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
5 Technical Field
[0001]
The present disclosure relates to a compressor including a compression
mechanism, a rotating shaft, and a motor and to a refrigeration cycle apparatus.
Background Art
10 [0002]
As Patent Literature 1 describes, a method of increasing condensation capacity
by cooling a refrigerant flow passage by a turbine disposed in a refrigerant circuit
driving a fan disposed in a unit has been known.
[0003]
15 In addition, as Patent Literature 2 describes, it has been known that, by using
an expansion turbine in a circuit of a unit, energy recovery efficiency, as the unit, is
increased.
Citation List
Patent Literature
20 [0004]
Patent Literature 1: Japanese Unexamined Patent Application Publication No.
61-79955
Patent Literature 2: Japanese Unexamined Patent Application Publication No.
2009-216090
25 Summary of Invention
Technical Problem
[0005]
However, regarding a technique described in Patent Literature 1, although a
cooling effect can be obtained, there arises a problem in that a complex system is
30 required to control the cooling effect as the unit.
3
[0006]
Regarding a technique described in Patent Literature 2, the expansion turbine
is a so-called generator. There is a problem in that costs of the unit increases due to
installation of the system of the expansion turbine. Another problem is that the
control regarding the handling of generated energy 5 becomes complex.
[0007]
The present disclosure has been made to solve the above-described problems
and aims to provide a compressor and a refrigeration cycle apparatus that can control
a cooling effect with a simple and inexpensive configuration.
10 Solution to Problem
[0008]
A compressor according to one embodiment of the present disclosure includes
a compression mechanism configured to compress refrigerant and discharge the
refrigerant, a rotating shaft configured to rotate to transmit power to the compression
15 mechanism, a motor configured to rotatably drive the rotating shaft, an impeller
disposed on the rotating shaft, and a flow passage through which the refrigerant
flows. The flow passage has a blowing port through which the refrigerant is blown
onto the impeller.
[0009]
20 A refrigeration cycle apparatus according to another embodiment of the present
disclosure includes the above-described compressor.
Advantageous Effects of Invention
[0010]
In the compressor and the refrigeration cycle apparatus according to the
25 embodiments of the present disclosure, the impeller is disposed on the rotating shaft,
and the flow passage has the blowing port through which refrigerant is blown onto the
impeller. Due to the configuration, the impeller onto which refrigerant is blown
through the blowing port rectifies the blown refrigerant, and a cooling effect can
thereby be obtained in the compressor. Thus, a cooling effect can be controlled with
30 a simple and inexpensive configuration.
4
Brief Description of Drawings
[0011]
[Fig. 1] Fig. 1 illustrates a longitudinal section of a compressor according to
Embodiment 1 of the present disclosure.
[Fig. 2] Fig. 2 illustrates the flow of refrigerant gas in the compressor 5 according
to Embodiment 1 of the present disclosure.
[Fig. 3] Fig. 3, which is a transverse section taken along line A-A in Fig. 2,
illustrates an operation state of an impeller of the compressor according to
Embodiment 1 of the present disclosure.
10 [Fig. 4] Fig. 4 illustrates the flow of refrigerant gas in a compressor according to
Modification 1 of Embodiment 1 of the present disclosure.
[Fig. 5] Fig. 5 illustrates a longitudinal section of the lower half body of a
compressor according to Embodiment 2 of the present disclosure.
[Fig. 6] Fig. 6, which is a transverse section taken along line B-B in Fig. 5,
15 illustrates an operation state of a reverse impeller of the compressor according to
Embodiment 2 of the present disclosure.
[Fig. 7] Fig. 7 illustrates a longitudinal section of a compressor according to
Embodiment 4 of the present disclosure.
[Fig. 8] Fig. 8 illustrates a longitudinal section of a compressor according to
20 Embodiment 5 of the present disclosure.
[Fig. 9] Fig. 9 is a refrigerant circuit diagram illustrating a refrigeration cycle
apparatus according to Embodiment 6 of the present disclosure, to which the
compressor is applied.
Description of Embodiments
25 [0012]
Hereinafter, embodiments of the present disclosure will be described based on
the drawings. In the drawings, constituents denoted by the same references are the
same or equivalent to one another, and the same applies throughout the description
in its entirety. Hatching is omitted appropriately in the sectional views for visibility.
30 In addition, the forms of constituents referred to in the description in its entirety are
5
merely examples, and the forms of constituents are thus not limited to those in the
description.
[0013]
Embodiment 1

Fig. 1 illustrates a longitudinal section of a compressor 100 according to
Embodiment 1 of the present disclosure. The compressor 100 illustrated in Fig. 1 is
a high-pressure shell-type scroll compressor. The compressor 100 includes a
compression mechanism 50, a rotating shaft 60, and a motor 7. The compression
10 mechanism 50, the rotating shaft 60, and the motor 7 are accommodated in a sealed
container 10. The compression mechanism 50 has a fixed scroll 1 and an orbiting
scroll 2 and compresses refrigerant and discharges the refrigerant. The rotating
shaft 60 rotates to transmit power to the compression mechanism 50 to cause the
orbiting scroll 2 to orbit. The motor 7 rotatably drives the rotating shaft 60.
15 Although an example in which the rotating shaft 60 extends in the vertical direction is
described here, the rotating shaft 60 is not limited to the example and may be inclined
and extend in the up-and-down direction.
