U.S. patent application number 17/535869 was filed with the patent office on 2022-03-17 for scroll compressor.
This patent application is currently assigned to LG ELECTRONICS INC.. The applicant listed for this patent is LG ELECTRONICS INC.. Invention is credited to Cheolhwan KIM, Taekyoung KIM, Byeongchul LEE, Kangwook LEE.
Application Number | 20220082098 17/535869 |
Document ID | / |
Family ID | 1000005996738 |
Filed Date | 2022-03-17 |
United States Patent
Application |
20220082098 |
Kind Code |
A1 |
LEE; Kangwook ; et
al. |
March 17, 2022 |
SCROLL COMPRESSOR
Abstract
A scroll compressor having a casing, a drive motor which is held
in place within the casing and has an internal flow passage and an
external flow passage to pass through, a rotation shaft which is
combined with the drive motor for rotation, a frame that is
provided under the drive motor and through which the rotation shaft
passes for support, a first scroll which is provided under the
frame and on which one flank surface a first wrap is formed, a
second scroll which is provided between the frame and the first
scroll, on which a second wrap that is engaged with the first wrap
is formed, with which the rotation shaft is eccentrically combined
and which forms a compression chamber, and a flow passage
separation unit which separates a space between the drive motor and
the frame into an internal space and an external space is
provided.
Inventors: |
LEE; Kangwook; (Seoul,
KR) ; KIM; Taekyoung; (Seoul, KR) ; LEE;
Byeongchul; (Seoul, KR) ; KIM; Cheolhwan;
(Seoul, KR) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
LG ELECTRONICS INC. |
Seoul |
|
KR |
|
|
Assignee: |
LG ELECTRONICS INC.
Seoul
KR
|
Family ID: |
1000005996738 |
Appl. No.: |
17/535869 |
Filed: |
November 26, 2021 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
15949890 |
Apr 10, 2018 |
11187230 |
|
|
17535869 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04C 29/0078 20130101;
F04C 29/0085 20130101; F04C 29/026 20130101; F04C 29/0057 20130101;
F04C 2240/40 20130101; F04C 29/12 20130101; F04C 23/008 20130101;
F04C 18/0215 20130101 |
International
Class: |
F04C 18/02 20060101
F04C018/02; F04C 29/00 20060101 F04C029/00; F04C 29/12 20060101
F04C029/12; F04C 29/02 20060101 F04C029/02; F04C 23/00 20060101
F04C023/00 |
Foreign Application Data
Date |
Code |
Application Number |
Apr 12, 2017 |
KR |
10-2017-0047554 |
Claims
1. A scroll compressor comprising: a casing; a drive motor located
within the casing, the drive motor having a first flow passage and
a second flow passage extending in an axial direction of the drive
motor; a rotation shaft connected to the drive motor, the rotation
shaft having an eccentric portion; a frame located below the drive
motor, the frame configured to receive the rotation shaft to
support the rotation shaft, the shaft extending through the frame;
a first scroll located below the frame, the first scroll having a
first wrap; a second scroll located between the frame and the first
scroll, the second scroll having a second wrap configured to engage
the first wrap, the second scroll being connected to the eccentric
portion of the rotation shaft; and a ring shaped flow passage
separation unit dividing a space between the drive motor and the
frame into an internal space that communicates with the first flow
passage of the drive motor and an external space that communicates
with the second flow passage of the drive motor, wherein the flow
passage separation unit includes one or more flow passage guides
separating the internal space and the external space, the one or
more flow passage guides protruding from at least one of a lower
surface of the drive motor and an upper surface of the frame toward
the other one of the lower surface of the drive motor and the upper
surface of the frame.
2. The scroll compressor of claim 1, wherein one end of the flow
passage separation unit is inserted into the lower surface of the
drive motor or the upper surface of the frame to form a sealing
portion.
3. The scroll compressor of claim 1, wherein the flow passage
separation unit includes: a first flow passage guide protruding
from an upper surface of the frame toward a lower surface of the
drive motor; and a second flow passage guide protruding from the
lower surface of the drive motor toward the upper surface of the
frame, wherein at least one of an upper surface of the first flow
passage guide and a lower surface of the second flow passage guide
includes a protrusion and at least the other one of the upper
surface of the first flow passage guide and the lower surface of
the second flow passage guide includes a groove, and wherein the
protrusion and the groove are engaged to form a sealing
portion.
4. The scroll compressor of claim 1, wherein the flow passage
separation unit includes: a first flow passage guide protruding
from an upper surface of the frame toward a lower surface of the
drive motor; and a second flow passage guide protruding from the
lower surface of the drive motor toward the upper surface of the
frame, wherein at least one of an upper surface of the first flow
passage guide and a lower surface of the second flow passage guide
includes a first step portion and at least the other one of the
upper surface of the first flow passage guide and the lower surface
of the second flow passage guide includes a second step portion,
and wherein the first step portion and the second step portion are
engaged to form a sealing portion.
5. The scroll compressor of claim 1, wherein the flow passage
separation unit includes: a first flow passage guide protruding
from an upper surface of the frame toward a lower surface of the
drive motor; and a second flow passage guide protruding from the
lower surface of the drive motor toward the upper surface of the
frame, and wherein a side surface of the first flow passage guide
and a side surface of the second flow passage guide facing each
other are adhered to form a sealing portion.
6. The scroll compressor of claim 1, wherein the flow passage
separation unit includes: a first flow passage guide protruding
from an upper surface of the frame toward a lower surface of the
drive motor; and a second flow passage guide protruding from the
lower surface of the drive motor toward the upper surface of the
frame, and wherein stepped portions located on a side surface of
the first flow passage guide and a side surface of the second flow
passage guide face each other so as to form a sealing portion.
7. The scroll compressor of claim 6, wherein one of the stepped
portions is formed as a hook protrusion and the other of the
stepped portions is formed as a hook groove, and wherein the hook
protrusion and the hook groove are engaged to form a sealing
portion.
8. A scroll compressor comprising: a casing having an inner
circumferential surface; a stator fixed within the casing, the
stator having an outer circumferential surface having one or more
first gaps located a distance away from the inner circumferential
surface of the casing, and the stator having an inner
circumferential surface defining a coil winding portion; a winding
coil wound around the coil winding portion; a rotor spaced from the
inner circumferential surface of the stator by a second gap; a
rotation shaft connected to the rotor, the rotation shaft having an
eccentric portion; a frame located below the stator, the frame
configured to receive the rotation shaft to support the rotation
shaft, the shaft extending through the frame; a first scroll
located below the frame, the first scroll having a first wrap; a
second scroll located between the frame and the first scroll, the
second scroll having a second wrap configured to engage the first
wrap, the second scroll being connected to the eccentric portion of
the rotation shaft; and a flow passage guide extending in an axial
direction of the rotation shaft from an upper surface of the frame
or a lower surface of the stator facing the upper surface of the
frame, the flow passage guide separating the second gap from the
one or more first gaps, the flow passage guide including: a ring
shaped first annular wall portion having a first height in the
axial direction, the first annular wall portion being located
between the coil winding portion and the one or more first gaps;
and a ring shaped second annular wall portion having a second
height in the axial direction, the second annular wall portion
being located between the second gap and the coil winding
portion.
9. The scroll compressor of claim 8, further comprising a member
extending from the other of the upper surface of the frame or the
lower surface of the stator from which the flow passage guide
extends, wherein the first annular wall portion faces the member,
and wherein the first annular wall portion is inserted into the
member.
10. The scroll compressor of claim 9, wherein the member is
provided with a groove so that the end of the first annular wall
portion is inserted to form a sealing portion.
11. The scroll compressor of claim 8, further comprising a member
extending from the other of the upper surface of the frame or the
lower surface of the stator from which the flow passage guide
extends, wherein the first annular wall portion faces the member,
and wherein the first annular wall portion directly contacts an
outer circumferential surface or an inner circumferential surface
of the member.
12. The scroll compressor of claim 8, wherein the first height is
greater than or equal to the second height.
13. The scroll compressor of claim 12, further comprising a balance
weight located on the rotor or the rotation shaft, the balance
weight being located inward from the second annular wall
portion.
14. The scroll compressor of claim 12, wherein an end portion of
the second annular wall portion is located a further distance away
from the member in the axial direction than from an end portion of
the first annular wall portion in the axial direction.
15. A scroll compressor comprising: an electric motor; a
compression unit; a casing accommodating the electric motor and the
compression unit therein, the casing having: a first space between
the electric motor and the compression unit; a second space above
the electric motor; and a third space below the compression unit; a
flow passage guide located in the first space of the casing, the
flow passage guide separating the first space into multiple spaces
in a radial direction from a center axis of the casing; and a
sealing portion located between the flow passage guide and a member
facing the flow passage guide.
16. The scroll compressor of claim 15, wherein the sealing portion
is defined by a portion of the flow passage guide being in direct
contact with a portion of the member.
17. The scroll compressor of claim 16, wherein the member is
provided with a sealing groove so that one end of the flow passage
guide is inserted to form the sealing portion.
18. The scroll compressor of claim 15, wherein the flow passage
guide includes: a ring shaped first annular wall portion, the first
annular wall portion having a first height in an axial direction
parallel to the center axis; a ring shaped second annular wall
portion, the second annular wall portion having a second height in
the axial direction, and the second annular wall portion being
located radially inward from the first annular wall portion; and an
annular surface portion connecting the first annular wall portion
and the second annular wall portion.
19. The scroll compressor of claim 18, wherein the compression unit
includes a refrigerant hole configured to guide a refrigerant that
is compressed in the compression unit to the first space, and
wherein the flow passage guide includes a refrigerant through-hole
located between the first annular wall portion and the second
annular wall portion.
20. The scroll compressor of claim 19, wherein an upper surface of
the compression unit includes an oil collection groove configured
to collect oil that flows down from the second space, and wherein
the multiple spaces in the first space are in communication via the
oil collection groove.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] This application is a Divisional of copending U.S.
application Ser. No. 15/949,890, filed on Apr. 10, 2018, which
claims priority under 35 U.S.C. .sctn.119(a) to Korean Application
No. 10-2017-0047554, filed on Apr. 12, 2017, the contents of all of
which are incorporated by reference herein in their entireties.
