U.S. patent number RE48,456 [Application Number 16/850,234] was granted by the patent office on 2021-03-02 for compressor.
This patent grant is currently assigned to LG ELECTRONICS INC.. The grantee listed for this patent is LG ELECTRONICS INC.. Invention is credited to Cheolhwan Kim, Byeongchul Lee, Kangwook Lee.
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United States Patent |
RE48,456 |
Lee , et al. |
March 2, 2021 |
Compressor
Abstract
A compressor is provided that may include a passage separator
provided between an electric motor drive and a compression device
to separate a refrigerant passage from an oil passage. The passage
separator may include a first partition wall and a second partition
wall. The first partition wall may be disposed between an inner
circumferential surface of a casing and a discharge hole of the
compression device, and the second partition wall may be disposed
between the discharge hole and a balance weight. Accordingly, the
refrigerant passage may be separated from the oil passage between
the compression device and electric motor drive, thereby
efficiently recovering oil to an oil storage space.
Inventors: |
Lee; Kangwook (Seoul,
KR), Kim; Cheolhwan (Seoul, KR), Lee;
Byeongchul (Seoul, KR) |
Applicant: |
Name |
City |
State |
Country |
Type |
LG ELECTRONICS INC. |
Seoul |
N/A |
KR |
|
|
Assignee: |
LG ELECTRONICS INC. (Seoul,
KR)
|
Family
ID: |
53365799 |
Appl.
No.: |
16/850,234 |
Filed: |
April 16, 2020 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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Reissue of: |
14587901 |
Dec 31, 2014 |
9945381 |
Apr 17, 2018 |
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Foreign Application Priority Data
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Aug 7, 2014 [KR] |
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10-2014-0101815 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04C
29/026 (20130101); F04C 29/028 (20130101); F04C
18/0215 (20130101); F04C 29/028 (20130101); F04C
29/0085 (20130101); F04C 29/0085 (20130101); F04C
29/026 (20130101); F04C 23/008 (20130101); F04C
18/0215 (20130101); F04C 23/008 (20130101); F04C
29/025 (20130101); F04C 29/025 (20130101); F04C
2240/807 (20130101); F04C 2240/807 (20130101) |
Current International
Class: |
F04C
29/02 (20060101); F04C 23/00 (20060101); F04C
29/00 (20060101); F04C 18/02 (20060101) |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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203500009 |
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Mar 2014 |
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CN |
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1956244 |
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Aug 2008 |
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EP |
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H07 279867 |
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Oct 1995 |
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JP |
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2009-264175 |
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Nov 2009 |
|
JP |
|
2013 137004 |
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Jul 2013 |
|
JP |
|
2013-231442 |
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Nov 2013 |
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JP |
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1995-0004542 |
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May 1995 |
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KR |
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WO 2004/010001 |
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Jan 2004 |
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WO |
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Other References
US. Office Action dated Jan. 27, 2017 issued in U.S. Appl. No.
14/587,901. cited by applicant .
U.S. Final Office Action dated Jul. 6, 2017 issued in U.S. Appl.
No. 14/587,901. cited by applicant .
U.S. Office Action issued in U.S. Appl. No. 16/850,303 dated Nov.
9, 2020. cited by applicant .
Korean Office Action dated Sep. 25, 2020 issued in Application No.
10-2014-0101815. cited by applicant .
European Search Report dated Feb. 11, 2016 issued in Application
No. 15169809.9 cited by applicant .
Chinese Office Action dated Mar. 30, 2017 issued in Application No.
201510166475.2 (with English translation). cited by
applicant.
|
Primary Examiner: Doerrler; William C
Attorney, Agent or Firm: Ked & Associates LLP
Claims
What is claimed is:
1. A compressor, comprising: a casing having an internal space; a
drive comprising a stator fixed to the internal space, a cut
surface being provided on an outer circumferential surface of the
stator to be separated from an inner circumferential surface of the
casing, and a rotor rotatably provided within the stator; a
compression device provided at one side of the drive and having a
discharge hole so as to discharge compressed refrigerant into an
internal space of the casing; a rotational shaft configured to
transfer a drive force from the drive to the compression device;
and a passage separator provided between the drive and the
compression device to separate a refrigerant passage .Iadd.that
communicates with the discharge hole .Iaddend.from an oil passage
.Iadd.that communicates with the cut surface.Iaddend., wherein the
passage separator surrounds at least a portion of the discharge
hole and guides compressed refrigerant coming out of the discharge
hole in an axial direction of the rotational shaft.
2. The compressor of claim 1, wherein .Iadd.a radial section of the
.Iaddend.the passage separator is .[.formed in a tube shape to
accommodate the discharge hole.]. .Iadd.provided in the form of a
tube shape.Iaddend., and wherein an end of the passage separator on
a side adjacent the drive is formed to have a height
difference.
3. The compressor of claim 2, wherein the end of the passage
separator .[.is formed such that.]. .Iadd.comprises .Iaddend.a
first .[.surface.]. .Iadd.partition wall .Iaddend.located at an
outer side of the discharge hole with respect to the rotational
shaft .[.is.]. .Iadd.and .Iaddend.formed to be higher than a second
.[.surface.]. .Iadd.partition wall .Iaddend.located at an inner
side thereof.
4. The compressor of claim 1, wherein the passage separator is
formed in an arcuate cross-sectional shape.
5. A compressor, comprising: a casing having an internal space; a
drive comprising a stator fixed in the internal space and a rotor
rotatably provided within the stator; a compression device provided
at one side of the drive and having a discharge hole so as to
discharge compressed refrigerant into the internal space of the
casing; a rotational shaft configured to transfer a drive force
from the drive to the compression device; a balance weight provided
on the rotor or the rotational shaft; and a passage separator
provided between the drive and the compression device to separate a
refrigerant passage .Iadd.that communicates with the discharge hole
.Iaddend.from an oil passage .Iadd.that communicates with an outer
circumference of the stator.Iaddend., wherein the passage separator
includes a first partition wall and a second partition wall,
wherein the first partition wall is provided between an inner
circumferential surface of the casing and the discharge hole of the
compression device, and the second partition wall is provided
between the discharge hole and balance weight, wherein the
compression device further includes at least one oil recovery
passage that communicates with the oil passage and is provided at
one side of the compression device, wherein the first partition
wall and second partition wall are connected by a third partition
wall, and wherein at least a portion of the oil recovery passage is
covered by the third partition wall.
6. The compressor of claim 5, wherein the first partition wall, the
second partition wall, and the third partition wall are formed as
an integral body.
7. The compressor of claim 6, wherein the integral body is fixed to
the compression device.
8. The compressor of claim 5, wherein the oil recovery passage is
covered by a member separate from the passage separator.
9. The compressor of claim 5, wherein the oil recovery passage
includes a hole that passes through the compression device.
