U.S. patent application number 10/556357 was filed with the patent office on 2007-11-22 for antennas array calibration arrangement and method.
Invention is credited to Hiroshi Hasegawa, Fumitoshi Nishiwaki, Atsuo Okaichi.
Application Number | 20070269328 10/556357 |
Document ID | / |
Family ID | 33458363 |
Filed Date | 2007-11-22 |
United States Patent
Application |
20070269328 |
Kind Code |
A1 |
Hasegawa; Hiroshi ; et
al. |
November 22, 2007 |
Antennas Array Calibration Arrangement and Method
Abstract
A compressor comprising a hermetical container, a compression
mechanism disposed in a lower portion in the hermetical container,
a rotational motor disposed in an upper portion in the hermetical
container and having a stator and a rotor, coil ends provided on
upper end lower ends of the stator, a discharge pipe provided on an
upper end of the hermetical container, and an oil reservoir
provided in a lower portion in the hermetical container, in which
working fluid compressed by the compression mechanism is introduced
into an upper space of the hermetical container from a gap between
the rotational motor and the hermetical container, and the working
fluid is discharged out from the hermetical container through the
discharge pipe, wherein an open end in the hermetical container of
the discharge pipe is located inside the upper end coil end.
Inventors: |
Hasegawa; Hiroshi; (Osaka,
JP) ; Okaichi; Atsuo; (Osaka, JP) ; Nishiwaki;
Fumitoshi; (Hyogo, JP) |
Correspondence
Address: |
KRATZ, QUINTOS & HANSON, LLP
1420 K Street, N.W.
Suite 400
WASHINGTON
DC
20005
US
|
Family ID: |
33458363 |
Appl. No.: |
10/556357 |
Filed: |
May 19, 2004 |
PCT Filed: |
May 19, 2004 |
PCT NO: |
PCT/JP04/07133 |
371 Date: |
October 17, 2006 |
Current U.S.
Class: |
418/83 |
Current CPC
Class: |
F04C 29/026 20130101;
F04C 23/008 20130101 |
Class at
Publication: |
418/083 |
International
Class: |
F01C 21/06 20060101
F01C021/06 |
Foreign Application Data
Date |
Code |
Application Number |
May 19, 2003 |
JP |
2003-139770 |
May 19, 2003 |
JP |
2003-139771 |
May 19, 2003 |
JP |
2003-139772 |
Claims
1-13. (canceled)
14. A system for controlling at least one of transmission and
reception of signals in a radio communication system having a
calibration antenna and an array of antenna elements, comprising: a
plurality of transceiving means, each connected to one element of
the array of antenna elements, at least one of said transceiving
means additionally connected to the calibration antenna, for at
least one of transmitting and receiving test signals via the
antenna elements; at least one calibration processor determining
variations of the test signals in said transceiving means; and a
beamforming processor taking into account the variations determined
by said calibration processor for at least one of beamforming and
determination of direction of arrival of radio signals respectively
transmitted and received by the antenna elements.
15. A system according to claim 14, wherein a transmission gap in a
time frame of a time division duplex system is used for
transmission of the test signals for determining variations in said
calibration processor.
16. A system according to claim 15, wherein in said at least one
transceiving means connected to the calibration antenna test
signals are switched via a switch to the calibration antenna in a
calibration process.
17. A system according to claim 16, wherein said calibration
processor is realized within said beamforming processor.
18. A system according to claim 17, further comprising at least one
lookup table storing information related to the variations of the
test signals.
19. A system according to claim 18, further comprising a base band
multiplexer connected to said transceiving means, and wherein said
at least one calibration processor includes at least two
calibration processors, each determining variations for a different
radio frequency, connected to said transceiving means via said base
band multiplexer.
20. A system according to claim 14, further comprising a base
station of the radio communication system, in which said
transceiving means, said at least one calibration processor and
said beamforming processor are located.
21. A method for controlling at least one of transmission and
reception of signals in a radio communication apparatus having
transceivers, each connected to one element of an array of antenna
elements, at least one of the transceivers being additionally
connected to a calibration antenna, said method comprising: at
least one of a receiver calibration procedure and a transmitter
calibration procedure, the receiver calibration procedure
including: generating test signals, feeding the test signals to the
at least one of the transceivers connected to the calibration
antenna, transmitting the test signals via the calibration antenna,
receiving the test signals by the antenna elements and
corresponding transceivers, determining, in at least one
calibration processor, reception variations of the test signals in
the transceivers, and taking into account the reception variations,
determined in the at least one calibration processor, for
determination of direction of arrival of respectively received
radio signals by the antenna elements; and the transmitter
calibration procedure, including generating the test signals,
feeding the test signals to the transceivers, transmitting the test
signals via the antenna elements, receiving the test signals by the
calibration antenna and the at least one of the transceivers
connected thereto, determining, in the at least one calibration
processor, transmission variations of the test signals in the
transceivers, and taking into account the transmission variations,
determined in the at least one calibration processor, for
beamforming of respectively transmitted radio signals from the
antenna elements.
22. A method according to claim 21, wherein at least one of the
reception and transmission variations of the test signals are
determined consecutively for different radio frequencies.
23. A method according to claim 22, wherein at least one of the
reception and transmission variations of the test signals are
determined concurrently for different radio frequencies, using
individual calibration processors for the different radio
frequencies.
24. A method according to claim 23, further comprising determining
transfer functions of at least one of transmitting and receiving
paths in the calibration processor.
25. A method according to claim 24, further comprising determining
a maximum of a phase and amplitude difference of a coupling
coefficient in each calibration processor.
26. (canceled)
27. A method according to claim 21, wherein said transmitting of
the test signals via the calibration antenna and the antenna
elements in the receiver and transmitter calibration procedures,
respectively, occurs in a transmission gap in a time frame of a
time division duplex system.
Description
TECHNICAL FIELD
[0001] The present invention relates to a compressor used for a
refrigerator-freezer, an air conditioner and the like.
BACKGROUND TECHNIQUE
[0002] A hermetical type rotary compressor is widely used for a
refrigerator-freezer, an air conditioners and the like because it
is small in size and its structure is simple. A structure of the
hermetical type rotary compressor such as a rotary compressor and a
scroll compressor is described in a non-patent document 1. The
structure of the hermetical type rotary compressor will be
explained with reference to FIGS. 19 and 20 based on a rotary
compressor (compressor, hereinafter). FIG. 19 is a vertical
sectional view of a conventional compressor.
[0003] The compressor shown in the drawings comprises a hermetical
container 1, a shaft 2 having an eccentric portion 2a, a cylinder
3, a roller 4, a vane 7, a spring 8, an upper bearing 9 and a lower
bearing 10. The compressor also comprises a compression mechanism
disposed in a lower portion of the hermetical container 1, and a
rotational motor having a stator 11 and a rotor 12. The stator 11
is provided at its upper end lower ends with coil ends 11b and 11d.
The rotational motor is disposed above the hermetical container
1.
[0004] A plurality of notches 11a are formed in an outer periphery
of the stator 11. The notches 11a serve as flow paths for working
fluid.
[0005] The hermetical container 1 is provided at its upper portion
with an introducing terminal 13 which energizing a rotational motor
in the hermetical container 1, and a discharge pipe 14 for
introducing working fluid from the hermetical container 1 into a
refrigeration cycle. The discharge pipe 14 is in communication with
inside the hermetical container 1. The discharge pipe 14 is located
above the upper coil end 11b of the stator 11 so that a suction
port 14a of the discharge pipe 14 does not come into contact with
the stator 11 and the rotor 12 of the rotational motor. The
hermetical container 1 is provided at its side surface with a
suction pipe 15 for introducing working fluid from the
refrigeration cycle into the compressor. Refrigeration oil is
reserved in an oil reservoir 16 formed in a bottom of the
hermetical container 1. A cluster 26 is mounted on the introducing
terminal 13, a lead wire 25 from the stator 11 of the rotational
motor is connected to the cluster 26 so that current is supplied to
the rotational motor from the introducing terminal 13.
[0006] The operation of the compressor will be explained. If the
rotational motor of the compressor is energized to rotate the rotor
12, the roller 4 rotates eccentrically by the eccentric portion 2a,
and capacities of the compressor (not shown) and a suction chamber
5 formed in the cylinder 3 are varied. With this eccentric
rotation, the working fluid is drawn into the suction chamber 5,
and compressed in a compression chamber. The compressed working
fluid is mixed with fog drip (oil mist, hereinafter) of
refrigeration oil which is supplied from the oil reservoir 16 and
lubricates the compression mechanism. This mixture is discharged
into a lower space 17 of the rotational motor through the
discharging hole 9b, and passes through the notches 11a of the
stator 11 and a gap 18 between the stator 11 and the rotor 12, and
flows into an upper space 19 of the rotational motor.
[0007] The working fluid is discharged out from the discharge pipe
14, but the refrigeration oil mixed with the working fluid is also
discharged at the same time. Therefore,in the conventional
compressor, in order to enhance the reliability of the compressor
and the efficiency of the refrigeration cycle, the oil is separated
from the working fluid to prevent the refrigeration oil from being
discharged out from the hermetical container 1.
[0008] To separate the refrigeration oil from the working fluid,
there is a method to use an oil-separating plate provided on an
upper portion of the rotor 12 as disclosed in a patent document 1.
FIG. 21 is a detailed sectional view of peripheries of the
oil-separating plate. The rotor 12 includes an upper end plate 21a
and a lower end plate 21b for closing an insertion hole of a
permanent magnet 20. A plurality of through holes 12a formed in the
rotor 12 in the vertical direction and an oil-separating plate 23
disposed above exits of the through holes 12a are fixed to the
rotor 12 by a fixing member 24. The oil-separating plate 23 forms
an oil-separating space 22 between an upper surface of the rotor 12
and the oil-separating plate 23.
[0009] In the compressor having such a structure, a portion of
working fluid including oil mist discharged from the compression
mechanism into the lower space 17 of the rotational motor flows
into the oil-separating space 22 through the through holes 12a. The
working fluid is radially discharged from an outer peripheral exit
of the oil-separating plate 23 by a centrifugal force, and the
working fluid is sprayed on the coil end 11b of the stator 11, and
the working fluid and the oil mist included therein are separated
from each other. Only the working fluid from which the oil is
separated flows upward and is discharged out from the discharge
pipe 14 provided in the upper portion in the hermetical container
1. The refrigeration oil attached to the coil end 11b of the stator
11 drops downward and is returned into the oil reservoir 16 formed
in the bottom of the hermetical container 1.
(Non-Patent Document 1)
[0010] "Air-Conditioning and Refrigeration handbook", new edition
5, volume 11, machine", Air-Conditioning and Refrigeration
Institute, 1993, paragraphs 30 to 43
(Patent Document 1)
[0011] Japanese Patent Application Laid-open No. H8-28476
(paragraph 6, FIGS. 1 to 3)
[0012] In the conventional compressor, a working fluid flows from
the lower space 17 of the rotational motor to the upper space 19
through the notches 11a formed in the outer periphery of the stator
11 and the gap 18 between the stator 11 and the rotor 12. In the
case of the compressor shown in FIG. 21, the working fluid passes
through the through holes 12a of the rotor 12. The gap 18 between
the stator 11 and the rotor 12 is as narrow as 0.5 mm to enhance
the efficiency of the rotational motor. Thus, a rate of the working
fluid flowing through the gap is extremely small. Concerning the
through holes 12a of the rotor 12 also, if a cross-sectional area
of a laminated core of the rotor 12 is reduced and a magnetic
circuit becomes narrow, the efficiency of the rotational motor is
deteriorated and thus, the through holes 12a can not be increased
in size. Thus, the rate of the working fluid passing through the
notches 11a of the stator 11 is extremely increased.