BACKGROUND OF THE DISCLOSURE
1. Field of the Disclosure
[0002] The present disclosure relates to a scroll compressor, and
particularly to a compressor in which a compression unit is
positioned under an electric motor.
2. Background of the Disclosure
[0003] A scroll compressor is a compressor in which, while an
orbiting motion is performed with multiple scrolls being engaged
with each other, a compression chamber which includes an absorption
chamber, an intermediate pressure chamber, and a discharge chamber
are formed between both scrolls. This type of scroll compressor
achieves not only a comparatively high compression when compared
with other types of compressor, but also a stable torque due to
smooth strokes for refrigerant absorption, compression, and
discharge. Therefore, the scroll compressor is widely used for
refrigerant compression in an air conditioning apparatus and the
like. In recent years, scroll compressors have been introduced in
which an eccentric load is reduced, resulting in an operating speed
of 180 Hz or higher.
[0004] The scroll compressors are categorized into low-pressure
compressors in which an absorption pipe communicates with an
internal space in a case, which serves as a low-pressure portion,
and high-pressure compressors in which the absorption pipe
communicates directly with a compression chamber. Thus, in the
high-pressure compressor, a drive unit is installed in an
absorption space that serves as the low-pressure portion, but in
the low-pressure compressor, the drive is installed in a discharge
space that serves as a high-pressure portion.
[0005] These types of scroll compressors are categorized into upper
compression types of scroll compressors and lower compression types
of scroll compressors according to positions of the drive unit and
a compression unit. In the upper compression type of scroll
compressor, the compression unit is positioned more upward than the
drive unit, but in the lower compression type of scroll compressor,
the compressor unit is positioned more downward than the drive
unit.
[0006] Normally, in compressors that include a high-pressure type
of scroll compressor, a discharge pipe is positioned far away from
the compression unit in such a manner that oil is separated from a
refrigerant in the internal space in the casing. Therefore, in the
high-pressure type of scroll compressor that belongs to the upper
compression type of scroll compressor, the discharge pipe is
positioned between an electric motor and the compression unit, but
the high-pressure type of scroll compressor that belongs to the
lower compression type of scroll compressor, the discharge pipe is
positioned over the electric motor.
[0007] Thus, in the upper compression type of scroll compressor,
the refrigerant that is discharged from the compression unit flows
from an intermediate space between the electric motor and the
compression unit toward the discharge pipe, without flowing up to
the electric motor. On the other hand, in the lower compression
type of scroll compressor, the refrigerant that is discharged from
the compression unit passes through the electric motor, and then
flows from an oil separation space, which is formed over the
electric motor, toward to the discharge pipe.
[0008] At this time, oil that is separated from the refrigerant in
an upper space that serves as the separation space passes through
the electric motor, and then flows into an oil storage space that
is formed under the compression unit. The refrigerant that is
discharged from the compression unit passes through the electric
motor as well and flows toward the oil separation space.
[0009] However, in the lower compression type of scroll compressor
in the related art, which is described above, a refrigerant
discharge path and an oil collection path, as described above, run
in opposite directions and thus interferes with each other. Thus,
the refrigerant and the oil cause flow passage resistance.
Particularly, the oil does not collect into the oil storage space
due to the high-pressure refrigerant. This causes an oil shortage
within the casing. Thus, frictional loss or abrasion occurs due to
the oil shortage on the compression unit.
[0010] Furthermore, as in the lower compression type of scroll
compressor in the related art, when the refrigerant discharge path
and the oil collection path interfere with each other, the oil that
is separated from the refrigerant in the internal space in the
casing is mixed again with the refrigerant that is discharged and
is discharged to the outside of the compressor. Thus, there occurs
a problem in that a severe oil shortage within the compressor
occurs.
[0011] Furthermore, the lower compression type of scroll compressor
in the related art, an oil collection flow passage along which the
oil that collects between the electric motor and the compression
unit flows into the lower space in the casing is sufficiently
secured. Thus, the oil stays over the compression unit. This
increases a likelihood that the oil that is mixed with the
refrigerant will flow into the upper space and will be then
discharged to the outside of the compressor. As a result, a severe
oil shortage within the compressor occurs.
SUMMARY OF THE DISCLOSURE
[0012] Therefore, an aspect of the detailed description is to
provide a scroll compressor in which oil that is separated from a
refrigerant in an upper space in a casing flows smoothly into a
lower space in the casing.
[0013] Another aspect of the detailed description is to provide a
scroll compressor in which oil that is separated from a refrigerant
in an upper space in a casing is prevented in advance from being
mixed with a refrigerant that flows from the lower space toward the
upper space in the casing.
[0014] Still another aspect of the detailed description is to
provide a scroll compressor in which oil that collects between an
electric motor and a compression unit collects into a lower space
in a casing without being mixed with a refrigerant that is
discharged from the compression unit.
[0015] Furthermore, still another aspect of the detailed
description is to provide a scroll compressor in which a
refrigerant flow passage and an oil flow passage are reliably
separated.
[0016] To achieve these and other advantages and in accordance with
the purpose of this specification, as embodied and broadly
described herein, there is provided a scroll compressor including:
a casing which has an internal space; an electric motor which has a
stator that is provided in the internal space and is connected to
the casing and a rotor that is rotatably provided within the
stator; a compression unit which is provided under the electric
motor; a rotation shaft which transfers drive force from the
electric motor to the compression unit; and a flow passage
separation unit that is installed between the electric motor and
the compression unit and separates a refrigerant flow passage and
an oil flow passage.
[0017] In the scroll compressor, the flow passage separation unit
may be installed between the electric motor and the compression
unit.
[0018] Then, in the scroll compressor, the flow passage separation
unit may be formed with a first flow passage guide that is combined
with the compression unit and a second flow passage guide that
extends from the electric motor, and the second flow passage guide
may be configured with an insulator that is provided in the
electric motor.
[0019] Furthermore, according to another aspect of the present
invention, there is provided a scroll compressor including: a
casing: a drive motor which is held in place within the casing and
has an internal flow passage and an external flow passage to pass
through in an axis direction; a rotation shaft which is combined
with the drive motor for rotation; a frame that is provided under
the drive motor and through which the rotation shaft passes for
support; a first scroll which is provided under the frame and on
whose one flank surface a first wrap is formed; a second scroll
which is provided between the frame and the first scroll, on which
a second wrap that is engaged with the first wrap is formed, with
which the rotation shaft is eccentrically combined in a manner that
overlaps the second wrap in a radial direction, and which forms a
compression chamber between the second scroll itself and the first
scroll, while performing an orbiting motion with respect to the
first scroll; and a flow passage separation unit which is formed in
the shape of a ring, and separates a space between the drive motor
and the frame into an internal space that communicates with the
internal flow passage in the drive motor and an external space that
communicates with the external flow passage.
[0020] In the scroll compressor, the flow passage separation unit
may include a flow passage guide that is provided between the
internal space and the external space to protrude from at least one
of a lower surface of the drive motor and an upper surface of the
frame toward to the other one, and a sealing member that is
provided to be brought into contact with the flow passage
guide.
[0021] Then, in the scroll compressor, the flow passage guide may
include a first flow passage guide that protrudes from the upper
surface of the frame toward the lower surface of the drive motor,
and a second flow passage guide that protrudes from the lower
surface of the drive motor toward the upper surface of the frame,
the first flow passage guide and the second flow passage guide may
be formed in such a manner that heights of the first flow passage
guide and the second follow passage guide overlap in the axial
direction, and the sealing member may be formed on both flank
surfaces of the first flow passage guide and the second flow
passage guide, which face each other.
[0022] Then, in the scroll compressor, the flow passage guide may
protrude from the upper surface of the frame toward the lower
surface of the drive motor or may protrude from the lower surface
of the drive motor toward the upper surface of the frame, and the
sealing member may be provided between an upper surface or a lower
surface of the flow passage guide and the lower surface of the
drive motor or the upper surface of the frame, which is brought
into contact with the upper surface or the lower surface of the
flow passage guide.
[0023] In the scroll compressor, the flow passage separation unit
may include at least one or more flow passage guides that are
provided between the internal space and the external space to
protrude from at least one of a lower surface of the drive motor
and an upper surface of the frame toward the other one, and one end
of the flow passage separation unit may be inserted into the lower
surface of the drive motor or the upper surface of the frame to
form a sealing portion.
[0024] Then, in the scroll compressor, the flow passage separation
unit may include a first flow passage guide that protrudes from an
upper surface of the frame toward a lower surface of the drive
motor, and a second flow passage guide that protrudes from the
lower surface of the drive motor toward the upper surface of the
frame, and a sealing portion may be formed as a result of combining
a lower surface of the first flow passage guide and an upper
surface of the second flow passage guide that faces the lower
surface of the first flow passage guide, in an interference
engagement manner. That is, at least one of an upper surface of the
first flow passage guide and a lower surface of the second flow
passage guide may be provided with a protrusion and another one is
provided with a groove, and the protrusion and the groove are
engaged with each other to form a sealing portion.
[0025] Then, in the scroll compressor, the flow passage separation
unit may include a first flow passage guide that protrudes from an
upper surface of the frame toward a lower surface of the drive
motor, and a second flow passage guide that protrudes from the
lower surface of the drive motor toward the upper surface of the
frame, and a sealing portion may be formed as a result of combining
a flank surface of the first flow passage guide and a flank surface
of the second flow passage guide that faces the flank surface of
the first flow passage guide in a manner that brings the two flank
surfaces into contact tightly with each other or in a stair-stepped
manner. That is, a flank surface of the first flow guide and a side
surface of the second flow guide facing each other are closely
adhered to form a sealing portion, or stepped portions are formed
respectively on the side surface of the first guide and the side
surface of the second guide facing each other so as to form the
sealing portion.