[0014]
The rotating shaft 60 is disposed such that the axis thereof extends in the up20
and-down direction defined by an upper side U and a lower side D. The rotating
shaft 60 has an orbiting shaft 61 in an upper side U portion thereof. The rotating
shaft 60 has a main shaft 62 in a lower side D portion thereof. In a region
surrounding a lower end portion of the rotating shaft 60, an oil sump 70 from which
refrigerating machine oil is supplied is formed. The refrigerating machine oil moves
25 from an oil supply pump 63 formed at the lower end portion of the rotating shaft 60
toward the upper side U through a center portion of the rotating shaft 60 to lubricate
various sliding portions. The compression mechanism 50 is disposed on the upper
end portion side of the rotating shaft 60.
[0015]
6
The motor 7 is disposed on the lower side D relative to the compression
mechanism 50. The motor 7 is located on the upper side U relative to the oil sump
70. The motor 7 includes a stator fixed to an inner wall surface of the sealed
container 10 and a permanent magnet-included rotor that is located on the center
side of the stator and rotated by the energized stator. The rotor 5 is attached to the
main shaft 62. The rotor has refrigerant flow passages 7a passing through in the upand-
down direction.
[0016]
A partition plate 21 in proximity to the fixed scroll 1 is disposed in the sealed
10 container 10 and separates a low-pressure side under a refrigerant atmosphere
before refrigerant gas flows into the compression mechanism 50, from a highpressure
side of an upper space 10a under a refrigerant atmosphere after refrigerant
gas is compressed by the compression mechanism 50. The low-pressure side
under the refrigerant atmosphere before refrigerant gas flows into the compression
15 mechanism 50 is formed in an entire region of an inflow pipe 11 and a suction
chamber 14a. Thus, the partition plate 21 separates the upper space 10a from a
lower space 10b in the sealed container 10. A first high-pressure side under the
refrigerant atmosphere after refrigerant gas is compressed by the compression
mechanism 50 is formed in the upper space 10a in the sealed container 10. A
20 second high-pressure side under the refrigerant atmosphere after refrigerant gas is
compressed by the compression mechanism 50 and under a refrigerant atmosphere
before the refrigerant gas is discharged from the compressor 100 is formed in the
lower space 10b in the sealed container 10 on the lower side D relative to the
compression mechanism 50. That is, the inside of the sealed container 10 is divided
25 into two high-pressure sides under the respective refrigerant atmospheres by the
compression mechanism 50.
[0017]
An outer periphery portion of the fixed scroll 1 is fastened to a fixed frame 4 by
a bolt 16. A plate-shaped scroll lap 1b is formed on a lower surface, on the lower
30 side D, of a base plate portion 1a of the fixed scroll 1. In addition, paired Oldham
7
guide grooves 1c are formed substantially on a straight line, on an outer periphery
portion of the lower surface, on the lower side D, of the base plate portion 1a of the
fixed scroll 1. Paired fixed-side keys 5a of an Oldham mechanism 5 are engaged
with the paired Oldham guide grooves 1c to slide back and forth.
5 [0018]
A plate-shaped scroll lap 2b is formed on an upper surface, on the upper side
U, of a base plate portion 2a of the orbiting scroll 2. The plate-shaped scroll lap 1b
of the fixed scroll 1 and the plate-shaped scroll lap 2b of the orbiting scroll 2 are
combined to mesh with one another. Between the combined plate-shaped scroll lap
10 1b and plate-shaped scroll lap 2b, plural compression chambers 14b in which the
refrigerant gas from the suction chamber 14a is compressed by both the scroll laps
are formed. Refrigerant gas is sucked into the plural compression chambers 14b
from the suction chamber 14a located at the outer periphery. The pressure of the
refrigerant gas that has been sucked into the compression chambers 14b increases
15 as the refrigerant gas moves toward a center portion of the compression mechanism
50. The high-pressure refrigerant gas is then discharged from an innermost
chamber 14c formed in the center portion of the compression mechanism 50 into the
upper space 10a in the sealed container 10.
[0019]
20 A boss 2c having a hollow cylindrical shape is formed on a center portion of the
lower surface, on the lower side D, of the base plate portion 2a facing away from the
upper surface on which the plate-shaped scroll lap 2b is formed. An orbiting bearing
2d is formed on an inner surface of the boss 2c. The orbiting shaft 61 of the rotating
shaft 60 is fitted in the orbiting bearing 2d to orbit. In addition, a thrust surface 2e
25 that can slide while being in contact with a thrust receiver 3a of a moving frame 3 is
formed in an outer periphery portion of the lower surface, on the lower side D, of the
base plate portion 2a, the lower surface, on which the boss 2c is also provided, facing
away from the upper surface on which the plate-shaped scroll lap 2b is formed.
[0020]
8
On the outer periphery portion of the base plate portion 2a of the orbiting scroll
2, paired Oldham guide grooves 2f having a phase difference of substantially 90
degrees relative to the Oldham guide grooves 1c of the fixed scroll 1 are formed
substantially on a straight line. Paired orbiting-side keys 5b of the Oldham
mechanism 5 are engaged with the paired Oldham guide grooves 2f 5 to slide back and
forth.
[0021]
In the moving frame 3, on the outer side relative to the thrust receiver 3a, a
sliding surface 3b that slides when an annular portion 5c of the Oldham mechanism 5
10 slides back and forth is formed. A main shaft bearing 3c supporting radially the main
shaft 62 that is rotatably driven by the motor 7 is formed in a center portion of the
moving frame 3.