10. A compressor, comprising: a casing having an internal space; a
drive comprising a stator fixed in the internal space and a rotor
rotatably provided within the stator; a compression device provided
at a lower side of the drive, having a plurality of compression
chambers and a discharge hole so as to discharge compressed
refrigerant from the plurality of compression chambers into the
internal space of the casing; a rotational shaft configured to
transfer a drive force from the drive to the compression device,
the .[.rotating.]. .Iadd.rotational .Iaddend.shaft having an
eccentric portion to be coupled through a central portion of the
compression device to overlap the compression chamber in a radial
direction; a balance weight provided on the rotor or the rotational
shaft; and a passage separator provided between the drive and the
compression device to separate a refrigerant passage .Iadd.that
communicates with the discharge hole .Iaddend.from an oil passage
.Iadd.that communicates with an outer circumference of the
stator.Iaddend., wherein the passage separator includes a first
partition wall and a second partition wall, wherein the first
partition wall is provided between an inner circumferential surface
of the casing and the discharge hole of the compression device, and
the second partition wall is provided between the discharge hole
and balance weight, wherein the compression device further includes
at least one oil recovery passage that communicates with the oil
passage and is provided at one side of the compression device,
wherein the first partition wall and second partition wall are
connected by a third partition wall, and wherein at least a portion
of the oil recovery passage is covered by the third partition
wall.
11. The compressor of claim 10, wherein the first partition wall,
the second partition wall, and the third partition wall are formed
as an integral body.
12. The compressor of claim 11, wherein the integral body is fixed
to the compression device.
13. The compressor of claim 10, wherein the oil recovery passage is
covered by a member separate from the passage separator.
14. The compressor of claim 10, wherein the oil recovery passage
includes a hole that passes through the compression device.
.Iadd.15. The compressor of claim 1, wherein the passage separator
comprises a first partition wall provided between the discharge
hole and the cut surface..Iaddend.
.Iadd.16. The compressor of claim 15, wherein the passage separator
comprises a second partition wall provided between the discharge
hole and the rotational shaft..Iaddend.
Description
CROSS-REFERENCE TO RELATED APPLICATION
.[.The present.]. .Iadd.This .Iaddend.application .Iadd.is a
Reissue Application of U.S. Pat. No. 9,945,381 issued Apr. 17, 2018
(U.S. patent application Ser. No. 14/587,901 filed Dec. 31, 2014),
which .Iaddend.claims priority to Korean Application No.
10-2014-0101815, filed in Korea on Aug. 7, 2014, .[.which is.].
.Iadd.whose disclosures are .Iaddend.herein expressly incorporated
by reference in .[.its.]. .Iadd.their .Iaddend.entirety.
BACKGROUND
1. Field
A compressor is disclosed herein.
2. Background
In general, a compressor is applicable to a vapor compression type
refrigeration cycle (hereinafter, referred to as a "refrigeration
cycle"), such as a refrigerator, or air conditioner, for example. A
compressor can typically be divided into a hermetic type
compressor, in which an electric motor drive, that is, a typical
electromotor, and a compression unit or device operated by the
electric motor drive are provided together at an inner space of a
sealed casing, and an open type compressor, in which an electric
motor drive is provided outside of the casing. The hermetic
compressor is generally used for household or commercial
refrigeration devices.
Compressors can further be divided into a reciprocating type, a
rotary type, or a scroll type, according to a type of compressing
method of a refrigerant. The reciprocating type compressor is a
type that compresses a refrigerant while a piston drive linearly
moves a piston. The rotary type compressor is a type that
compresses a refrigerant using a rolling piston to perform an
eccentric rotational movement in a compression space of the
cylinder and a vane in contact with the rolling piston to partition
the compression space of the cylinder into a suction chamber and a
discharge chamber.
The scroll type compressor is a compressor in which a fixed scroll
is fixed to an inner space of a hermetic container, and two pairs
of compression chambers including a suction chamber, an
intermediate pressure chamber, and a discharge chamber are
consecutively formed between a fixed wrap of the fixed scroll and
an orbiting wrap of a orbiting wrap while the orbiting scroll
engaged with the fixed scroll performs an orbiting movement. The
scroll compressor is widely used in air conditioners to compress a
refrigerant due to an advantage of obtaining a relatively high
compression ratio compared to the other types of compressors, as
well as obtaining a stable torque as suction, compression, and
discharge strokes are smoothly carried out.
Such a compressor can be divided into an upper compression type and
a lower compression type according to a location of the electric
motor drive and compression device. The upper compression type is a
type in which the compression device is located at an upper side
above the electric motor drive, and the lower compression type is a
type in which the compression device is located at a lower side
lower than the electric motor drive. In particular, in a case of
the lower compression type, refrigerant discharged into an internal
space of the casing moves to a discharge pipe located at an upper
portion thereof, while oil is recovered to an oil storage space,
and thus, there is a concern that oil may be mixed with the
refrigerant to be discharged out of the compressor, or pushed by a
pressure of the refrigerant to be stagnant at an upper side of the
electric motor drive during the process. According to the present
disclosure, a technique in which a passage to recover oil and a
passage to discharge refrigerant are divided within the casing to
reduce oil spill will be described using a high-pressure, lower
compression type scroll compressor (hereinafter, referred to as a
lower compression type scroll compressor) as an example.
FIG. 1 is a cross-sectional view illustrating an example of a lower
compression type scroll compressor according to the related art. As
illustrated in FIG. 1, a lower compression type scroll compressor
according to the related art may include an electric motor drive 2
provided in an internal space of a casing 1 and having a stator and
a rotor, a compression unit or device 3 provided at a lower side of
the electric motor drive 2, and a rotational shaft 5 that transmits
a rotational force of the electric motor drive 2 to the compression
device 3. A refrigerant discharge pipe 16 may be provided at an
upper portion of the casing 1. A passage (Pm) to guide oil
separated from refrigerant to be recovered to an oil storage space
(V3) in the electric motor drive 2, while at a same time guiding
refrigerant discharged from the compression device 3 to move in a
direction of the refrigerant discharge pipe 16, is formed on an
inner circumferential surface of the casing 1 and an outer
circumferential surface of the electric motor drive 2 or an inner
portion of the electric motor drive 2.
According to the foregoing lower compression type scroll compressor
according to the related art, refrigerant and oil discharged from
the compression device 3 may move to an upper side of the electric
motor drive 2 through the passage (Pm) provided in the electric
motor drive 2, and then, may be discharged outside of the
compressor through the refrigerant discharge pipe 16. At this time,
oil separated from refrigerant between the electric motor drive 2
and the compression device 3 moves to the oil storage space (V3)
through a passage (Pc) provided in the compression device 3, while
oil separated from refrigerant at an upper side of the electric
motor drive 2 moves to the oil storage space (V3) at a lower side
of the compressor device 3 through the passage (Pm) provided in the
electric motor drive 2 and the passage (Pc) provided in the
compression device 3.
However, according to the foregoing lower compression type scroll
compressor according to the related art, as both refrigerant and
oil move through the passage (Pm) provided in the electric motor
drive 2, oil being moved from an upper side of the electric motor
drive 2 to a lower side thereof is mixed with refrigerant
discharged from the compression device 3 to be discharged out of
the compressor along with the refrigerant, or is not allowed to
pass through the passage (Pm) of the electric motor drive 2 due to
high-pressure refrigerant stagnant at an upper space of the
electric motor drive 2. Then, there is a problem in that an amount
of oil supplied to the compression device 3 is reduced while an
amount of oil recovered to the oil storage space (V3) is rapidly
reduced, thereby causing friction loss or abrasion of the
compression device 3.