[0013] In the conventional compressor having the structure shown in
FIG. 21, only oil can be separated from the working fluid passing
through the plurality of through holes 12a formed in the rotor 12
in the vertical direction, and it is difficult to separate oil from
working fluid having high flow rate and passing through the notches
11a formed in the outer periphery of the stator 11.
[0014] As shown in FIGS. 19 and 20, the cluster 26 disposed in the
upper space 19 is a thin and long rectangular solid and is
eccentric from the axial center of the hermetical container 1.
Therefore, there is generated a force which hinders a turning flow
around a rotation center axis L in the upper space 19 caused by
rotation of the rotor 12. Therefore, the flow velocity of turning
flow is slow and uneven. Thus, the working fluid and the
refrigeration oil are not separated from each other
sufficiently.
[0015] When the conventional compressor using a working fluid
mainly comprising carbon dioxide is applied to a refrigeration
cycle, since a pressure of the working fluid discharged from the
compression chamber 6 exceeds a critical pressure, the working
fluid in the hermetical container 1 is brought into a supercritical
state, meltage of the refrigeration oil with respect to the working
fluid is increased, and it is difficult to separate oil in the
hermetical container 1.
[0016] The present invention has been accomplished to solve the
above problems, and it is an object of the invention to obtain a
refrigeration cycle having high efficiency by easily and
inexpensively enhancing the oil-separating efficiency to reduce an
amount of refrigeration oil which is taken out from a hermetical
container and to enhance the reliability of the compressor without
deteriorating the efficiency of a rotational motor.
DISCLOSURE OF THE INVENTION
[0017] A first aspect of the present invention provides a
compressor comprising: a container; a compression mechanism
disposed in a lower portion of said container: a rotational motor
disposed in an upper portion of said container, said rotational
motor having a stator and a rotor; a coil end provided on each of
upper and lower ends of said stator; a discharge pipe provided on
an upper end of said container; an oil reservoir provided in a
lower portion of said container; and a gap provided between said
rotational motor and said container, said gap being operable to
introduce working fluid, which is compressed by said compression
mechanism, into an upper space of said container; wherein the
working fluid is discharged from said container through said
discharge pipe; and wherein said discharge pipe has an open end in
said container, the open end being located inside said coil end
provided on the upper end of said stator.
[0018] According to this aspect, since the open end in the
hermetical container is located inside the coil end, the working
fluid introduced into the upper space of the container from the gap
between the rotational motor and the container flows from upward to
downward toward the inside of the coil end, and the working fluid
introduced into the coil end flows toward the open end of the
discharge pipe. Therefore, when the flowing direction of the
working fluid is changed in this manner, the oil mist of the
refrigeration oil having high density reaches closer to the rotor
than the working fluid. The oil mist of the refrigeration oil which
reaches the vicinity of the rotor is separated from the working
fluid by centrifugal force by means of the rotational flow caused
by rotation of the rotor, and attaches to the inner peripheral
surface of the coil end. Thus, it is possible to prevent the
refrigeration oil from being delivered outside of the hermetical
container from the discharge pipe together with the working
fluid.
[0019] According to the second aspect of the invention, in the
compressor of the first aspect said discharge pipe has a curved
portion in said container.
[0020] According to this aspect, it is possible to position the
open end in the container inside the coil end irrespective of a
position where the suction port is mounted on the container.
Therefore, it is possible to largely enhancing the flexibility in
design of the compressor.
[0021] According to a third aspect of the invention, in the
compressor of the second aspect, said discharge pipe is provided on
a side surface of said container.
[0022] With this aspect, since the discharge pipe passing through
the side surface of the container has the curved portion in the
hermetical container, the open end in the container can easily be
located inside the coil end. Therefore, the oil is separated by the
gravity caused by changing the flowing direction and by the
centrifugal force of the turning flow, and it is possible to
prevent the refrigeration oil from being delivered outside the
container. Since the upper portion in the container can freely be
used, the flexibility in design of the compressor can be
enhanced.
[0023] According to the fourth aspect of the invention, in the
compressor of the first aspect, the open end of said discharge pipe
in said container is disposed to face downstream of a rotational
direction of said rotor.
[0024] With this aspect, since the open end in the container is
opened toward downstream of a rotational direction of the rotor,
the oil mist of refrigeration oil having high density is prevented
from being drawn into the discharge pipe, and the oil can be
separated from the working fluid more efficiently.
[0025] According to a fifth aspect of the invention, in the
compressor of the first aspect, the open end of said discharge pipe
in said container is located in a vicinity of a rotation center
axis of said rotor.
[0026] With this aspect, since the open end in the container is
located in the vicinity of the rotation center axis of the rotor,
working fluid from which the oil mist is sufficiently separated can
be introduced into the discharge pipe.
[0027] According to a sixth aspect of the invention, in the
compressor of the first aspect, an inner diameter of the open end
of said discharge pipe located inside said container is larger than
an inner diameter of said discharge pipe located outside of said
container.
[0028] With this aspect, since an inner diameter of the open end in
the container is increased, the flow velocity of the working fluid
in the vicinity of the open end in the container is reduced, and
the amount of oil mist drawn together with the working fluid can be
reduced.
[0029] A seventh aspect of the present invention provides a
compressor comprising: a container; a compression mechanism
disposed in a lower portion of said container; a rotational motor
disposed in an upper portion of said container, said rotational
motor having a stator and a rotor; a coil end provided on each of
upper and lower ends of said stator; a discharge pipe provided on
an upper end of said container; an oil reservoir provided in a
lower portion of said container; and a gap provided between said
rotational motor and said container, said gap being operable to
introduce working fluid, which is compressed by said compression
mechanism, into an upper space of said container; and a
substantially cylindrical dividing member provided in the upper
space of said container and being operable to divide the upper
space into an inner space and an outer space; wherein said
discharge pipe has an open end in said container, the open end
being located inside said substantially cylindrical dividing
member; and wherein the working fluid is discharged from said
container through said discharge pipe.
[0030] With this aspect, since the dividing member is provided, the
turning flow of the working fluid generated by the rotor in the
inner space is not dispersed to the outer space, the development of
the turning flow is accelerated, and the oil is sufficiently
separated by the centrifugal force caused by the turning flow.
Thus, the oil mist can attach the inner wall surface of the
dividing member reliably, and the oil mist can be returned into the
oil reservoir as liquid drop. Therefore, it is possible to prevent
the refrigeration oil from being discharged from the discharge pipe
together with the working fluid.
[0031] According to an eighth aspect of the invention, in the
compressor of the seventh aspect, a gap is provided between an
upper end of said dividing member and said container.
[0032] With this aspect, a narrow gap is formed in the upper
portion in the hermetical container. Since the working fluid which
passed through the gap spreads and flows downward in the wider
inner space, the oil mist having higher density than the working
fluid which is largely affected by the gravity receives a great
downward speed component, and the oil separation is
facilitated.
[0033] According to a ninth aspect of the invention, in the
compressor of the seventh aspect, said dividing member is provided
with a communication hole between the inner space and the outer
space.
[0034] With this aspect, since the dividing member is provided with
the communication hole which brings the inner space and the outer
space into communication with each other, the upper end of the
dividing member can be brought into contact with the upper end
surface in the container and fixed thereto, and the positioning
precision of the dividing member when the compressor is assembled
is enhanced.
[0035] According to a tenth aspect of the invention, in the
compressor of any of the seventh aspects, said dividing member is
provided inside said coil end provided on the upper end of said
stator.
[0036] With this aspect, since the dividing member is provided
inside, the region of the inner space is reduced, the dispersion of
the rotational motion energy of the turning flow is suppressed, and
the working fluid receives strong centrifugal force. Therefore, the
oil mist separation effect by the centrifugal force is
enhanced.
[0037] According to an eleventh aspect of the invention, in the
compressor of any of the seventh aspects, said dividing member is
provided outside said coil end provided on the upper end of said
stator.
[0038] With this aspect, since the dividing member is provided
outside, the coil end having complicated surface shape comes inside
the dividing member. With this, the refrigeration oil attached to
the surface of the coil end is prone to grow into the liquid drop,
and the oil separation effect is enhanced.
[0039] According to a twelfth aspect of the invention, in the
compressor of any of the seventh aspects, an inner diameter of an
upper portion of said dividing member is smaller than an inner
diameter of a lower portion of said dividing member.
[0040] With this aspect, a downward component of force of the
centrifugal force which is in parallel to the inner wall surface of
the dividing member is applied to the liquid drop of the
refrigeration oil attached to the inner wall surface, which
reliably allows the liquid drop to flow and drop downward along the
inner wall surface, and the oil separation effect is enhanced.
[0041] According to a thirteenth aspect of the invention, in the
compressor of any of the first aspects, an upper portion of said
container is domical in shape.
[0042] With this aspect, since the working fluid is smoothly
collected in the central portion from the outer periphery along the
inner surface of the domical container, the flow velocity of the
deviation flow is prevented from being lowered. With this the
oil-separating effect by the gravity and the centrifugal force is
further enhanced.
[0043] A fourteenth aspect of the present invention provides a
compressor comprising: a container; a compression mechanism
disposed in a lower portion of said container; a rotational motor
disposed in an upper portion of said container, said rotational
motor having a stator and a rotor; a coil end provided on each of
upper and lower ends of said stator; a discharge pipe provided on
an upper end of said container; an oil reservoir provided in a
lower portion of said container; a gap provided between said
rotational motor and said container, said gap being operable to
introduce working fluid, which is compressed by said compression
mechanism, into an upper space of said container; an introduction
terminal provided in said container and being operable to supply
electricity to said rotational motor: and a cluster provided in
said container and being adapted to connect a lead wire from said
rotational motor to said introduction terminal; wherein said
cluster is symmetric with respect to an axis thereof, the axis of
said cluster being substantially coincident with a rotation central
axis of said rotational motor: and wherein the working fluid is
discharged from said container through said discharge pipe.
[0044] With this aspect, the turning flow is generated in the upper
space of the container by the high speed rotation of the rotational
motor, but since the cluster is symmetric with respect to the axis
and the cluster and the rotation center axis of the rotational
motor substantially coincide with each other, the turning flow is
also generated around the cluster. Therefore, the oil mist
introduced into the upper space of the container together with the
working fluid is separated by centrifugal force caused by the
turning flow and the oil mist attaches to the inner wall surface of
the hermetical container, and the oil mist flows and drops downward
ad oil drop. Therefore, the refrigeration oil is prevented from
being discharged from the discharge pipe together with the working
fluid.
[0045] According to a fifteenth aspect of the invention, in the
compressor of any one of the first aspects, further comprising: an
introduction terminal provided in said container and being operable
to supply electricity to said rotational motor; and a cluster
adapted to connect a lead wire from said rotational motor to said
introduction terminal, wherein said cluster is symmetric with
respect to a center axis thereof, the center axis being
substantially coincident with a rotation center axis of said
rotational motor.
[0046] With this aspect, the turning flow is generated in the upper
space of the container by the high speed rotation of the rotational
motor, but since the cluster is symmetric with respect to the axis
and the cluster and the rotation center axis of the rotational
motor substantially coincide with each other, the turning flow is
also generated around the cluster. Therefore, the oil mist
introduced into the upper space of the container together with the
working fluid is separated by centrifugal force caused by the
turning flow and the oil mist attaches to the inner wall surface of
the container, and the oil mist flows and drops downward ad oil
drop. Therefore,the refrigeration oil is prevented from being
discharged from the discharge pipe together with the working
fluid.
[0047] According to a sixteenth aspect of the invention, in the
compressor of the fourteenth aspect, said cluster is columnar in
shape.
[0048] With this aspect, the generation effect of the turning flow
around the cluster is enhanced.
[0049] According to a seventeenth aspect of the invention, in the
compressor of the fourteenth aspect, said cluster is polygonal
columnar in shape.