[0022]
The partition plate 21 disposed in proximity to the fixed scroll 1 separates the
15 upper space 10a from the lower space 10b in the sealed container 10. The upper
space 10a and the lower space 10b are connected to one another by a blowing pipe
22. The blowing pipe 22 is used as a main flow passage for refrigerant gas. The
refrigerant gas compressed in the compression mechanism 50 is sent from the upper
space 10a into the lower space 10b through the blowing pipe 22. The refrigerant
20 gas sent into the lower space 10b flows into a refrigerant circuit through a discharge
pipe 12. Here, the discharge pipe 12 is disposed with an inlet portion thereof being
inserted in the fixed frame 4 and being fixed to the fixed frame 4 at a height in the upand-
down direction between the fixed frame 4 and the motor 7.
[0023]
25
An impeller 30a is disposed on the main shaft 62 of the rotating shaft 60. The
impeller 30a is disposed between the motor 7 on the upper side U and the oil sump
70 on the lower side D. Regarding the impeller 30a, refrigerant gas is blown onto
blades from the outer periphery side, and the impeller 30a thereby disperses the
30 blown refrigerant gas in the up-and-down direction while the impeller 30a itself being
9
rotated. The impeller 30a has a known configuration in which, for example, plural
plate-shaped blades for receiving wind are interspersed in the outer periphery portion.
The impeller 30a is fixed completely to the rotating shaft 60. Thus, by refrigerant gas
being blown onto the impeller 30a from the outer periphery side, the impeller 30a is
rotated with the plural blades of the impeller 30a itself receiving the 5 refrigerant gas
and rotatably drives the main shaft 62 of the rotating shaft 60 in an auxiliary manner.
[0024]
Note that the impeller 30a may alternatively be fixed completely to the main
shaft 62 on the upper side U relative to the motor 7.
10 [0025]

The blowing pipe 22 constitutes a discharge flow passage for causing
refrigerant gas to flow in a manner such that the refrigerant gas once discharged
outside the sealed container 10 from the upper space 10a of the first high-pressure
15 side of the sealed container 10 is caused to flow into the lower space 10b of the
second high-pressure side of the sealed container 10 again. A blowing port 22a
through which refrigerant gas is blown onto the impeller 30a is formed in a
downstream end portion of the blowing pipe 22 inserted in the lower space 10b.
That is, the blowing port 22a is formed in an end portion of the blowing pipe 22
20 serving as the discharge flow passage through which the refrigerant gas discharged
from the compression mechanism 50 flows. The single blowing pipe 22 and the
single blowing port 22a are provided. The blowing port 22a is disposed at a position
away from the center portion of the lower space 10b and at the same level as the
level of the impeller 30a in the up-and-down direction.
25 [0026]

Fig. 2 illustrates the flow of refrigerant gas in the compressor 100 according to
Embodiment 1 of the present disclosure. Fig. 3, which is a transverse section taken
along line A-A in Fig. 2, illustrates an operation state of the impeller 30a of the
30 compressor 100 according to Embodiment 1 of the present disclosure.
10
[0027]
As Figs. 2 and 3 illustrate, the refrigerant gas compressed in the compression
mechanism 50 is sent into the lower space 10b through the blowing pipe 22. The
refrigerant gas is blown through the blowing port 22a of the blowing pipe 22 to rotate
the impeller 30a in the same direction as a rotation direction 80c of 5 the rotating shaft
60. The refrigerant gas blown onto the impeller 30a collides with the plural blades of
the impeller 30a and disperses in the up-and-down direction while rotating the
impeller 30a itself.
[0028]
10 The refrigerant gas dispersing toward the upper side U from the impeller 30a
flows through the refrigerant flow passages 7a of the motor 7 further toward the upper
side U and is discharged outside the compressor through the discharge pipe 12.
Because refrigerant gas is sucked into the discharge pipe 12, a region in proximity to
the discharge pipe 12 in the lower space 10b is lower in pressure than a region on the
15 lower side U of the lower space 10b. Thus, the refrigerant gas in the lower space
10b flows smoothly toward the upper side U in such a way being sucked into the
discharge pipe 12. At this time, the refrigerant gas flowing in the refrigerant flow
passages 7a of the motor 7 toward the upper side U cools the motor 7 generating
heat. Here, the high-pressure refrigerant gas compressed in the compression
20 mechanism 50 has a temperature of about 120 degrees C. In contrast, the motor 7
generating heat has a temperature of about 130 degrees C. Thus, the cooling effect
on the motor 7 can be obtained by the refrigerant gas flowing in the refrigerant flow
passages 7a of the motor 7.
[0029]
25 On the other hand, the refrigerant gas dispersing toward the lower side D from
the impeller 30a, while turning around, flows toward the upper side U of the lowpressure
side of the lower space 10b in such a way being sucked into the abovedescribed
discharge pipe 12. The refrigerant gas flows in the refrigerant flow
passages 7a of the motor 7 toward the upper side U to merge with the refrigerant gas
30 to be discharged through the discharge pipe 12. Thus, the refrigerant gas dispersing
11
toward the lower side D from the impeller 30a is dispersed by the impeller 30a, the
amount of the refrigerant gas that stirs or causes refrigerating machine oil to rise up
and move around is reduced, and oil outflow to the outside of the compressor is
thereby suppressed from occurring.
5 [0030]
As Fig. 3 illustrates, the refrigerant gas sent from the upper space 10a into the
lower space 10b through the blowing pipe 22 flows from the blowing port 22a, thereby
rotating the impeller 30a fixed to the main shaft 62 in the same rotation direction 80a
as the rotation direction 80c in which the main shaft 62 rotates due to the operation of
10 the compressor. Thus, the flow of the refrigerant gas rotates the impeller 30a,
thereby, in addition to the motor 7, aiding the rotation of the main shaft 62, and the
electric power input into the motor 7 of the compressor 100 is reduced.