[0026] Furthermore, to achieve these and other advantages and in
accordance with the purpose of this specification, as embodied and
broadly described herein, there is provided a scroll compressor
including: a casing; a stator which is held in place within the
casing, on whose outer circumferential surface at least one or more
first gaps that are positioned a distance away from an inner
circumferential surface of the casing are formed, and on whose
inner circumferential surface a coil winding portion around which a
winding coil is wound; a rotor which is rotatably provided to be
positioned a second gap away from the inner circumferential surface
of the stator; a rotation shaft which is combined with the rotor
for concurrent rotation; a frame which is provided under the stator
and through which the rotation shaft passes for support; a first
scroll which is provided under the frame and on whose one flank
surface a first wrap is formed; a second scroll on whose surface
that is brought into contact with the frame a sealing member
insertion groove is formed, which is provided between the frame and
the first scroll, on which a second wrap that is engaged with the
first wrap is formed, with which the rotation shaft is
eccentrically combined in a manner that overlaps the second wrap in
a radial direction, and which forms a compression chamber between
the second scroll itself and the first scroll, while performing an
orbiting motion with respect to the first scroll; and a flow
passage guide that extends from an upper surface of the frame or a
lower surface of the stator that faces the upper surface of the
frame, in an axial direction and that separates the first gap and
the second gap, in which the flow passage guide includes a first
annular wall portion that is formed in the shape of a ring and has
a height in a first axial direction, which is positioned between
the first gap and the coil winding portion, and a second annular
wall portion that is formed in the shape of a ring and has a height
in a second axial direction, which is positioned between the second
gap and the coil winding portion.
[0027] In the scroll compressor, the first annular wall portion may
further include a sealing member between the first annular wall
portion and a member that the first annular wall portion faces.
[0028] Then, in the scroll compressor, for combination, the first
annular wall portion may be inserted into a member that the first
annular wall portion faces.
[0029] Then, in the scroll compressor, for combination, the first
annular wall portion may be brought into contact tightly with an
outer circumferential surface or an inner circumferential surface
of a member that the first annular wall portion faces.
[0030] Then, in the scroll compressor, the first annular wall
portion may be formed to have a greater height than the second
annular wall portion, or to have the same height as the second
annular wall portion.
[0031] Then, in the scroll compressor, a balance weight may be
provided on the rotor or the rotation shaft, and the balance weight
may be positioned inward from the second annular wall portion.
[0032] Then, in the scroll compressor, an end portion of the second
annular wall portion may be positioned a distance away in the axial
direction from the member that the end portion of the annular wall
portion face.
[0033] Furthermore, To achieve these and other advantages and in
accordance with the purpose of this specification, as embodied and
broadly described herein, there is provided a scroll compressor
including: an electric motor; a compression unit; a casing which
accommodates the electric motor and the compression unit, and that
has a first space between the electric motor and the compression
unit, a second space over the electric motor, and a third space
under the compression unit, and a flow passage guide which is
included in the first space and that separates the first space into
multiple spaces along the radial direction; and a sealing portion
which is provided between the flow passage guide and a member that
the flow passage guide face.
[0034] In the scroll compressor, the sealing portion may be a
sealing member that is inserted between the flow passage guide and
the member that the flow passage guide faces.
[0035] Then, in the scroll compression, the sealing portion may be
formed to be brought into contact tightly with the flow passage
guide and a member that the flow passage guide faces.
[0036] Then, in the scroll compressor, the flow passage guide may
include a first annular wall portion which is formed in the shape
of a ring, and which has a first height in an axial direction; a
second annular wall portion which is formed in the shape of a ring,
has a second height in the axial direction, and which is positioned
inward from the first annular wall portion; and an annular surface
portion that connects between the first annular wall portion and
the first annular wall portion.
[0037] Then, in the scroll compressor, a refrigerant hole which
guides a refrigerant that is compressed in the compression unit, to
the first space may be formed in the compression unit, and a
refrigerant through-hole may be formed between the first annular
wall portion and the second annular wall portion.
[0038] Then, in the scroll compressor, an oil collection groove for
collecting oil that flows down on an upper surface of the
compression unit may be formed in the upper surface of the
compression unit, and the oil collection groove may be formed in
such a manner that both spaces that result from separation by the
flow passage guide communicate with each other.
[0039] A scroll compressor according to the present invention, a
refrigerant flow passage and an oil flow passage are separated in
such a manner that a refrigerant which is discharged from a
compression unit flows into a discharge pipe along the refrigerant
flow passage, and that oil which is separated from the refrigerant
over an electric motor flows in a lower space along the oil flow
passage. Thus, the flow passage along which the refrigerant is
discharged and the flow passage along which the oil collects is
prevented from interfering with each other and thus the flow of the
oil can be prevented from being blocked due to the high-pressure
refrigerant. As a result, the oil collects smoothly into the lower
space, thereby preventing an oil shortage in advance.
[0040] Furthermore, a sealing member or a sealing portion is
provided on a flow passage separation unit that separates the
refrigerant flow passage and the oil flow passage. A gap is
prevented from occurring to the flow passage separation unit. As a
result, the refrigerant flow passage and the oil flow passage are
tightly separated, thereby minimizing a decrease in oil collection
due to the refrigerant.
BRIEF DESCRIPTION OF THE DRAWINGS
[0041] The accompanying drawings, which are included to provide a
further understanding of the disclosure and are incorporated in and
constitute a part of this specification, illustrate exemplary
embodiments and together with the description serve to explain the
principles of the disclosure.
[0042] In the drawings:
[0043] FIG. 1 is a vertical cross-sectional diagram illustrating a
lower compression type of scroll compressor according to the
present invention;
[0044] FIG. 2 is a horizontal cross-sectional diagram illustrating
a compression unit in FIG. 1;
[0045] FIG. 3 is a front-view diagram illustrating a portion of a
rotation shaft for describing a sliding member in FIG. 1;
[0046] FIG. 4 is a vertical cross-sectional diagram for describing
an oil supply path between a backpressure chamber and a compression
chamber in FIG. 1;
[0047] FIG. 5 is an exploded perspective diagram illustrating a
flow passage separation unit in the scroll compressor in FIG.
1;
[0048] FIG. 6 is a plan-view diagram illustrating a first flow
passage guide in the flow passage separation unit in FIG. 5, when
viewed from above;
[0049] FIG. 7 is a plan-view diagram illustrating the first flow
passage guide and a second flow passage guide in the flow passage
separation unit in FIG. 5, when viewed from below;
[0050] FIG. 8 is a cross-sectional diagram illustrating an
assembled state of that the flow passage separation unit, taken
along line VIII-VIII in FIG. 7;
[0051] FIGS. 9A to 10E are enlarged cross-sectional diagrams of
portions of flow passage separation units according to embodiments
for describing the flow passage separation units; and
[0052] FIG. 11 is a schematic diagram for describing flows of
refrigerant and oil that is separated from the refrigerant in the
scroll compressor in FIG. 1.
DETAILED DESCRIPTION OF THE DISCLOSURE
[0053] Description will now be given in detail of the exemplary
embodiments, with reference to the accompanying drawings. For the
sake of brief description with reference to the drawings, the same
or equivalent components will be provided with the same reference
numbers, and description thereof will not be repeated.
[0054] A scroll compressor according to an embodiment of the
present invention will be described in detail below with reference
to the accompanying drawing. For reference, the scroll compressor
according to the present invention relates to a structure for
increasing the sealing property and the durability of a sealing
member that is installed between an orbiting scroll and a frame
that corresponds to the orbiting scroll and that forms a
backpressure chamber. Therefore, the sealing member between the
orbiting scroll and a member that is brought into contact with the
orbiting scroll finds application in any type of scroll compressor.
For convenience, as a typical example, a type of scroll compressor
in which a rotation shaft overlaps a volute wrap in the same plane
will be described, among lower compression types of scroll
compressors in which a compression unit is positioned more downward
than an electric motor. It is known that this type of scroll
compressor is suitable for application in a freezing cycle under
the condition of a high pressure ratio at high-temperature.
[0055] FIG. 1 is a vertical cross-sectional diagram illustrating a
lower compression type of scroll compressor according to the
present invention. FIG. 2 is a horizontal cross-sectional diagram
for describing a sliding member in FIG. 1, illustrating a
compression unit in FIG. 1. FIG. 3 is a front-view diagram
illustrating a portion of a rotation shaft. FIG. 4 is a vertical
cross-sectional diagram for describing an oil supply path between a
backpressure chamber and a compression chamber.
[0056] With reference to FIG. 1, a lower compression type of scroll
compressor according to the present embodiment includes an electric
motor 20 and a compression unit 30 within a casing 10. The electric
motor 20 serves as a drive motor and generates rotary force. The
compression unit 30 is installed under the electric motor 20
between a prescribed space (hereinafter referred to as an
intermediate space) 10a. The compression unit 30 is provided with
the rotary force of the electric motor 20 and compresses a
refrigerant.
[0057] The casing 10 is configured to include a cylindrical shell
11 that makes up a sealed receptacle, an upper shell 12 that covers
an upper portion of the cylindrical shell 11 to make up the sealed
receptacle along with the cylindrical shell 11, and a lower shell
13 that makes up the sealed receptacle along with the cylindrical
shell 11 and, at the same time, forms an oil storage space 10c.
[0058] A refrigerant absorption pipe 15 passes through a flank
surface of the cylindrical shell 11 and communicates directly with
an absorption chamber of the compression unit 30. A refrigerant
discharge pipe 16 that communicates with an upper space 10b in the
casing 10 is installed in an upper portion of the upper shell 12.
The refrigerant discharge pipe 16A corresponds to a path along
which a compressed refrigerant that is discharged from the
compression unit 30 to the upper space 10b in the casing 10 is
exhausted to the outside. The refrigerant discharge pipe 16 is
inserted into up to the middle of the upper space 10b in the casing
10 in such a manner that a type of oil separation space is formed
in the upper space 10b. Then, whenever necessary, an oil separator
(not illustrated) that separates oil from an oil-mixed refrigerant
may be installed within the casing 10 including the upper space
10b, or within the upper space 10b, in a manner that is connected
to the refrigerant absorption pipe 15.