In addition, there is also a problem in that oil supplied to the
compression device 3 through an oil passage of the rotational shaft
5 to lubricate the compression device 3, and then, flowing into a
space between the electric motor drive 2 and compression device 3
is mixed with refrigerant discharged from the compression device 3
to be discharged out of the compressor while being moved to an
upper side of the electric motor drive 2 along with the
refrigerant, thereby further aggravating oil shortage.
BRIEF DESCRIPTION OF THE DRAWINGS
Embodiments will be described in detail with reference to the
following drawings in which like reference numerals refer to like
elements, and wherein:
FIG. 1 is a cross-sectional view of a compressor according to the
related art;
FIG. 2 is a cross-sectional view of a compressor according to an
embodiment;
FIG. 3 is a cross-sectional view of the compressor of FIG. 2,
viewed from another angle;
FIG. 4 is an exploded perspective view of a passage separator and a
main frame of the compressor of FIG. 2;
FIG. 5 is a cross-sectional view taken along line V-V in FIG.
2;
FIGS. 6 through 8 are partial cross-sectional views illustrating a
passage separator in a compressor according to other
embodiments;
FIGS. 9 and 10 are exploded perspective views of a passage
separator and a main frame in a compressor according to still
another embodiment;
FIG. 11 is a cross-sectional view illustrating an oil recovery
passage according to another embodiment;
FIG. 12 is an exploded perspective view illustrating a passage
separator according to another embodiment; and
FIG. 13 is a cross-sectional view illustrating a compressor
according to still another embodiment.
DETAILED DESCRIPTION
Hereinafter, a compressor according to embodiments will be
described in detail with reference to the accompanying drawings.
Where possible, like reference numerals have been used to indicate
like elements, and repetitive disclosure has been omitted.
FIG. 2 is a cross-sectional view of a compressor according to an
embodiment. FIG. 3 is a cross-sectional view of the compressor of
FIG. 2, viewed from another angle. FIG. 4 is an exploded
perspective view of a passage separator and a main frame of the
compressor of FIG. 2. FIG. 5 is a cross-sectional view taken along
line V-V in FIG. 2, in which a balance weight and a coil are not
shown for the sake of convenience of explanation.
As illustrated in FIGS. 2 through 5, a compressor according to an
embodiment may include a casing 1 having an internal space, an
electric motor drive 2 provided at an upper portion of the internal
space, a compression unit or device 3 provided at a lower portion
of the electric motor drive 2, a rotational shaft 5 configured to
transfer a drive force from the electric motor drive 2 to the
compression device 3, and a passage separator 8 provided between
the electric motor drive 2 and the compression device 3 to separate
a refrigerant passage from an oil passage. The internal space of
the casing 1 may be partitioned into a first space (V1) at an upper
side of the electric motor drive 2, a second space (V2) between the
electric motor drive 2 and the compression device 3, and a third
space (V3) at a lower side of the compression device 3. Further,
the passage separator 8 may be provided in the second space
(V2).
The casing 1 may include a cylindrical shell 11, and an upper shell
12 and a lower shell 13 that cover an upper portion and a lower
portion of the cylindrical shell 11, respectively. The upper shell
12 and lower shell 13 may be coupled to the cylindrical shell 11
by, for example, welding, to form the enclosed internal space along
with the cylindrical shell 11.
A refrigerant discharge pipe 16 to guide refrigerant, discharged to
an internal space of the casing 1, from the compression device 3
outside of the casing 1 to, for example, a condensing unit or
condenser (not shown) of a vapor compression type cooling cycle
device may be provided in the upper shell 12. In other words, the
refrigerant discharge pipe 16 may be provided in the first space
(V1). A refrigerant suction pipe 15 to guide refrigerant to be
compressed from outside of the casing 1 to a compression chamber
(S1) of the compression device 3, which will be described herein
below, may be provided on or at a lateral surface of the
cylindrical shell 11.
The lower shell 13 may function as an oil chamber to store oil
supplied to efficiently operate the compressor. In other words, an
oil storage space may be provided in the third space (V3).
The electric motor drive 2 to generate a rotational force may be
provided at a substantially upper portion within the cylindrical
shell 11. The electric motor drive 2 may include a stator 21 fixed
to an inner surface of the cylindrical shell 11 and a rotor 22
located within the stator 21 to be rotated by an interaction with
the stator 21.
The stator 21 may be formed in a substantially annular shape, and
may include an iron core 212 laminated with multiple sheets, and a
coil 216 wound around the iron core 212. An outer circumferential
surface of the iron core 212 may be formed with a cut surface 212a
angulated along a circumferential direction thereof, and thus, a
space (G1) may be formed between the outer circumferential surface,
more particularly, cut surface 212a, of the iron core 212 and the
cylindrical shell 11. The space (G1) between the outer
circumferential surface of the iron core 212 and the cylindrical
shell 11 may also be formed in another manner. For example, the
space (G1) may be provided by forming an outer circumferential
surface of the iron core 212 in a circular shape while forming an
engraved groove (not shown) on the outer circumferential surface. A
plurality of slots 212b formed on an inner circumferential surface
of the iron core 212 in an axial direction may be provided along a
circumferential direction thereof. The coil 216 may be wound around
a teeth portion 212c between the slots 212b. An insulator 214 to
insulate the coil 216 from the iron core 212 may be provided
between the coil 216 and iron core 212.
The rotor 22 may be formed in a substantially cylindrical shape,
and an outer circumferential surface of the rotor 22 may be
provided to face an inner circumferential surface of the stator 21
with a predetermined gap (G2) therebetween. Further, the rotational
shaft 5 may be inserted into and coupled to a center of the rotor
22.
The space (G1) between the stator 21 and the cylindrical shell 11,
and the gap (G2) between the stator 21 and the rotor 22 may form a
first passage and a second passage, respectively, thereby allowing
the first space (V1) to communicate with the second space (V2).
Accordingly, oil may move from the first space (V1) to the second
space (V2) through first passage (G1), and refrigerant may move
from the second space (V2) to the first space (V1) through second
passage 212b (G2).
A main frame 31 of the compression device 3 may be provided fixed
to a lower side of the electric motor drive 2. The main frame 31
may include a frame end plate 312 (hereinafter, referred to as a
"first end plate") having a substantially circular shape, a frame
side wall 314 (hereinafter, referred to as a "first side wall")
that protrudes from an outer circumferential portion of the first
end plate 312 toward a lower side thereof, and a frame bearing 318
(hereinafter, referred to as a "first bearing") provided at a
center of the first end plate 312 through which the rotational
shaft 5 may pass.
An outer circumferential portion of the first side wall 314 may
face or be brought into contact with an inner circumferential
surface of the cylindrical shell 11, and a lower end portion
thereof may be brought into contact with an upper end portion of a
fixed scroll side wall 324, which will be described hereinbelow.
Further, the first side wall 314 may be formed with a plurality of
frame discharge grooves 314a (hereinafter, referred to as a "first
groove") formed in an engraved manner along an axial direction on
an outer circumferential surface thereof, and both axial sides of
which may be open to form an oil path in a circumferential
direction. An inlet of the first groove 314a may communicate with
the second space (V2), and an outlet of which may communicate with
an inlet of a fixed scroll groove 324a, which will be described
hereinbelow, and a space may be formed between the first groove
314a and the cylindrical shell 11.