Consequently, the high-performance compressor 100 can be obtained.
[0031]
15
Fig. 4 illustrates the flow of refrigerant gas in a compressor 100 according to
Modification 1 of Embodiment 1 of the present disclosure. In Modification 1,
descriptions of features similar to those in the above-described embodiment will be
omitted, and only specific features thereof will be described.
20 [0032]
As Fig. 4 illustrates, a blowing port 22a is formed in a downstream end portion
of a discharge flow passage 22c through which the refrigerant gas discharged from
the compression mechanism 50 flows. Here, in the sealed container 10, by using,
for example, a pipe part and a space portion, the discharge flow passage 22c is
25 formed to be a single flow passage connecting the upper space 10a and the lower
space 10b to one another.
[0033]

According to Embodiment 1, the compressor 100 includes the compression
30 mechanism 50 configured to compress refrigerant and discharge the refrigerant.
12
The compressor 100 includes the rotating shaft 60 configured to rotate to transmit
power to the compression mechanism 50. The compressor 100 includes the motor 7
configured to rotatably drive the rotating shaft 60. The compressor 100 includes the
impeller 30a disposed on the rotating shaft 60. The compressor 100 includes the
blowing pipe 22 serving as a discharge flow passage through which refrigerant 5 flows.
The blowing pipe 22 has the blowing port 22a through which refrigerant gas is blown
onto the impeller 30a.
[0034]
Due to the configuration, the impeller 30a onto which the refrigerant gas is
10 blown through the blowing port 22a rectifies the blown refrigerant gas, and a cooling
effect can thereby be obtained in the compressor 100. Thus, a cooling effect can be
controlled with a simple and inexpensive configuration.
[0035]
According to Embodiment 1, the rotating shaft 60 is disposed such that an axis
15 thereof extends in the up-and-down direction. The oil sump 70 is formed in a region
surrounding the lower end portion of the rotating shaft 60. The compression
mechanism 50 is disposed on the upper end portion side of the rotating shaft 60.
The motor 7 is disposed on the lower side D relative to the compression mechanism
50. The impeller 30a is disposed between the motor 7 and the oil sump 70.
20 [0036]
Due to the configuration, the impeller 30a onto which refrigerant gas is blown
through the blowing port 22a disperses and rectifies the blown refrigerant gas in the
up-and-down direction, the rising refrigerant gas cools the motor 7 in the compressor
100, and a cooling effect can thereby be obtained. In addition, turbulent swirl flow
25 can be suppressed from being generated in the sealed container 10 by the impeller
30a dispersing the blown refrigerant gas in the up-and-down direction, the separation
between refrigerant gas and refrigerating machine oil is promoted, and oil outflow,
which is a phenomenon where refrigerating machine oil is brought outside the
compressor with refrigerant gas, can thereby be suppressed from being caused.
30 [0037]
13
According to Embodiment 1, refrigerant is blown through the blowing port 22a
to rotate the impeller 30a in the same rotation direction 80a as the rotation direction
80c of the rotating shaft 60.
[0038]
Due to the configuration, because not resisting the rotation direction 5 80c of the
rotating shaft 60, the impeller 30a can be smoothly rotated with the rotating shaft 60.
[0039]
According to Embodiment 1, the blowing port 22a is one blowing port.
[0040]
10 Due to the configuration, through the blowing port 22a, refrigerant gas is
strongly blown onto the impeller 30a, and the rectification effect on the refrigerant gas
can thereby be increased.
[0041]
According to Embodiment 1, the impeller 30a is fixed to the rotating shaft 60.
15 [0042]
Due to the configuration, in addition to the motor 7, the impeller 30a fixed to the
rotating shaft 60 can add an auxiliary driving force to the rotating shaft 60 as
refrigerant gas is blown onto the impeller 30a through the blowing port 22a, and the
auxiliary effect on the driving force of the motor 7 can thereby be obtained. In
20 particular, when refrigerant is blown through the blowing port 22a to rotate the
impeller 30a in the same rotation direction 80a as the rotation direction 80c of the
rotating shaft 60, the auxiliary effect on the driving force of the motor 7 can more
preferably be obtained.
[0043]
25 According to Embodiment 1, the blowing port 22a is formed in the end portion
of the blowing pipe 22 or the end portion of the discharge flow passage 22c through
which the refrigerant gas discharged from the compression mechanism 50 flows.
[0044]
14
Due to the configuration, the high-pressure refrigerant gas discharged from the
compression mechanism 50 is blown onto the impeller 30a through the blowing port
22a, and the momentum of the refrigerant gas blown onto the impeller 30a increases.
[0045]
According to Embodiment 1, the compressor 100 has the sealed 5 container 10
in which the high-pressure side under a refrigerant atmosphere after refrigerant gas is
compressed by the compression mechanism 50 is divided into two. The blowing
pipe 22 serving as a discharge flow passage is a pipe for causing the refrigerant gas
once discharged outside the sealed container 10 from the first high-pressure side of
10 the sealed container 10 to flow into the second high-pressure side of the sealed
container 10 again.
[0046]
Due to the configuration, in the high-pressure shell-type scroll compressor, the
high-pressure refrigerant gas discharged from the compression mechanism 50 is
15 blown onto the impeller 30a through the blowing port 22a via the blowing pipe 22.