[0059] Teeth and slots that make up multiple coil winding portions
(each of which has a reference numeral) are formed along a
circumferential direction on an inner circumferential surface of a
stator 21, and a coil 25 is wound around the stator 21. A second
refrigerant flow passage PG2 is formed that results from combining
a gap between the inner circumferential surface of the stator 21
and an outer circumferential surface of a rotor 22 and the coil
winding portions. Accordingly, the refrigerant, which is discharged
to the intermediate space 10c between the electric motor 20 and the
compression unit 30 through a first refrigerant flow passage PG1
that will be described above, moves to the upper space 10b that is
formed above the electric motor 20, through the second refrigerant
flow passage PG2 that is formed in the electric motor 20.
[0060] Then, multiple D-cut surfaces are formed along the
circumferential direction on an outer circumferential surface of
the stator 21. A first oil flow passage PO1 is formed on the D-cut
surface 21a in such a manner that oil passes between the D-cut
surface 21a itself and an inner circumferential surface of the
cylindrical shell 11. Accordingly, the oil, which is separated from
the refrigerant, moves to a lower space 10c through the first oil
flow passage PO1 and through a second oil flow passage PO2 that
will be described below.
[0061] A frame 31, which serves as the compression unit 30 with a
prescribed gap between the frame 31 itself and the stator 21, is
combined fixedly with the inner circumferential surface of the
casing 10 under the stator 21. The frame 31 is fixedly combined
with the inner circumferential surface of the cylindrical shell 11
using a shrink fitting method or a welding manner.
[0062] Then, a frame side-wall portion (a first side-wall portion)
311 that takes the shape of a ring is formed on an edge of the
frame 31. Multiple communicating grooves 311b are formed along the
circumferential direction in an outer circumferential surface of
the first side-wall portion 311. The communicating groove 311b,
along with a communicating groove 322b in a first scroll 32 that
will be described above, forms the second oil flow passage PO2.
[0063] Furthermore, a first shaft bearing unit 312 for supporting a
main bearing unit 51 of a rotation shaft 50 that will be described
below is formed on the center of the frame 31. A first shaft
bearing hole 312a, into which the main bearing unit 51 of the
rotation shaft 50 is rotatably inserted for support in a radial
direction, is formed in the first shaft bearing unit 312 to pass
through the first shaft bearing unit 312 in an axial direction.
[0064] Then, a stationary scroll (hereinafter referred to as a
first scroll) 32 is installed on a lower surface of the frame 31
with the lower surface itself of the frame 31 and an orbiting
scroll (hereinafter referred to as a second scroll) 33
eccentrically combined with the rotation shaft 50 in between. The
first scroll 32 may be combined with the frame 31 in a fixed
manner, or may be combined with the frame 31 in a manner that is
movable in the axial direction.
[0065] On the other hand, on the first scroll 32, a stationary disc
portion (hereinafter referred to as a first disc portion) 321 is
formed in approximately the shape of a circle. A scroll side-wall
portion (hereinafter referred to as a second side-wall portion)
322, which is combined with an edge of a lower surface of the frame
31, is formed on an edge of the first disc portion 321.
[0066] An absorption inlet 324, through which the refrigerant
absorption pipe 15 and the absorption chamber communicate with each
other, is formed one side of the second side-wall portion 322 to
pass through the one side of the second side-wall portion 322.
Discharge outlets 325a and 325b, which communicate with a discharge
chamber and through which the compressed refrigerant is discharged,
are formed in a center portion of the first disc portion 321. One
discharge outlet 325a or 325b may be formed in such a manner as to
communicate with both a first compression chamber V1 and a second
compression chamber V2, which will be described below, and multiple
discharge outlets, that is, the discharge outlets 325a and 325b may
be formed independently in such a manner as to communicate with the
compression chambers V1 and V2, respectively.
[0067] Then, the communicating groove 322b, which is described
above, is formed in an outer circumferential surface in the second
side-wall portion 322. The communicating groove 322b, along with
the communicating groove 311b in the first side-wall portion 311,
forms the second oil flow passage PO2 for guiding oil that is
collected, to the lower space 10c.
[0068] Furthermore, a discharge cover 34 for guiding a refrigerant
that is discharged from the compression chamber V, to a refrigerant
flow passage, which will be described below, is combined with a
lower side of the first scroll 32. An internal space in the
discharge cover 34 is formed in such a manner as to accommodate the
discharge outlets 325a and 325b, and, at the same time, in such a
manner as to accommodate an entrance to the first refrigerant flow
passage PG1 that guides the refrigerant that is discharged from the
compression chamber V through the discharge outlet 325 a or 325b,
to the upper space 10b in the casing 10, more precisely, to a space
between the electric motor 20 and the compression unit 30.
[0069] At this point, the first refrigerant flow passage PG1 is
formed to pass through the second side-wall portion 322 of the
stationary scroll 32 and the first side-wall portion 311 of the
frame 31, sequentially, starting from inside of a flow passage
separation unit 40, that is, from the rotation shaft 50 that is
positioned inward from the flow passage separation unit 40.
Accordingly, the second oil flow passage PO2, which is described
above, is formed outside of the flow passage separation unit 40 in
such a manner as to communicate with the first oil flow passage
PO1. The oil separation unit will be described in detail below.
[0070] A stationary wrap (hereinafter referred to as a first wrap)
323 is formed on an upper surface of the first disc portion 321.
The stationary wrap intermeshes with an orbiting wrap (hereinafter
referred to as a second wrap) 332, which will be described below,
and thus makes up the compression chamber V. The first wrap 323
will be described below along with the second wrap 332.
[0071] Furthermore, a second shaft bearing unit 326, which supports
a sub-bearing unit 52 of the rotation shaft 50, which will be
described below, is formed on the center of the first disc portion
321. A second shaft bearing hole 326a, through which the
sub-bearing unit 52 passes in the axial direction to be supported
in the radial direction, is formed in the second shaft bearing unit
326.
[0072] On the other hand, an orbiting disc portion (hereinafter
referred to as a second disc portion) 331 of the second scroll 33
is formed approximately in the shape of a disk. The second wrap
332, which intermeshes with the first wrap 322 and thus makes up
the compression chamber, is formed on a lower surface of the second
disc portion 331.
[0073] Along with the first wrap 323, the second wrap 332 may be
formed in an involute shape, and may be formed in various shapes
other than the involute shape. For example, as illustrated in FIG.
2, the second wrap 332 may take a shape in which multiple circular
arcs that have different diameters and origins are connected to
each other, and the outermost curved line is formed in the shape of
approximately an ellipse that has a long axis and a short axis. The
first wrap 323 may be formed in the same manner.
[0074] A rotation shaft combination portion 333, into which an
eccentricity portion 53 of the rotation shaft 50 is rotatably
inserted for combination, is formed in a center portion of the
second disc portion 331 to pass through the center portion of the
second disc portion 331 in the axial direction. The rotation shaft
combination portion 333 is an internal end portion of the second
wrap 332. The eccentricity portion 53 of the rotation shaft 50 will
be described below.
[0075] An outer circumferential portion of the rotation shaft
combination portion 333 is connected to the second wrap 332 and
plays the role of forming the compression chamber V along with the
first wrap 322 during a compression process.
[0076] Furthermore, the rotation shaft combination portion 333 is
formed to such a height that rotation shaft combination portion 333
overlaps the second wrap 332 in the same plane, and thus the
eccentricity portion 53 of the rotation shaft 50 is positioned at
such a height that the eccentricity portion 53 overlaps the second
wrap 332 in the same plane. When this is done, counterforce by the
refrigerant and compression force against the refrigerant are
applied to the same plane with respect to the second disc portion
331, and thus cancel each other out. As a result, the second scroll
33 can be prevented from being inclined due to the exertion of
compression force and counterforce.
[0077] Furthermore, a recessed portion 335 that is engaged with a
protruding portion 328 of the first wrap 323, which will be
described below, is formed the outer circumferential portion of the
rotation shaft combination portion 333 that faces an internal end
portion of the first wrap 323. An increment portion 335a is formed
on one side of the recessed portion 335. A thickness of the
increment portion 335 increases over portions of the rotation shaft
combination portion 333, starting with an inner circumferential
portion thereof, ending with the outer circumferential portion
thereof, upstream along a direction of forming the compression
chamber V. This increases a compression path in the first
compression chamber V1 immediately before discharge, and
consequently, a compression ratio in the first compression chamber
V1 is increased closely to a compression ratio in the second
compression chamber V2. The first compression chamber V1, which is
a compression chamber that is formed between an internal flank
surface of the first wrap 323 and an external flank surface of the
second wrap 332, will be described below separately from the second
compression chamber V2.
[0078] A circular-arc compression surface 335b that takes the shape
of a circular arc is formed on the other side of the recessed
portion 335. A diameter of the circular-arc compression surface
335b is determined by an internal end portion thickness (that is, a
thickness of a discharge end) of the first wrap 323 and an orbiting
radius of the second wrap 332. When the internal end portion
thickness of the first wrap 323 is increased, the diameter of the
circular-arc compression surface 335b is increased. As a result, a
thickness of the second wrap in the vicinity of the circular-arc
compression surface 335b is increased, and the compression path is
lengthened. The compression ratio in the second wrap V2 is
increased as much as the compression path is lengthened.
[0079] Furthermore, the protruding portion 328, which protrudes
from the outer circumferential portion side of the rotation shaft
combination portion 333, is formed in the vicinity of an internal
end portion (an absorption end or a start end) of the first wrap
323, which corresponds to the rotation shaft combination portion
333. A contact portion 328a, which protrudes from the protruding
portion 328 and is engaged with the recessed portion 335, is formed
on the protruding portion 328. That is, the internal end portion of
the first wrap 323 is formed in such a manner that the internal end
portion has a greater thickness than other portions. As a result,
wrap strength of the internal end portion of the first warp 323, on
which the largest compression force is exerted is improved, thereby
increasing the durability.
