0016]
For example, in the heating operation of the air-conditioning apparatus, the
connection state of the four-way switching valve 103 is switched to a state indicated by
solid lines in Fig. 2. High-temperature and high-pressure refrigerant obtained by
compression by the scroll compressor 100 flows into the indoor heat exchanger 106,15
which operates as a condenser, and is condensed and liquefied to change into liquid
refrigerant. The liquid refrigerant is reduced in pressure in the pressure reducing
device 105 to change low-temperature and low-pressure two-phase gas-liquid
refrigerant. The low-temperature and low-pressure two-phase gas-liquid refrigerant
flows into the outdoor heat exchanger 104. The two-phase gas-liquid refrigerant is20
evaporated and gasified in the outdoor heat exchanger 104, which operates as an
evaporator, to change into gas refrigerant. The gas refrigerant returns to the scroll
compressor 100 through the four-way switching valve 103. That is, in the heating
operation of the refrigeration cycle apparatus 200, the refrigerant circulates as indicated
by solid arrows in Fig. 2. In this circulation, at the outdoor heat exchanger 10425
operating as an evaporator, the refrigerant sent thereto exchanges with outdoor air to
receive heat. The refrigerant that has received heat is sent to the indoor heat
exchanger 106 operating as a condenser, and exchanges heat with indoor air to heat
the indoor air.
[0017]30
9
In the cooling operation of the air-conditioning apparatus, the connection state of
the four-way switching valve 103 is switched to a state indicated by dashed arrows in
Fig. 2. The high-temperature and high-pressure gas refrigerant obtained by
compression by the scroll compressor 100 flows into the outdoor heat exchanger 104,
which operates as a condenser, and is condensed and liquefied to change into liquid5
refrigerant. The liquid refrigerant is reduced in pressure in the pressure reducing
device 105 to change low-temperature and low-pressure two-phase gas-liquid
refrigerant, and the low-temperature and low-pressure two-phase gas-liquid refrigerant
flows into the indoor heat exchanger 106. The two-phase gas-liquid refrigerant is
evaporated and gasified in the indoor heat exchanger 106, which operates as an10
evaporator, to change into gas refrigerant. The gas refrigerant returns to the scroll
compressor 100 through the four-way switching valve 103.
[0018]
That is, when the operation is changed from the heating operation to the cooling
operation, the indoor heat exchanger 106 which operates as a condenser is changed to15
operate as an evaporator, and the outdoor heat exchanger 104 which operates as an
evaporator is changed to operate as a condenser. Thus, the refrigerant circulates as
indicated by dashed arrows in Fig. 2. In this circulation, the refrigerant exchanges heat
with indoor air in the indoor heat exchanger 106 operating as an evaporator to receive
heat from the indoor air, that is, to cool the indoor air. The refrigerant that has received20
heat is sent to the outdoor heat exchanger 104 operating as a condenser, and
exchanges heat with outdoor air to transfer heat to the outdoor air.
[0019]
In this case, for example, R410A refrigerant, R32 refrigerant, or R290 refrigerant
is generally used as the refrigerant which circulates in the refrigeration cycle apparatus25
200.
[0020]
Scroll Compressor 100
As described above, the scroll compressor 100 sucks the refrigerant which
circulates in the refrigeration cycle apparatus 200, compresses the sucked refrigerant to30
10
change it into high-temperature and high-pressure refrigerant, and discharges the high-
temperature and high-pressure refrigerant. The scroll compressor 100 includes a
compression mechanism unit 14 provided in a hermetic container 10. The
compression mechanism unit 14 is a combination of a fixed scroll 1 and an orbiting
scroll 2 that revolves (orbits) relative to the fixed scroll 1. In addition, the scroll5
compressor 100 includes an electric motor 5 that drives the orbiting scroll 2 via a
rotation shaft 6. Regarding Embodiment 1, the following description is made by way of
example with respect to the case where the scroll compressor 100 is the vertical scroll
compressor 100. In the vertical scroll compressor 100, for example, the compression
mechanism unit 14 is provided in an upper portion of the hermetic container 10, and the10
electric motor 5 is provided below the compression mechanism unit 14.
[0021]
Compression Mechanism Unit 14
The compression mechanism unit 14 includes the fixed scroll 1, the orbiting scroll
2, a compliant frame 3, and the guide frame 4. The fixed scroll 1 includes a base plate15
portion 1a and a plate-like scroll wrap 1b. The plate-like scroll wrap 1b projects from a
one surface (lower surface in Fig. 1) of the base plate portion 1a that faces a side where
the electric motor 5 is provided. The orbiting scroll 2 includes a base plate portion 2a
and a plate-like scroll wrap 2b. The plate-like scroll wrap 2b projects from a surface
(upper surface in Fig. 1) of the base plate portion 2a that faces the fixed scroll 1, and20
has substantially the same shape as the plate-like scroll wrap 1b. The plate-like scroll
wrap 1b of the fixed scroll 1 and the plate-like scroll wrap 2b of the orbiting scroll 2 are
engaged with each other, thereby forming a compression chamber 1f whose volume is
relatively changed by revolution of the orbiting scroll 2.
[0022]25
The scroll compressor 100 includes the guide frame 4, which supports the
compression mechanism unit 14 from below. The guide frame 4 is fixed to the inside
of the hermetic container 10. The fixed scroll 1 is fastened to the guide frame 4 by
bolts (not illustrated) at its outer peripheral portion. A suction pipe 13 which guides
refrigerant gas into the compression chamber 1f is provided at an outer peripheral30
11
portion of the base plate portion 1a of the fixed scroll 1. The suction pipe 13 is
connected to a suction port 1e where a suction check valve 1g is provided. At a
central portion of the base plate portion 1a of the fixed scroll 1, a discharge port 1d is
provided to allow the high-pressure refrigerant gas obtained by compression to be
discharged through the discharge port 1d. The high-pressure refrigerant gas obtained5
by compression is to be discharged to an upper space 10a in the hermetic container 10.
As described below, the refrigerant gas discharged to the upper space 10a is guided to
an oil separating mechanism through a refrigerant flow passage 30, and the refrigerant
gas separated from a refrigeration machine oil is discharged through a discharge pipe
12.10
[0023]
The orbiting scroll 2 is prevented by an Oldham mechanism 9 from rotating on the
axis of the orbiting scroll 2. The orbiting scroll 2 is configured to revolve (orbit) relative
to the fixed scroll 1 without rotating on its axis. At an outer peripheral portion of the
base plate portion 1a of the fixed scroll 1, a pair of two Oldham guide grooves 1c are15
formed substantially linearly. With the Oldham guide grooves 1c, a pair of two fixed-
side keys 9a of the Oldham mechanism 9 are engaged such that the fixed-side keys 9a
are slidable in a reciprocating manner. Furthermore, at an outer peripheral portion of
the base plate portion 2a of the orbiting scroll 2, a pair of two Oldham guide grooves 2c
are formed substantially linearly. The Oldham guide grooves 2c have a phase20
difference of 90 degrees relative to the Oldham guide grooves 1c of the fixed scroll 1.
With the Oldham guide grooves 2c, a pair of two orbiting-side keys 9b of the Oldham
mechanism 9 are engaged such that the orbiting-side keys 9b are slidable in a
reciprocating manner. The Oldham mechanism 9 formed as described above enables
the orbiting scroll 2 to orbit (revolve) without rotating on its axis.25
[0024]
A boss portion 2d having a hollow cylindrical shape is formed at a central portion
of a surface (the lower side in Fig. 1) of the orbiting scroll 2 that is located opposite to a
surface on which the plate-like scroll wrap 2b is formed. Into the boss portion 2d, an
12
eccentric shaft portion 6a provided at an upper end portion of the rotation shaft 6 is
inserted.