[0050] With this aspect, the side surface of the polygonal shape
becomes an obstruction, and downward flow along the side surface is
generated. Thus, the effect for downwardly dropping the oil mist as
oil drop is enhanced, and the refrigeration oil is prevented from
being discharged from the discharge pipe together with the working
fluid.
[0051] According to an eighteenth aspect of the invention, in the
compressor of any of the fourteenth aspects, an outer diameter of
said cluster is smaller than an inner diameter of said coil
end.
[0052] With this aspect, the space of flow is increased, the
turning flow of space inside the coil end is prone to grow to the
turning flow around the cluster.
[0053] According to a nineteenth aspect of the invention, in the
compressor of any of the first aspects, carbon dioxide is used as
the working fluid.
[0054] With this aspect, carbon dioxide can be used as the working
fluid.
BRIEF DESCRIPTION OF THE DRAWINGS
[0055] FIG. 1 is a vertical sectional view of a compressor
according to a first embodiment of the present invention;
[0056] FIG. 2 is a lateral sectional view of the compressor shown
in FIG. 1 taken along arrows X-X;
[0057] FIG. 3 is a vertical sectional view of a compressor
according to a second embodiment of the invention;
[0058] FIG. 4 is a lateral sectional view of the compressor shown
in FIG. 3 taken along arrows Y-Y;
[0059] FIG. 5 is a vertical sectional view of a compressor
according to a third embodiment of the invention;
[0060] FIG. 6 is a lateral sectional view of the compressor shown
in FIG. 5 taken along arrows Z-Z;
[0061] FIG. 7 is a vertical sectional view of a compressor
according to a fourth embodiment of the invention;
[0062] FIG. 8 is a vertical sectional view of a compressor
according to a fifth embodiment of the invention;
[0063] FIG. 9 is a vertical sectional view of a compressor
according to a sixth embodiment of the invention;
[0064] FIG. 10 is a vertical sectional view of a compressor
according to a seventh embodiment of the invention;
[0065] FIG. 11 is a lateral sectional view of the compressor shown
in FIG. 10 taken along arrows X-X:
[0066] FIG. 12 is a vertical sectional view of a compressor
according to an eighth embodiment of the invention;
[0067] FIG. 13 is a vertical sectional view of a compressor
according to a ninth embodiment of the invention;
[0068] FIG. 14 is a vertical sectional view of a compressor
according to a tenth embodiment of the invention;
[0069] FIG. 15 is a lateral sectional view of the compressor shown
in FIG. 14 taken along arrows X-X;
[0070] FIG. 16 is a lateral sectional view of the compressor shown
in FIG. 14 taken along arrows Y-Y;
[0071] FIG. 17 is a lateral sectional view of the compressor shown
in FIG. 14 taken along arrows Z-Z;
[0072] FIG. 18 is a lateral sectional view of a compressor
according to an eleventh embodiment of the invention;
[0073] FIG. 19 is a vertical sectional view of a conventional
compressor;
[0074] FIG. 20 is a perspective view of a cluster of the
conventional compressor; and
[0075] FIG. 21 is a detailed sectional view of peripheries of an
oil-separating plate.
BEST MODE FOR CARRYING OUT THE INVENTION
[0076] Several embodiments of the present invention will be
explained below with reference to the drawings.
First Embodiment
[0077] FIG. 1 is a vertical sectional view of a compressor
according to the first embodiment of the present invention, and
FIG. 2 is a lateral sectional view of the compressor shown in FIG.
1 taken along arrows X-X. The compressor of the first embodiment of
the invention has almost the same structure as that of the
above-described conventional compressor, and the same elements are
designated with the same symbols.
[0078] The compressor of this embodiment comprises a hermetical
container 1, a compression mechanism disposed in a lower portion in
the hermetical container 1, and a rotational motor disposed above
the compression mechanism. The compression mechanism comprises a
shaft 2 which can rotate about a rotation center axis L, a cylinder
3 having a cylindrical surface 3a therein, a roller 4 which is
fitted over an eccentric portion 2a of the shaft 2 and which
eccentrically rotates in the cylinder 3 as the shaft 2 rotates, a
vane 7 which reciprocates in a vane groove 3b of the cylinder 3
while a tip end of the vane 7 being in contact with the roller 4
and which divides a space defined by the cylinder 3 and the roller
4 into a suction chamber 5 and a compression chamber 6, a spring 8
which is disposed on a back surface of the vane 7 and which pushes
the vane 7 against the roller 4, and an upper bearing 9 and a lower
bearing 10 which support the shaft 2. The upper bearing 9 includes
a flow path 9a which is connected to a suction pipe 15 and which
introduces working fluid drawing from the suction pipe 15 into the
suction chamber 5, and a discharging hole 9b which discharges
working fluid compressed in the compression chamber 6 into the
lower space 17 of the rotational motor.
[0079] The rotational motor comprises a stator 11 shrinkage fitted
into the hermetical container 1, and a rotor 12 shrinkage fitted to
the shaft 2. The stator 11 is provided at its upper end with a coil
end 11b and at its lower end with a coil end lid. The stator 11 is
provided at its outer periphery with a plurality of notches 11a
which bring the lower space 17 and the upper space 19 into
communication with each other. The notches 11a serve as flow paths
for working fluid.
[0080] The hermetical container 1 is provided at its upper portion
with an introducing terminal 13 which energizes the rotational
motor in the hermetical container 1, and a discharge pipe 31 which
introduces working fluid from the upper space 19 in the hermetical
container 1 into a refrigeration cycle outside the hermetical
container 1. Refrigeration oil is reserved in an oil reservoir 16
formed in a bottom of the hermetical container 1.
[0081] The discharge pipe 31 is in communication with inside of the
hermetical container 1. A suction port 31a as an open end of the
hermetical container is located at inner side of an upper coil end
11b of the stator 11, i.e., below an upper end surface 11c of the
coil end 11b. The discharge pipe 31 is a straight pipe, and is
mounted on an upper portion of the hermetical container 1 at a
location closer to a center than an inner diameter of the coil end
11b. Thus, the introducing terminal 13 is mounted at a position of
the upper portion of the hermetical container 1 where the mounting
of the discharge pipe 31 is not hindered. In this embodiment, the
through holes 12a (see FIG. 11) of the rotor 12 by the same
oil-separating plate method as that of the conventional technique
is not provided.
[0082] Next, the operation of the compressor having the
above-described structure will be explained. The working fluid is
introduced from the suction pipe 15 into the suction chamber 5
through the flow path 9a provided in the upper bearing 9. If the
rotational motor is energized and the shaft 2 which is integral
with the rotor 12 is rotated, the roller 4 eccentrically rotates,
the capacities of the suction chamber 5 and the compression chamber
6 are varied. With this, the working fluid is drawn and compressed.
When a discharge valve (not shown) of the discharging hole 9b is
opened, oil mist which is supplied from the oil reservoir 16 and
which lubricated the compression mechanism is mixed into the
compressed working fluid, and this mixture is discharged into the
lower space 17 of the rotational motor. The working fluid in the
lower space 17 passes through notches 11a formed in the outer
periphery of the stator 11 as gaps between the rotational motor and
the hermetical container 1, and through a gap 18 (air gap) between
the stator 11 and the rotor 12, and flows into the upper space 19
of the rotational motor. The working fluid is separated from the
refrigeration oil in the upper space 19, and is discharged from the
discharge pipe 14.
[0083] This oil-separating operation will be explained. As
described above, the working fluid including oil mist discharged
from the compression mechanism into the lower space 17 of the
rotational motor passes through the notches 11a of the stator 11
and the gap 18 between the stator 11 and the rotor 12, and moves
into the upper space 19 of the rotational motor. At that time,
since the gap 18 is extremely narrow, the rate of working fluid
passing through the notches 11a of the stator 11 becomes extremely
large.
[0084] The working fluid which passed through the notches 11a of
the stator 11 flows upward to the vicinity of the coil end 11b of
the stator 11 and then, flows toward a central portion of the
hermetical container 1 through an upper portion of the coil end
11b. Thereafter, the working fluid flows downward toward the
suction port 31a of the discharge pipe 31 which is disposed inside
the coil end 11b and directed downward. When the working fluid is
drawn into the suction port 31a of the discharge pipe 31, the
working fluid again flows upward. At that time, the oil mist having
high density drop downward due to gravity, and reaches closer to an
upper surface 12b of the rotor 12 as compared with the working
fluid.
[0085] Since the upper surface 12b of the rotor 12 is rotational
immediately below the suction port 31a of the discharge pipe 31,
the working fluid flows such as to turn due to the viscosity, and
as closer to the upper surface 12b of the rotor 12, the turning
flow velocity is increased. Therefore, the oil mist has higher
density than the working fluid and the oil mist reaches a region
where the flow velocity of the turning flow in the vicinity of the
upper surface 12b of the rotor 12 is greater. Thus, the oil mist
attaches to an inner peripheral surface of the stator 11 or the
coil end 11b by the centrifugal force and becomes liquid drop and
is returned to the oil reservoir 16 formed in the bottom of the
hermetical container 1. In the state which the refrigeration oil is
separated from the working fluid which is less affected by the
turning flow, the working fluid is introduced into the suction port
31a of the discharge pipe 31.
[0086] The suction port 31a is located inside the coil end 11b in
this embodiment as described above. Therefore, when the working
fluid flowing from the notches 11a toward the suction port 31a
flows through the upper space 19 upward, downward and upward, the
gravity acts on the oil mist, and when the working fluid entering
into the coil end 11b and coming into contact with the rotor 12
turns together with the rotor 12 by the viscosity, the centrifugal
force is applied to the oil mist and the refrigeration oil is
separated from the working fluid. With this, an amount of the
refrigeration oil delivered to the refrigeration cycle out from the
compressor together with the working fluid can be reduced. The
refrigeration oil is not attached to an inner wall of a heat
exchanger tube of a heat exchanger, and it is possible to prevent
the heat exchanging efficiency from being deteriorated. An amount
of refrigeration oil in the oil reservoir 16 can always be
maintained constantly, and it is possible to enhance the
reliability and efficiency of the compressor.
[0087] Further, it is only necessary to extend the discharge pipe
and to locate the suction port inside the coil end close to the
upper end of the stator. Therefore, oil can be separated easily
only with slight change, and it is possible to provide a compressor
extremely inexpensively.
Second Embodiment
[0088] A compressor according to the second embodiment of the
present invention has the same structure as that of the compressor
of the first embodiment as shown in FIGS. 1 and 2 except the
discharge pipe and the introducing terminal. The same elements are
designated with the same symbols.
[0089] FIG. 3 is a vertical sectional view of a compressor
according to the second embodiment of the invention, and FIG. 4 is
a lateral sectional view of the compressor shown in FIG. 3 taken
along arrows Y-Y. The compressor of this embodiment comprises the
hermetical container 1, the compression mechanism disposed at a
lower portion in the hermetical container 1 and having the shaft 2,
the cylinder 3, the roller 4, the vane 7 and the like. The
compressor also comprises the rotational motor disposed above the
compression mechanism and having the stator 11, the rotor 12 and
the like. Refrigeration oil is reserved in the oil reservoir 16
formed in the bottom of the hermetical container 1. In an upper
portion of the hermetical container 1, there are provided the
introducing terminal 13 for energizing the rotational motor in the
hermetical container 1, and the discharge pipe 32 for introducing
the working fluid from the hermetical container 1 into the
refrigeration cycle.
[0090] The discharge pipe 32 extends into the hermetical container
1, and has a curved portion 32b inside the hermetical container 1.
A suction port 32a of the discharge pipe 32 is located inside the
coil end 11b on the upper end of the stator 11. The suction port
32a of the discharge pipe 32 is located closer to an inner
peripheral surface of the coil end 11b than a central portion of
the hermetical container 1. The suction port 32a extends diagonally
downward toward substantially the downstream in the rotation
direction of the upper surface 12b of the rotor 12. In this
embodiment, the through holes 12a (see FIG. 11) of the rotor 12 is
not provided.