[0080] On the other hand, the compression chamber V is formed
between the first disc portion 321 and the first wrap 323, and
between the second wrap 332 and the second disc portion 331, and is
configured to include an absorption chamber, an intermediate
pressure chamber, and a discharge chamber that are successively
formed along a direction in which a wrap progresses.
[0081] As illustrated in FIG. 2, the compression chamber V is
configured to include the first compression chamber V1 that is
formed between the internal flank surface of the first wrap 323 and
the external flank surface of the second wrap 332, and the second
compression chamber V2 that is formed between an external flank
surface of the first wrap 323 and an internal flank surface of the
second wrap 332.
[0082] That is, the first compression chamber V1 includes a
compression chamber that is formed between two contact points P11
and P12 which occur when the internal flank surface of the first
wrap 323 and the external flank surface of the second wrap 332 are
brought into contact with each other. The second compression
chamber V2 includes a chamber that is formed between two contact
points P21 and P22 which occur when the external flank surface of
the first warp 323 and the internal flank surface of the second
wrap 332 are brought into contact with each other.
[0083] At this point, when the greater of angles that the two
contact points P11 and P12 that connect the center of the
eccentricity portion 53, that is, the center O of the rotation
shaft combination portion 333 and the two contact points P11 and
P12, respectively, make with respect to each other is defined as
having a value of .alpha., .alpha.<360.degree. at least
immediately before discharge start, and a distance I between normal
vectors at the two contact points P11 and P12 has a value of 0 or
greater.
[0084] For this reason, the first compression chamber immediately
before the discharge has a smaller volume than is the case when the
stationary wrap and the orbiting wrap that take the shape of an
involute curve, and thus the compression ratio in the compression
chamber V1 and the compression ratio in the compression chamber V2
are both improved without increasing sizes of the first wrap 323
and the second wrap 332.
[0085] On the other hand, as described above, the second scroll 33
is installed, in a manner that enables the second scroll 33 to
orbit, between the frame 31 and the stationary scroll 32. Then, an
oldham ring 35 that prevents the second scroll 33 from rotating
about its axis is installed between an upper surface of the second
scroll 33 and a lower surface of the frame 31 that corresponds to
the upper surface of the second scroll 33. A sealing member 36,
which forms a backpressure chamber S1 that will be described below,
is installed more inward than the oldham ring 35.
[0086] Then, as a result of an oil supply hole 321a that is
provided in the second scroll 32, an intermediate pressure space is
formed outside of the sealing member 36. The intermediate pressure
space communicates with the compression chamber V and, when filled
with an intermediate-pressure refrigerant, plays the role of the
backpressure chamber. Accordingly, the counterpressure chamber that
is formed more inward than the sealing member 36 is defined as a
backpressure chamber S1, the counterpressure chamber that is formed
more outward than the sealing member 36 is defined as a second
backpressure chamber S2. Consequently, the backpressure chamber S1
is a space that is formed by a lower surface the frame 31 and an
upper surface of the second scroll 33 with the sealing member 36 in
between. The backpressure chamber S1 will be again described below
along with the sealing member.
[0087] On the other hand, an upper portion of the rotation shaft 50
is pressure-inserted into the center of the rotor 22 for
combination and a lower portion thereof is combined with the
compression unit 30 for support in the radial direction.
Accordingly, the rotation shaft 50 transfers the rotary power of
the electric motor 20 to the orbiting scroll 33 of the compression
unit 30. Then, the second scroll 33 that is eccentrically combined
with the rotation shaft 50 performs an orbiting motion with respect
to the first scroll 32.
[0088] The main bearing unit (hereinafter referred to as the first
bearing unit) 51, which is inserted into the first shaft bearing
hole 312a in the frame 31 for support in the radial direction, is
formed on a lower half portion of the rotation shaft 50. The
sub-bearing unit 52 (hereinafter referred to as the second bearing
unit) 52, which is inserted into the second shaft bearing hole 326a
in the first scroll 32 for support in the radial direction, is
formed under the first bearing unit 51. Then, the eccentricity
portion 53, which is inserted into the rotation shaft combination
portion 333 for combination, is formed between the first bearing
unit 51 and the second bearing unit 52.
[0089] The first bearing unit 51 and the second bearing unit 52 is
formed on the same axial line, in such a manner as to have the same
axial center. The eccentricity portion 53 is essentially formed in
the radial direction with respect to the first bearing unit 51 or
the second bearing unit 52. The second bearing unit 52 may be
eccentrically formed with respect to the first bearing unit 51.
[0090] In a case where an outside diameter of the eccentricity
portion 53 is formed to be smaller than an outside diameter of the
first bearing unit 51, but to be greater than an outside diameter
of the second bearing unit 52, is advantageous in that the rotation
shaft 50 passes the shaft bearing holes 312a and 326a and the
rotation shaft combination portion 333 for combination. However, in
a case where the eccentricity portion 53 is formed using a separate
bearing, without being integrally with the rotation shaft 50, the
rotation shaft 50 is inserted for combination even if the outside
diameter of the second bearing unit 52 is formed to be smaller than
the outside diameter of the eccentricity portion 53.
[0091] Then, an oil supply flow passage 50a for supplying oil to
each bearing unit and the eccentricity portion is formed, along the
axial direction, inside of the rotation shaft 50. The compression
unit 30 is positioned more downward than the electric motor 20, and
thus the oil supply flow passage 50a is formed, by grooving, to a
height from a lower end of the rotation shaft 50 to approximately a
lower end of the stator 21, to the middle of the height, or to a
position that is higher than an upper end of the first bearing unit
51. Of course, when necessary, the oil supply path 50a may be
formed to pass through the rotation shaft 50 in the axial
direction.
[0092] Then, an oil feeder 60 for pumping the oil with which the
lower space 10c is combined with the lower end of the rotation
shaft 50, that is, a lower end of the second bearing unit 52. The
oil feeder 60 is configured to include an oil supply pipe 61 that
is inserted into the oil supply flow passage 50a in the rotation
shaft 50 for combination, and a blocking member 62 that accommodate
the oil supply pipe 61 and block introduction of a foreign
material. The oil supply pipe 61 is positioned to pass through the
discharge cover 34 and to be immersed in the oil in the lower space
10c.
[0093] On the other hand, as illustrated in FIG. 3, a sliding
member oil supply path F1 for supplying oil to each sliding member,
which is connected to the oil supply flow passage 50a, is formed in
each bearing unit 51 or 52 of the rotation shaft 50 and the
eccentricity portion 53.
[0094] The sliding member oil supply path F1 is configured to
include a plurality of oil supply holes, that is, oil supply holes
511, 521, and 531 to pass through in the oil supply flow passage
50a toward an outer circumferential surface of the rotation shaft
50, and a plurality of oil supply grooves, that is, oil supply
grooves 512, 522, and 532 in the bearing units 51 and 52 and an
outer circumferential surface of the eccentricity portion 53, which
communicate with the oil supply holes 511, 521, and 531,
respectively, for lubricating the bearing units 51 and 52 and the
eccentricity portion 53 with oil.
[0095] For example, the first oil supply hole 511 and the first oil
supply groove 512 are formed in the first bearing unit 51, the
second oil supply hole 521 and the second oil supply groove 522 are
formed in the second bearing unit 52, and the third oil supply hole
531 and the third oil supply groove 532 are formed in the
eccentricity portion 53. The first oil supply groove 512, the
second oil supply groove 522, and the third oil supply groove 532
each are formed in the shape of a longitudinal groove that runs
lengthwise in the axial direction or in an inclination
direction.
[0096] Then, a first connection groove 541 and a second connection
groove 542 are formed between the first bearing unit 51 and the
eccentricity portion 53, and the eccentricity portion 53 and the
second bearing unit 52, respectively. A lower end of the first oil
supply groove 512 communicates with the first connection groove
541, and an upper end of the second oil supply groove 522
communicates with the second connection groove 542. Thus, a portion
of the amount of oil with which the first bearing unit 51 is
lubricated along the first oil supply groove 512 flows along the
first connection groove 541, and collects. This oil is in turn
introduced into the first backpressure chamber S1 and forms
backpressure of discharge pressure. Furthermore, oil with which the
second bearing unit 52 is lubricated along the second oil supply
groove 522, and oil with which the eccentricity portion 53 is
lubricated along the third oil supply groove 532 collects on the
second connection groove 542. This oil in turn passes between a
front surface of the rotation shaft combination portion 333 and the
first disc portion 321 and is introduced into the compression unit
30.
[0097] Then, a small amount of oil that is absorbed upward above
the first bearing unit 51 flows out from an upper end of the first
shaft bearing unit 312 of the frame 31 to outside of the bearing
surface, then flows over the first shaft bearing unit 312 down to
an upper surface 31a of the frame 31, and lastly flows over the oil
flow passages PO1 and PO2, which are successively formed on an
outer circumferential surface (or a groove in an upper surface,
which communicates with the outer circumferential surface) of the
frame 21 and an outer circumferential surface of the first scroll
32, respectively, into the lower space 10c for collection.
[0098] In addition, oil that, along with the refrigerant, is
discharged from the compression chamber V to the upper space 10b in
the casing 10 is separated from the refrigerant in the upper space
10b in the casing 10, and then flows along the first oil flow
passage PO1, which is formed in an outer circumferential surface of
the electric motor 20, and the second oil flow passage PO2, which
is formed in an outer circumferential surface of the compression
unit 30, into the lower space 10c for collection. The flow passage
separation unit 40, which will be described below, is provided
between the electric motor 20 and the compression unit 30. Thus,
the oil, which is separated from the refrigerant in the upper space
10b and flows into the lower space 10c, interferes with and is
mixed again with the refrigerant that is discharged in the
compression unit 20 and flows into the upper space 10b. The oil and
the refrigerant flow along paths PO1 and PO2 and the paths PG1 and
PG2, which are different from each other, into the lower space 10c
and the upper space 10b, respectively.
[0099] On the other hand, a compression chamber oil-supply path F2
for supplying the oil that flows along the oil supply flow passage
50a and then is absorbed upward, to the compression chamber V is
formed in the second scroll 33. The compression chamber oil-supply
path F2 is connected to the sliding member oil supply path F1,
which is described above.