[0047]
Embodiment 2
Fig. 5 illustrates a longitudinal section of the lower half body of a compressor
100 according to Embodiment 2 of the present disclosure. Fig. 6, which is a
20 transverse section taken along line B-B in Fig. 5, illustrates an operation state of a
reverse impeller 30b of the compressor 100 according to Embodiment 2 of the
present disclosure. In Embodiment 2, descriptions of features similar to those in the
above-described embodiment and modification will be omitted, and only specific
features thereof will be described.
25 [0048]
As Figs. 5 and 6 illustrate, the impeller 30a is rotatable about the rotating shaft
60. In addition, the reverse impeller 30b is disposed on the rotating shaft 60 in
proximity to and on the lower side D relative to the impeller 30a. The reverse
impeller 30b is rotatable about the rotating shaft 60. The reverse impeller 30b has a
30 known configuration in which, for example, plural plate-shaped blades for receiving
15
wind are interspersed in the outer periphery portion. As a method of attaching the
impeller 30a and the reverse impeller 30b to the rotating shaft 60 so that the impellers
can rotate, a known method in which, for example, a bearing is interposed between
the rotating shaft 60 and the impeller is employed.
5 [0049]
The compressor 100 includes a branch blowing pipe 23, which is a branch flow
passage, branching from the blowing pipe 22 that is a discharge flow passage for the
refrigerant gas flowing to the blowing port 22a. Outside the sealed container 10, the
branch blowing pipe 23 branches from a middle point of the blowing pipe 22. A
10 downstream end of the branch blowing pipe 23 has a reverse blowing port 22b
through which refrigerant is blown onto the reverse impeller 30b to rotate the reverse
impeller 30b in a rotation direction 80b opposite to the rotation direction 80c of the
rotating shaft 60. The single branch blowing pipe 23 and the single reverse blowing
port 22b are provided.
15 [0050]
As Fig. 6 illustrates, the reverse blowing port 22b and the blowing port 22a are
arranged in line symmetry relative to a first orthogonal line C1 orthogonal to the
central axis line of the rotating shaft 60. The direction in which the refrigerant gas is
blown through each of the reverse blowing port 22b and the blowing port 22a crosses
20 over a second orthogonal line C2 orthogonal to the central axis line of the rotating
shaft 60 and the first orthogonal line C1.
[0051]
Here, in Embodiment 2, the two impellers: the impeller 30a and the reverse
impeller 30b are provided. However, the configuration thereof is not limited to this.
25 One or more impellers similar to any or both of the impeller 30a and the reverse
impeller 30b may further be provided.
[0052]
As Fig. 3 illustrates, refrigerant gas is blown onto the impeller 30a through the
blowing port 22a, and the impeller 30a is thereby rotated in the rotation direction 80a
30 that is a counterclockwise direction as viewed from above. As Fig. 6 illustrates,
16
refrigerant gas is blown onto the reverse impeller 30b through the branch blowing
pipe 23, and the reverse impeller 30b is thereby rotated in the rotation direction 80b
that is a clockwise direction as viewed from above. Thus, the impeller 30a and the
reverse impeller 30b constitute so-called contra-rotating blade assemblies, the
refrigerant gas passing through the impeller 30a and the reverse 5 impeller 30b is
rectified, and it is thereby possible to suppress the flow loss when the refrigerant gas
passes through the refrigerant flow passages 7a provided in the motor 7. As
described above, when a flow-passage resistance hardly affects, the flow amount of
the refrigerant gas passing through the motor 7 increases, and, as a result, the
10 cooling effect of suppressing the motor 7 from generating heat can be obtained.
[0053]
Moreover, because the flow of refrigerant gas is rectified, and turbulent swirl
flow can be suppressed from being generated in the sealed container 10, the
separation between refrigerant gas and refrigerating machine oil is facilitated.
15 Furthermore, the separated refrigerant gas and refrigerating machine oil can be
prevented from being stirred again, and oil outflow, which is a phenomenon where
refrigerating machine oil is brought outside the compressor, can be suppressed from
being caused.
[0054]
20
According to Embodiment 2, the impeller 30a c is rotatable about the rotating
shaft 60.
[0055]
Due to the configuration, the impeller 30a onto which refrigerant is blown
25 through the blowing port 22a rectifies the blown refrigerant gas, and a cooling effect
can thereby be obtained in the compressor 100.
[0056]
According to Embodiment 2, the reverse impeller 30b is provided on the
rotating shaft 60 and in proximity to the impeller 30a. The reverse blowing port 22b
30 through which refrigerant is blown onto the reverse impeller 30b to rotate the reverse
17
impeller 30b in the rotation direction 80b opposite to the rotation direction 80c of the
rotating shaft 60 is formed.
[0057]
Due to the configuration, the impeller 30a and the reverse impeller 30b
constitute a so-called contra-rotating blade assembly pair, and the 5 refrigerant-gas
flows that are dispersed by both the impellers rotating opposite to one another can
cancel out one another. The flow of the blown refrigerant gas at each of the impeller
30a and the reverse impeller 30b does not twist, and the effect of dispersing the
blown refrigerant gas straight in the up-and-down direction and rectifying the blown
10 refrigerant gas can be increased.
[0058]
According to Embodiment 2, the reverse blowing port 22b is one reverse
blowing port.
[0059]
15 Due to the configuration, refrigerant gas is strongly blown onto the reverse
impeller 30b through the reverse blowing port 22b, and the rectification effect on the
refrigerant gas can thereby be increased.