[0025]
A thrust surface 2f is formed at a surface (the lower side in Fig. 1) of the base
plate portion 2a of the orbiting scroll 2 that is located opposite to the plate-like scroll5
wrap 2b. The thrust surface 2f is slidable into a pressure contact with a thrust bearing
3a of the compliant frame 3. In addition, a bleeding hole 2g is provided in the base
plate portion 2a of the orbiting scroll 2 such that the bleeding hole 2g extends through
the compression chamber 1f and the thrust surface 2f, thus forming a structure in which
refrigerant gas being compressed is extracted and guided to the thrust surface 2f.10
[0026]
The compliant frame 3 is accommodated in space defined by the guide frame 4.
The compliant frame 3 supports the orbiting scroll 2 and the Oldham mechanism 9 from
below and supports the rotation shaft 6 in an axial direction and a radial direction of the
rotation shaft 6. In addition, the compliant frame 3 is supported by the guide frame 4.15
[0027]
The compliant frame 3 has an upper cylindrical surface 3p and a lower cylindrical
surface 3s at its outer peripheral portion. An inner peripheral portion of the guide
frame 4 has an upper cylindrical surface 4c, to which the upper cylindrical surface 3p of
the compliant frame 3 is fitted, and a lower cylindrical surface 4d, to which the lower20
cylindrical surface 3s of the compliant frame 3 is fitted. At the upper cylindrical surface
4c and the lower cylindrical surface 4d, the compliant frame 3 is supported by the guide
frame 4 in the radial direction.
[0028]
At a central portion of the lower cylindrical surface 3s of the compliant frame 3, a25
main bearing 3c and an auxiliary main bearing 3d are provided. The main bearing 3c
and the auxiliary main bearing 3d support, in the radial direction, the rotation shaft 6,
which is driven to rotate by the rotor 5a of the electric motor 5.
[0029]
13
A communication hole 3e is provided to extend from a surface of the thrust
bearing 3a through the outer peripheral portion of the compliant frame 3 in the axial
direction from a surface of the thrust bearing 3a. A thrust bearing opening 3t which is
open at the upper end of the communication hole 3e is provided to face the bleeding
hole 2g which extends through the base plate portion 2a of the orbiting scroll 2.5
[0030]
At the outer periphery of the thrust bearing 3a of the compliant frame 3, a
reciprocation slide surface 3b is formed. The reciprocation slide surface 3d is a
surface over which an Oldham mechanism annular portion 9c slides in a reciprocating
manner. In addition, the compliant frame 3 has a communication hole 3f which10
extends from its inner peripheral surface to an outer peripheral surface thereof. The
communication hole 3f is formed in such a manner as to cause a base-plate outer
peripheral portion space 2k and a frame upper space 4a to communicate with an
internal space of the Oldham mechanism annular portion 9c. At the compliant frame 3,
an intermediate pressure adjusting valve 3g, an intermediate pressure adjusting valve15
holder 3h, and an intermediate pressure adjusting spring 3k are provided between the
frame upper space 4a and a boss-portion outer space 2n. The intermediate pressure
adjusting valve 3g adjusts the pressure in the boss-portion outer space 2n The
intermediate pressure adjusting spring 3k is accommodated in an intermediate pressure
adjusting valve space 3n such that the intermediate pressure adjusting spring 3k is20
contracted shorter than its equilibrium length. In Embodiment 1, the compliant frame 3
and the guide frame 4 are formed as separate components, but are not limited thereto
and may be formed as a single frame.
[0031]
A frame lower space 4b is defined by an inner surface of the guide frame 4 and25
an outer surface of the compliant frame 3, and is partitioned into an upper region and a
lower region by ring-shaped sealing members 7a and 7b. In this example, two ring-
shaped sealing grooves that accommodate the ring-shaped sealing members 7a and 7b
are formed in the outer peripheral surface of the compliant frame 3, but may be formed
in an inner peripheral surface of the guide frame 4. The frame lower space 4b30
14
communicates only with the communication hole 3e of the compliant frame 3 and has a
structure in which the refrigerant gas that is being compressed and is supplied through
the bleeding hole 2g is enclosed. In addition, the base-plate outer peripheral portion
space 2k is a space which is located at the outer periphery of the thrust bearing 3a and
whose upper and lower sides are surrounded by the base plate portion 2a of the orbiting5
scroll 2 and the compliant frame 3, and is also a low-pressure space having a suction
gas atmosphere (suction pressure).
[0032]
Fig. 3 is a cross-sectional view illustrating first passages 4f provided at an outer
peripheral portion of the guide frame 4 as illustrated in Fig. 1. As illustrated in Fig. 3,10
an outer peripheral surface 40 of the guide frame 4 is fixed to the hermetic container 10
by, for example, shrinkage fitting or welding. The outer peripheral portion of the guide
frame 4 and the outer peripheral portion of the fixed scroll 1 has cutouts forming the first
passages 4f. That is, an outer peripheral portion of the compression mechanism unit
14 has the first passages 4f, which cause a space located above the compression15
mechanism unit 14 and a space located below the compression mechanism unit 14 to
communicate with each other.
[0033]
The refrigerant gas discharged to the upper space 10a of the hermetic container
10 through the discharge port 1d flows downward in the hermetic container 10 through20
the first passages 4f. The refrigerant gas that has passed through the electric motor 5
provided below the compression mechanism unit 14 flows to a bottom portion of the
hermetic container 10 in which an oil reservoir portion 10b is formed. The oil reservoir
portion 10b located in the bottom portion of the hermetic container 10 stores the
refrigeration machine oil 11.25
[0034]
The hermetic container 10 is provided with the discharge pipe 12, through which
the refrigerant gas compressed in the hermetic container 10 is discharged to the outside
of the hermetic container 10. The first passages 4f are provided opposite to the
discharge pipe 12, with a central axis of the rotation shaft 6 interposed between the first30
15
passages 4f and the discharge pipe 12. The guide frame 4 has a first discharge
passage 4g which communicates with the discharge pipe 12. The first discharge
passage 4g is formed to be open in a side and a portion closer to the center of a lower
end face and to cause a space below the guide frame 4 and the discharge pipe 12 fixed
to the hermetic container 10 to communicate with each other.5
[0035]
At a lower end portion of the guide frame 4, a lower cylindrical portion 41 (where
the lower cylindrical surface 4d is formed) which supports the lower cylindrical surface
3s of the compliant frame 3 from the outside in the radial direction is formed. In
addition, a discharge cover 16 is fixed to an end face of the guide frame 4 that faces the10
electric motor 5 and at which the first discharge passage 4g is open, such that the
discharge cover 16 surrounds the lower cylindrical portion 41. The discharge cover 16
has an opening 16b which is located at the central portion thereof and faces downward.
A second discharge passage 16a is defined by the discharge cover 16 and the end face
of the guide frame 4, and communicates with the first discharge passage 4g.15
[0036]
Electric Motor 5
The electric motor 5 drives the rotation shaft 6 to rotate the rotation shaft 6 with a
driving force generated by electric power, and includes the rotor 5a, which is fixed to the
rotation shaft 6, and a stator 5b, which is fixed to the hermetic container 10. The rotor20
5a is fixed to the rotation shaft 6 by, for example, shrinkage fitting. When energization
of the stator 5b is started, the rotor 5a is driven and rotated to rotate the rotation shaft 6.
In addition, at the upper end portion of the rotation shaft 6, the eccentric shaft portion 6a
is formed. The eccentric shaft portion 6a is rotatably engaged with an orbiting bearing
2e of the orbiting scroll 2. In addition, a rotation shaft balance weight 6f is fixed to a25
lower part of the eccentric shaft portion 6a by, for example, shrinkage fitting.