[0100] The compression chamber oil-supply path F2 is configured to
include a communicating first oil supply flow path 371 that
connects between the oil supply flow passage 50a and the second
backpressure chamber S2 that serves as the intermediate pressure
space, and a second oil supply flow path 372 that communicates with
the intermediate pressure chamber of the compression chamber V.
[0101] Of course, the directly-communicating compression chamber
oil-supply path F2 may be formed to connect between the oil supply
flow passage 50a and the intermediate pressure chamber without the
second backpressure chamber S2 being involved. However, in this
case, a communicating refrigerant flow passage needs to be
separately provided between the second backpressure chamber S2 and
the intermediate pressure chamber V, and an oil flow passage for
supplying oil to the oldham ring 35 that is positioned in the
second backpressure chamber S2 needs to be separately provided.
This increases the number of paths and makes processing complex.
Therefore, at least to unify the refrigerant flow passage and the
oil flow passage and thus to decrease the number of paths, as in
the present embodiment, it is desirable that the oil supply flow
passage 50a and the second backpressure chamber S2 communicates
with each other and that the second backpressure chamber S2
communicates with the intermediate pressure chamber V.
[0102] To do this, the first oil supply path 371 includes a first
orbiting path portion 371a that is formed in the lower surface of
the second disc portion 331 to run up to the middle in the
thickness direction, a second orbiting path portion 371b that is
formed to extend from the first orbiting path portion 371a toward
an outer circumferential surface of the second disc portion 331,
and third orbiting path portion 371c to pass through toward the
upper surface of the second disc portion 331, which is formed to
extend from the second orbiting path portion 371b.
[0103] Then, the first orbiting path portion 371a is formed in a
position in which the first backpressure chamber S1 is positioned,
and the third orbiting path portion 371c is formed in a position in
which the second backpressure chamber S2 is positioned. Then, a
pressure reducing bar 375 is inserted into the second orbiting path
portion 371b in such a manner that pressure of oil that flows from
the first backpressure chamber S1 to the second backpressure
chamber S2 along the first oil supply path 371 is reduced.
Accordingly, a cross-sectional area of the second orbiting path
portion 371b except for the pressure reducing bar 375 is smaller
than that of the first orbiting path portion 371a or the third
orbiting path portion 371c.
[0104] At this point, in a case where an end portion of the third
orbiting path portion 371c is formed in such a manner that the end
portion is positioned inward than the oldham ring 35, that is, is
positioned between the oldham ring 35 and the sealing member 36,
oil that flows along the first oil supply path 371 is blocked by
the oldham ring 35 and thus does not flow smoothly to the second
backpressure chamber S2. Therefore, in this case, a fourth orbiting
path portion 371d is formed to extend from an end portion of the
third orbiting path portion 371c toward the outer circumferential
surface of the second disc portion 331. The fourth orbiting path
portion 371d, as illustrated in FIG. 4, may be formed to be a
groove in an upper surface of the second disc portion 331, and may
be formed to be a hole in the inside of the second disc portion
331.
[0105] The second oil supply path 372 includes a first stationary
path portion 372a that is formed in an upper surface of the second
side-wall portion 322 in the thickness direction, a second
stationary path portion 372b that is formed to extend from the
first stationary path portion 372a in the radial direction, and
third stationary path portion 372c that is formed to extend from
the second stationary path portion 372b and to communicate with the
intermediate pressure chamber V.
[0106] A reference numeral 70 in the drawing, which is not
described, indicates an accumulator.
[0107] The lower compression type of scroll compressor according to
the present embodiment, which is described above, operates as
follows.
[0108] That is, when the electric motor 20 is powered on, rotary
power occurs to the rotor 22 and the rotation shaft 50, and the
rotor 22 and the rotation shaft 50 rotate. As the rotation shaft 50
rotates, with the Oldham ring 35, the orbiting scroll 33 that is
eccentrically combined with the rotation shaft 50 performs the
orbiting motion.
[0109] Then, a refrigerant that is supplied from outside of the
casing 10 through the refrigerant absorption pipe 15 is introduced
into the compression chamber V. This refrigerant is compressed as
the volume of the compression chamber V decreases by the orbiting
motion of the orbiting scroll 33. The compressed refrigerant is
discharged into the internal space in the discharge cover 34
through the discharge outlets 325a and 325b.
[0110] Then, the refrigerant that is discharged into the internal
space in the discharge cover 34 circulates in the internal space in
the discharge cover 34. After noise decreases, the refrigerant
flows into a space between the frame 31 and the stator 21, and
flows into an upper space over the electric motor 20 through a
space between the stator 21 and the rotor 22.
[0111] Then, the refrigerant that results from separating the oil
from the refrigerant in the upper space over the electric motor 20
is discharged to outside of the casing 10 through the refrigerant
discharge pipe 16, and on the other hand, the oil flows into the
lower space 10c that is the oil storage space in the casing 10
through a passage between the inner circumferential surface of the
casing 10 and the stator 21 and a passage between the inner
circumferential surface of the casing 10 and the outer
circumferential surface of the compression unit 30. A sequence of
these processes is repeated.
[0112] At this time, the oil in the lower space 10c is absorbed
upward flowing along the oil supply flow passage 50a in the
rotation shaft 50, and the first bearing unit 51 and the second
bearing unit 52, and the eccentricity portion 53 are lubricated
with the oil that flows along the oil supply holes 511, 521, and
531 and the oil supply grooves 512, 522, and 532, respectively.
[0113] The oil that flows along the first oil supply hole 511 and
the first oil supply groove 512, with which the first bearing unit
51 is lubricated, collects in the first connection groove 541
between the first bearing unit 51 and the eccentricity portion 53
and is introduced into the first backpressure chamber S1. The oil
generates almost discharge pressure and thus pressure in the first
backpressure chamber S1 is increased to the discharge pressure.
Therefore, the center portion side of the second scroll 33 is
supported, in the axial direction, by the discharge pressure.
[0114] On the other hand, the oil in the first backpressure chamber
S1 flows into the second backpressure chamber S2 along the first
oil supply path 371 due to a pressure difference with the second
backpressure chamber S2. At this time, the pressure reducing bar
375 is provided in the second orbiting path portion 371b that
serves as the first oil supply path 371, and thus pressure of the
oil that flows toward the second backpressure chamber S2 is
reduced.
[0115] Then, the oil that flows into the second backpressure
chamber (the intermediate pressure space) S2 supports an edge
portion of the second scroll 33, and at the same time, flows into
the intermediate pressure chamber V along the second oil supply
path 372 due to a pressure difference with the intermediate
pressure chamber V.
[0116] However, when pressure in the intermediate pressure chamber
V is higher than pressure in the second backpressure chamber S2
during the operation of the compressor, the refrigerant flows from
the intermediate pressure chamber V toward the second backpressure
chamber S2 along the second oil supply path 372. In other words,
the second oil supply path 372 plays the role of a passage along
which the refrigerant and the oil flow in opposite directions due
to the pressure difference between the second backpressure chamber
S2 and the intermediate pressure chamber V.
[0117] On the other hand, as described above, the oil separation
unit 40 is installed in the intermediate space (hereinafter
referred to as a first space) 10a that is a passing-through space
which is formed between a lower surface of the electric motor 20
and an upper surface of the compression unit 30. The oil separation
unit 40 plays the role of preventing the refrigerant that is
discharged from the compression unit 30 from interfering with the
oil that flows from the upper space (hereinafter referred to as a
second space) 10b in the electric motor 20, which is the oil
separation space, into a lower space (hereinafter referred to as a
third space) 10c in the compression unit 30 that is the oil storage
space.
[0118] To do this, the flow passage separation unit 40 according to
the present embodiment includes a passage guide that separates the
first space 10a into a space (hereinafter referred to as a
refrigerant flow space) in which the refrigerant flows, and a space
(hereinafter referred to as an oil flow space) in which the oil
flows. Only with the passage guide itself, the first space 10a is
separated into the refrigerant flow space and the oil flow space,
but whenever necessary, a combination of multiple passage guides
may play the role of the passage guide. In the present embodiment,
as a typical example, the latter is first described, and then the
former will be described in detail below.
[0119] FIGS. 5 to 7 are diagrams illustrating a state where the
passage separation unit according to the present embodiment is
dismantled or assembled. FIG. 8 is a vertical cross-sectional
diagram illustrating a state where the passage separation unit
which is illustrated in FIG. 5 is assembled. FIGS. 9A to 10E are
magnified cross-sectional diagrams of a portion of the passage
separation unit for describing passage separation units according
to embodiments.
[0120] As illustrated in FIGS. 5 to 7, a first flow passage guide
410 that is formed in the shape of a ring is fixedly combined with
the upper surface 31a of the frame 31. The first flow passage guide
410, along with a second flow passage guide 420 that extends from
the stator 21, makes up the flow passage separation unit. The first
flow passage guide 410 that is manufactured in the shape of a ring
is fixedly combined with the upper surface 31a of the frame 31. The
second flow passage guide 420 is formed to extend from an insulator
that is inserted into the stator 21 and insulates a winding coil.
Alternatively, the second flow passage guide 420 is separately
manufactured and is combined with the stator 21. As an example, the
second flow passage guide that extends from the insulator will be
described below.
[0121] Multiple second refrigerant holes 311a that, along with a
first refrigerant hole (which has no reference numeral) in the
first scroll 32, makes up the first refrigerant flow passage PG1,
are formed in the axial direction in the frame 31 in such a manner
as to pass through the frame 31. On one side of the second
refrigerant hole 311a, an oil collection groove 311c is formed in
the radial direction in the upper surface 31a of the frame 31.
[0122] The oil collection groove 311c is connected to the
communicating groove 311b in the first side-wall portion 311. Thus,
the oil that is separated from the refrigerant on the upper surface
31as of the frame 31 is introduced into the second oil flow passage
PO2 along the oil collection groove 311c, and flows into the lower
space 10c, along with the oil that flows along the first oil flow
passage PO1 and collects.