[0091] The oil-separating operation of the compressor having the
above structure will be explained. The working fluid including oil
mist discharged from the compression mechanism into the lower space
17 of the rotational motor passes through the notches 11a of the
stator 11 and the gap 18 between the stator 11 and the rotor 12 and
moves to the upper space 19 of the rotational motor. At that time,
since the gap 18 is extremely narrow, the rate of working fluid
passing through the notches 11a of the stator 11 becomes extremely
large.
[0092] The working fluid which passed through the notches 11a of
the stator 11 flows upward to the vicinity of the coil end 11b of
the stator 11 and then, flows toward a central portion of the
hermetical container 1 through an upper portion of the coil end
11b. Thereafter, the working fluid flows downward toward the
suction port 32a of the discharge pipe 32 which is disposed inside
the coil end 11b. Then, the working fluid is drawn into the suction
port 32a and again flows upward. Since the suction port 32a of the
discharge pipe 32 extends diagonally downward as in the first
embodiment, the oil-separating effect of the refrigeration oil when
the flow of the working fluid is changed from downward to the
upward can be obtained.
[0093] If the working fluid reaches the vicinity of the suction
port 32a of the discharge pipe 32, since the upper surface 12b of
the rotor 12 is rotational immediately below the suction port 32a,
the working fluid turns by the viscosity. Since the suction port
32a of the discharge pipe 32 is directed downstream of the turning
flow, when the turning flow is drawing from the suction port 32a,
the direction of the flow is abruptly changed from the downstream
direction to the upstream direction with respect to the turning
flow. At that time, the oil mist having high density flows further
downstream by the inertial force and at the same time, the oil mist
attaches to the inner peripheral surface of the coil end 11b and
becomes liquid drop by the centrifugal force of the turning flow,
and the oil mist is returned to the oil reservoir 16 formed in the
bottom of the hermetical container 1 by the gravity. In the state
which the refrigeration oil is separated from the working fluid
which is less affected by the turning flow, the working fluid is
introduced into the suction port 32a of the discharge pipe 32.
[0094] According to the second embodiment, since the suction port
32a is located inside the coil end 11b and is opened toward the
downstream of the rotational direction of the rotor 12, the
oil-separating effect is further enhanced as compared with the
first embodiment by the change of flowing direction of the working
fluid, and by the gravity and the centrifugal force applied to the
oil mist which turns, and by the inertial force applied to the oil
mist when the flowing direction of the working fluid is changed
from the downstream flowing to the upstream flowing. With this, it
is possible to further suppress the amount of refrigeration oil
delivered to the refrigeration cycle outside the compressor
together with the working fluid. The refrigeration oil is not
attached to an inner wall of a heat exchanger tube of a heat
exchanger, and it is possible to more efficiently prevent the heat
exchanging efficiency from being deteriorated. An amount of
refrigeration oil in the oil reservoir 16 can always be maintained
constantly, and it is possible to further enhance the reliability
and efficiency of the compressor.
[0095] Since the discharge pipe 32 has the curved portion 32b, it
is possible to position the suction port 32a inside the coil end
11b irrespective of a position where the suction port 32a is
mounted on the hermetical container 1. Therefore, it is possible to
give a high priority to the position of the introducing terminal 13
and the like in the upper portion in the hermetical container 1,
and the flexibility in design can largely be enhanced. For example,
it is unnecessary to deviate the mounting position of the
introducing terminal 13 so that the introducing terminal 13 does
not hinder the discharge pipe 31 unlike the first embodiment, and
the introducing terminal 13 can be disposed in the center of the
container.
Third Embodiment
[0096] A compressor according to the third embodiment of the
present invention has the same structure as that of the compressor
of the second embodiment as shown in FIGS. 3 and 4 except the
discharge pipe. The same elements are designated with the same
symbols.
[0097] FIG. 5 is a vertical sectional view of a compressor
according to the third embodiment of the invention, and FIG. 6 is a
lateral sectional view of the compressor shown in FIG. 5 taken
along arrows Z-Z. The compressor of this embodiment comprises the
hermetical container 1, the compression mechanism disposed at a
lower portion in the hermetical container 1 and having the shaft 2,
the cylinder 3, the roller 4, the vane 7 and the like. The
compressor also comprises the rotational motor disposed above the
compression mechanism and having the stator 11, the rotor 12 and
the like. Refrigeration oil is reserved in the oil reservoir 16
formed in the bottom of the hermetical container 1. In an upper
portion of the hermetical container 1, there are provided the
introducing terminal 13 for energizing the rotational motor in the
hermetical container 1, and the discharge pipe 33 for introducing
the working fluid from the hermetical container 1 into the
refrigeration cycle.
[0098] The discharge pipe 33 extends into the hermetical container
1, and has a curved portion 33b inside the hermetical container 1.
A suction port 33a of the discharge pipe 33 is located inside the
coil end 11b on the upper end of the stator 11. The suction port
33a of the discharge pipe 33 is disposed in the vicinity of the
rotation center axis L of the rotor 12 and is directed diagonally
downward. In this embodiment, the through holes 12a (see FIG. 11)
of the rotor 12 is not provided.
[0099] This oil-separating operation will be explained. As
described above, the working fluid including oil mist discharged
from the compression mechanism into the lower space 17 of the
rotational motor passes through the notches 11a of the stator 11
and the gap 18 between the stator 11 and the rotor 12, and moves
into the upper space 19 of the rotational motor. At that time,
since the gap 18 is extremely narrow, the rate of working fluid
passing through the notches 11a of the stator 11 becomes extremely
large.
[0100] The working fluid which passed through the notches 11a of
the stator 11 flows upward to the vicinity of the coil end 11b of
the stator 11 and then, flows toward a central portion of the
hermetical container 1 through an upper portion of the coil end
11b. Thereafter, the working fluid flows downward toward the
suction port 33a of the discharge pipe 33 located inside the coil
end 11b. Then, the working fluid is drawn into the suction port 33a
which is directed diagonally downward and again flows upward. With
this change in flowing direction, the oil mist having high density
drops downward by the gravity, and the refrigeration oil is
separated.
[0101] If the working fluid reaches the vicinity of the suction
port 33a of the discharge pipe 33, since the upper surface 12b of
the rotor 12 is rotational immediately below the suction port 33a,
the working fluid turns by the viscosity. At that time, since the
oil mist has higher density than that of the working fluid, the oil
mist moves outward by the centrifugal force, the oil mist attaches
to the inner peripheral surface of heat exchanger stator 11 or the
coil end 11b and becomes liquid drop, and is returned to the oil
reservoir 16 formed in the bottom of the hermetical container 1.
Since the suction port 33a of the discharge pipe 33 is located at
substantially the central portion in the turning flow in the
vicinity of the rotation center axis L, the oil mist which is
largely affected by the centrifugal force is removed substantially
completely, and the refrigeration oil is separated from the working
fluid which is less affected by the centrifugal force, and the
working fluid is introduced into the suction port 33a of the
discharge pipe 33.
[0102] The oil-separating efficiency by the centrifugal force will
be further enhanced if the following structure (not shown) is
employed. That is, the introducing terminal 13 is disposed on the
upper end of the hermetical container 1, the discharge pipe 33
passes through from the center of the upper portion of the
hermetical container 1, and the suction port 33a is straight in
shape and is located inside the coil end 11b.
[0103] According to this embodiment, the suction port 33a is
located inside the coil end 11b. With this structure, the oil mist
can be removed by the gravity of the change of flowing direction.
Further, since the suction port 33a is opened in the vicinity of
the rotation center axis L of the rotor 12, the working fluid from
which the oil mist is sufficiently removed can be drawn by the
effect of the centrifugal force of the turning flow. Thus, the
oil-separating operation is further facilitated as compared with
the first embodiment. With this, it is possible to further suppress
the amount of refrigeration oil delivered to the refrigeration
cycle outside the compressor together with the working fluid. The
refrigeration oil is not attached to an inner wall of a heat
exchanger tube of a heat exchanger, and it is possible to more
efficiently prevent the heat exchanging efficiency from being
deteriorated. An amount of refrigeration oil in the oil reservoir
16 can always be maintained constantly, and it is possible to
further enhance the reliability and efficiency of the
compressor.
Fourth Embodiment
[0104] A compressor according to the fourth embodiment of the
present invention has the same structure as that of the compressor
of the first embodiment as shown in FIGS. 1 and 2 except the
discharge pipe and the introducing terminal. The same elements are
designated with the same symbols.
[0105] FIG. 7 is a vertical sectional view of a compressor
according to the fourth embodiment of the invention. The compressor
of this embodiment comprises the compression mechanism disposed at
a lower portion in the hermetical container 1 and having the shaft
2, the cylinder 3, the roller 4, the vane 7 and the like. The
compressor also comprises the rotational motor disposed above the
compression mechanism and having the stator 11, the rotor 12 and
the like. Refrigeration oil is reserved in the oil reservoir 16
formed in the bottom of the hermetical container. The introducing
terminal 13 for energizing the rotational motor in the hermetical
container 1 is provided in an upper portion of the hermetical
container 1. The hermetical container 1 is provided at its side
surface with a discharge pipe 34 for introducing working fluid from
the hermetical container 1 into the refrigeration cycle. The
discharge pipe 34 passes through the side surface of the hermetical
container 1, and has a curved portion 34b. A suction port 34a as an
open end of the hermetical container is located inside the coil end
11b of the stator 11. In this embodiment, the through holes 12a
(see FIG. 11) of the rotor 12 is not provided.
[0106] According to the compressor of the fourth embodiment having
such a structure, since the suction port 34a of the discharge pipe
34 is located inside the coil end 11b as in the first embodiment,
the same effect as that of the first embodiment can be obtained of
course and thus, detailed explanation thereof will be omitted.
[0107] In the compressor of this embodiment, the discharge pipe 34
passes through the side surface of the hermetical container 1, an
upper portion in the hermetical container 1 can be used freely, and
layout of the introducing terminal 13 is not limited. When the
compressor is mounted in the refrigeration cycle, even if a high
pressure side pipe is directed laterally, the discharge pipe 34 can
be connected directly, and there is effect that the structure of
the refrigeration cycle becomes simple. In other words, the
flexibility in design of the compressor can largely be
enhanced.
[0108] The same effect as that of the second embodiment can be
obtained if the following structure is employed. That is, in the
compressor of the fourth embodiment, the suction port 34a of the
discharge pipe 34 is disposed closer to the inner peripheral
surface of the coil end 11b than the central portion of the
hermetical container 1 as in the second embodiment, and the suction
port 34a is directed toward substantially the downstream in the
rotation direction of the upper surface 12b of the rotor 12.
[0109] In the compressor of the fourth embodiment, the same effect
as that of the third embodiment can be obtained if the suction port
34a of the discharge pipe 34 is disposed in the vicinity of the
rotation center axis L as in the third embodiment.
Fifth Embodiment
[0110] A compressor according to the fifth embodiment of the
present invention has the same structure as that of the compressor
of the first embodiment as shown in FIGS. 1 and 2 except the
discharge pipe. The same elements are designated with the same
symbols.
[0111] FIG. 8 is a vertical sectional view of a compressor
according to the fifth embodiment of the invention. The compressor
of this embodiment comprises the compression mechanism disposed at
a lower portion in the hermetical container land having the shaft
2, the cylinder 3, the roller 4, the vane 7 and the like. The
compressor also comprises the rotational motor disposed above the
compression mechanism and having the stator 11, the rotor 12 and
the like. Refrigeration oil is reserved in the oil reservoir 16
formed in the bottom of the hermetical container. In an upper
portion of the hermetical container 1, there are provided the
introducing terminal 13 for energizing the rotational motor in the
hermetical container 1, and the discharge pipe 35 for introducing
the working fluid from the hermetical container 1 into the
refrigeration cycle.