[0037]
As illustrated in Fig. 1, a glass terminal 10c is provided in a side surface of the
hermetic container 10, and is connected to the stator 5b of the electric motor 5 by leads
5j.30
16
[0038]
A main shaft portion 6b is formed at a lower side of the eccentric shaft portion 6a
and a fixation portion 6g to which the rotation shaft balance weight 6f is fixed. The
main shaft portion 6b is rotatably engaged with the main bearing 3c and the auxiliary
main bearing 3d of the compliant frame 35
[0039]
A sub-shaft portion 6c is formed at a lower end portion of the rotation shaft 6.
The sub-shaft portion 6c is rotatably engaged with a sub-bearing 8a of a sub-frame 8
fixed to a lower portion of the hermetic container 10. The sub-frame 8 is fixed to the
lower portion of the hermetic container 10 by, for example, shrinkage fitting, and has an10
inflow hole 8b through which the refrigeration machine oil 11 flows into the oil reservoir
portion 10b formed at a lower end portion of the hermetic container 10.
[0040]
The rotor 5a of the electric motor 5 is fixed, between the sub-shaft portion 6c
located at the lower end portion of the rotation shaft 6 and the main shaft portion 6b15
located at the upper end portion of the rotation shaft 6, to the rotation shaft 6 by, for
example, shrinkage fitting. The rotation shaft 6 has an oil supply passage 6d, which is
a hole extending therethrough in the axial direction. An oil supply port 6e is attached to
a lower end of the oil supply passage 6d. The oil supply port 6e is soaked in the
refrigeration machine oil 11 stored in the bottom portion of the hermetic container 10.20
Thus, the refrigeration machine oil 11 is sucked up through the oil supply port 6e by an
oil supply mechanism or a pump mechanism provided at a lower part of the rotation
shaft 6. The upper end of the oil supply passage 6d is open in the boss portion 2d of
the orbiting scroll 2. The sucked-up refrigeration machine oil 11 flows out to the
orbiting bearing 2e through an upper end opening of the oil supply passage 6d and25
lubricates the eccentric shaft portion 6a and the orbiting bearing 2e.
[0041]
The rotation shaft 6 has an oil supply hole 6h which branches from the oil supply
passage 6d. The oil supply hole 6h extends in a direction crossing the oil supply
passage 6d. The refrigeration machine oil 11 is supplied to the auxiliary main bearing30
17
3d through the oil supply hole 6h and lubricates the auxiliary main bearing 3d and the
main shaft portion 6b. The rotation shaft 6 has an oil supply hole (not illustrated)
through which the refrigeration machine oil 11 is supplied to the main bearing 3c and
which is omitted in Fig. 1.
[0042]5
Rotor 5a
Fig. 4 includes sectional views of the rotor 5a of the scroll compressor 100
according to Embodiment 1. Fig. 4, (a), is a vertical sectional view including the central
axis of the rotor 5a. Fig. 4, (b), is a cross sectional view perpendicular to the central
axis of the rotor 5a. The rotor 5a has a cylindrical shape and has a shaft fixing hole 5h10
to which the rotation shaft 6 is fixed at a central portion of the rotor 5a. In addition,
through-passages 5f are formed around the shaft fixing hole 5h such that the through-
passages 5f extend parallel to the central axis and extend through the rotor 5a in an up-
down direction. In Embodiment 1, the through-passages 5f are provided at four
positions around the central axis of the rotor 5a and are equidistant from the central15
axis.
[0043]
A first balance weight 15a is fixed to an upper end face 52 of the rotor 5a. A
second balance weight 15i is fixed to a lower end face 53 of the rotor 5a. The first
balance weight 15a and the second balance weight 15i are fixed symmetrical with20
respect to the central axis of the rotation shaft 6 as viewed in the axial direction of the
rotation shaft 6. In other words, the first balance weight 15a and the second balance
weight 15i are provided such that their centers of gravity are eccentric relative to the
central axis of the rotation shaft 6 and are located symmetrical relative to the central
axis.25
[0044]
Fig. 5 includes diagrams of a configuration of an upper portion of the rotor 5a of
the scroll compressor 100 according to Embodiment 1. Fig. 5, (a), is a diagram
obtained as the rotor 5a is viewed in the axial direction. Fig. 5, (b), illustrates a section
taken along A-A in Fig. 5, (a). As illustrated in Fig. 5, the first balance weight 15a has30
18
an annular shape such that a light weight portion 15b having an arc shape and a heavy
weight portion 15c having an arc shape are connected to surround the central axis. In
addition, the first balance weight 15a is fixed to the upper end face of the rotor 5a.
Between the first balance weight 15a and the upper end face of the rotor 5a, a first cup-
shaped member 17 is provided.5
[0045]
As illustrated in Fig. 5, (a), the light weight portion 15b includes an arc portion 15p
located along the outer periphery of the rotor 5a, and two projecting portions 15q formed
such that an inner peripheral surface 15k of the arc portion 15p partially projects toward
the center. The projecting portions 15q project to the vicinity of the shaft fixing hole 5h10
of the rotor 5a, and have fastener holes 15d through which fasteners 15h for fixation of
the first balance weight 15a to the rotor 5a pass.
[0046]
The heavy weight portion 15c has a semicylindrical shape and is thicker in a
direction along the central axis of the rotor 5a than the light weight portion 15b. In15
addition, the heavy weight portion 15c includes a contact portion 15f having fastener
holes 15d which allow fasteners 15h to pass therethrough, and separation portions 15g
which are formed to face the upper end face of the rotor 5a and are recessed from a
surface which is in contact with the first cup-shaped member 17. As illustrated in Fig.
5, (b), the separation portions 15g are recessed portions formed at a surface facing the20
upper end face of the rotor 5a. The recessed portions are open in an outer peripheral
surface of the first balance weight 15a. The separation portions 15g are formed at
respective positions associated with the through-passages 5f in the rotor 5a. That is,
the separation portions 15g are recessed portions formed at portions of a lower end
face of the first balance weight 15a, and spaces surrounded by the recessed portions25
are provided to communicate with the outside from the outer peripheral surface of the
first balance weight 15a.
[0047]
Together with the second balance weight 15i fixed to the lower end face of the
rotor 5a and the rotation shaft balance weight 6f fixed to the upper end portion of the30
19
rotation shaft 6, the first balance weight 15a counteracts an imbalance between a
moment force and a centrifugal force generated by the orbital motion of the orbiting
scroll 2. That is, the compression mechanism unit 14 catches dynamic balance and
static balance with the first balance weight 15a, the second balance weight 15i, and the
rotation shaft balance weight 6f.5
[0048]
First Cup-shaped Member 17 and Second Cup-shaped Member 18
As illustrated in Fig. 1, the first cup-shaped member 17, which surrounds the
outer peripheral surface of the first balance weight 15a from the outside in the radial
direction, is fixed to the upper end face of the rotor 5a. The second cup-shaped10
member 18, which surrounds an outer peripheral surface of the second balance weight
15i from the outside, is fixed to the lower end face of the rotor 5a. The first cup-shaped
member 17 and the second cup-shaped member 18 each formed in the shape of a
cylinder having a bottom and each have holes that are located at the central portion
thereof into which the rotation shaft 6 is inserted, at respective positions associated with15
the through-passages 5f in the rotor 5a, and at portions thereof into which the fasteners
15h are inserted.
[0049]
Fig. 6 is an enlarged view of a surrounding structure of the first cup-shaped
member 17 of the scroll compressor 100 according to Embodiment 1. At an upper end20
of the first cup-shaped member 17, an opening 17a is provided opposite to the opening
16b of the discharge cover 16. A distal end of a side wall 17c of the first cup-shaped
member 17 further projects toward the compression mechanism unit 14 than an end
face of the first balance weight 15a. In Embodiment 1, the distal end of the side wall
17c of the first cup-shaped member 17 is located below the opening 16c of the25
discharge cover 16 in the axial direction, but may be located above the opening 16c or
at a position that is the same as the opening 16c in the axial direction. The side wall
17c of the first cup-shaped member 17 has outlet portions 17b located at respective
positions which overlap with the positions of the separation portions 15g which are open
in the radial direction of the first balance weight 15a. The refrigerant that has passed30
20
through the through-passages 5f passes through the separation portions 15g and then
through the outlet portions 17b to flow to the outside of the side wall 17c of the first cup-
shaped member 17.