Further, the first side wall 314 may be provided with a frame
discharge hole 314b (hereinafter, referred to as a "first discharge
hole") that passes through an inner portion of the first side wall
314 to form a refrigerant path. An inlet of the first discharge
hole 314b may communicate with an outlet of the fixed scroll
discharge hole 324b, which will be described hereinbelow, and an
outlet of which may communicate with the second space (V2).
The first bearing 318 may protrude from an upper surface of the
first end plate 312 to a side of the electric motor drive 2. The
first bearing 318 to support a main bearing 51 of the rotational
shaft 5, which will be described hereinbelow, to pass
therethrough.
An oil pocket 312a to collect oil discharged between the first
bearing 318 and the rotational shaft 5 may be formed on an upper
surface of the first end plate 312, and an oil recovery passage
312b forming a fifth passage to communicate the oil pocket 312a
with the first groove 314a may be formed at one side of the oil
pocket 312a. The oil pocket 312a may be formed as an engraved
manner on an upper surface of the first end plate 312, and formed
in an annular shape along an outer circumferential surface of the
first bearing 318.
The oil recovery passage 312b may be formed as an engraved groove
on an upper surface of the first end plate 312. In this case, the
oil recovery passage 312b may communicate with a space between a
first partition wall 82 and a second partition wall 84, which will
be described hereinbelow, to be exposed to refrigerant, and thus, a
cover may be provided between a space between the first partition
wall 82 and the second partition wall 84 and the oil recovery
passage 312b.
A fixed scroll 32 forming a first scroll may be coupled to a bottom
surface of the main frame 31. The fixed scroll 32 may include a
fixed scroll end plate 322 (hereinafter, referred to as "second end
plate") having a substantially circular shape, the fixed scroll
side wall 324 (hereinafter, referred to as a "second side wall")
that protrudes toward an upper side from an outer circumferential
portion of the second end plate 322, a fixed wrap 326 that
protrudes from an upper surface of the second end plate 322 and
combined with an orbiting wrap 336 of an orbiting scroll 33, which
will be described hereinbelow, to form compression chamber (S1),
and a fixed scroll bearing 328 (hereinafter, referred to as a
"second bearing") formed at a center of a rear surface of the
second end plate 322 through which the rotational shaft 5 may
pass.
A discharge port 322a to guide compressed refrigerant from the
compression chamber (S1) to an internal space of a discharge cover
34 may be formed on the second end plate 322. A location of the
discharge port 322a may be arbitrarily set by taking a required
discharge pressure into consideration.
The discharge cover 34, which may accommodate discharged
refrigerant and guide it to the fixed scroll discharge hole 324b,
which will be described hereinbelow, may be coupled to a bottom
surface of the fixed scroll 32, as the discharge port 322a may be
formed to extend toward the lower shell 13. The discharge cover 34
may be sealed and coupled to a bottom surface of the fixed scroll
32 to separate a discharge passage of refrigerant from the oil
storage space (V3).
An internal space of the discharge cover 34 may be formed to
accommodate the discharge port 322a, as well as accommodate an
inlet of the fixed scroll groove 324a, which will be described
hereinbelow. A through hole 348 may be formed in the discharge
cover 34 to allow an oil feeder 6 coupled to a sub-bearing 52 of
the rotational shaft 5, which will be described hereinbelow, to
form a second bearing, and be submerged into the oil storage space
(V3) of the casing 1, to pass therethrough.
An outer circumferential portion of the first partition 82 may be
brought into contact with the inner circumferential surface of the
cylindrical shell 11, and a lower end thereof may be brought into
contact with an upper end of the first side wall 314.
Further, the fixed scroll groove 324a (hereinafter, referred to as
a "second groove") formed in an engraved manner along an axial
direction on an outer circumferential surface thereof, and both
axial sides of which are open to form the oil path may be provided
on the second side wall 324. The second groove 324a may be formed
to correspond to the first groove 314a of the main frame 31, and an
inlet of which may communicate with an outlet of the first groove
314a, and an outlet of which may communicate with the oil storage
space of the third space (V3). The second groove 324a may form a
space between the second partition wall 84 and the cylindrical
shell 11.
The first groove 314a and the second groove 324a may provide
communication between the second space (V2) and the third space
(V3), to move oil from the second space (V2) to the third space
(V3). Hereinafter, a passage formed by the first groove 314a and
the second groove 324a may be referred to as a "third passage".
The fixed scroll discharge hole 324b (hereinafter, referred to as a
"second discharge hole") may pass through an inner portion of the
second side wall 324 in an axial direction to form a refrigerant
path along with the first discharge hole 314b. The second discharge
hole 324b may correspond to the first discharge hole 314b, and an
inlet of which may communicate with an internal space of the
discharge cover 34, and an outlet of which may communicate with an
inlet of the first discharge hole 314b.
The second discharge hole 324b and the first discharge hole 314b
may provide communication between an internal space of the
discharge cover 34 and the second space (V2) to guide refrigerant
discharged from the compression chamber (S1) to an internal space
of the discharge cover 34 to the second space (V2). A passage
formed by the second discharge hole 324b and the first discharge
hole 314b may be referred to as a "fourth passage".
The refrigerant suction pipe 15 may be provided on the second side
wall 324 and communicate with the suction side of the compression
chamber (S1). The refrigerant suction pipe 15 maybe separated from
the second discharge hole 324b.
The second bearing 328 may protrude from a lower surface of the
second end plate 322 to or at a side of the oil storage space. The
second bearing 328 may support a sub-bearing 52, which will be
described hereinbelow, of the rotational shaft 5 and be inserted
therein. Further, a lower end portion of the second bearing 328 may
be bent toward a center of the rotational shaft 5 to support a
lower end of the sub-bearing 52 so as to form a thrust bearing
surface.
The orbiting scroll 33 may be coupled to the rotational shaft 5 to
form two pairs of compression chambers (S1) between the fixed
scroll 32 and the orbiting scroll 33 while performing an orbiting
movement. The orbiting scroll 33 may be provided between the main
frame 31 and the fixed scroll 32. The orbiting scroll 33 may
include an orbiting scroll end plate 332 (hereinafter, referred to
as a "third end plate") having a substantially circular shape, the
orbiting wrap 336 which protrudes from a lower surface of the third
end plate 332 to be teeth-combined with the fixed wrap 326, and a
rotational shaft coupling portion 338 provided at a center of the
third end plate 332 to be rotatably coupled to an eccentric portion
53, which will be described hereinbelow, of the rotational shaft
5.
The orbiting scroll 33 may be supported by the fixed scroll 32 in
such a manner that an outer circumferential portion of the third
end plate 332 is placed on an upper end portion of the second side
wall 324, and a lower end portion of the orbiting wrap 336 is
closed adhered to an upper surface of the second end plate 322. An
outer circumferential portion of the rotational shaft coupling
portion 338 may be coupled to the orbiting wrap 336 to perform a
role of forming the compression chamber (S1) along with the fixed
wrap 326 during a compression process. The fixed wrap 326 and
orbiting wrap 336 may be formed in an involute shape, but may also
be formed in other various shapes.