[0112] The discharge pipe 35 is mounted in an upper portion of the
hermetical container 1 closer to the center thereof than an inner
diameter of the coil end 11b, and passes through the hermetical
container 1. A suction port 35a of the discharge pipe 35 is located
inside the coil end 11b of the stator 11. The discharge pipe 35 is
straight pipe having a step, i.e., an inner diameter of the
discharge pipe 35 in the vicinity of the suction port 35a is
enlarged. In this embodiment, the through holes 12a (see FIG. 11)
of the rotor 12 is not provided.
[0113] According to the compressor of the fifth embodiment having
such a structure, since the suction port 35a of the discharge pipe
35 is located inside the coil end 11b as in the first embodiment,
the same effect as that of the first embodiment can be obtained of
course.
[0114] As the flow velocity of the working fluid at the suction
port 35a is greater, the refrigeration oil near the suction port
35a is more prone to be drawn together with the working fluid
before the refrigeration oil is separated from the working fluid by
the gravity and the centrifugal force. However, since the inner
diameter of the discharge pipe 35 in the vicinity of the suction
port 35a is enlarged, the flow velocity of the working fluid in the
vicinity of the suction port 35a of the discharge pipe 35 is
smaller as compared with a case in which the inner diameter is
enlarged. Therefore, the amount of oil mist which is drawn together
with the working fluid can be reduced, and the refrigeration
oil-separating effect of the first to third embodiments can further
be enhanced.
[0115] The same effect as that of the second embodiment can be
obtained if the following structure is employed. That is, in the
compressor of the fifth embodiment, the suction port 35a of the
discharge pipe 35 is disposed closer to the inner peripheral
surface of the coil end 11b than the central portion of the
hermetical container 1 as in the second embodiment, and the suction
port 35a is directed diagonally downward toward substantially the
downstream in the rotation direction of the upper surface 12b of
the rotor 12.
[0116] In the compressor of the fifth embodiment, the same effect
as that of the third embodiment can be obtained if the suction port
35a of the discharge pipe 35 is disposed in the vicinity of the
rotation center axis L as in the third embodiment and the discharge
pipe 35 is directed diagonally downward.
Sixth Embodiment
[0117] A compressor according to the sixth embodiment of the
present invention has the same structure as that of the compressor
of the second embodiment as shown in FIGS. 3 and 4 except the
hermetical container and the discharge pipe. The same elements are
designated with the same symbols.
[0118] FIG. 9 is a vertical sectional view of a compressor
according to the sixth embodiment of the invention. According to
the compressor of this embodiment, the compression mechanism
comprising the shaft 2, the cylinder 3, the roller 4, the vane 7
and the like is disposed in a lower portion in a hermetical
container 36, and the rotational motor comprising the stator 11 and
the rotor 12 is disposed in an upper portion in the hermetical
container 36. Refrigeration oil is reserved in the oil reservoir 16
formed in the bottom of the hermetical container 36. Each of the
upper portion of the bottom (including inner surface of the
container) of the hermetical container 36 is domical in shape which
comprises a combination of a peripheral r-portion 36a having a
smaller diameter and an inner R-portion 36b having a larger
diameter.
[0119] The introducing terminal 13 for energizing the rotational
motor in the hermetical container 36 and a discharge pipe 37 for
introducing working fluid from the hermetical container 36 into the
refrigeration cycle are provided in an upper portion of the
hermetical container 36. The discharge pipe 37 passes through the
hermetical container 36, and the suction port 37a is located inside
the coil end 11b on the upper end of the stator 11.
[0120] According to the compressor of the sixth embodiment having
such a structure, since the suction port 37a of the discharge pipe
37 is located inside the coil end 11b as in the first embodiment,
the same effect as that of the first embodiment can be obtained of
course.
[0121] The working fluid which passed through the notches 11a of
the stator 11 flows upward to the vicinity of the coil end 11b of
the stator 11 and then, passes through the upper portion of the
coil end 11b and flows toward the center of the hermetical
container 36. Here, since at least the upper portion of the
hermetical container 36 is domical in shape, the working fluid
flows toward the center of the hermetical container 36 along the
r-portion 36a and the R-portion 36b, and it is possible to prevent
the flow velocity from being lowered. Therefore, after that, the
downward flow velocity toward the suction port 37a of the discharge
pipe 37 located inside the coil end 11b is also increased. When the
working fluid is drawn into the suction port 37a of the discharge
pipe 37, the flow of the working fluid is again changed into the
upward flow, but the oil-separating effect by the gravity and the
centrifugal force at that time can further be enhanced.
[0122] Since the hermetical container 36 is domical in shape, the
refrigeration cycle is a supercritical cycle of working fluid
having carbon dioxide as main composition. Thus, even when a
pressure in the hermetical container 36 is extremely high, the
strength of the hermetical container 36 can be maintained and
safety can be secured.
[0123] In the compressors of the first to sixth embodiments,
working fluid having the environment-friendly carbon dioxide as
main composition, the working fluid in the hermetical container 1
or 36 is in the supercritical state, and the meltage of the
refrigeration oil with respect to the working fluid is increased.
Thus, the oil-separating effect obtained by the gravity and the
centrifugal force is enhanced, and the object of the present
invention can be achieved.
Seventh Embodiment
[0124] FIG. 10 is a vertical sectional view of a compressor
according to the seventh embodiment of the invention, and FIG. 11
is a lateral sectional view of the compressor shown in FIG. 10
taken along arrows X-X. The compressor according to the seventh
embodiment of the present invention has almost the same structure
as that of the conventional compressor. The same elements are
designated with the same symbols.
[0125] The compressor of this embodiment comprises the hermetical
container 1, the compression mechanism disposed in a lower portion
in the hermetical container 1, and the rotational motor disposed in
an upper portion in the hermetical container 1. The compression
mechanism comprises the shaft 2 capable of rotational around the
rotation center axis L, the cylinder 3 having the cylindrical
surface 3a therein, the roller 4 fitted over the eccentric portion
2a of the shaft 2 and eccentrically rotational inside the cylinder
3 with the rotation of the shaft 2, the vane 7 which reciprocates
within the vane groove 3b of the cylinder 3 while a tip end of the
vane 7 being in contact with the roller 4 and which divides a space
defined by the cylinder 3 and the roller 4 into the suction chamber
5 and the compression chamber 6, the spring 8 which is disposed on
a back surface of the vane 7 and which pushes the vane 7 against
the roller 4, and the upper bearing 9 and a lower bearing 10 which
support the shaft 2. The upper bearing 9 includes a flow path 9a
which is connected to the suction pipe 15 and which introduces
working fluid drawing from the suction pipe 15 into the suction
chamber 5, and the discharging hole 9b which discharges working
fluid compressed in the compression chamber 6 into the lower space
17 of the rotational motor.
[0126] The rotational motor comprises the stator 11 shrinkage
fitted into the hermetical container 1, and the rotor 12 which is
shrinkage fitted to the shaft 2 and rotates in the inner periphery
of the stator 11. The stator 11 is provided at its upper end with
the coil end 11b and at its lower end with the coil end 11d. The
stator 11 is provided at its outer periphery with a plurality of
notches 11a which bring the lower space 17 and the upper space 19
into communication with each other. The notches 11a serve as flow
paths for working fluid. Refrigeration oil is reserved in the oil
reservoir 16 formed in the bottom of the hermetical container
1.
[0127] A thin cylinder 41 as a dividing member is fitted over the
coil end 11b formed on the upper end of the stator 11, and an upper
space 19 of the rotational motor is divided by the thin cylinder 41
into an inner space 19a and an outer space 19b. This thin cylinder
41 is made of insulative Teflon (registered trademark), and its
thickness of about 1 mm. The thin cylinder 41 has a bent portion
41a formed in the vicinity of the upper end surface 11c of the coil
end 11b. An inner diameter of the bent portion 41a of the thin
cylinder 41 is reduced toward its top, and a gap 44 serving as a
flow path of the working fluid is formed between an upper end 41b
of the thin cylinder 41 and an upper end surface 1a of the
hermetical container 1.
[0128] The introducing terminal 13 for energizing the rotational
motor in the hermetical container 1 and the discharge pipe 40 for
introducing the working fluid from the upper space 19 in the
hermetical container 1 into the refrigeration cycle are provided in
an upper portion in the hermetical container 1. The discharge pipe
40 passes through the hermetical container 1, and has a curved
portion 40b inside the hermetical container 1. A suction port 40a
of the discharge pipe 40 as an open end of the hermetical container
is located below the gap 44 inside the thin cylinder 41 (i.e.,
inside the inner space 19a). That is, the suction port 40a is
disposed at a lower position than the upper end 41b of the thin
cylinder 41. The suction port 40a of the discharge pipe 40 is
disposed in the vicinity of the rotation center axis L of the rotor
12 and is directed diagonally downward. Therefore, the introducing
terminal 13 is mounted at a position where the mounting of the
discharge pipe 40 provided on the upper portion of heat exchanger
hermetical container 1 is not hindered. In this embodiment, the
through holes 12a (see FIG. 6) of the rotor 12 by the same
oil-separating plate method as that of the conventional technique
is not provided.
[0129] Next, the operation of the compressor having the
above-described structure will be explained. The working fluid is
introduced from the suction pipe 15 into the suction chamber 5
through the flow path 9a provided in the upper bearing 9. If the
rotational motor is energized and the shaft 2 which is integral
with the rotor 12 is rotated, the roller 4 eccentrically rotates,
the capacities of the suction chamber 5 and the compression chamber
6 are varied. With this, the working fluid is drawn and compressed.
When a discharge valve (not shown) of the discharging hole 9b is
opened, oil mist which is supplied from the oil reservoir 16 and
which lubricated the compression mechanism is mixed into the
compressed working fluid, and this mixture is discharged into the
lower space 17 of the rotational motor. The working fluid in the
lower space 17 passes through notches 11a formed in the outer
periphery of the stator 11 as gaps between the hermetical container
1 and the rotational motor formed on the outer periphery of the
stator 11, and through a gap 18 (air gap) between the stator 11 and
the rotor 12, and flows into the upper space 19 of the rotational
motor. The working fluid is separated from the refrigeration oil in
the upper space 19, and is discharged from the discharge pipe
14.
[0130] This oil-separating operation will be explained. As
described above, the working fluid including oil mist discharged
from the compression mechanism into the lower space 17 of the
rotational motor passes through the gap 18 between the stator 11
and the rotor 12 and the notches 11a of the stator 11, and moves
into the inner space 19a and the outer space 19b of the upper space
19 of the rotational motor. At that time, since the gap 18 is
extremely narrow, the rate of working fluid passing through the
notches 11a of the stator 11 becomes extremely large.
[0131] The working fluid which flowed into the outer space 19b of
the thin cylinder 41 through the notches 11a of the stator 11
passes through the gap 44 between the upper end 41b of the thin
cylinder 41 and the upper end surface 1a in the hermetical
container 1, and flows into the inner space 19a of the thin
cylinder 41. The working fluid in the inner space 19a of the thin
cylinder 41 is drawn into the suction port 40a located below the
gap 44, and is discharged into the outside refrigeration cycle.
Since the rotor 12 rotates at high speed in the inner space 19a of
the thin cylinder 41, a turning flow around the rotation center
axis L is generated in the working fluid in the inner space 19a of
the thin cylinder 41.
[0132] The oil-separating operation and its effect will be
explained in detail.
[0133] The thin cylinder 41 is fitted over the coil end 11b and the
upper space 19 of the rotational motor is divided into the inner
space 19a and the outer space 19b of the thin cylinder 41.
Therefore, it is possible to limit the flow path of the working
fluid which flowed into the upper space 19 through the notches 11a
of the stator 11.