[0123] At this point, the oil collection groove 311c that is formed
in the upper surface 31a of the frame 31 serves as a communicating
path between the refrigerant flow space and the oil flow space that
make up the first space. However, an annular surface portion 413 of
the first flow passage guide 410, which will be described below,
covers the oil collection groove 311c and thus a state where the
refrigerant flow space and the oil flow space communicate with each
other is reduced to a minimum. Moreover, in the present embodiment,
a first oil supply groove 512 is formed to have a structure in
which an upper end of the first oil supply groove 512 is blocked in
the bearing unit 51, and thus an amount of oil that flows over the
first shaft bearing unit 312 and flows on the upper surface 31a of
the frame 31 is very small. Because of this, a very small
cross-sectional area of the oil collection groove 311c can be
formed. Therefore, a situation where the refrigerant in the
refrigerant flow space passes through the oil collection groove
311c and flows into the oil flow space seldom occurs.
[0124] On the other hand, the first flow passage guide 410 includes
first annular wall portion 411 that separates the refrigerant flow
passage and the oil flow passage in the first space 10a. Thus, an
intermediate space 10a is separated by the first annular wall
portion 411 into a refrigerant flow space A1 and an oil flow space
A2. The refrigerant that is discharged into the upper space 10b
flows along the refrigerant flow passages PG1 and PG2, and the oil
that collects into the lower space 10c flows along the oil flow
passages PO1 and PO2.
[0125] Furthermore, the first flow passage guide 410 further
includes a second annular wall portion 412, in addition to the
first annular wall portion 411. The second annular wall portion 412
is formed more inward than the first annular wall portion 411, that
is, is formed to the side of the rotation shaft 50, and separates
the refrigerant flow space A1 into a first refrigerant flow space
A1l and a second refrigerant flow space A12.
[0126] At this point, the first annular wall portion 411 and the
second annular wall portion 412 may be formed independently of each
other. In this case, any one of the first annular wall portion 411
and the second annular wall portion 412 may be integrally combined
with the upper surface 31a of the frame 31 using a molding or
processing method, or both of the first annular wall portion 411
and the second annular wall portion 412 may be integrally combined
with the upper surface 31a of the frame 31 using a molding or
processing method.
[0127] However, with the annular surface portion 413, the first
annular wall portion 411 and the second annular wall portion 412
are connected to each other. Thus, the first flow passage guide 410
that includes the first annular wall portion 411 and the second
annular wall portion 412 can be manufactured as a single product.
Thus, not only is a manufacturing processing simplified, but an
assembling process is also easily performed. In this case, a
refrigerant through-hole 413a is formed in the annular surface
portion 413 to pass through the annular surface portion 413 in the
axial direction, and the refrigerant through-hole 413a communicates
with a second refrigerant hole 311a that makes up the first
refrigerant flow passage PG1.
[0128] In the present embodiment, as a typical example, an example
in which a first annular wall portion and a second annular wall
portion are integrally combined with an annular surface portion is
described. Another example in which the second annular wall portion
of the first annular wall portion and the second annular wall
portion will be described below. An example in which each of the
first annular wall portion and the second annular wall portions is
integrally combined with the frame is apparent from the embodiments
described above, and thus is not separately described.
[0129] As illustrated in FIGS. 6 and 7, the first annular wall
portion 411 is formed in the shape of a ring. A lower end in the
axial direction, of the first annular wall portion 411 sits on the
upper surface 31a of the frame 31 for support, and on the other
hand, an upper end in the axial direction, of the first annular
wall portion 411 is formed in such a manner as to be close to the
lower surface 21b of the stator 21. Thus, the first annular wall
portion 411 is formed in the shape of a cylinder with a prescribed
height.
[0130] In addition, it is desirable that the first annular wall
portion 411 is positioned between the outer circumferential surface
of the stator 21 and an external flank surface of the coil winding
portion, more precisely, between the D-cut surface 21a of the
stator 21 and an external end 212a of the slot 211 that makes up
the coil winding portion. Thus, the first annular wall portion 411
is positioned more outward than an external extension (hereinafter
referred to as a first extension portion) of the second flow
passage guide 420, which will be described above. Therefore, when a
sealing member 430, which will be described below, is provided
between the first annular wall portion 411 and the first extension
portion 421, ideally, the refrigerant in the refrigerant flow space
A1 does not flow into the flow space A2, and the oil that flows
into the oil flow space A2 and collects does not flow into the
refrigerant flow space A1.
[0131] At this point, the second flow passage guide 420 is formed
to extend from the insulator that is inserted into the slot 211 of
the stator 21 and plays the role of insulating the stator 21 from a
winding coil 25. Normally, the second flow passage guide 420
includes the first extension portion 421 and an external extension
portion (hereinafter referred to as a second extension portion)
422, which extend more downward than a winding body of the winding
coil 25, from both the ends, the upper end and the lower end,
respectively, of the stator 21.
[0132] Then, the first extension portion 421 is formed in the shape
of a ring or is formed in the shape of multiple protrusions, but as
in the present embodiment, it is desirable that the first extension
portion 421 is formed in the shape of a ring in order to play the
role of separating the first space 10a along with the first annular
wall portion 411.
[0133] As illustrated in FIG. 8, instead of an upper end in the
axial direction, of the first annular wall portion 411 being
positioned a fixed distance away from the lower surface 21b of the
stator 21, the sealing member 430 is provided between an inner
circumferential surface 411a of the first annular wall portion 411
and a member that comes into contact with the inner circumferential
surface 411a, that is, an outer circumferential surface 421a of the
external extension portion 421 of the second flow passage guide
420. Thus, the refrigerant flow space A1 that is an internal space
of the first annular wall portion 411 and the oil flow space A2
that is an external space of the first annular wall portion 411 are
reliably separated by the first annular wall portion 411, the first
extension portion 421, and the sealing member 430.
[0134] Then, sealing grooves 411c and 421b may be formed in any one
of the inner circumferential surface 411b of the first annular wall
portion 411 and the outer circumferential surface 421a of the first
extension portion, and the sealing member 430 in the shape of a
ring may be inserted into the sealing grooves 411c and 421b for
combination. However, the first annular wall portion 411 of the
first flow passage guide 410 and the first extension portion 421 of
the second flow passage guide 420 cannot be thickened due to a
spatial restriction. Therefore, as illustrated in FIG. 8, the
sealing grooves 411c and 421b are formed on the inner
circumferential surface 411b of the first annular wall portion 411
and the outer circumferential surface 421a of the first extension
portion 421, respectively. Halves of the sealing member 430 are
inserted into both the sealing grooves 411c and 421c,
respectively.
[0135] As illustrated in FIGS. 6 and 7, like the first annular wall
portion 411, the second annular wall portion 412 is formed to have
a prescribed height. A lower end in the axial direction, of the
second annular wall portion 412 sits on the upper surface 31a of
the frame 31, and on the other hand, an upper end 412a in the axial
direction, of the second annular wall portion 412 is formed to
extend toward the stator 21 in such a manner that the upper end
412a is positioned a fixed distance away from the lower surface 21b
of the stator 21.
[0136] However, it is desirable that the second annular wall
portion 412 is formed in such a manner that a height H2 of the
second annular wall portion 412 is lower than a height H1 of the
first annular wall portion 411. The reason for this is as follows.
When the height H 2 of the second annular wall portion 412 is so
high that contact with the lower surface 21b of the stator 21 takes
place, or when a distance G2 is too short, a gap G2 between the
stator 21 and the rotor 22 is an obstacle to the flow of the
refrigerant because most of the refrigerant that is discharged
inward from the first annular wall portion 411 along the first
refrigerant flow passage PG1 flows into the second space 10b only
along the slot 211.
[0137] Therefore, it is desirable that the second annular wall
portion 412 of the first flow passage guide 410 is positioned more
outward than a second extension unit 422 of the second flow passage
guide 420, and that the second annular wall portion 412 is formed
in such a manner that a height H2 of the second annular wall
portion 412 is smaller than a height H1 of the first annular wall
portion 411 and is smaller than a height H3 of the second extension
portion 422 of the second flow passage guide 420 from the lower
surface 21b of the stator 21, more precisely, the upper surface 31a
of the frame 31.
[0138] Furthermore, the second annular wall portion 412 has a
balance weight 26 inside, and thus it is desirable that a position
and a height are set considering tracks of the balance weight 26.
That is, the second annular wall portion 412 is provided to prevent
the refrigerant, which is discharged into the first space 10a along
the first refrigerant flow passage PG1, from being agitated due to
the balance weight 26 that rotates. In this respect, it is
desirable that the second annular wall portion 412 is formed to be
positioned outside of the tracks of the balance weight 26 and to
have a height that is equal to or greater than a height H4 of an
eccentricity mass portion 262 of the balance weight 26. The height
H4 is set to be lower than a lower end of the winding coil 25 in
order to prevent the balance weight 26 from colliding with the
winding coil 25. In this respect, as described above, it is
desirable that the second annular wall portion 412 is formed to be
positioned more outward than the second extension unit 422, but
more inward than the first extension portion 421 in such a manner
that the height H2 of the second annular wall portion 412 is
smaller than that of the winding coil 25 and is smaller than that
of a lower end 422a of the second extension portion 422 of the
second flow passage guide 420.
[0139] At this point, the balance weight 26 may be combined with
the rotation shaft 50, but, in the present embodiment, is fixedly
combined with a lower end of the rotor 22 and thus rotates along
with the rotor 22.
[0140] That is, the balance weight 26 is configured to include a
stationary portion 261 that is combined with the rotor 22, and an
eccentricity mass portion 262 that extends eccentrically in the
radial direction from the stationary portion 261. Therefore, the
eccentricity mass portion 262 extends more outward than the rotor
22. Thus, the eccentricity mass portion 262 extends out of the gap
G2 between the stator 21 and the rotor 22. Because of this, the
second annular wall portion 412 is positioned at least out of the
gap G2 between the stator 21 and the rotor 22. Thus, in a case
where the second annular wall portion 412 is formed to too high a
height and thus the distance G to the winding coil 25 is decreased
or the upper end 412a of the second annular wall portion 412 is
bent in a rotary axial direction, the refrigerant that is
discharged into the first space 10a is not guided into the gap G2
between the stator 21 and the rotor 22, thereby increasing flow
passage resistance. Therefore, it is desirable that the height H2
of the second annular wall portion 412 is not smaller than a height
H4 of an upper surface of the balance weight 26, but the distance
G1 to the winding coil 25 is greatly increased. Of course, a
protrusion length of the second extension unit 422 from the lower
surface 21b of the stator 21 is equal to or smaller than a
protrusion length of the wing coil 25.