In addition, the eccentric portion 53, which will be described
hereinbelow, of the rotational shaft 5 may be inserted into the
rotational shaft coupling portion 338, such that the eccentric
portion 53 may be coupled to the orbiting wrap 336 or fixed wrap
326 to be overlapped therewith in a radial direction of the
compressor. As a result, a repulsive force of refrigerant may be
applied to the fixed wrap 326 and the orbiting wrap 336, and a
compressive force applied between the rotational shaft coupling
portion 338 and the eccentric portion 53 as a reaction force with
respect to this during the compression process. As described above,
when the eccentric portion 53 of the rotational shaft 5 passes
through the end plate portion 332 of the orbiting scroll 33 and is
overlapped with the orbiting wrap 336 in the radial direction, the
repulsive force and compressive force of refrigerant may be
cancelled out by each other while being applied on a same plane
based on the end plate 332. Because of this, tilting of the
orbiting scroll 33 due to operation of the compressive force and
the repulsive force may be prevented.
A lower portion of the rotational shaft 5 may be coupled to the
compression device 3 to be supported in a radial direction while an
upper portion thereof may be inserted into a center of the rotor 22
to be coupled thereto. As a result, the rotational shaft 5 may
transfer a rotational force of the electric motor drive 2 to the
orbiting scroll 33 of the compression device 3. Then, the orbiting
scroll 33 eccentrically coupled to the rotational shaft 5 may
perform an orbiting movement with respect to the fixed scroll
32.
The main bearing 51 may be formed at the lower portion of the
rotational shaft 5 to be inserted into the first bearing 318 of the
main frame 31 and supported in a radial direction, and the
sub-bearing 52 may be formed at a lower side of the main bearing 51
to be inserted into the second bearing 328 of the fixed scroll 32
and supported in a radial direction. Further, the eccentric portion
53 may be formed between the main bearing 51 and sub-bearing 52 to
be inserted into and coupled to the rotational shaft coupling
portion 338 of the orbiting scroll 33. The main bearing 51 and the
sub-bearing 52 may be formed on a coaxial line to have a same axial
center, and the eccentric portion 53 may be eccentrically formed in
a radial direction with respect to the main bearing 51 or the
sub-bearing 52. The sub-bearing 52 may be eccentrically formed with
respect to the main bearing 51.
It may be advantageous in allowing the rotational shaft 5 to pass
through each of the bearings 318, 328, and rotational shaft
coupling portion 338 to be coupled thereto, for an outer diameter
of the eccentric portion 53 to be formed to be less than an outer
diameter of the main bearing 51 and larger than an outer diameter
of the sub-bearing 52. However, in a case in which the eccentric
portion 53 is not integrated into the rotational shaft 5, but
rather, is formed using an additional bearing, the rotational shaft
5 may be inserted thereinto and coupled thereto, even when the
outer diameter of the sub-bearing 52 is not formed to be less than
the outer diameter of the eccentric portion 53.
Moreover, an oil passage 5a to supply oil to bearings 51, 52 and
eccentric portion 53 may be formed within the rotational shaft 5.
The oil passage 5a may be formed by forming a groove that extends
from a lower end of the rotational shaft 5 to a substantially lower
end or intermediate height of the stator 21, or a height higher
than a height of an upper end of the main bearing 51, as the
compression device 3 is located at a lower side of the electric
motor drive 2.
Further, an oil feeder 6 to pump oil filled in the oil storage
space may be coupled to a lower end of the rotational shaft 5,
namely, a lower end of the sub-bearing 52. The oil feeder 6 may
include an oil supply pipe 61 inserted into and coupled to the oil
passage 5a of the rotational shaft 5, and an oil suction member 62,
such as a propeller, inserted into the oil supply pipe 61 to suck
oil. The oil supply pipe 61 may be provided to pass through the
through hole 348 of the discharge cover 34 to be submerged in the
oil storage space.
A balance weight 7 to suppress noise vibration may be coupled to
the rotor 22 or the rotational shaft 5. The balance weight 7 may be
provided between the electric motor drive 2 and the compression
device 3, namely, in the second space (V2). The balance weight 7
may include a coupling portion 72 coupled to a bottom surface of
the rotor 22 or an outer circumferential surface of the rotational
shaft 5, an extension portion 74 that extends from the coupling
portion 72 at a lower side of the rotor 22, and a bent portion 76
bent from the extension portion 74 to protrude in a radial
direction of the rotational shaft 5. According to this embodiment,
an end portion of the bent portion 76 may be a portion which is
farthest from a rotational center of the balance weight 7.
The passage separator 8 may include the first partition wall 82,
which may be interposed between a refrigerant passage and an oil
passage in the second space (V2), the second partition wall 84,
which may be interposed between the rotational shaft 5 and the
first partition wall 82, and a connector 86 that traverses or
connects the first partition wall 82 and the second partition wall
84. The first partition wall 82 may be formed in a substantially
annular shape, a first end 822 and a second end 824 may be located
between an outlet of the first passage (G1) and an inlet of the
second passage 212b (G2), and between an inlet of the third passage
314a, 324a and an outlet of the fourth passage 314b, 324b,
respectively. Accordingly, the first partition wall 82 may allow
the third passage 314a, 324a to communicate with the first passage
(G1) formed between an inner circumferential surface of the
cylindrical shell 11 and an outer circumferential surface of the
compression device 3, and allow the fourth passage 314b, 324b to
communicate with the second passage 212b (G2) formed between an
outlet side of the compression device 3 and the second space (V2).
Both ends 822, 824 of the first partition wall 82 may be closely
adhered to the main frame 31 and stator 21, respectively, or
alternatively, either one may be separated from its counterpart by
an assembly tolerance to minimally reduce refrigerant leakage by
taking damage during the assembly process into consideration.
The second partition wall 84 may be provided between the inlet of
the second passage 212b (G2) and the rotational shaft 5, or between
the outlet of the fourth passage 314b, 324b and the balance weight
7 to suppress refrigerant and oil from being mixed by the
rotational shaft 5 and the balance weight 7 in the second space
(V2). The second partition wall 84 may be formed in an annular
shape with a smaller radius than a radius of the first partition
wall 82. Further, the second partition wall 84 may be provided such
that a first end 842 thereof is interposed between an outlet of the
fourth passage 314b, 324b and the rotational shaft 5 or the balance
weight 7, and a second end 844 is interposed between the gap (G2)
between the stator 21 and the rotor 22 and a bottom surface of the
slot 212b. In other words, the second partition wall 84 may be
provided at an inner side (center side of the compressor) than the
bottom surface of the slot 212b within a range of an axial
projection space of the stator 21.
Further, the second partition wall 84 may be provided in such a
manner that the first end 842 is closely adhered to the main frame
31, and the second end 844 is separated from the stator 21
similarly to the first partition wall 82. As a result, it may be
possible to prevent the second partition wall 84 from being damaged
between the stator 21 and the main frame 31 during assembly of the
compressor, and increase an area of the second passage 212b (G2),
thereby efficiently moving refrigerant from the second space (V2)
to the first space (V1).