[0050]
The relationship between an inside diameter D of the opening 16b of the5
discharge cover 16 and an inside diameter d of the opening 17a of the first cup-shaped
member 17 satisfies D < d. That is, the inside diameter of the opening 16b of the
discharge cover 16 is smaller than the inside diameter d of the opening 17a located at
the upper end of the first cup-shaped member 17. This reduces the flow of the
refrigeration machine oil discharged to the outside of the first cup-shaped member 17,10
into the opening 16b located inward of the side wall 17c of the first cup member 17.
[0051]
The second cup-shaped member 18 is attached to the lower end face of the rotor
5a such that an opening of the second cup-shaped member 18 faces downward. The
second cup-shaped member 18 is formed such that the bottomed cylindrical portion15
having a bottom surrounds the outer peripheral surface of the second balance weight
15i from the outside.
[0052]
Through-passage 5f
As illustrated in Figs. 1 and 4, the rotor 5a has the through-passages 5f which20
extend through the rotor 5a in the axial direction. The through-passages 5f are
provided to avoid the contact portion 15f of the first balance weight 15a.
[0053]
Of the through-passages 5f, through-passages 5f located closer to the heavy
weight portion 15c of the first balance weight 15a have openings which are provided so25
as not to face the contact portion 15f of the first balance weight 15a, and through-
passages 5f provided closer to the light weight portion 15b of the first balance weight
15a have openings which are provided in such a manner as to avoid the contact portion
15f of the first balance weight 15a, that is, in such a manner as to avoid the projecting
portions 15q of the light weight portion 15b of the first balance weight 15a.30
21
[0054]
Relationships between Through-passages 5f and Peripheral Components
The through-passages 5f are provided to avoid the position where the second
balance weight 15i fixed to the lower end face of the rotor 5a is provided. The bottom
portion of each of the first cup-shaped member 17 and the second cup-shaped member5
18 has through-holes provided at respective positions associated with the through-
passages 5f.
[0055]
Preferably, the first cup-shaped member 17 and the second cup-shaped member
18 should be made of a non-magnetic material. The through-passages 5f may be10
formed to extend through the second balance weight 15i or may be provided to avoid
the position of the second cup-shaped member 18. In addition, the through-passages
5f are formed symmetrically or point-symmetrically with respect to the central axis of the
rotor 5a.
[0056]15
Stator 5b
Fig. 7 is a sectional view of the stator 5b of the electric motor 5 of the scroll
compressor 100 according to Embodiment 1. Fig. 7 illustrates a section perpendicular
to the central axis of the stator 5b. An outer peripheral surface of the stator 5b of the
electric motor 5 is fixed to the hermetic container 10 by, for example, shrinkage fitting or20
welding. As illustrated in Fig. 7, the stator 5b has flat surfaces 5r which are located at
respective portions of its outer peripheral surface and are parallel to the central axis
thereof. In other words, in the stator 5b, portions of an outer peripheral portion which is
cylindrically shaped are cut out along the flat surfaces 5r. Second passages 5g are
formed such that they are surrounded by the respective flat surfaces 5r formed at the25
stator 5b and an inner peripheral surface of the hermetic container 10.
[0057]
The first passages 4f formed at the outer peripheral surface of the guide frame 4
and the second passages 5g formed at the outer peripheral surface of the stator 5b
form the refrigerant flow passage 30, which guide the refrigerant gas discharged30
22
through the discharge port 1d of the compression mechanism unit 14 to the bottom
portion of the hermetic container 10.
[0058]
Operation of Scroll Compressor 100
At the time of starting the scroll compressor 100 according to Embodiment 1 and5
during operation of the scroll compressor 100, refrigerant is sucked through the suction
pipe 13 and enters the compression chamber 1f, which is formed by engagement of the
plate-like scroll wrap 1b of the fixed scroll 1 and the plate-like scroll wrap 2b of the
orbiting scroll 2 with each other. The volume of the compression chamber 1f is
reduced when the orbiting scroll is driven by the electric motor to eccentrically revolve.10
In this compression process, the sucked refrigerant is changed into high-pressure
refrigerant. In the compression process, intermediate-pressure refrigerant gas being
compressed is guided from the bleeding hole 2g of the orbiting scroll 2 to the frame
lower space 4b through the communication hole 3e of the compliant frame 3. By the
bleeding hole 2g and the communication hole 3e, the frame lower space 4b is kept in15
such a manner as to have an intermediate-pressure atmosphere.
[0059]
After the compression process, a gas mixture of the refrigerant and the
refrigeration machine oil is discharged to the upper space 10a of the hermetic container
10 through the discharge port 1d of the fixed scroll 1. The gas mixture is guided to a20
space located below the electric motor 5, that is, the bottom portion of the hermetic
container 10, through the refrigerant flow passage 30 which includes the first passages
4f, which are provided at the outer peripheral portion of the compression mechanism
unit 14, and the second passages 5g, which are provided at the outer peripheral portion
of the stator 5b of the electric motor 5. The refrigeration machine oil is separated from25
the gas mixture in the process in which the gas mixture is guided to the bottom portion
of the hermetic container 10.
[0060]
The refrigerant gas separated from the refrigeration machine oil enters the
second cup-shaped member 18 attached to the lower end face of the rotor 5a of the30
23
electric motor 5, through an opening 18a of the second cup-shaped member 18, and
flows into the through-passages 5f provided in the rotor 5a. The refrigerant gas and
part of the refrigeration machine oil that have moved upward through the through-
passages 5f provided in association with the separation portions 15g of the first balance
weight 15a collide with the separation portions 15g of the first balance weight 15a. The5
refrigerant gas and the refrigeration machine oil that have collided with the separation
portions 15g flow outward in the radial direction and are let out to the outside of the first
cup-shaped member 17 through the outlet portions 17b.
[0061]
The refrigerant gas that has passed through the through-passages 5f which do10
not face the separation portions 15g flows upward in the first cup-shaped member 17
and flows into the discharge cover 16. Then, the refrigerant gas passes through the
second discharge passage 16a in the discharge cover 16 and then through the first
discharge passage 4g, and is discharged to the outside of the hermetic container 10
through the discharge pipe 12.15
[0062]
Next, discharge of the refrigeration machine oil to the outside of the scroll
compressor 100 will be described. When the scroll compressor 100 is in operation, the
refrigeration machine oil is supplied to the bearings and slide portions. Thereafter,
together with the refrigerant, some of the refrigeration machine oil circulates in the20
hermetic container 10 and returns to the oil reservoir portion 10b, and some other of the
refrigeration machine oil is discharged to the outside of the hermetic container 10
through the discharge pipe 12. When the amount of the refrigeration machine oil
discharged to the outside of the hermetic container 10 is large, the amount of the
refrigeration machine oil stored in the oil reservoir portion 10b is reduced. When the25
amount of the refrigeration machine oil in the hermetic container 10 is reduced, the
amount of the oil supplied to the bearings and the slide portions is reduced, and the
refrigeration machine oil is finally exhausted. Consequently, abnormal wear or
adhesion occurs at the bearings and the slide portions, resulting in breakage of the
compressor.30
24
[0063]
In order to reduce the amount of the refrigeration machine oil 11 discharged to
the outside of the hermetic container 10, the scroll compressor 100 according to
Embodiment 1 causes the refrigerant and the refrigeration machine oil which flow to the
upper end of the rotor 5a through the through-passages 5f in the rotor 5a to collide with5
the separation portions 15g of the heavy weight portion 15c of the first balance weight
15a to guide the refrigerant and the refrigeration machine oil outwardly in the radial
direction. The separation portions 15g are formed in such a manner as to face the
through-passages 5f. The refrigerant and the refrigeration machine oil that have
collided with the separation portions 15g through the through-passages 5f are changed10
in flow direction, and flow outwardly from the separation portions 15g by a centrifugal
force. The side wall 17c of the first cup-shaped member 17 has the outlet portions
17b. The outlet portions 17b of the first cup-shaped member 17 are provided in
association with the respective positions where the separation portions 15g at the outer
peripheral surface of the first balance weight 15a are provided, and are provided to face15
the separation portions 15g in the radial direction.