[0060]
According to Embodiment 2, the reverse blowing port 22b and the blowing port
20 22a are arranged in line symmetry relative to the first orthogonal line C1 orthogonal to
the central axis line of the rotating shaft 60. The direction in which the refrigerant
gas is blown through each of the reverse blowing port 22b and the blowing port 22a
crosses over the second orthogonal line C2 orthogonal to the central axis line of the
rotating shaft 60 and the first orthogonal line C1.
25 [0061]
Due to the configuration, the direction of the refrigerant gas blown through the
reverse blowing port 22b is away from the direction of the refrigerant gas blown
through the blowing port 22a in the compressor 100, and the refrigerant gas from the
reverse blowing port 22b and the refrigerant gas from the blowing port 22a are
30 strongly blown separately. Thus, the impeller 30a and the reverse impeller 30b
18
constitute a so-called contra-rotating blade assembly pair, the refrigerant-gas flows
that are dispersed by both the impellers rotating opposite to one another can more
strongly cancel out one another, the flow of the blown refrigerant gas at each of the
impeller 30a and the reverse impeller 30b does not twist, and the effect of dispersing
the blown refrigerant gas straight in the up-and-down direction 5 and rectifying the
blown refrigerant gas can further be increased.
[0062]
According to Embodiment 2, the reverse impeller 30b is rotatable about the
rotating shaft 60.
10 [0063]
Due to the configuration, the reverse impeller 30b onto which the refrigerant
gas is blown through the reverse blowing port 22b rectifies the blown refrigerant gas,
and a cooling effect can thereby be obtained in the compressor 100. In addition,
because rotating in the rotation direction 80b opposite to the rotation direction 80c of
15 the rotating shaft 60, the reverse impeller 30b does not impede the rotation of the
rotating shaft 60.
[0064]
According to Embodiment 2, through the reverse blowing port 22b, the
refrigerant gas in the branch blowing pipe 23, which serves as a branch flow passage,
20 branching from the blowing pipe 22 serving as a discharge flow passage for the
refrigerant gas flowing to the blowing port 22a is blown.
[0065]
Due to the configuration, the reverse blowing port 22b can be formed in a
simple and inexpensive manner by components being minimally added.
25 [0066]
Embodiment 3
In Embodiment 3, descriptions of features similar to those in the abovedescribed
embodiments and modification will be omitted, and only specific features
thereof will be described.
30 [0067]
19
In Embodiment 3, the impeller 30a of Embodiment 2 is fixed completely to the
main shaft 62. Refrigerant gas is blown through the blowing port 22a to rotate the
fixed impeller 30a in the same rotation direction 80a as the rotation direction 80c of
the main shaft 62 during the operation of the compressor. The reverse impeller 30b
is attached to the main shaft 62 to rotate about the main shaft 62. Refrigerant 5 gas is
blown onto the reverse impeller 30b through the reverse blowing port 22b to rotate
the reverse impeller 30b in the rotation direction 80b opposite to the rotation direction
of the impeller 30a.
[0068]
10 Thus, it is possible to obtain a high-performance compressor 100 that has the
characteristics described in Embodiment1 and Embodiment 2 and with which oil
outflow is reduced.
[0069]

15 According to Embodiment 3, the reverse impeller 30b is disposed on the
rotating shaft 60 and in proximity to the impeller 30a. The compressor 100 includes
the reverse blowing port 22b through which refrigerant is blown onto the reverse
impeller 30b to rotate the reverse impeller 30b in the rotation direction 80b opposite to
the rotation direction 80c of the rotating shaft 60. The impeller 30a is fixed to the
20 rotating shaft 60. The reverse impeller 30b is rotatable about the rotating shaft 60.
[0070]
Due to the configuration, the impeller 30a and the reverse impeller 30b
constitute a so-called contra-rotating blade assembly pair, the refrigerant-gas flows
that are dispersed by both the impellers rotating opposite to one another can cancel
25 out one another, the flow of the blown refrigerant gas at each of the impeller 30a and
the reverse impeller 30b does not twist, and the effect of dispersing the blown
refrigerant gas straight in the up-and-down direction and rectifying the blown
refrigerant gas can be increased. Moreover, the impeller 30a fixed to the rotating
shaft 60 can add an auxiliary driving force to the rotating shaft 60 as refrigerant gas is
30 blown onto the impeller 30a through the blowing port 22a, and the auxiliary effect on
20
the driving force of the motor 7 can be obtained. Furthermore, the rotatable reverse
impeller 30b does not impede the rotation of the rotating shaft 60.
[0071]
Embodiment 4
Fig. 7 illustrates a longitudinal section of a compressor 5 100 according to
Embodiment 4 of the present disclosure. In Embodiment 4, descriptions of features
similar to those in the above-described embodiments and modification will be omitted,
and only specific features thereof will be described.
[0072]
10 The compressor 100 illustrated in Fig. 7 is a low-pressure shell-type scroll
compressor. In the sealed container 10, a low-pressure side under the refrigerant
atmosphere before refrigerant gas flows into the compression mechanism 50 is
formed in the lower space 10b. In the sealed container 10, a high-pressure side
under the refrigerant atmosphere after the refrigerant gas is compressed by the
15 compression mechanism 50 is formed in the upper space 10a. The inside of the
sealed container 10 is divided into the lower space 10b and the upper space 10a by
the fixed scroll 1. The refrigerant gas in the lower space 10b is sucked into a suction
chamber 14a via a suction flow passage 4a formed in the fixed frame 4.