In other words, the second partition wall 84 may be provided to be
separated from the stator 21 to allow refrigerant discharged from
the fourth passage 314b, 324b to move through the gap (G2) between
the stator 21 and the rotor 22 as well as the slot 212b. Of course,
the slot 212b may communicate with the gap (G2) between the stator
21 and the rotor 22 to allow a portion of refrigerant that flows
into the slot 212b to flow out to a side of the gap (G2) between
the stator 21 and the rotor 22 and move into the first space (V1)
through the gap (G2) even when the second partition wall 84 is
closely adhered to the stator 21. However, the second partition
wall 84 may be separated from the stator 21 to have a path
(hereinafter, referred to as a "direct path") to allow refrigerant
between the second partition wall 84 and the first partition wall
82 to directly flow into a gap between the stator 21 and the rotor
22 in order to more efficiently move refrigerant.
A separation distance (axial distance) between the second partition
wall 84 and the stator 21 may be formed to be the same as a
separation distance (axial distance) between a portion (bent
portion) which is farthest from the rotational center of the
balance weight 7 and the stator 21. This is to secure a direct path
while effectively suppressing agitation due to the balance weight 7
because a portion which is the farthest from the rotational center
of the balance weight 7 has a larger rotational radius than that of
the other portions thereof, and thus, the resultant agitation
effect is large.
As illustrated in FIG. 6, the second end 844 of the second
partition wall 84 may extend in a bent manner to cover an upper
side of the balance weight 7 to further suppress agitation due to
the balance weight 7, while maintaining the secured area of the
direct path. A case in which the separation distance (axial
distance) between the second partition wall 84 and the stator 21 is
smaller than the separation distance (axial distance) between the
portion (bent portion) which is the farthest from the rotational
center of the balance weight 7 and the stator 21, it may be
advantageous with respect to suppressing agitation, but
disadvantageous with respect to securing the direct path. In
contrast, in a case in which the separation distance (axial
distance) between the second partition wall 84 and the stator 21 is
larger than the separation distance (axial distance) between the
portion (bent portion) which is farthest from the rotational center
of the balance weight 7 and the stator 21, vice versa.
The connector portion 86 may extend between the first partition
wall 82 and the second partition wall 84, thereby modularizing the
first partition wall 82 and the second partition wall 84 into an
integral body. Due to this, it may be possible to facilitate
fabrication of the compressor, and reduce fabrication costs.
In case of this embodiment, the connector 86 may prevent
refrigerant discharged from the fourth passage 314b, 324b from
leaking between the connector 86 and the main frame 31, and prevent
a space between the first partition wall 82 and the second
partition wall 84 from communicating with the oil recovery passage
312b (to operate as a cover portion of the oil recovery passage).
In other words, the connector 86 may be formed in an annular and
traverse the entire end 822 of the first partition wall 82 and the
entire end 842 of the second partition wall 84, and an entire lower
surface of the connector 86 may be provided to be closely adhered
to the main frame 31.
A through hole 862 may be formed on a portion corresponding to an
outlet of the fourth passage 314b, 324b, that is, an outlet of the
first discharge hole 314b.
In the drawing, reference numeral 35 is an oldham ring to prevent
the rotation of the orbiting scroll 33.
Hereinafter, operation of a compressor according to this embodiment
will be described hereinbelow.
When power is applied to the electric motor drive 2 to generate a
rotational force on the stator 21 and the rotational shaft 5, the
orbiting scroll 33 eccentrically coupled to the rotational shaft 5
may perform an orbiting movement. Then, refrigerant supplied
through the refrigerant suction pipe 15 from outside of the casing
1 may directly flow into the compression chamber (S1), and the
refrigerant may be compressed by orbiting movement of the orbiting
scroll 33, and then, discharged into an internal space of the
discharge cover 34 through the discharge port 322a from the
compression chamber (S1). The refrigerant discharged into the
internal space of the discharge cover 34 may reduce noise while
being circulated in the internal space of the discharge cover 34,
and then move into the second space (V2) through the fourth passage
314b, 324b.
Then, a series of processes may be repeated, including guiding the
refrigerant moved into the second space (V2) to the second passage
212b (G2) formed at the slot 212b of the stator 21 and the gap (G2)
between the stator 21 and rotor 22 by the passage separator 8 and
moved into the first space (V1), and then discharging the
refrigerant outside of the compressor through the refrigerant
discharge pipe 16, and separating oil from the refrigerant moved
into the first space (V1) and recovered to an oil storage space
through the first passage (G1) and third passage 314a, 324a. More
specifically, refrigerant discharged into the second space (V2)
from the fourth passage 314b, 324b may be blocked by the first
partition wall 82 in a direction of the first passage (G1) and
guided into the second passage 212b (G2). Accordingly,
high-pressure refrigerant does not flow into the first passage (G1)
so as not to generate a passage resistance in the first passage
(G1), and thus, oil in the first space (V1) may be move to a side
of a second space (V2) through the first passage (G1), and then, be
recovered to an oil storage space through the third passage 314a,
324a.
Then, as the second partition wall 84 is formed between the outlet
of the fourth passage 314b, 324b and the rotational shaft 5 or
between the fourth passage 314b, 324b and the balance weight 7 in
the second space (V2), refrigerant discharged into the second space
(V2) may swiftly move into the first space (V1) through the slot
212b or the gap (G2) between the stator 21 and rotor 22 due to the
second partition wall 84. On the other hand, refrigerant in the
second space (V2) may be closely adhered to the main frame 31 to
suppress the refrigerant from flowing into the first passage (G1),
the third passage 314a, 324a, and oil recovery passage 312b by the
connecting portion 86 covering the oil recovery passage 312b.
Accordingly, most of the refrigerant in the second space (V2) may
flow into the second passage 212b (G2) without flowing into the
first passage (G1) or the third passage 314a, 324a or the oil
recovery passage 312b.
On the other hand, refrigerant having flowed into the second
passage 212b (G2) may move into the first space (V1), and oil may
be separated from the refrigerant in the first space (V1). The oil
may sequentially pass through the first passage (G1) and the third
passage 314a, 324a to be recovered to the oil storage space of the
third space (V3). At this time, as high-pressure refrigerant
discharged from the compression device 3 may be prevented from
flowing into the first passage (G1) or the third passage 314a, 324a
by the first partition wall 82 of the passage separator 8, oil is
not subject to resistance due to refrigerant, and thus, flows into
the first passage (G1) to be efficiently recovered to the oil
storage space.
On the other hand, oil supplied to sliding portions may perform a
lubrication function and discharged to the side of the second space
(V2) between the first bearing 318 and the rotational shaft 5. The
oil may be collected in the oil pocket 312a, and then, may be
recovered to the oil storage space of the third space (V3) through
the oil recovery passage 312b and the third passage 314a, 324a. At
this time, high-pressure refrigerant discharged from the fourth
passage 314b, 324b may be prevented from flowing into the oil
recovery passage 312b by the passage separator 8. Accordingly, oil
in the oil recovery passage 312b is not subject to resistance due
to refrigerant, and thus, may be efficiently recovered to the third
passage 314a, 324a. Further, oil in the oil recovery passage 3126
may be blocked from being brought into contact with refrigerant
discharged from the compression device 3 to prevent refrigerant and
oil in the second space (V2) from being agitated by the rotational
shaft 5 or the balance weight 7, thereby preventing oil in the
second space (V2) from being mixed with refrigerant flowing in the
second space (V2).