[0064]
The first cup-shaped member 17 surrounds, from the outside in the radial
direction of the rotor 5a, the first balance weight 15a provided at the upper end of the
rotor 5a, and is open at the top thereof. However, the side wall 17c of the first cup-20
shaped member 17 has the outlet portions 17b which are provided in association with
the separation portions 15g. Thus, the refrigeration machine oil and the refrigerant gas
are discharged to the outside of the first cup-shaped member 17 through the outlet
portions 17b located in the side wall 17c.
[0065]25
The refrigerant gas and the refrigeration machine oil that have flowed out through
the outlet portions 17b of the first cup-shaped member 17 blow out to a position located
outward of the opening 16b of the discharge cover 16 and thus do not easily flow into
the opening 16b of the discharge cover 16. In addition, the refrigeration machine oil
flows outward through the outlet portions 17b and thus flows together with the30
25
refrigerant gas which flows from the upper portion to the lower part of the hermetic
container 10, to the lower part of the hermetic container 10.
[0066]
As described above, in the scroll compressor 100 according to Embodiment 1,
the refrigeration machine oil 11 is separated from the gas mixture in the process in5
which the gas mixture of the refrigeration machine oil and the refrigerant gas
compressed by the compression mechanism unit 14 circulates to flow downward and to
re-flow upward in the hermetic container 10. Therefore, in the scroll compressor 100
according to Embodiment 1, the amount of the refrigeration machine oil discharged to
the outside of the hermetic container 10 is greatly reduced, as compared with existing10
compressors. Thus, in the scroll compressor 100, the amount of the refrigeration
machine oil that can be held in the oil reservoir portion 10b is increased. As a result, it
is possible to reduce a decrease in the amount of oil which is supplied to the bearings
and the slide members in the scroll compressor 100 and to thus obtain the scroll
compressor 100 and the refrigeration cycle apparatus 200 which has high reliability.15
[0067]
Embodiment 2
A scroll compressor 100 according to Embodiment 2 will be described. The
scroll compressor 100 according to Embodiment 2 is the same as the scroll compressor
100 according to Embodiment 1 except for the configuration of the first cup-shaped20
member 17.
[0068]
Fig. 8 includes diagrams of a configuration of an upper portion of the rotor 5a of
the scroll compressor 100 according to Embodiment 2. Fig. 8, (a), is a diagram
obtained as the rotor 5a is viewed in the axial direction. Fig. 8, (b), illustrates a section25
taken along A-A in Fig. 8, (a). In Embodiment 2, at least one outlet portion 17d is
added to part of the side wall 17c of the first cup-shaped member 17 that is adjacent to
the light weight portion 15b of the first balance weight 15a. In Embodiment 1, together
with refrigerant gas that has flowed out through the through-passages 5f which do not
face the separation portions 15g of the first balance weight 15a, the refrigeration30
26
machine oil may flow into the opening 16b of the discharge cover 16. In Embodiment
2, since the first cup-shaped member 17 further includes the outlet portion 17d, the
refrigerant gas and the refrigeration machine oil that flow out through the through-
passages 5f provided closer to the light weight portion 15b are guided to the outside of
the first cup-shaped member 17 in the radial direction. The outlet portion 17d may be5
referred to as a second outlet portion.
[0069]
In the first cup-shaped member 17 according to Embodiment 2, the outlet portion
17d is provided adjacent to the light weight portion 15b of the first balance weight 15a
and close to the boundary between the light weight portion 15b and the heavy weight10
portion 15c. However, the position of the outlet portion 17d is not limited to the position
adjacent to the light weight portion 15b. The outlet portion 17d is provided at a position
other than positons of outer portions of the separation portions 15g in the radial
direction, and the separation portions 15g are not provided on an imaginary straight line
connecting the central axis and the outlet portion 17d.15
[0070]
In the scroll compressor 100 according to Embodiment 2, since the first cup-
shaped member 17 additionally includes the outlet portion 17b, it is possible to increase
the amount of refrigeration machine oil to be discharged to the outside of the first cup-
shaped member 17. Since the refrigeration machine oil is discharged to the first cup-20
shaped member 17, the amount of refrigeration machine oil that flows into the opening
16b of the discharge cover 16 can be reduced. Thus, the scroll compressor 100 can
reduce the amount of refrigeration machine oil that is discharged to the outside of the
scroll compressor 100.
[0071]25
Embodiment 3
The scroll compressor 100 according to Embodiment 3 will be described. The
scroll compressor 100 according to Embodiment 3 is the same as the scroll compressor
100 according to Embodiment 1 except for the configurations of the first cup-shaped
member 17 and the first balance weight 15a.30
27
[0072]
Fig. 9 includes diagrams of a configuration of an upper portion of the rotor 5a of
the scroll compressor 100 according to Embodiment 3. Fig. 9, (a), is a diagram
obtained as the rotor 5a is viewed in the axial direction. Fig. 9, (b), illustrates a section
taken along B-B in Fig. 9, (a). In the scroll compressor 100 according to Embodiment5
3, the contact portion 15f of the light weight portion 15b of the first balance weight 15a
also has the separation portions 15g which are open outward in the radial direction, as
well as the separation portions 15g of the heavy weight portion 15c. In addition, the
through-passages 5f in the rotor 5a are provided to face the respective separation
portions 15g provided at the light weight portion 15b. In the side wall 17c of the first10
cup-shaped member 17 located outward of the separation portions 15g of the light
weight portion 15b in the radial direction, the outlet portions 17b are provided. The
separation portions 15g provided at the heavy weight portion 15c may be referred to as
first separation portions 15g, and the separation portions 15g provided at the light
weight portion 15b may be referred to as second separation portions 15g.15
[0073]
In the scroll compressor 100, refrigerant gas flows together with a refrigeration
machine oil through the through-passages 5f in the rotor 5a of the electric motor 5 and
flows upward to an upper side of the rotor 5a. The refrigerant gas and the refrigeration
machine oil that have moved upward from the through-passages 5f which face the20
respective separation portions 15g of the first balance weight 15a are discharged to the
outside of the first cup-shaped member 17 as described above. In Embodiment 1, the
through-passages 5f provided closer to the light weight portion 15b flow toward the
discharge cover 16 as they are. However, in Embodiment 3, the second separation
portions 15g and the respective through-passages 5f provided closer to the light weight25
portion 15b face each other, and the refrigerant gas and the refrigeration machine oil
that have passed through the through-passages 5f thus collide with the second
separation portions 15g and flow outward in the radial direction. Outer peripheral
portions of the second separation portions 15g in the radial direction are open in the
28
outer peripheral surface of the first balance weight 15a, and the outlet portions 17b are
provided opposite to those outer peripheral portions.
[0074]
As well as the first separation portions 15g provided at the heavy weight portion
15c as described regarding Embodiment 1, the second separation portions 15g also5
change the flow direction of the refrigerant that has flowed through the respective
through-passages 5f to cause the refrigerant to flow outward in the radial direction and
to flow along with the refrigeration machine oil to the outside of the first cup-shaped
member 17 in the radial direction. Thus, it is possible to reduce the flow of the
refrigeration machine oil and the refrigerant into the opening 16b of the discharge cover10
16 located inward of the opening 17a of the first cup-shaped member 17.