[0134] That is, since there is provided the thin cylinder 41 which
divides the upper space 19 into the inner space 19a and the outer
space 19b, it is possible to prevent the turning flow of the inner
space 19a of the thin cylinder 41 from being dispersed to the outer
space 19b of the thin cylinder 41. Thus, attenuation of rotational
motion energy is suppressed. Therefore, it becomes easily to
maintain the turning flow velocity of the inner space 19a of the
thin cylinder 41 in a portion of the coil end 11b higher than the
upper end surface 11c, and strong centrifugal force is applied to
the working fluid and oil mist which flow toward the suction port
40a provided in a lower portion of the gap 44 through the gap 44
between the upper end 41b of the thin cylinder 41 and the upper end
surface 1a in the hermetical container 1. Therefore, the oil mist
having higher density than the working fluid attaches to the inner
side surface of the thin cylinder 41 and becomes liquid drop. Since
the the liquid drop has higher density than the working fluid, the
liquid drop flows lower than the working fluid and is separated
from the working fluid.
[0135] Since the gap 44 is provided between the upper end 41b of
the thin cylinder 41 and the upper end surface 1a in the hermetical
container 1, the working fluid which passed through the notches 11a
of the stator 11 and which includes oil mist flows upward to the
vicinity of the upper end of the hermetical container 1 through the
outer space 19b and then, passes through the gap 44 and flows into
the inner space 19a of the thin cylinder 41. The gap 44 is formed
immediately below the upper end surface 1a in the hermetical
container 1 and the inner space 19a of the thin cylinder 41 spreads
below the gap 44. Thus, the working fluid which flowed into the
inner space 19a of the thin cylinder 41 forms a flow having
downward flow velocity component while enlarging the flow width.
The oil mist mixed into the working fluid which flows downward
receives downward flow velocity component from the peripheral
working fluid. Since the oil mist has higher density than the
working fluid and gravity acting on the refrigeration oil is
greater than gravity acting on the working fluid, the oil mist has
greater downward velocity component than the working fluid. Thus,
the oil mist flows downward of the working fluid and is separated
from the working fluid. That is, since the working fluid flows into
the inner space 19a of the thin cylinder 41 through the gap 44
between the upper end 41b of the thin cylinder 41 and the upper end
surface 1a in the hermetical container 1, the oil mist is separated
from the working fluid.
[0136] In this embodiment, since the discharge pipe 40 passes
through the hermetical container 1 and the suction port 40a of the
discharge pipe 40 is located lower than the gap 44 at the inner
space 19a of the thin cylinder 41, the working fluid flowing into
the inner space 19a from the gap 44 flows more downward toward the
suction port 40a. Thus, the oil mist receives strong downward
external force from the working fluid, and the oil mist is prone to
be separated from the working fluid. The suction port 40a of the
discharge pipe 40 opens diagonally downward, and the flowing
direction of the working fluid drawn into the suction port 40a is
abruptly changed from downward to upward. Thus, the oil mist which
is attracted by the suction port 40a and flows downward has higher
density and greater inertial force than the working fluid. Thus,
the oil mist downwardly flows into the upper surface 12b of the
rotor 12 without changing the flowing direction to the upward. The
working fluid having lower density and smaller inertial force than
the refrigeration oil is drawing into the suction port 40a. Thus,
the working fluid and the oil mist are separated from each
other.
[0137] Since the rotor 12 is rotational in the inner space 19a of
the thin cylinder 41, the turning flow is generated in viscosity in
the vicinity of the upper surface 12b of the rotor 12. As the
working fluid in the inner space 19a of the thin cylinder 41
reaches the vicinity of the upper surface 12b of the rotor 12 by a
shearing force received from the turning flow, the flow velocity
component in the rotational direction is increased. In a portion of
the coil end 11b higher than the upper end surface 11c, a region
which receives heat exchanger influence of the turning flow is
increased to the inner side surface of the thin cylinder 41 fitted
over the coil end 11b and thus, the flow velocity in the rotational
direction of the working fluid is abruptly reduced. However, since
the inner side surface of the thin cylinder 41 is cylindrical in
shape, the loss of the flow velocity in the rotational direction of
the working fluid given by the inner side surface of the thin
cylinder 41 higher than the upper end surface 11c of the coil end
11b becomes extremely small.
[0138] Further, since a higher portion of bent portion 41a of the
thin cylinder 41 has smaller inner diameter, an external force
acting toward the inner side surface of the thin cylinder 41 by the
centrifugal force of the working fluid which rotates inside is
applied to the liquid drop of the refrigeration oil attached to the
upper portion of the bent portion 41a of the thin cylinder 41. A
component of force perpendicular to the inner side surface of the
thin cylinder 41 of the external force acting torward the inner
side surface of the thin cylinder 41 is in balance with a reaction
force from the inner side surface of the thin cylinder 41, but
there remains a component of force which is parallel to the inner
side surface of the thin cylinder 41. Therefore, a downward force
which is in parallel to the inner side surface of the thin cylinder
41 acts on the liquid drop of the refrigeration oil attached to the
upper portion of the bent portion 41a of the thin cylinder 41, and
the downward flow of the working fluid is accelerated.
[0139] Oil mist which is not attached to the inner side surface of
the thin cylinder 41 and is not drawn into the suction port 40a of
the discharge pipe 40 has higher density than the working fluid in
a lower portion of the suction port 40a of the discharge pipe 40,
the oil mist reaches nearer to the upper surface 12b of the rotor
12 than the working fluid.
[0140] Since the thin cylinder 41 is fixed to the outer side of the
coil end 11b, oil mist which received greater turning flow velocity
and greater centrifugal force in the vicinity of the upper surface
12b of the rotor 12 attaches to the coil end 11b which comprises a
plurality of copper wires and provided at its surface with
complicated bumps and dips. Therefore, the oil mist is prone to
grow into the liquid drop and the oil mist is separated from the
working fluid easily.
[0141] With the above effect, the refrigeration oil which grew into
the liquid drop from the fog drip and which was separated from the
working fluid passes through the gap 18 between the stator 11 and
the rotor 12 by the gravity, and is returned into the oil reservoir
16 formed in the bottom of the hermetical container 1. The working
fluid having smaller centrifugal force caused by turning flow than
the refrigeration oil and collected to the center of the inner
space 19a of the thin cylinder 41 is introduced into the suction
port 40a of the discharge pipe 40 in a state where the
refrigeration oil is separated from the working fluid.
[0142] As described above, in this embodiment, an amount of the
refrigeration oil delivered to the refrigeration cycle out from the
compressor together with the working fluid can be reduced. The
refrigeration oil is not attached to an inner wall of a heat
exchanger tube of a heat exchanger, and it is possible to prevent
the heat exchanging efficiency from being deteriorated. An amount
of refrigeration oil in the oil reservoir 16 can always be
maintained constantly, and it is possible to enhance the
reliability and efficiency of the compressor.
[0143] In this embodiment, the thin cylinder 41 is fitted over the
coil end 11b, the gap is provided between the upper end of the thin
cylinder 41 and the upper end surface in the hermetical container
1, and the discharge pipe 40 is extended and its suction port 40a
is located inside the thin cylinder 41. Therefore, the effect of
this embodiment can easily be obtained only by slightly changing
the conventional compressor, and the compressor is extremely
inexpensive.
Eighth Embodiment
[0144] FIG. 12 is a vertical sectional view of a compressor
according to the eighth embodiment of the invention. The compressor
according to the eighth embodiment of the present invention has the
same structure as that of the compressor of the seventh embodiment
as shown in FIGS. 10 and 11 except the thin cylinder. The same
elements are designated with the same symbols. Explanation of the
same structure and effect as those of the seventh embodiment will
be omitted.
[0145] In the compressor of this embodiment, a thin cylinder 42 as
a dividing member is fitted into the coil end 11b on the upper end
of the stator 11, and the upper space 19 of the rotational motor is
divided by the thin cylinder 42 into the inner space 19a and the
outer space 19b. An inner diameter of an inner side surface of the
thin cylinder 42 is reduced from its lower end toward the upper
end. A gap 44 is provided between the upper end 42b of the thin
cylinder 42 and the upper end surface 1a in the hermetical
container 1.
[0146] Nest the oil-separating operation of the thin cylinder 42
and its effect will be explained.
[0147] The rotational motion energy caused by shrinkage fit is
given to the working fluid in the inner space 19a of the thin
cylinder 42 by a turning flow generated in the vicinity of the
upper surface 12b of the rotor 12, and the turning flow is
generated in the working fluid. However, by fitting the thin
cylinder 42 into the coil end 11b, a region of the inner space 19a
is reduced as compared with a case in which the thin cylinder 42 is
fitted over the coil end 11b and thus, the dispersion of the
rotational motion energy is suppressed. Thus, as compared with the
seventh embodiment, the turning flow velocity of the inner space
19a of the thin cylinder 42 is increased as a whole. The working
fluid which flowed into the inner space 19a from the gap 44 of the
upper end 42b of the thin cylinder 42 receives stronger centrifugal
force than the seventh embodiment. Therefore, oil mist is prone to
attach to the inner side surface of the thin cylinder 42 due to a
difference in centrifugal force caused by difference in density
between the working fluid and the refrigeration oil, the growth of
the oil mist into the liquid drop is facilitated, and the
refrigeration oil is separated from the working fluid easily.
[0148] Since the thin cylinder 42 is fitted into the coil end 11b,
there is no obstruction in the thin cylinder 42 which limits the
flexibility in shape of the thin cylinder 42. Therefore, the inner
diameter of the inner side surface of the thin cylinder 42 can
further be reduced from its lower end toward its upper ends as
compared with the compressor of the seventh embodiment. Thus, the
component of force perpendicular to the inner side surface of the
thin cylinder 42 of the centrifugal force applied to the liquid
drop of the refrigeration oil attached to the inner side surface of
the thin cylinder 42 is brought into balance with the reaction
force from the inner side surface of the thin cylinder 42, and
there remains a component of force which is parallel to the inner
side surface of the thin cylinder 42 of the centrifugal force
applied to the liquid drop of the refrigeration oil attached to the
inner side surface of the thin cylinder 42. Therefore, the downward
flow of the liquid drop of the refrigeration oil attached to the
inner side surface from the lower end to the upper end of the thin
cylinder 42 is accelerated, and the refrigeration oil is returned
into the oil reservoir 16 formed in the bottom of the hermetical
container 1 more easily as compared with the compressor of the
seventh embodiment.
[0149] In addition to the above-described effect, the eighth
embodiment can obtain the effect of the seventh embodiment of
course.
[0150] As described above, in this embodiment, an amount of the
refrigeration oil delivered to the refrigeration cycle out from the
compressor together with the working fluid can be reduced. The
refrigeration oil is not attached to an inner wall of a heat
exchanger tube of a heat exchanger, and it is possible to prevent
the heat exchanging efficiency from being deteriorated. An amount
of refrigeration oil in the oil reservoir 16 can always be
maintained constantly, and it is possible to enhance the
reliability and efficiency of the compressor.
Ninth Embodiment
[0151] FIG. 13 is a vertical sectional view of a compressor
according to the ninth embodiment of the invention. The compressor
according to the eighth embodiment of the present invention has the
same structure as that of the compressor of the seventh embodiment
as shown in FIGS. 10 and 11 except the thin cylinder. The same
elements are designated with the same symbols. Explanation of the
same structure and effect as those of the seventh embodiment will
be omitted.
[0152] In the compressor of this embodiment, a thin cylinder 43 as
a dividing member is fitted into the coil end 11b on the upper end
of the stator 11, and the upper space 19 of the rotational motor is
divided by the thin cylinder 43 into the inner space 19a and the
outer space 19b. At that time, an upper end of the thin cylinder 43
is brought into contact with the upper end surface 1a in the
hermetical container 1 and fixed thereto. A plurality of
communication holes 45 are formed in the upper portion of the thin
cylinder 43 as flow paths for working fluid which brings the inner
space 19a and the outer space 19b into communication with each
other. A flange 43a extending inside the thin cylinder 43 from a
lower inner side surface of the thin cylinder 43 is provided in the
vicinity of the upper surface 12b of the rotor 12. The inner space
19a of the thin cylinder 43 is divided by the flange 43a into an
upper space 19a' and a lower space 19c. A flow path 46 which brings
the upper space 19a' and the lower space 19c into communication
with each other is formed in a center of the flange 43a.