In this manner, in a compressor according to this embodiment, the
passage separator 8 may be provided between the electric motor
drive 2 and the compression device 3, thereby separating a
refrigerant passage from an oil passage. As a result, it may be
possible to efficiently recover oil to the oil storage space as
well as efficiently supply oil to the sliding portions.
The passage separator 8 may be provided as an additional member to
be fastened to the main frame 31, as discussed with respect to the
previous embodiment; however, alternatively, according to
circumstances, the passage separator 8 may also be formed on the
main frame 31 as an integral body. Further, the passage separator 8
may extend in an upward direction with respect to the stator 21
from the main frame 31 as discussed with respect to the previous
embodiment; however, alternatively, according to circumstances, the
passage separator 8 may extend in a downward direction with respect
to the stator 21 from the main frame 31. In this case, though not
shown in the drawings, the passage separator 8 may extend from the
insulator 214 formed of a material, such as plastic. When the
passage separator 8 is formed on the insulator 214 as described
above, only the first partition wall 82 may be formed thereon due
to a structural characteristic in which a coil is wound around the
insulator 214. As a result, the second partition wall 84 may be
provided on the main frame 31 as needed.
Further, in the case of the previous embodiment, the passage
separator 8 is configured with the first partition wall 82, the
second partition wall 84, and the connector 86; however,
alternatively, according to circumstances, the passage separator 8
may be configured with only the first partition wall 82 or only the
first partition wall 82. Further, in the case of the previous
embodiment, as the passage separator 8 is provided on the main
frame 31, the first end 822, 842 of the first partition wall 82 and
second partition wall 84 is closely adhered to the main frame 31,
and the second end 824, 844 is separated from the stator 21, but
according to this embodiment, as illustrated in FIG. 7, the passage
separator 8 may be provided on the stator 21 in such a manner that
first end 822 of the first partition wall 82 is separated from the
main frame 31 and the second end 824 thereof is closely adhered to
the stator 21. Otherwise, as illustrated in FIG. 8, both ends 822,
824, 842, 844 of the first partition wall 82 and second partition
wall 84, respectively, may all be closely adhered to the main frame
31 and stator 21 with the passage separator 8 provided on the main
frame 31 (or stator 21). In this case, it may be advantageous for
sealing. In this case, a hole or groove-shaped opening 846 to
communicate spaces partitioned by the second partition wall 84 with
each other may be provided thereon. In this case, the opening 846
of the second partition wall 84 may be formed at a position where
it does not overlap with the portion which is the farthest from the
rotational center of the balance weight 7 to suppress an agitation
effect due to the balance weight 7 to a maximum. In other words,
the opening 846 may be provided at an upper side or a lower side of
the bent portion 76 of the balance weight 7. Of course, the opening
846 may not be provided thereon. In this case, a portion of
refrigerant having flowed into the slot 212b may move to the first
space (V1) through the gap (G2) of the stator 21 and rotor 22.
However, the opening 846 may be provided thereon to secure the
direct path.
Furthermore, in the case of the previous embodiment, the second
partition wall 84 may be provided at an outside of the gap (G2)
between the stator 21 and the rotor 22 by taking the balance weight
7 into consideration, but when the balance weight 7 is removed or
provided on the stator 21 as illustrated in this embodiment, the
second wall portion 84 may be provided at an inside of the gap (G2)
between the stator 21 and the rotor 22 in a radial direction. In
this case, the second passage 212b (G2) may not be blocked by the
second partition wall 84, and thus, refrigerant may swiftly move to
the first space (V1).
Also, in the case of the previous embodiment, the connector 86 may
be formed in an annular shape, and the entire lower surface of the
connector 86 may be closely adhered to the main frame 31, but as
illustrated in this embodiment, the connector 86 may be closely
adhered to only a portion forming an outlet of the fourth passage
314b, 324b of the main frame 31, and other portions of the
connector 86 may be separated from other portions of the main frame
31. Accordingly, an area for precision machining may be decreased,
thereby reducing fabrication costs. As another example, as
illustrated in FIG. 9, the connector 86 may be formed in a pier
shape traversing or connecting a portion of the first partition
wall 82 and a portion of the second partition wall 84, and formed
in such a manner that the connector 86 in the pier shape covers the
oil recovery passage 312b.
According to this embodiment, the connector 86 may be integrated
into the first partition wall 82 and second partition wall 84 while
forming a third partition wall; however, according to this
embodiment, the connector 86 may be independently formed to be
separated from the first partition wall 82 or second partition wall
84 as illustrated in FIG. 10.
According to the previous embodiment, the oil recovery passage 312b
may be formed as an engraved groove on an upper surface of the
first end plate 312 to be covered by the connector 86. However, in
this case, the connector 86 forming a third partition wall may be
required on the passage separator 8, thereby causing difficulties
in fabrication or assembly of the passage separator 8. Accordingly,
according to this embodiment, as illustrated in FIG. 11, the oil
recovery passage 312b may be formed as a hole passing through an
inner portion of the first end plate 312 of the main frame 31. In
this case, an additional connector 86 may not be required on the
passage separator 8, thereby simplifying a fabrication or assembly
process of the passage separator 8.
Still another embodiment of a passage separator according to
embodiments will be described below.
According to the previous embodiment, a first partition wall and a
second partition wall forming the passage separator 8 may be formed
in an annular shape and provided at an outside and inside of a
discharge hole, but according to this embodiment, the passage
separator 8 may be formed in a tube shape, and thus, provided to
accommodate each discharge hole 314b, as illustrated in FIG. 12. In
this case, the passage separator 8 may be formed in a square tube
cross-sectional shape, as illustrated in FIG. 12; however,
alternatively, according to circumstances, the passage separator
may be formed in various shapes, such as a circular cross-sectional
shape, or an arcuate cross-sectional shape.
Further, one end of the passage separator 8, namely, an end
adjacent the electric motor drive 2 may be formed at a same height,
or may have a height difference, such that refrigerant discharged
through the first discharge hole 314b may be effectively prevented
from flowing into the first passage, as well as efficiently guided
to the second passage along an axial direction. To this end, an
outer lateral surface 8a (hereinafter, referred to as a "first
surface") in contact with the first passage may be formed at a
height to contact with a bottom surface of the electric motor drive
2, and an inner lateral surface 8b (hereinafter, referred to as a
"second surface") in contact with the second passage may be lower
than that of the first surface 8a to have a predetermined distance
from the bottom surface of the electric motor drive 2. Both side
wall surfaces (third surfaces) 8c may be formed at a same height as
that of the first surface 8a, or formed at a same height as that of
the second surface 8b, or both sides may be formed at a same height
as those of the first surface 8a and second surface 8b, but in a
stepped or inclined manner at a middle thereof.
On the other hand, according to embodiments, a scroll compressor
among lower compression type compressors has been described as a
representative example; however, embodiments may be applicable to
other type compressors according to circumstances. FIG. 13 is a
cross-sectional view illustrating a rotary compressor.