[0075]
Embodiment 4
The scroll compressor 100 according to Embodiment 4 will be described. The
scroll compressor 100 according to Embodiment 4 is the same as the scroll compressor15
100 according to Embodiment 1 except for the configurations of the separation portion
15g and the outlet portion 17b.
[0076]
Fig. 10 includes diagrams of a configuration of an upper portion of the rotor 5a of
the scroll compressor 100 according to Embodiment 4. Fig. 10, (a), is a diagram20
obtained as the rotor 5a is viewed in the axial direction. Fig. 10, (b), illustrates a
section taken along A-A in Fig. 10, (a). In the first balance weight 15a according to
Embodiment 4, a single separation portion 15g is located to face two through-passages
5f in the rotor 5a provided closer to the heavy weight portion 15c. That is, the single
separation portion 15g is formed by connection of the two separation portions 15g which25
are formed at the heavy weight portion 15c of the first balance weight 15a according to
Embodiment 1 as illustrated in Fig. 5. In the case where it can be ensured that the first
balance weight 15a has a sufficient strength, the single separation portion 15g is
provided to face the through-passages 5f as illustrated in Fig. 10, whereby the
configuration of the first balance weight 15a can be simplified.30
29
[0077]
The first cup-shaped member 17 as illustrated in Fig. 10 has a single outlet
portion 17b in association with the position of the single separation portion 15g provided
at the heavy weight portion 15c. That is, the outlet portion 17b is provided on an
extension of a straight line connecting the central axis and the separation portion 15g as5
viewed in the axial direction.
[0078]
As described above, in the scroll compressor 100 according to Embodiment 4, it
is possible to obtain advantages similar to those of Embodiment 1, and simplify the
configurations of the first balance weight 15a and the first cup-shaped member 17. It is10
therefore possible to easily manufacture the scroll compressor 100 according to
Embodiment 4 at a lower cost.
[0079]
Modifications
Fig. 11 includes diagrams of a configuration of an upper portion of the rotor 5a of15
a modification of the scroll compressor 100 according to Embodiment 4. Fig. 11, (a), is
a diagram obtained as the rotor 5a is viewed in the axial direction. Fig. 11, (b),
illustrates a section taken along A-A in Fig. 11(a). The first cup-shaped member 17 of
the scroll compressor 100 according to Embodiment 4 may has the outlet portion 17d
which is located closer to the light weight portion 15b of the first balance weight 15a and20
in the vicinity of the boundary between the light weight portion 15b and the heavy weight
portion 15c, as in Embodiment 2. Accordingly, the scroll compressor 100 according to
Embodiment 4 obtains advantages similar to those of Embodiment 2.
[0080]
Fig. 12 includes diagrams of a configuration of an upper portion of the rotor 5a of25
another modification of the scroll compressor 100 according to Embodiment 4. Fig. 12,
(a), is a diagram obtained as the rotor 5a is viewed in the axial direction. Fig. 12, (b),
illustrates a section taken along A-A in Fig. 12, (a). The first cup-shaped member 17
as illustrated in Fig. 12, (a), has a single outlet portion 17b in association with the
separation portion 15g formed at the heavy weight portion 15c, but may have two outlet30
30
portions 17b in association with two through-passages 5f. That is, each of the two
outlet portions 17b may be provided on an extension of a straight line connecting the
central axis and an associated one of the through-passages 5f as viewed in the axial
direction. In the first cup-shaped member 17 as illustrated in Fig. 12, (a), each outlet
portion 17b has a small area, and can thus keep its strength higher than that of each5
first cup-shaped member 17 as illustrated in Figs. 10, (a) and 11, (a). In addition, the
first cup-shaped member 17 as illustrated in Fig. 12, (a), has two or more outlet portions
17b located at respective positions which overlap with the separation portion 15g and
can thus more efficiently discharge a refrigeration machine oil.
[0081]10
Fig. 13 includes diagrams of a configuration of an upper portion of the rotor 5a of
still another modification of the scroll compressor 100 according to Embodiment 4. Fig.
13, (a), is a diagram obtained as the rotor 5a is viewed in the axial direction. Fig. 11,
(b), illustrates a section taken along A-A in Fig. 13, (a). The first cup-shaped member
17 as illustrated in Fig. 12, (a), may have the outlet portion 17d located closer to the15
light weight portion 15b of the first balance weight 15a and in the vicinity of the
boundary between the light weight portion 15b and the heavy weight portion 15c.
Accordingly, the scroll compressor 100 according to Embodiment 4 obtains advantages
similar to those of Embodiment 2.
[0082]20
Embodiment 5
The scroll compressor 100 according to Embodiment 5 will be described. The
scroll compressor 100 according to Embodiment 5 is the same as the scroll compressor
100 according to Embodiment 3 which is provided as illustrated in Fig. 9, except for the
configurations of the separation portion 15g and the outlet portion 17b.25
[0083]
Fig. 14 includes diagrams of a configuration of an upper portion of the rotor 5a of
the scroll compressor 100 according to Embodiment 5. Fig. 14, (a), is a diagram
obtained as the rotor 5a is viewed in the axial direction. Fig. 14, (b), illustrates a
section taken along B-B in Fig. 14, (a). In the scroll compressor 100 according to30
31
Embodiment 5, the light weight portion 15b of the first balance weight 15a also has the
separation portion 15g as in Embodiment 3. In the first balance weight 15a according
to Embodiment 5, a single separation portion 15g provided at the light weight portion
15b is provided to face the two through-passages 5f.
[0084]5
The first cup-shaped member 17 as illustrated in Fig. 14 has the outlet portions
17b which are located at outer peripheral portions of the respective separation portions
15g provided at the light weight portion 15b and the heavy weight portion 15c in the
radial direction. Each of the outlet portions 17b has a width which depends on the
width of the separation portion 15g in the circumferential direction. That is, each of the10
outlet portions 17b is provided on an extension of a straight line connecting the central
axis and an associated one of the separation portions 15g as viewed in the axial
direction. By virtue of the above configuration, in the first balance weight 15a and the
first cup-shaped member 17 of the scroll compressor 100 according to Embodiment 5, a
refrigeration machine oil can be more efficiently separated from the refrigerant that flows15
out through the through-passages 5f. The scroll compressor 100 according to
Embodiment 5 can be more simply manufactured.
[0085]
Modification
Fig. 15 includes diagrams of a configuration of an upper portion of the rotor 5a of20
a modification of the scroll compressor 100 according to Embodiment 5. Fig. 15, (a), is
a diagram obtained as the rotor 5a is viewed in the axial direction. Fig. 15, (b),
illustrates a section taken along B-B in Fig. 15, (a). The first cup-shaped member 17
according to Embodiment 5 may have outlet portions 17b in associated with the
respective positions of through-passages 5f. To be more specific, as illustrated in Fig.25
15, (a), in the first cup-shaped member 17, two outlet portions 17b may be provided in
association with the single separation portion 15g. In this case, each of the outlet
portions 17b is provided on an extension of a straight line connecting the central axis
and an associated one of the through-passages 5f as viewed in the axial direction.
[0086]30
32
Embodiment 6
The scroll compressor 100 according to Embodiment 6 will be described. The
scroll compressor 100 according to Embodiment 6 is the same as the scroll compressor
100 according to Embodiment 1 which is provided as illustrated in Fig. 5, except for the
configuration of the outlet portion 17b of the first cup-shaped member 17.5
[0087]
Fig. 16 includes diagrams of a configuration of an upper portion of the rotor 5a of
the scroll compressor 100 according to Embodiment 6. Fig. 16, (a), is a diagram
obtained as the rotor 5a is viewed in the axial direction. Fig. 16, (b), illustrates a
section taken along A-A in Fig. 16, (a). In the scroll compressor 100 according to10
Embodiment 6, the configuration of the first balance weight 15a is the same as that
according to Embodiment 1 as illustrated in Fig. 5; however, the configuration of the
outlet portion 17b of the first cup-shaped member 17 is different from the configuration
of the outlet portion 17b of the first cup-shaped member 17 according to Embodiment 1
as illustrated in Fig. 5. In Embodiment 6, a single outlet portion 17b is provided for two15
separation portions 15g provided at the heavy weight portion 15c. Also, in this
configuration, it is possible to obtain advantages similar to those of the scroll
compressor 100 according to Embodiment 1 and simplify the configuration of the first
cup-shaped member 17.