[0153] Next, the oil-separating operation of the thin cylinder 43
and the flange 43a and its effect will be explained.
[0154] Since the inner space 19a and the outer space 19b divided by
the thin cylinder 43 are in communication with each other through
the plurality of communication holes 45 formed in the upper portion
of the thin cylinder 43, the upper end of the thin cylinder 43 can
be brought into contact with the upper end surface 1a in the
hermetical container 1 and fixed thereto. Therefore, the
positioning precision of the dividing member in the vertical
direction when the compressor is assembled is enhanced irrespective
of the installation place of the dividing member inside or outside
the coil end. If the thin cylinder is provided outside the coil
end, the possibility of contact with the thin cylinder and the
rotor which rotates at high speed is lowered, damage caused by
contact between the thin cylinder and the rotor is prevented, and a
compressor having high reliability can be provided.
[0155] The flange 43a extending toward the rotation center axis L
is provided on the inner periphery of the thin cylinder 43, the
inner space 19a of the thin cylinder 43 is divided by the flange
43a into the upper space 19a' and the lower space 19c, and the flow
path 46 for bringing the upper space 19a' and the lower space 19c
into communication with each other is formed in the center of the
flange 43a. Therefore, in the lower space 19c of the thin cylinder
43, strong centrifugal force acting outwardly from the rotation
center axis L is applied to the working fluid which receives the
rotational motion energy by viscosity from the upper surface 12b of
the rotational rotor 12. The working fluid on which the strong
centrifugal force acts flows in the radial direction toward the
inner side surface of the thin cylinder 43 through the lower space
19c between the flange 43a and the upper surface 12b of the rotor
12, and flows downwardly through the gap 18 between the rotor 12
and the stator 11 along a corner formed between the flange 43a and
the inner side surface of the thin cylinder 43.
[0156] At that time, since the working fluid flows outwardly in the
vicinity of the rotation center axis L of the upper surface 12b of
the rotor 12, the pressure is lowered, and the working fluid flows
into the lower space 19c of the flange 43a through the flow path 46
from the upper space 19a' of the flange 43a. Thus, since the thin
cylinder 43 is fitted into the coil end 11b and the working fluid
is allowed to flow into the inner space 19a of the thin cylinder 43
from the upper portion of the thin cylinder 43, fog drip and liquid
drop of the refrigeration oil separated from the working fluid and
collected into the lower portion of the upper space 19a' of the
flange 43a are forcibly returned into the oil reservoir 16 formed
in the bottom of the hermetical container 1 from the flow path 46
of the flange 43a through the the lower space 19c and the gap 18
between the rotor 12 and the stator 11. Since the fog drip and
liquid drop of the refrigeration oil collected into the lower
portion of the upper space 19a' of the flange 43a are forcibly
returned into the oil reservoir 16 in this manner, it is possible
to further prevent the concentration of the oil mist of the upper
space 19a' of the flange 43a from being lowered, and to prevent the
refrigeration oil from being discharged from the compressor.
[0157] Although the flange 43a is formed on the inner periphery of
the thin cylinder 43, it is possible to independently provide the
flange on the inner periphery of the upper end coil end (this
structure is not shown). By the same effect as that of this
embodiment, it is possible to forcibly return the fog drip and
liquid drop of the refrigeration oil in the vicinity of the flange
into the oil reservoir from the lower space formed by the
flange.
[0158] In addition to the above-described effect, the ninth
embodiment can obtain the effect of the seventh and eighth
embodiments of course.
[0159] As described above, in this embodiment, an amount of the
refrigeration oil delivered to the refrigeration cycle out from the
compressor together with the working fluid can be reduced. The
refrigeration oil is not attached to an inner wall of a heat
exchanger tube of a heat exchanger, and it is possible to prevent
the heat exchanging efficiency from being deteriorated. An amount
of refrigeration oil in the oil reservoir 16 can always be
maintained constantly, and it is possible to enhance the
reliability and efficiency of the compressor.
[0160] In in the compressor of any of the seventh to ninth
embodiments, the working fluid in the hermetical container 1 is
brought into the supercritical state using working fluid comprising
environment-friendly carbon dioxide, and the meltage of the
refrigeration oil with respect to the working fluid is increased.
The oil-separating effect is enhanced by effect of the thin
cylinder 41 and the like.
Tenth Embodiment
[0161] FIG. 14 is a vertical sectional view of a compressor
according to a tenth embodiment of the invention, FIG. 15 is a
lateral sectional view of the compressor shown in FIG. 14 taken
along arrows X-X, FIG. 16 is a lateral sectional view of the
compressor shown in FIG. 14 taken along arrows Y-Y and FIG. 17 is a
lateral sectional view of the compressor shown in FIG. 14 taken
along arrows Z-Z. The compressor according to the tenth embodiment
of the present invention has almost the same structure as that of
the conventional compressor. The same elements are designated with
the same symbols.
[0162] The compressor of this embodiment comprises the hermetical
container 1, the compression mechanism disposed in a lower portion
in the hermetical container 1, and the rotational motor disposed in
an upper portion in the hermetical container 1. The compression
mechanism comprises the shaft 2 capable of rotational around the
rotation center axis L, the cylinder 3 having the cylindrical
surface 3a therein, the roller 4 fitted over the eccentric portion
2a of the shaft 2 and eccentrically rotational inside the cylinder
3 with the rotation of the shaft 2, the vane 7 which reciprocates
within the vane groove 3b of the cylinder 3 while a tip end of the
vane 7 being in contact with the roller 4 and which divides a space
defined by the cylinder 3 and the roller 4into the suction chamber
5 and the compression chamber 6, the spring 8 which is disposed on
a back surface of the vane 7 and which pushes the vane 7 against
the roller 4, and the upper bearing 9 and a lower bearing 10 which
support the shaft 2. The upper bearing 9 includes a flow path 9a
which is connected to the suction pipe 15 and which introduces
working fluid drawing from the suction pipe 15 into the suction
chamber 5, and the discharging hole 9b which discharges working
fluid compressed in the compression chamber 6 into the lower space
17 of the rotational motor.
[0163] The rotational motor comprises the stator 11 shrinkage
fitted into the hermetical container 1, and the rotor 12 which is
shrinkage fitted to the shaft 2 and rotates in the inner periphery
of the stator 11. The stator 11 is provided at its upper end with
the coil end 11b and at its lower end with the coil end 11d. The
stator 11 is provided at its outer periphery with a plurality of
notches 11a which bring the lower space 17 and the upper space 19
into communication with each other. The notches 11a serve as flow
paths for working fluid. Refrigeration oil is reserved in the oil
reservoir 16 formed in the bottom of the hermetical container
1.
[0164] The hermetical container 1 comprises three elements, i.e.,
an upper shell 50, a barrel shell 51 and a lower shell 52. The
hermetical container 1 is formed by welding. An introducing
terminal 54 for energizing the rotational motor in the hermetical
container 1 is disposed in the center of the upper shell 50. A
columnar cluster 55 is mounted on the introducing terminal 54 in
the hermetical container 1 such that a mounting gap is not
substantially generated, and the stator 11 of the rotational motor
is energized through the lead wire 25. This columnar cluster 55 is
provided in the upper central portion of the hermetical container
such that a center axis of the cluster 55 substantially coincides
with the rotation center axis L of the rotational motor. An outer
diameter of the cluster 55 is smaller than an inner diameter of the
coil end 11b on the upper end of the stator 11.
[0165] A discharge pipe 53 is provided on a side surface of an
upper portion of the hermetical container 1 (upper shell 50) for
introducing the working fluid into the refrigeration cycle outside
the hermetical container 1 from the upper space 19 in the
hermetical container 1. The discharge pipe 53 passes through the
hermetical container 1 from a side surface of the upper shell 50.
The discharge pipe 53 is formed at a lower position than a lower
surface of the cluster 55. A suction port 53a of the discharge pipe
53 as an open end into the hermetical container projects from an
inner wall surface of the hermetical container 1.
[0166] A carbon dioxide refrigerant which is a natural refrigerant
is used as the working fluid. In this embodiment, the through holes
12a (see FIG. 8) of the rotor 12 by the same oil-separating plate
method as that of the conventional technique is not provided.
[0167] Next, the operation of the compressor having the
above-described structure will be explained. The working fluid is
introduced from the suction pipe 15 into the suction chamber 5
through the flow path 9a provided in the upper bearing 9. If the
rotational motor is energized and the shaft 2 which is integral
with the rotor 12 is rotated, the roller 4 eccentrically rotates,
the capacities of the suction chamber 5 and the compression chamber
6 are varied. With this, the working fluid is drawn and compressed.
When a discharge valve (not shown) of the discharging hole 9b is
opened, oil mist which is supplied from the oil reservoir 16 and
which lubricated the compression mechanism is mixed into the
compressed working fluid, and this mixture is discharged into the
lower space 17 of the rotational motor. The working fluid in the
lower space 17 passes through notches 11a formed in the outer
periphery of the stator 11 as gaps between the rotational motor and
the hermetical container 1, and through a gap 18 (air gap) between
the stator 11 and the rotor 12, and flows into the upper space 19
of the rotational motor. The working fluid is separated from the
refrigeration oil in the upper space 19, and is discharged from the
discharge pipe 14.
[0168] This oil-separating operation will be explained. As
described above, the working fluid including oil mist discharged
from the compression mechanism into the lower space 17 of the
rotational motor passes through the notches 11a of the stator 11
and the gap 18 between the stator 11 and the rotor 12, and moves
into the upper space 19 of the rotational motor. At that time,
since the gap 18 is extremely narrow, the rate of working fluid
passing through the notches 11a of the stator 11 becomes extremely
large.
[0169] The working fluid including the oil mist passing through the
notches 11a of the stator 11 flows into the upper space 19 of the
rotational motor along a wall surface of the hermetical container 1
(barrel shell 51 and the upper shell 50) and then, the working
fluid flows downward toward the inner space of the coil end 11b
along a side surface of the cluster 55 disposed in the center of
the upper shell 50.
[0170] Since the rotor 12 of the rotational motor is rotational at
high speed, a shearing force caused by the upper surface 12b of the
rotor 12 is applied to the downward flow of the working fluid, and
turning flow around the rotation center axis L of the rotor 12 is
generated. At that time, since the cluster 55 is columnar in shape
which is symmetric with respect to the rotation center axis L, the
turning flow around the cluster 55 is further prone to be
generated, and the flow velocity of the turning flow is uniformly
increased. Therefore, the working fluid and the refrigeration oil
are separated by a centrifugal force caused by a difference in
density therebetween, the oil mist moves toward the outer
peripheral portion of the turning flow, and attaches to the inner
wall surface of the upper shell 50 and becomes oil drop. The oil
drop drops downward and is returned into the oil reservoir 16
formed in the bottom of the hermetical container 1.
[0171] The working fluid which flowed to the inner space of the
coil end 11b on the upper end of the stator 11 and which includes
the oil mist turns and flows in the inner space of the coil end
11b, and the oil mist is separated from the working fluid by the
centrifugal force, the oil mist attaches to the inner peripheral
surface of the coil end 11b and becomes oil drop and drops
downward, and the oil drop is returned to the oil reservoir 16
formed in the bottom of the hermetical container 1.
[0172] The working fluid from which the oil mist is separated flows
around a region close to the center of the turning flow which is
away from an inner wall surface of the hermetical container 1.
