U.S. patent application number 15/740195 was filed with the patent office on 2018-07-05 for scroll compressor.
The applicant listed for this patent is SANDEN AUTOMOTIVE COMPONENTS CORPORATION. Invention is credited to Sozaburo ASAKAWA, Hiroshi FUJITA, Tomokazu MIYAJI, Masayuki NOBE, Tatsuki NOMURA.
Application Number | 20180187679 15/740195 |
Document ID | / |
Family ID | 57608560 |
Filed Date | 2018-07-05 |
United States Patent
Application |
20180187679 |
Kind Code |
A1 |
NOMURA; Tatsuki ; et
al. |
July 5, 2018 |
SCROLL COMPRESSOR
Abstract
A scroll compressor 1 includes: a scroll unit 6; a crank
mechanism 44; a housing 2, 4 in which the scroll unit 6 is
accommodated and which has a suction port 22 of refrigerant
provided in an outer peripheral wall 2b located on the outer
peripheral side of the scroll unit 6; and a sealing device 30 which
seals between the housing 2, 4 and a rotary shaft 24, wherein the
housing 2, 4 includes: a crank chamber 48 in which the crank
mechanism 44 is positioned; a seal chamber 50 in which the sealing
device 30 is positioned; a communication hole 52, 58 which
communicates the crank chamber 48 with the seal chamber 50; and a
first guide groove 54 which extends from an opening of the
communication hole 52, 58 in the seal chamber 50 to the vicinity of
the sealing device 30.
Inventors: |
NOMURA; Tatsuki;
(Isesaki-shi, JP) ; FUJITA; Hiroshi; (Isesaki-shi,
JP) ; ASAKAWA; Sozaburo; (Isesaki-shi, JP) ;
NOBE; Masayuki; (Isesaki-shi, JP) ; MIYAJI;
Tomokazu; (Isesaki-shi, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
SANDEN AUTOMOTIVE COMPONENTS CORPORATION |
Isesaki-shi |
|
JP |
|
|
Family ID: |
57608560 |
Appl. No.: |
15/740195 |
Filed: |
June 3, 2016 |
PCT Filed: |
June 3, 2016 |
PCT NO: |
PCT/JP2016/066651 |
371 Date: |
December 27, 2017 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04C 2240/50 20130101;
F04C 29/021 20130101; F04C 18/07 20130101; F04C 29/028 20130101;
F04C 2240/808 20130101; F04C 2240/807 20130101; F04C 18/0215
20130101; F04C 27/009 20130101; F04C 29/0057 20130101 |
International
Class: |
F04C 18/07 20060101
F04C018/07; F04C 29/02 20060101 F04C029/02; F04C 27/00 20060101
F04C027/00; F04C 29/00 20060101 F04C029/00 |
Foreign Application Data
Date |
Code |
Application Number |
Jul 1, 2015 |
JP |
2015-132670 |
Claims
1. A scroll compressor, comprising: a scroll unit for compressing a
refrigerant by orbiting of a movable scroll relative to a fixed
scroll; a crank mechanism for converting rotary motion of a rotary
shaft into orbiting motion of the movable scroll and transferring
the orbiting motion; a housing for accommodating the scroll unit,
the housing including a suction port of the refrigerant on an outer
peripheral wall located on an outer peripheral side of the scroll
unit; and a sealing device for sealing between the housing and the
rotary shaft, wherein the housing includes: a crank chamber in
which the crank mechanism is positioned, a seal chamber in which
the sealing device is positioned, a communication hole for
communicating the crank chamber with the seal chamber, and a first
guide groove extending from an opening of the communication hole in
the seal chamber to a vicinity of the sealing device, and wherein
the crank mechanism includes a counterweight attached to the rotary
shaft, and the communication hole is formed at a position which is
intermittently covered with the counterweight as the counterweight
circles.
2. The scroll compressor according to claim 1, wherein the housing
further includes a second guide groove in which an opening of the
communication hole in the crank chamber is positioned.
3. (canceled)
4. The scroll compressor according to claim 1, wherein the
communication hole is inclined along a circling direction of the
counterweight with respect to a radial direction of the rotary
shaft.