In this case, a fundamental configuration and operation effect of
passage separator 8 may be substantially the same as those of the
previous embodiment. In other words, in this embodiment, the
passage separator 8 may be provided between the electric motor
drive 2 and the compression device 3 to separate a refrigerant
passage from an oil passage. However, in this case, discharge cover
34 is provided on main frame 31, and thus, second partition wall 84
is not formed thereon, but rather, the second partition wall 84 is
provided separate from the discharge cover a shape of the discharge
cover 34 and a shape of the main frame 31 are changed.
Embodiments disclosed herein provide a compressor in which a
refrigerant passage is separated from an oil passage within the
casing, thereby efficiently recovering oil to an oil storage
space.
Embodiments disclosed herein further provide a compressor in which
oil that has lubricated a compressor device and flowed out into a
space between the compressor device and an electric motor drive may
be prevented from being mixed with refrigerant discharged from the
compressor device, thereby efficiently recovering oil.
Embodiments disclosed herein provide a compressor that may include
a casing having an internal space; an electric motor drive having a
stator fixed to the internal space and a rotor rotatably provided
within the stator; a compression unit or device provided at one
side of the electric motor drive to have a discharge hole so as to
discharge compressed refrigerant into the internal space of the
casing; a rotating shaft configured to transfer a drive force from
the electric motor drive to the compression unit; a balance weight
provided on the rotor or the rotating shaft; and a passage
separation portion or separator provided between the electric motor
drive and the compression unit to separate a refrigerant passage
from an oil passage. The passage separation portion may have a
first partition wall portion or first partition wall, and a second
partition wall portion or second partition wall. The first
partition wall portion may be disposed between an inner
circumferential surface of the casing and the discharge hole of the
compression unit, and the second partition wall portion may be
disposed between the discharge hole and the balance weight.
A slot, around which a coil may be wound, may be formed on the
stator, and the first partition wall portion may be disposed at an
outside of the slot. Further, both axial sides of the first
partition wall portion may be closely adhered to the compression
unit and electric motor drive, respectively. Furthermore, the
second partition wall portion may have a path formed at either one
of both sides to face the electric motor drive or compression
unit.
The first partition wall portion or second partition wall portion
may be formed to extend from the compression unit. Further, a slot,
around which a coil may be wound, may be formed on the stator, and
an insulator may be inserted into the slot, and the first partition
wall portion may be formed to extend from the insulator.
Furthermore, the second partition wall portion may be bent to cover
an axial direction of the balance weight.
The compression unit may further include an oil recovery passage
that communicates with an oil passage at one side of the
compression unit. Further, the first partition wall portion and
second partition wall portion may be connected to a third partition
wall portion or third partition wall, and at least a part or
portion of the oil recovery passage may be covered by the third
partition wall portion. Furthermore, the first partition wall
portion, second partition wall portion, and third partition wall
portion may be formed as an integral body and fixed to the
compression unit.
The oil recovery passage may be covered by a member separated from
the passage separation portion. Further, the oil recovery passage
may be formed with a hole that passes through the compression unit.
Furthermore, at least one of the first partition wall portion or
the second partition wall portion may be formed in an annular
shape. Also, the first partition wall portion and the second
partition wall portion may be formed as an integral body and fixed
to the compression unit.
Embodiments disclosed herein further provide a compressor that may
include a casing having an internal space; an electric motor drive
having a stator fixed to the internal space, a cut surface of which
is formed on an outer circumferential surface thereof to be
separated from an inner circumferential surface of the casing and a
rotor rotatably provided within the stator; a compression unit or
device provided at one side of the electric motor drive and having
a discharge hole so as to discharge compressed refrigerant into an
internal space of the casing; a rotating shaft configured to
transfer a drive force from the electric motor drive to the
compression unit; and a passage separation portion or separator
provided between the electric motor drive and the compression unit
to separate a refrigerant passage from an oil passage. The passage
separation portion may have a first partition wall portion or first
partition wall, and a second partition wall portion or second
partition wall. The first partition wall portion may be disposed
between the discharge hole and the cut surface of the stator, and
the second partition wall portion may be disposed between the
discharge hole and a gap between the stator and rotor.
A balance weight may be formed on the rotor or rotating shaft, and
the second partition wall portion may be provided between the
discharge hole and the balance weight.
Embodiments disclosed herein further provide a compressor that may
include a casing having an internal space; an electric motor drive
having a stator fixed to the internal space, a cut surface of which
is formed on an outer circumferential surface thereof to be
separated from an inner circumferential surface of the casing and a
rotor rotatably provided within the stator; a compression unit or
device provided at one side of the electric motor drive to have a
discharge hole so as to discharge compressed refrigerant into an
internal space of the casing; a rotating shaft configured to
transfer a drive force from the electric motor drive to the
compression unit; and a passage separation portion or separator
provided between the electric motor drive and the compression unit
to separate a refrigerant passage from an oil passage. The passage
separation portion is formed to surround at least a part or portion
of the discharge hole, and guide compressed refrigerant coming out
of the discharge hole in an axial direction.
The passage separation portion may be formed in a tube shape to
accommodate the discharge hole, and an end portion of the electric
motor drive side may be formed to have a height difference.
Further, an end portion of the electric motor drive side of the
passage separation portion may be formed such that a first surface
located at an outer side of the discharge hole is formed to be
higher than a second surface located at an inner side thereof based
on the rotating shaft. Furthermore, the passage separation portion
may be formed in an arcuate cross-sectional shape.
In a compressor according to embodiments, refrigerant discharged
from the compressor may move to a refrigerant discharge pipe
through a refrigerant passage, while oil separated from an upper
side of the electric motor drive may move to an oil storage space
through an oil passage, and thus, a passage to discharge the
refrigerant may be separated from a passage to recover the oil to
prevent the oil from being blocked by the refrigerant, and through
this, oil may be efficiently recovered to the oil storage space of
the casing, thereby preventing oil shortage in the compressor. In
addition, oil that has lubricated the compressor and flowed out
therefrom may be prevented from being mixed with refrigerant
discharged from the compressor, as well as recovered to an oil
storage space through an additional recovery passage to prevent the
oil from being discharged out of the compressor along with the
refrigerant, thereby more effectively reducing oil shortage in the
compressor.
Any reference in this specification to "one embodiment," "an
embodiment," "example embodiment," etc., means that a particular
feature, structure, or characteristic described in connection with
the embodiment is included in at least one embodiment of the
invention. The appearances of such phrases in various places in the
specification are not necessarily all referring to the same
embodiment. Further, when a particular feature, structure, or
characteristic is described in connection with any embodiment, it
is submitted that it is within the purview of one skilled in the
art to effect such feature, structure, or characteristic in
connection with other ones of the embodiments.
Although embodiments have been described with reference to a number
of illustrative embodiments thereof, it should be understood that
numerous other modifications and embodiments can be devised by
those skilled in the art that will fall within the spirit and scope
of the principles of this disclosure. More particularly, various
variations and modifications are possible in the component parts
and/or arrangements of the subject combination arrangement within
the scope of the disclosure, the drawings and the appended claims.
In addition to variations and modifications in the component parts
and/or arrangements, alternative uses will also be apparent to
those skilled in the art.
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