Since the suction port 53a projects from the inner wall surface of
the hermetical container 1 and the suction port 53a is inserted
into this region in this embodiment, most of refrigeration oil is
separated from the working fluid which flowed into the discharge
pipe 53 and discharged from the compressor.
[0173] Since the discharge pipe 53 is lower than the lower surface
of the cluster 55, the flow of the working fluid flowing into the
upper space 19 is shut off by the side surface of the cluster 55,
and the working fluid does not flow into the suction port 53a of
the discharge pipe 53 directly. Further, since the cluster 55 is
disposed in the introducing terminal 54 such that a mounting gap is
not generated and thus, the working fluid which flowed into the
upper space 19 does not pass through the mounting gap between the
cluster 55 and the introducing terminal 54. Therefore, the turning
flow is not disturbed.
[0174] The hermetical container 1 is divided into the upper shell
50, the barrel shell 51 and the lower shell 52. Therefore, the
discharge pipe 53 and the introducing terminal 54 can be bonded to
the upper shell 50 previously, or the compression mechanism and the
rotational motor can be fitted to the barrel shell 51. Therefore,
the assembling operation of the compressor is facilitated. The
outer diameter of the cluster 55 is set smaller than the inner
diameter of the coil end 11b. Therefore, there is effect that a
space for flowing is increased, and the turning flow of the inner
space of the coil end 11b can easily be developed into turning flow
around the cluster 55.
[0175] As described above, in this embodiment, an amount of the
refrigeration oil delivered to the refrigeration cycle out from the
compressor together with the working fluid can be reduced
extremely. Therefore, the refrigeration oil is not attached to an
inner wall of a heat exchanger tube of a heat exchanger, and it is
possible to prevent the heat exchanging efficiency from being
deteriorated. An amount of refrigeration oil in the oil reservoir
16 can always be maintained constantly, and it is possible to
enhance the reliability and efficiency of the compressor.
[0176] To prevent the global warming, it is proposed to employ, as
a refrigerant, a carbon dioxide refrigerant which is a natural
refrigerant having lower worming coefficient. If the carbon dioxide
refrigerant is used as the working fluid, a pressure of the
compressed working fluid becomes extremely high, a mixing rate of
the refrigeration oil into the working fluid is increased, and it
becomes difficult to separate the oil from the working fluid. In
this regard, according to this embodiment, since the turning flow
around the columnar cluster 55 is accelerated, it is possible to
easily separate the working fluid and the oil mist from each
other.
[0177] In the tenth embodiment, only the cluster 55 and the
discharge pipe 53 are changed and oil can easily be separated with
slight change. Therefore, there is effect that the compressor can
be provided extremely inexpensively.
[0178] In the compressor of the tenth embodiment, the radial gap
between the cluster 55 and the upper shell 50 of the hermetical
container 1 is equal to or smaller than the outer diameter of the
cluster 55, the turning flow around the cluster 55 can further be
accelerated and thus, the oil-separating efficiency can be
enhanced. For example, if the outer diameter of the columnar
cluster 55 is 28 mm and the inner diameter of the upper shell 50 is
about 84 mm or less, it is possible to remarkably reduce the amount
of refrigeration oil delivered to the refrigeration cycle outside
the compressor.
[0179] The flow velocity of the turning flow is increased as the
inner diameter of the hermetical container 1 is smaller. Thus, the
oil-separating effect by the turning flow becomes higher. The
oil-separating effect can be enhanced only by forming the cluster
55 into the columnar shape and by allowing the discharge pipe 53 to
pass through the side surface of the upper shell 50. Therefore, the
tenth embodiment can easily be applied to the compressor with the
hermetical container 1 having the outer diameter as extremely small
as about 80 mm or less.
[0180] The discharge pipe 53 passes through the side surface of the
upper shell 50 in the compressor of the tenth embodiment. If the
height of the upper shell 50 is reduced and the height of the
barrel shell 51 is increased, the discharge pipe 53 can pass
through the side surface of the barrel shell 51, and the same
effect can be obtained also in this structure (not shown).
Eleventh Embodiment
[0181] A compressor of the eleventh embodiment is the same as the
compressor of the tenth embodiment shown in FIGS. 14, 15 and 16. A
vertical sectional view of the compressor of the eleventh
embodiment is the same as that shown in FIG. 14. FIG. 18 is a
lateral sectional view of a compressor according to the eleventh
embodiment of the invention taken along arrows Z-Z in FIG. 14. The
same elements are designated with the same symbols. Explanation of
the same structure and effect as those of the tenth embodiment will
be omitted.
[0182] The eleventh embodiment is the same as the tenth embodiment
except a discharge pipe 63, an introducing terminal 64, and a
hexagonal columnar cluster 65 mounted on the introducing terminal
64. The hexagonal columnar cluster 65 is mounted on the introducing
terminal 64 disposed in the center of the upper shell 50 such that
almost no mounting gap is generated, and the stator 11 of the
rotational motor is energized through the lead wire 25. The cluster
65 is provided in an upper central portion in the hermetical
container 1 such that a center axis of the cluster 65 substantially
coincides with the rotation center axis L of the rotational motor.
A side surface 65a of the hexagonal columnar cluster 65 is opposed
to the notches 11a formed in the stator 11. An outer diameter of
the hexagonal columnar cluster 65 is smaller than an inner diameter
of the coil end 11b on the upper end of the stator 11.
[0183] The discharge pipe 63 pass through a side surface of the
upper shell 50 and extends into the hermetical container 1, and the
discharge pipe 63 is located lower than a lower surface of the
cluster 65. A suction port 63a of the discharge pipe 63 as an open
end in the hermetical container projects from an inner wall surface
of the hermetical container 1. A hydrocarbon refrigerant which is a
natural refrigerant is used as the working fluid.
[0184] The oil-separating operation will be explained. The working
fluid including oil mist discharged from the compression mechanism
into the lower space 17 of the rotational motor passes through the
notches 11a of the stator 11 and the gap 18 between the stator 11
and the rotor 12, and moves into the upper space 19 of the
rotational motor. At that time, since the gap 18 is extremely
narrow, the rate of working fluid passing through the notches 11a
of the stator 11 becomes extremely large.
[0185] The working fluid including the oil mist passing through the
notches 11a of the stator 11 flows into the upper space 19 of the
rotational motor along a wall surface of the hermetical container 1
(barrel shell 51 and the upper shell 50). Thereafter, the side
surface 65a of the cluster 65 disposed in the central portion of
the upper shell 50 becomes an obstruction, and a downward flow
toward the inner space of the coil end 11b along the side surface
65a is generated. At that time, the side surface 65a of the cluster
65 is opposed to the flow of the working fluid which flows from the
notches 11a of the stator 11 and which includes the oil mist. Since
the side surface 65a of the cluster 65 is flat as compared with the
tenth embodiment, especially the downward flow having no component
in the circumferential direction toward the inner space of the coil
end 11b is accelerated. Especially the polygonal side surface
becomes an obstruction, and the effect for dropping the oil mist
downward as the oil drop is enhanced.
[0186] Since the rotor 12 of the rotational motor is rotational at
high speed, a shearing force caused by the upper surface 12b of the
rotor 12 is applied to the downward flow of the working fluid, and
turning flow around the rotation center axis L is generated. At
that time, since the cluster 65 is hexagonal columnar in shape
which is symmetric wither respect to the rotation center axis L,
the turning flow around the cluster 65 is further prone to be
generated without being hindered, and the flow velocity of the
turning flow is uniformly increased. Therefore, the working fluid
and the refrigeration oil are separated by a centrifugal force
caused by a difference in density therebetween, the oil mist moves
toward the outer peripheral portion of the turning flow, and
attaches to the inner wall surface of the upper shell 50 and
becomes oil drop. The oil drop drops downward and is returned into
the oil reservoir 16 formed in the bottom of the hermetical
container 1.
[0187] The working fluid which flowed to the inner space of the
coil end 11b on the upper end of the stator 11 and which includes
the oil mist turns and flows in the inner space of the coil end
11b, and the oil mist is separated from the working fluid by the
centrifugal force, the oil mist attaches to the inner peripheral
surface of the coil end 11b and becomes oil drop and drops
downward, and the oil drop is returned to the oil reservoir 16
formed in the bottom of the hermetical container 1.
[0188] The working fluid from which the oil mist is separated flows
around a region close to the center of the turning flow which is
away from an inner wall surface of the hermetical container 1.
Since the suction port 63a projects from the inner wall surface of
the hermetical container 1 and the suction port 63a is inserted
into this region in this embodiment, most of refrigeration oil is
separated from the working fluid which flowed into the discharge
pipe 63 and discharged from the compressor.
[0189] Since the discharge pipe 63 is lower than the lower surface
of the cluster 65, the flow of the working fluid flowing into the
upper space 19 is shut off by the side surface of the cluster 65,
and the working fluid does not flow into the suction port 63a of
the discharge pipe 63 directly. Further, since the cluster 65 is
disposed in the introducing terminal 64 such that a mounting gap is
not generated and thus, the working fluid which flowed into the
upper space 19 does not pass through the mounting gap between the
cluster 65 and the introducing terminal 64. Therefore, the turning
flow is not disturbed.
[0190] In this embodiment, like the tenth embodiment, the
hermetical container 1 is divided into three. Therefore, the
discharge pipe 63 and the introducing terminal 64 can be bonded to
the upper shell 50 previously, or the compression mechanism and the
rotational motor can be fitted to the barrel shell 51. Therefore,
the assembling operation of the compressor is facilitated. The
outer diameter of the cluster 65 is set smaller than the inner
diameter of the coil end 11b. Therefore, there is effect that the
inner space of the coil end 11b is increased, and the turning flow
of the inner space can easily be developed into turning flow around
the cluster 65.
[0191] As described above, in this embodiment, an amount of the
refrigeration oil delivered to the refrigeration cycle out from the
compressor together with the working fluid can be reduced
extremely. Therefore, the refrigeration oil is not attached to an
inner wall of a heat exchanger tube of a heat exchanger, and it is
possible to prevent the heat exchanging efficiency from being
deteriorated. An amount of refrigeration oil in the oil reservoir
16 can always be maintained constantly, and it is possible to
enhance the reliability and efficiency of the compressor.
[0192] To prevent the global warming, it is proposed to employ, as
a refrigerant, a hydrocarbon refrigerant which is a natural
refrigerant having lower worming coefficient. If the hydrocarbon
refrigerant is used as the working fluid, it is necessary to take
the combustible nature of the refrigerant into consideration and to
reduce the amount of refrigerant to be charged into the
refrigeration cycle for enhancing the safety, and it is required to
reduce the compressor in size. According to this embodiment, the
oil-separating efficiency can be enhanced only by forming the
cluster 65 into the hexagonal columnar shape and by allowing the
discharge pipe 63 to pass through the side surface of the upper
shell 50. This embodiment can easily be applied to the compressor
with the hermetical container 1 having the outer diameter as
extremely small as about 80 mm or less. Thus, according to this
embodiment, even if the compressor is small in size using
combustible hydrocarbon refrigerant, it is possible to easily
reduce the amount of oil to be discharged.
[0193] The amount of oil can easily be reduced only by slightly
changing the cluster 65 and the discharge pipe 63 and thus, it is
possible to provide an extremely inexpensive compressor.
[0194] Although the cluster 65 has the regular hexagonal columnar
shape in the eleventh embodiment, any shapes (not shown) other than
the regular hexagonal columnar can also be employed, and the same
effect can be obtained only if the cluster is symmetric with
respect to the center axis of the cluster, and the center axis of
the cluster substantially coincides with the rotation center axis L
of the rotational motor (i.e., rotor 12).
INDUSTRIAL APPLICABILITY
[0195] The compressor of this invention is used for a refrigeration
cycle such as a refrigerator-freezer or an air conditioner. Carbon
dioxide is preferably used as the working fluid.
* * * * *