5. The scroll compressor according to claim 1, wherein the
counterweight has an inclined surface inclined with respect to an
axis of the rotary shaft.
6. The scroll compressor according to claim 1, wherein the
counterweight has a stepped surface protruding in a radial
direction of the rotary shaft.
Description
TECHNICAL FIELD
[0001] The present invention relates to a scroll compressor, and
particularly to a scroll compressor for use in a refrigeration
circuit of an air conditioner for vehicles.
BACKGROUND ART
[0002] Patent Document 1 discloses a scroll compressor including: a
fixed scroll and a movable scroll accommodated in a housing, the
housing supporting a rotary shaft via a bearing; and a shaft seal
mechanism fitted between the rotary shaft and the housing, in which
a communication passage for communicating the seal chamber with the
side of a suction chamber of refrigerant is formed as lubricating
means of the shaft seal mechanism.
PRIOR ART DOCUMENT
Patent Document
[0003] Patent Document 1: Japanese Patent No. 2868998
SUMMARY OF THE INVENTION
Problems to be Solved by the Invention
[0004] When a compressor has a structure in which a suction port is
provided on an outer peripheral side of a scroll unit in an outer
peripheral wall of a housing, since a refrigerant introduced from
the suction port can be immediately sucked into the scroll unit,
improvement of compression efficiency of the refrigerant can be
expected. On the other hand, in the compressor having such a
structure, the flow rate of the refrigerant flowing into a portion
apart from the suction port in the housing is reduced and thus,
particularly, deterioration of lubrication of a shaft seal
mechanism or a lip seal which is a sealing device, has
conventionally been a concern.
[0005] In a case such as Patent Document 1, in which a
communication passage for communicating the seal chamber with the
side of the suction chamber of refrigerant is simply formed, the
communication passage will become long when the lip seal is away
from the suction port, making it difficult to sufficiently supply
lubricating oil to the lip seal.
[0006] The present invention has been made in view of the
above-mentioned problems, and has its object to provide a scroll
compressor which allows to significantly reduce wear of the sealing
device while enhancing the compression efficiency of the compressor
by actively guiding lubricating oil to the sealing device and, by
extension, ensures a residual fastening margin of the sealing
device with respect to the rotary shaft, thereby maintaining the
sealing performance of the compressor over a long period of
time.
Means for Solving the Problems
[0007] In order to achieve the above described object, a scroll
compressor of the present invention includes: a scroll unit for
compressing a refrigerant by orbiting of a movable scroll relative
to a fixed scroll; a crank mechanism for converting rotary motion
of a rotary shaft into orbiting motion of the movable scroll and
transferring the orbiting motion; a housing for accommodating the
scroll unit, the housing including a suction port of the
refrigerant on an outer peripheral wall located on an outer
peripheral side of the scroll unit; and a sealing device for
sealing between the housing and the rotary shaft, wherein the
housing includes: a crank chamber in which the crank mechanism is
positioned, a seal chamber in which the sealing device is
positioned, a communication hole for communicating the crank
chamber with the seal chamber, and a first guide groove extending
from an opening of the communication hole in the seal chamber to a
vicinity of the sealing device.
[0008] Preferably, the housing further includes a second guide
groove in which an opening of the communication hole in the crank
chamber is positioned.
[0009] Preferably, the crank mechanism includes a counterweight
attached to the rotary shaft, and the communication hole is formed
at a position which is intermittently covered by the counterweight
as the counterweight circles.
[0010] Preferably, the communication hole is inclined along a
circling direction of the counterweight with respect to a radial
direction of the rotary shaft.
[0011] Preferably, the counterweight has an inclined surface
inclined with respect to an axis of the rotary shaft.
[0012] Preferably, the counterweight has a stepped surface
protruding in a radial direction of the rotary shaft.
Advantageous Effects of the Invention
[0013] According to the scroll compressor of the present invention,
it is possible to significantly reduce wear of the sealing device
while enhancing the compression efficiency of the compressor by
actively guiding lubricating oil to the sealing device and, by
extension, ensure a residual fastening margin of the sealing device
with respect to the rotary shaft, thereby maintaining the sealing
performance of the compressor over a long period of time.