[0073]
20 A blowing port 22a formed in an inflow pipe 11 is formed in an end portion of
the inflow pipe 11 through which refrigerant gas flows from a refrigerant circuit of a
refrigeration cycle apparatus 101 into the lower space 10b of the low-pressure side of
the sealed container 10. The impeller 30a is fixed to the rotating shaft 60. In the
low-pressure shell-type scroll compressor, because the refrigerant gas compressed
25 by the compression mechanism 50 cannot be guided into the lower space 10b, the
blowing port 22a through which refrigerant gas is blown onto the impeller 30a is
formed in the end portion of the inflow pipe 11 through which the refrigerant gas from
the refrigerant circuit is sucked into the sealed container 10.
[0074]
30
21
According to Embodiment 4, the compressor 100 has the sealed container 10
divided into the low-pressure side under the refrigerant atmosphere before refrigerant
flows into the compression mechanism 50 and the high-pressure side under the
refrigerant atmosphere after refrigerant is compressed by the compression
mechanism 50. The blowing port 22a is formed in the end portion 5 of the inflow pipe
11 through which refrigerant flows from the refrigerant circuit of the refrigeration cycle
apparatus 101 into the low-pressure side of the sealed container 10.
[0075]
Due to the configuration, in the low-pressure shell-type scroll compressor,
10 refrigerant gas is blown onto the impeller 30a through the blowing port 22a connected
to the inflow pipe 11. The refrigerant gas blown onto the impeller 30a is then
rectified, and a cooling effect can thereby be obtained in the compressor 100. Thus,
a cooling effect can be controlled with a simple and inexpensive configuration. In
addition, when refrigerant gas is blown onto the impeller 30a through the blowing port
15 22a with the impeller 30a being fixed to the rotating shaft 60, the impeller 30a can add
an auxiliary driving force to the rotating shaft 60, and the auxiliary effect on the driving
force of the motor 7 can thereby be obtained.
[0076]
Embodiment 5
20 Fig. 8 illustrates a longitudinal section of a compressor 100 according to
Embodiment 5 of the present disclosure. In Embodiment 5, descriptions of features
similar to those in the above-described embodiments and modification will be omitted,
and only specific features thereof will be described.
[0077]
25 As Fig. 8 illustrates, the compressor 100 is a low-pressure shell-type scroll
compressor. A reverse blowing port 22b through which refrigerant gas is blown onto
the reverse impeller 30b is formed in an end portion of a branch inflow pipe 13, which
is a branch flow passage, branching from the inflow pipe 11 through which refrigerant
flows to the blowing port 22a.
30 [0078]
22
Note that the impeller 30a may be fixed to the rotating shaft 60 or may be
rotatable about the rotating shaft 60. The reverse impeller 30b is rotatable about the
rotating shaft 60.
[0079]

According to Embodiment 5, through the reverse blowing port 22b, the
refrigerant gas in the branch inflow pipe 13, which serves as a branch flow passage,
branching from the inflow pipe 11 for the refrigerant gas flowing to the blowing port
22a is blown.
10 [0080]
Due to the configuration, the reverse blowing port 22b can be formed in a
simple and inexpensive manner by components being minimally added.
[0081]
Note that Embodiments 1 to 5 of the present disclosure may be combined or
15 may each be applied to a part in any one of the other embodiments. Here, the highpressure
shell-type and low-pressure shell-type scroll compressors are described as
examples. However, the configuration of the compressor is not limited to these
types. For example, the compressor 100 is not limited to a scroll compressor, as
long as the compressor 100 includes a motor 7 in a sealed container 10 and includes
20 a rotating shaft 60 to which an impeller 30a can be attached.
[0082]
Embodiment 6

Fig. 9 is a refrigerant circuit diagram illustrating a refrigeration cycle apparatus
25 101 according to Embodiment 6 of the present disclosure, to which the compressor
100 is applied.
[0083]
As Fig. 9 illustrates, the refrigeration cycle apparatus 101 includes the
compressor 100, a condenser 102, an expansion valve 103, and an evaporator 104.
30 The compressor 100, the condenser 102, the expansion valve 103, and the
23
evaporator 104 are connected to one another by refrigerant pipes to form a
refrigeration cycle circuit. The refrigerant that has flowed out of the evaporator 104
is sucked into the compressor 100 to turn into high-temperature and high-pressure
refrigerant. The high-temperature and high-pressure refrigerant is condensed in the
condenser 102 to turn into liquid refrigerant. The liquid refrigerant 5 is reduced in
pressure and expanded in the expansion valve 103 to turn into low-temperature and
low-pressure two-phase gas-liquid refrigerant, and the low-temperature and lowpressure
two-phase gas-liquid is subjected to heat exchange in the evaporator 104.
[0084]
10 The compressor 100 of each of Embodiments 1 to 5 can be applied to the
refrigeration cycle apparatus 101 of this kind. Note that an example of the
refrigeration cycle apparatus 101 is an air-conditioning apparatus, a refrigeration
apparatus, or a water heater.
[0085]
15
According to Embodiment 6, the refrigeration cycle apparatus 101 includes the
above-described compressor 100.
[0086]
Due to the configuration, in the refrigeration cycle apparatus 101 including the
20 compressor 100, a cooling effect can be controlled with a simple and inexpensive
configuration.