[0141] On the other hand, a position in which the sealing member is
installed in the flow passage separation unit according to the
present embodiment is changed in various ways.
[0142] For example, as illustrated in FIG. 9A, the sealing member
may be installed between an upper end surface 411a of the first
annular wall portion 411 and the lower surface 21b of the stator
21, or a lower surface 423a of the plane portion 423 of the second
flow passage guide 420 that extends outward in the radial direction
of the first extension portion 421. Even in this case, a sealing
groove 411c into which the sealing member 430 is inserted is formed
in the upper end surface 411a of the first annular wall portion
411. Of course, the halves of the sealing groove may be formed in
the upper end surface 411a of the first annular wall portion 411
and the lower surface 21b of the stator 21 (or the lower surface
423a of the plane portion 423 of the second flow passage guide
420), respectively.
[0143] As described above, even in a case where the sealing member
430 is installed between the upper end surface 411a of the first
annular wall portion 411 and the lower surface 21b of the stator 21
(or the lower surface 423a of the plane portion 423 of the second
flow passage guide 420), basic configuration of the first annular
wall portion and the second annular wall portion, and the second
flow passage guide that corresponds to the first annular wall
portion and the second annular wall portion, and effects that
results from the basic configurations are similar to those in the
embodiments described above. However, in the present embodiment,
not only is the staying of the oil between the first annular wall
portion 411 and the first extension portion 421 minimized, but the
oil is also prevented from being introduced inward from the first
annular wall portion 411 due to a machine error or vibration.
[0144] Furthermore, the first flow passage guide that makes up the
flow passage separation unit may be integrally combined with the
frame in a manner that extends from the frame, and at the same
time, may be formed to be combined with the extension portion of
the second flow passage guide, without being separately
manufactured and assembled.
[0145] For example, as illustrated in FIG. 9B, the second annular
wall portion 412 is formed to extend from the upper surface 31a of
the frame 21, and the first extension portion 421 of the second
flow passage guide 420 is formed to have a long length. The sealing
member may be installed between a lower end surface 421 of the
first extension portion 421 and the upper surface 31a of the frame
31 with which the lower end surface 421c of the first extension
portion 421 comes into contact. In this case, sealing grooves 421
and 311d in which the sealing member 430 is inserted are formed in
the lower end surface 421c of the first extension portion 421 and
the upper surface 31a of the frame 31, respectively. Of course, the
sealing groove may be formed in any one of the lower end surface
421c of the first extension portion 421 and the upper surface 31a
of the frame 31.
[0146] As described above, even in a case where the sealing member
430 is installed between the lower end surface 421c of the first
extension portion 421 and the upper surface 31a of the frame 31,
basic configurations of the second extension portion 422 including
the first extension portion 421, and the second annular wall
portion 412 and effects that results from the basic configurations
are similar to those in the embodiments described above. However,
in the present embodiment, not only does the first extension
portion 421 play the role of the first annular wall portion 411
concurrently, but the second annular wall portion 412 is also
integrally combined with the frame 31 in a manner that extends from
the frame 31. As a result, flow resistance of the refrigerant is
reduced. Furthermore, a structure of the flow passage separation
unit is simplified thereby saving a manufacturing cost.
[0147] On the other hand, in addition to the flow passage
separation unit according to the present embodiment, a flow passage
separation unit according to another embodiment is as follows.
[0148] That is, in the embodiment described above, a separate
sealing member is used to provide tight sealing between the first
flow passage guide and the second flow passage guide, but in the
present embodiment, only with the first flow passage guide or the
second flow passage guide, the refrigerant flow passage and the oil
passage flow passage are tightly separated.
[0149] For example, as illustrated in FIG. 10A, stepped portions
411d and 421d may be formed on the upper end surface 411a of the
first annular wall portion 411 and the lower end surface 421c of
the first extension portion 421, prospectively, and may be combined
with each other in a stair-stepped manner. Alternatively, as
illustrated in FIG. 10B, the upper end surface 411a and the lower
end surface 421c may be combined with each other in a manner that
engages a protrusion 411e and a groove 421e with each other. When
this is done, a sealing area between the upper end surface 411a of
the first annular wall portion 411 and the lower end surface 421c
of the first extension portion 421 is increased and thus both the
paths are tightly separated.
[0150] Furthermore, as illustrated in FIG. 10C, the inner
circumferential surface 411b of the first annular wall portion 411
and the outer circumferential surface 421a of the first extension
portion 421 may be formed in a position where interference with
each other takes place. Thus, the inner circumferential surface
411b of the first annular wall portion 411 and the outer
circumferential surface 421a of the first extension portion 421 are
forcefully brought into contact tightly with each other and thus
both the paths can be tightly separated.
[0151] Furthermore, as illustrated in FIG. 10D, a hook protrusion
411f and a hook groove 421d may be formed on the inner
circumferential surface 411b of the first annular wall portion 411
and the outer circumferential surface 421a of the first extension
portion 421, respectively, and may be combined with each other in a
hooked manner. Thus, the inner circumferential surface 411b of the
first annular wall portion 411 and the outer circumferential
surface 421a of the first extension portion 421 are combined each
other and thus both the paths can be separated more tightly.
[0152] Furthermore, as illustrated in FIG. 10E, the first extension
portion 421 further extends without separately manufacturing and
assembling the first flow passage guide, and thus a lower end 421c
of the first extension portion 421 is inserted into a sealing
groove 311d that is provided in the upper surface 31a of the frame
31. Thus, both the paths can be more tightly. In this case, the
first extension portion 421 described above extends to take place
of the first annular wall portion, and on the other hand, the
second annular wall portion 412 is formed to be integrally combined
with the fame 31 in such a manner as to extend from the upper
surface 31a of the frame 31. Furthermore, although not illustrated
in the drawings, the first annular wall portion 411 may extend so
much that the first annular wall portion is inserted into a lower
surface of the second flow passage guide 420.
[0153] The flow of the refrigerant and the oil in the scroll
compressor according to the present invention is described as
follows.
[0154] That is, as illustrated in FIG. 11, the internal space in
the case 10 is divided into three spaces, that is, a first space
10a between the lower surface of the electric motor 20 and the
upper surface of the compression unit 30, a second space 10b that
is a space over the electric motor 20, and a third space 10c that
is a space under the compression unit 30, which serves as a free
space.
[0155] Then, the first space 10a is further divided by the flow
passage separation unit 40 into the internal refrigerant flow space
A1 and the external oil flow space A2. The refrigerant flow space
A1 communicates with the first refrigerant flow passage PG1 and the
second refrigerant flow passage PG2. The oil flow space A2
communicates the first oil flow passage PO1 and the second oil flow
passage PO2.
[0156] Thus, the refrigerant (indicated by a dotted-line arrow)
that is discharged from the compression unit 30 into the internal
space in the discharge cover 34 flows into the refrigerant flow
space A1 of the first space 10a along the first refrigerant flow
passage PG1. Then, the refrigerant flows by the flow passage
separation unit 40 into the second space 10b along the second
refrigerant flow passage PG2. At this time, the second annular wall
portion 412 of the first flow passage guide 410 that makes up the
oil separation unit 40 is further divided into the first
refrigerant flow space A1l and the second refrigerant flow space
A12, and thus the refrigerant is prevented from being introduced
into a space the falls within a rotation shaft range of the balance
weight 26. Thus, the balance weight 26 is prevented in advance from
agitating the refrigerant.
[0157] On the other hand, the oil is included in the refrigerant
that flows into the second space 10b is separated from the
refrigerant while the refrigerant circulates in the second space
10b. The refrigerant from which the oil is separated is discharged
to the outside of the compressor through the refrigerant discharge
pipe 16, and on the other hand, the oil that is separated from the
refrigerant (indicated by a solid-line arrow) flows down along the
first oil flow passage PO1 that is formed in the outer
circumferential surface of the stator 21.
[0158] Then, the oil that flows down along the first oil flow
passage PO1 does not flow by the flow passage separation unit 40
from the first space 10a into the internal space. Instead, the oil,
as is, flows into the third space 10c along the second oil flow
passage PO2 and collects. Thus, the oil that is separated in the
second space 10b that is the oil separation space quickly flows
into the third space 10c that is the oil storage space. Thus, an
oil shortage in the compressor can be prevented in advance.
Particularly, the sealing member 430 is provided on the oil
separation unit 40, or the sealing area is enlarged. As a result,
the internal space and the external space in the first space 10a
are tightly separated. Thus, the refrigerant that is discharged
into the first space 10a is suppressed from being introducing into
the oil flow passages PO1 and PO2, thereby increasing the oil
collection effect.
[0159] The foregoing embodiments and advantages are merely
exemplary and are not to be considered as limiting the present
disclosure. The present teachings can be readily applied to other
types of apparatuses. This description is intended to be
illustrative, and not to limit the scope of the claims. Many
alternatives, modifications, and variations will be apparent to
those skilled in the art. The features, structures, methods, and
other characteristics of the exemplary embodiments described herein
may be combined in various ways to obtain additional and/or
alternative exemplary embodiments.
[0160] As the present features may be embodied in several forms
without departing from the characteristics thereof, it should also
be understood that the above-described embodiments are not limited
by any of the details of the foregoing description, unless
otherwise specified, but rather should be considered broadly within
its scope as defined in the appended claims, and therefore all
changes and modifications that fall within the metes and bounds of
the claims, or equivalents of such metes and bounds are therefore
intended to be embraced by the appended claims.
* * * * *