[0088]20
Modification
Fig. 17 includes diagrams of a configuration of an upper portion of the rotor 5a of
a modification of the scroll compressor 100 according to Embodiment 6. Fig. 17, (a), is
a diagram obtained as the rotor 5a is viewed in the axial direction. Fig. 17, (b),
illustrates a section taken along A-A in Fig. 17, (a). The first cup-shaped member 17 of25
the scroll compressor 100 according to Embodiment 4 may be provided with the outlet
portion 17d located closer to the light weight portion 15b of the first balance weight 15a
and in the vicinity of the boundary between the light weight portion 15b and the heavy
weight portion 15c, as in Embodiment 2. By virtue of this configuration, the scroll
33
compressor 100 according to Embodiment 6 obtains advantages similar to those of
Embodiment 2.
[0089]
Embodiment 7
The scroll compressor 100 according to Embodiment 7 will be described. The5
scroll compressor 100 according to Embodiment 7 is the same as the scroll compressor
100 according to Embodiment 3 which is provided in illustrated in Fig. 9, except for the
configuration of the outlet portion 17b of the first cup-shaped member 17.
[0090]
Fig. 18 includes diagrams of a configuration of an upper portion of the rotor 5a of10
the scroll compressor 100 according to Embodiment 7. Fig. 18, (a), is a diagram
obtained as the rotor 5a is viewed in the axial direction. Fig. 18, (b), illustrates a
section taken along B-B in Fig. 18, (a). In the scroll compressor 100 according to
Embodiment 7, the configuration of the first balance weight 15a is the same as that of
the first balance weight 15a according to Embodiment 3 as illustrated in Fig. 9; however,15
the configuration of the outlet portion 17b of the first cup-shaped member 17 is different
from the configuration of the outlet portion 17b of the first cup-shaped member 17
according to Embodiment 3 as illustrated in Fig. 9. In Embodiment 7, a single outlet
portion 17b is provided for two separation portions 15g provided at the heavy weight
portion 15c. Also, in this configuration, in the scroll compressor 100 according to20
Embodiment 7, it is possible to obtain advantages similar to those of Embodiment 3 and
simplify the first cup-shaped member 17.
[0091]
Modification
In the first cup-shaped member 17 as illustrated in Fig. 18, (a), the outlet portion25
17b to be provided in association with the separation portions 15g of one of the light
weight portion 15b and the heavy weight portion 15c may be changed to a plurality of
outlet portions 17b. That is, one of the two outlet portions 17b of the first cup-shaped
member 17 as illustrated in Fig. 18, (a), may be changed to the plurality of outlet
portions 17b as illustrated in Fig. 15, (a).30
34
[0092]
Embodiment 8
The scroll compressor 100 according to Embodiment 8 will be described. The
scroll compressor 100 according to Embodiment 8 is the same as the scroll compressor
100 according to Embodiment 8 except for the shape of the first balance weight 15a.5
[0093]
Fig. 19 illustrates a configuration of an upper portion of the rotor 5a of the scroll
compressor 100 according to Embodiment 8. Fig. 19 is a diagram obtained as the
rotor 5a is viewed in the axial direction. In the scroll compressor 100 according to
Embodiment 8, the shape of the light weight portion 15b is changed for the first balance10
weight 15a according to Embodiment 1 which is provided as illustrated in Fig. 5. A light
weight portion 215b of a first balance weight 215a according to Embodiment 8 has two
arc portions 215p which are connected to respective ends of the heavy weight portion
15c. That is, the first balance weight 215a is formed in the shape of an arc that
surrounds the central axis and that is formed by the heavy weight portion 15c and the15
arc portions 215p. The heavy weight portion 15c forms a semicircle of the first balance
weight 215a around the central axis. The arc portions 215p are smaller than a quarter
circle of the first balance weight 215a and are connected to the respective ends of the
heavy weight portion 15c. As illustrated in Fig. 19, in the scroll compressor 100
according to Embodiment 8, the through-passages 5f provided closer to the light weight20
portion 215b are provided in a region where the arc portions 215p are not provided.
[0094]
Also, in the scroll compressor 100 according to Embodiment 8, the outlet portion
17b may be provided in part of the first cup-shaped member 17 that is closer to the light
weight portion 215b, as in Embodiment 2. In addition, although as the separation25
portions 15g closer to the heavy weight portion 15c, a plurality of separation portions
15g are provided, a single separation portion 15g may be provided for the through-
passages 5f, as in Embodiment 4 as described with reference Fig. 10. Similarly,
although the outlet portions 17b are provided, a single outlet portion 17b may also be
provided for the separation portions 15g, as Embodiment 6 as described with reference30
35
to Fig. 16. The scroll compressor 100 according to Embodiment 8 can also obtain
advantages similar to those of Embodiment 1.
[0095]
The light weight portion 215b according to Embodiment 8 may be formed to have
the same thickness, the same inside diameter, and the same outside diameter as the5
heavy weight portion 15c. In this case, the first balance weight 215a is formed in the
shape of an arc and such that the center of gravity of the first balance weight 215a is
eccentric relative to the central axis, and can be simplified in configuration.
[0096]
Embodiment 910
The scroll compressor 100 according to Embodiment 9 will be described. The
scroll compressor 100 according to Embodiment 9 is the same as the scroll compressor
100 according to Embodiment 5 which is provided as illustrated in Fig. 14, except for the
shape of the first balance weight 15a.
[0097]15
Fig. 20 illustrates a configuration of an upper portion of the rotor 5a of the scroll
compressor 100 according to Embodiment 9. Fig. 20 is a diagram obtained as the
rotor 5a is viewed in the axial direction. In the scroll compressor 100 according to
Embodiment 9, the shape of the light weight portion 15b is changed for the first balance
weight 15a in Embodiment 5 which is provided as illustrated in Fig. 14. The light20
weight portion 15b of a first balance weight 315a has two arc portions 215p and 315p
that are connected to the respective ends of the heavy weight portion 15c. That is, the
first balance weight 315a is formed in the shape of an arc that surrounds the central
axis and includes the heavy weight portion 15c and the arc portions 215p and 315p.
The heavy weight portion 15c forms a semicircle of the first balance weight 315a around25
the central axis. The arc portions 215p and 315p are connected to the respective ends
of the heavy weight portion 15c.
[0098]
As illustrated in Fig. 20, in the scroll compressor 100 according to Embodiment 9,
the through-passages 5f closer to the light weight portion 215b are provided in30
36
association with the separation portion 15g provided at the arc portion 315p. It should
be noted that in Embodiment 9, the locations of the separation portions 15g and the
through-passages 5f can be changed as appropriate. That is, some of the through-
passages 5f may be provided below the arc portion 315p, the others may be provided
below the arc portion 215p, and each of the arc portions 215p and 315p may be formed5
to have the separation portion 15g. The scroll compressor 100 according to
Embodiment 9 can also obtain advantages similar to those of the scroll compressor 100
according to Embodiment 3.
[0099]
The two arc portions 215p and 315p of the light weight portion 315b according to10
Embodiment 9 may be formed to have the same thickness, the same inside diameter,
and the same outer diameter as the heavy weight portion 15c. In this case, the first
balance weight 315a is formed in the shape of an arc and such that the center of gravity
of the first balance weight 315a is eccentric relative to the central axis, and can be
simplified in configuration.15
[0100]
Embodiments 1 to 9 of the present disclosure are described above, but are
described by way of example. The embodiments and the modifications thereof can be
combined with each other and can be combined with other well-known techniques. In
addition, some of the components can be omitted or modified without departing from the20
gist of the present disclosure.