Reference Signs List
[0087]
1: fixed scroll, 1a: base plate portion, 1b: plate-shaped scroll lap, 1c: Oldham
25 guide groove, 2: orbiting scroll, 2a: base plate portion, 2b: plate-shaped scroll lap, 2c:
boss, 2d: orbiting bearing, 2e: thrust surface, 2f: Oldham guide groove, 3: moving
frame, 3a: thrust receiver, 3b: sliding surface, 3c: main shaft bearing, 4: fixed frame,
4a: suction flow passage, 5: Oldham mechanism, 5a: fixed-side key, 5b: orbiting-side
key, 5c: annular portion, 7: motor, 7a: refrigerant flow passage, 10: sealed container,
30 10a: upper space, 10b: lower space, 11: inflow pipe, 12: discharge pipe, 13: branch
24
inflow pipe, 14a: suction chamber, 14b: compression chamber, 14c: innermost
chamber, 16: bolt, 21: partition plate, 22: blowing pipe, 22a: blowing port, 22b: reverse
blowing port, 22c: discharge flow passage, 23: branch blowing pipe, 30a: impeller,
30b: reverse impeller, 50: compression mechanism, 60: rotating shaft, 61: orbiting
shaft, 62: main shaft, 63: oil supply pump, 70: oil sump, 80a: rotation 5 direction, 80b:
rotation direction, 80c: rotation direction, 100: compressor, 101: refrigeration cycle
apparatus, 102: condenser, 103: expansion valve, 104: evaporator
25
We Claim :
[Claim 1]
A compressor comprising:
a compression mechanism configured to compress refrigerant and discharge
5 the refrigerant;
a rotating shaft configured to rotate to transmit power to the compression
mechanism;
a motor configured to rotatably drive the rotating shaft;
an impeller disposed on the rotating shaft; and
10 a flow passage through which the refrigerant flows,
wherein the flow passage has a blowing port through which the refrigerant is
blown onto the impeller.
[Claim 2]
The compressor of claim 1,
15 wherein the rotating shaft is disposed such that an axis thereof extends in an
up-and-down direction,
wherein an oil sump is formed in a region surrounding a lower end portion of
the rotating shaft,
wherein the compression mechanism is disposed on an upper end portion side
20 of the rotating shaft,
wherein the motor is disposed below the compression mechanism, and
wherein the impeller is disposed between the motor and the oil sump.
[Claim 3]
The compressor of claim 1 or claim 2,
25 wherein, through the blowing port, the refrigerant is blown to rotate the impeller
in a same direction as a rotation direction of the rotating shaft.
[Claim 4]
The compressor of any one of claims 1 to 3,
wherein the blowing port is one blowing port.
30 [Claim 5]
26
The compressor of any one of claims 1 to 4,
wherein the impeller is fixed to the rotating shaft.
[Claim 6]
The compressor of any one of claims 1 to 4,
wherein the impeller is rotatable about the 5 rotating shaft.
[Claim 7]
The compressor of any one of claims 1 to 6,
wherein a reverse impeller is disposed on the rotating shaft and in proximity to
the impeller, and
10 wherein a reverse blowing port through which the refrigerant is blown onto the
reverse impeller to rotate the reverse impeller in a direction opposite to a rotation
direction of the rotating shaft is formed.
[Claim 8]
The compressor of claim 7,
15 wherein the reverse impeller is one reverse impeller.
[Claim 9]
The compressor of claim 8,
wherein the reverse impeller and the blowing port are arranged in line
symmetry relative to a first orthogonal line orthogonal to a central axis line of the
20 rotating shaft, and
wherein a direction in which the refrigerant is blown through each of the
reverse blowing port and the blowing port crosses over a second orthogonal line
orthogonal to the central axis line of the rotating shaft and the first orthogonal line.
[Claim 10]
25 The compressor of any one of claims 7 to 9,
wherein the reverse impeller is rotatable about the rotating shaft.
[Claim 11]
The compressor of any one of claims 1 to 10,
27
wherein the blowing port is formed in an end portion of a discharge flow
passage through which the refrigerant discharged from the compression mechanism
flows.
[Claim 12]
The compressor of claim 7 or any one of claims 8 to 11 as 5 dependent on claim
7,
wherein, through the reverse blowing port, the refrigerant in a branch flow
passage branching from the discharge flow passage for the refrigerant flowing to the
blowing port is blown.
10 [Claim 13]
The compressor of claim 11 or claim 12,
including a sealed container including a high-pressure side, which is divided
into two, under a refrigerant atmosphere after the refrigerant is compressed by the
compression mechanism,
15 wherein the discharge flow passage is a blowing pipe for causing the
refrigerant once discharged outside the sealed container from a first high-pressure
side of the sealed container to flow into a second high-pressure side of the sealed
container again.
[Claim 14]
20 The compressor of any one of claims 1 to 10,
including a sealed container divided into a low-pressure side under a
refrigerant atmosphere before the refrigerant flows into the compression mechanism
and a high-pressure side under a refrigerant atmosphere after the refrigerant is
compressed by the compression mechanism,
25 wherein the blowing port is formed in an end portion of an inflow pipe through
which the refrigerant flows from a refrigerant circuit of a refrigeration cycle apparatus
into the low-pressure side of the sealed container.
[Claim 15]
The compressor of claim 14 as dependent on claim 6 or claim 7,
28
wherein, through the reverse blowing port, the refrigerant in a branch flow
passage branching from the inflow pipe for the refrigerant flowing to the blowing port
is blown.
[Claim 16]
A refrigeration cycle apparatus, 5 comprising:
the compressor of any one of claims 1 to 15.