Reference Signs List
[0101]
1: fixed scroll, 1a: base plate portion, 1b: plate-like scroll wrap, 1c: Oldham guide
groove, 1d: discharge port, 1e: suction port, 1f: compression chamber, 1g: suction25
check valve, 2: orbiting scroll, 2a: base plate portion, 2b: plate-like scroll wrap, 2c:
Oldham guide groove, 2d: boss portion, 2e: orbiting bearing, 2f: thrust surface, 2g:
bleeding hole, 2k: base-plate outer peripheral portion space, 2n: boss-portion outer
space, 3: compliant frame, 3a: thrust bearing, 3b: reciprocation slide surface, 3c: main
bearing, 3d: auxiliary main bearing, 3e: communication hole, 3f: communication hole,30
37
3g: intermediate pressure adjusting valve, 3h: intermediate pressure adjusting valve
holder, 3k: intermediate pressure adjusting spring, 3n: intermediate pressure adjusting
valve space, 3p: upper cylindrical surface, 3s: lower cylindrical surface, 3t: thrust
bearing opening, 4: guide frame, 4a: frame upper space, 4b: frame lower space, 4c:
upper cylindrical surface, 4d: lower cylindrical surface, 4f: first passage, 4g: first5
discharge passage, 5: electric motor, 5a: rotor, 5b: stator, 5f: through-passage, 5g:
second passage, 5h: shaft fixing hole, 5j: lead, 5r: flat surface, 6: rotation shaft, 6a:
eccentric shaft portion, 6b: main shaft portion, 6c: sub-shaft portion, 6d: oil supply
passage, 6e: oil supply port, 6f: rotation shaft balance weight, 6g: fixation portion, 6h: oil
supply hole, 7a: ring-shaped sealing member, 7b: ring-shaped sealing member, 8: sub-10
frame, 8a: sub-bearing, 8b: inflow hole, 9: Oldham mechanism, 9a: fixed-side key, 9b:
orbiting-side key, 9c: Oldham mechanism annular portion, 10: hermetic container, 10a:
upper space, 10b: oil reservoir portion, 10c: glass terminal, 11: refrigeration machine oil,
12: discharge pipe, 13: suction pipe, 14: compression mechanism unit, 15a: first
balance weight, 15b: light weight portion, 15c: heavy weight portion, 15d: fastener hole,15
15f: contact portion, 15g: separation portion, 15h: fastener, 15i: second balance weight,
15k: inner peripheral surface, 15p: arc portion, 15q: projecting portion, 16: discharge
cover, 16a: second discharge passage, 16b: opening, 17: first cup-shaped member,
17a: opening, 17b: outlet portion, 17c: side wall, 17d: outlet, 18: second cup-shaped
member, 18a: opening, 30: refrigerant flow passage, 40: outer peripheral surface, 41:20
lower cylindrical portion, 52: upper end face, 53: lower end face, 100: scroll compressor,
101: suction muffler, 103: four-way switching valve, 104: outdoor heat exchanger, 105:
pressure reducing device, 106: indoor heat exchanger, 200: refrigeration cycle
apparatus, 215a: first balance weight, 215b: light weight portion, 215p: arc portion,
315a: first balance weight, 315b: light weight portion, 315p: arc portion, D: inside25
diameter, d: inside diameter
38
We Claim :
[Claim 1]
A compressor comprising:
a hermetic container including an oil reservoir configured to store a refrigeration
machine oil;5
a compression mechanism unit provided in the hermetic container and configured
to compress refrigerant;
an electric motor provided in the hermetic container and configured to generate a
driving force; and
a rotation shaft configured to transmit the driving force generated by the electric10
motor to the compression mechanism unit,
wherein the electric motor includes
a rotor fixed to the rotation shaft,
a stator fixed to the hermetic container and including a refrigerant flow
passage through which refrigerant gas discharged from the compression mechanism15
unit is guided to a lower portion of the hermetic container,
a first balance weight fixed to an end face of the rotor that faces the
compression mechanism unit, and
a first cup-shaped member having a side wall that surrounds an outer
peripheral surface of the first balance weight,20
wherein the first balance weight includes a light weight portion having an arc
shape and a heavy weight portion having an arc shape, the light weight portion and the
heavy weight portion being connected to each other, and the first balance weight further
includes a separation portion that is a recessed portion formed at an end face of the first
balance weight and that is open in the outer peripheral surface of the first balance25
weight, the end face of the first balance weight facing the rotor.
wherein the separation portion is provided to face an opening of a through-
passage that is provided to extend through the rotor in an axial direction, and
wherein the side wall of the first cup-shaped member has an outlet portion that is
located outward of the separation portion in a radial direction.30
39
[Claim 2]
The compressor of claim 1, wherein
as the separation portion, a first separation portion formed at the heavy weight
portion is provided, and
the outlet portion is located outward of the first separation portion in the radial5
direction as viewed in the axial direction of the rotation shaft.
[Claim 3]
The compressor of claim 2, wherein the side wall of the first cup-shaped member
has a second outlet portion that is located at a position other than a position of an outer
portion of the first separation portion in the radial direction as viewed in the axial10
direction of the rotation shaft.
[Claim 4]
The compressor of claim 3, wherein
in addition to the separation portion, a second separation portion formed at the
light weight portion is further provided, and15
the outlet portion is located outward of the second separation portion in the radial
direction.
[Claim 5]
The compressor of any one of claims 1 to 4, wherein the outlet portion is provided
on an extension of a straight line connecting a central axis and the through-passage as20
viewed in the axial direction.
[Claim 6]
The compressor of any one of claims 1 to 5, wherein the outlet portion is provided
on an extension of a straight line connecting a central axis and the separation portion as
viewed in the axial direction.25
[Claim 7]
The compressor of any one of claims 1 to 6, wherein
as the through-passage in the rotor, a plurality of through-passages are provided,
and
the separation portion communicates with the plurality of through-passages.30
40
[Claim 8]
The compressor of claim 7, wherein
a plurality of outlet portions including the outlet portion are provided, and
each of the plurality of outlet portions is provided on an extension of a straight line
connecting a central axis and an associated one of the plurality of through-passages as5
viewed in the axial direction.
[Claim 9]
The compressor of any one of claims 1 to 8, wherein the heavy weight portion is
thicker in the axial direction than the light weight portion.
[Claim 10]10
The compressor of any one of claims 1 to 9, wherein the center of gravity of the
first balance weight is eccentric toward the heavy weight portion with reference to a
central axis as viewed in the axial direction.
[Claim 11]
The compressor of any one of claims 1 to 10, wherein the side wall of the first15
cup-shaped member further projects toward the compression mechanism unit than the
first balance weight.
[Claim 12]
The compressor of any one of claims 1 to 11, wherein the first balance weight has
an annular shape such that the heavy weight portion and the light weight portion are20
connected to surround the rotation shaft.
[Claim 13]
The compressor of any one of claims 1 to 11, wherein the first balance weight has
an arc shape such that the heavy weight portion and the light weight portion are
connected to surround the rotation shaft.25
[Claim 14]
The compressor of claim 13, wherein the light weight portion includes two arc
portions connected to respective ends of the heavy weight portion.
[Claim 15]
The compressor of any one of claims 1 to 14, further comprising30
41
a discharge cover attached to an end face of the compression mechanism unit
that faces the electric motor,
wherein
the discharge cover has an opening provided to face the rotor, and
the opening is located inward of the side wall of the first cup-shaped member as5
viewed in the axial direction of the rotation shaft.
[Claim 16]
A refrigeration cycle apparatus comprising the compressor of any one of claims 1
to 15.