BRIEF DESCRIPTION OF THE DRAWINGS
[0014] FIG. 1 is a vertical cross-sectional view of a scroll
compressor according to a first embodiment of the present
invention.
[0015] FIG. 2 is a vertical cross-sectional view of a scroll
compressor with parts of the crank chamber and the seal chamber of
FIG. 1 being enlarged.
[0016] FIG. 3 is a plan view of the front housing of FIG. 1 as
viewed from its opening end side.
[0017] FIG. 4 is a plan view showing a variant of FIG. 3.
[0018] FIG. 5 is a plan view showing a further variant of FIG.
3.
[0019] FIG. 6 is a vertical cross-sectional view of a scroll
compressor with parts of the crank chamber and the seal chamber
according to the second embodiment of the present invention being
enlarged.
[0020] FIG. 7 is a plan view of the front housing of FIG. 6 as
viewed from its opening end side.
[0021] FIG. 8 is a plan view of a front housing according to a
third embodiment of the present invention as viewed from its
opening end side.
[0022] FIG. 9 is a side view showing a counterweight according to a
fourth embodiment of the present invention, with the counterweight
being mounted on a rotary shaft.
[0023] FIG. 10 is a side view showing a variant of FIG. 9.
[0024] FIG. 11 is a side view illustrating a further variant of
FIG. 9.
MODE FOR CARRYING OUT THE INVENTION
[0025] Hereinafter, each embodiment of the present invention will
be described based on the drawings.
First Embodiment
[0026] FIG. 1 is a vertical cross-sectional view of a scroll
compressor 1 according to a first embodiment of the present
invention. This compressor 1 is incorporated, for example, in a
refrigeration circuit of a vehicle air-conditioner mounted on a
vehicle and is used for compressing refrigerant circulating in a
refrigeration circuit.
[0027] The compressor 1 includes a rear housing (housing) 2 and a
front housing (housing) 4, and a scroll unit 6 is disposed in the
rear housing 2. The scroll unit 6 is made up of a fixed scroll 8
fixed to the rear housing 2, and a movable scroll 10 assembled so
as to engage with the fixed scroll 8. The fixed scroll 8 includes
an end plate 8a, and a fixed spiral body 8b integrally formed with
the end plate 8a, and the movable scroll 10 includes an end plate
10a, and a movable spiral body 10b integrally molded with the end
plate 10a, and the fixed spiral body 8b and the movable spiral body
10b are engaged with each other.
[0028] An ejection chamber 12 is formed between an end wall 2a of
the rear housing 2 and the fixed scroll 8 in the rear housing 2.
This ejection chamber 12 can communicate an ejection hole 14 formed
in the end plate 8a of the fixed scroll 8 with a compression
chamber 18 formed between the fixed scroll 8 and the movable scroll
10 via an ejection valve 16 of a reed valve type. In the outer
peripheral wall 2b of the rear housing 2, an ejection port 20 is
formed at a position proximal to the end wall 2a, and the ejection
chamber 12 is communicated with a refrigerant circulation passage
of the refrigeration circuit via the ejection port 20.
[0029] Moreover, a suction port 22 of the refrigerant is provided
on the outer peripheral side of the scroll unit 6 in the outer
peripheral wall 2b of the rear housing 2, and the refrigerant
introduced via the suction port 22 from the refrigerant circulation
passage is quickly sucked into the scroll unit 6.
[0030] On the other hand, the rotary shaft 24 is disposed in the
front housing 4, and the rotary shaft 24 has a large-diameter shaft
part 24a and a small-diameter shaft part 24b. Moreover, a
large-diameter inner peripheral surface 4b, an
intermediate-diameter inner peripheral surface 4c, and a
small-diameter inner peripheral surface 4d are formed in the order
from an opening end 4a located on the rear housing 2 side in the
front housing 4 by stepwisely reducing the diameter of the inner
periphery thereof.
[0031] A large-diameter shaft part 24a is rotatably supported on an
intermediate-diameter inner peripheral surface 4c of the front
housing 4 via a bearing 26 which is a needle bearing, and the
small-diameter shaft part 24b is rotatably supported on the
small-diameter inner peripheral surface 4d of the front housing 4
via a bearing 28 which is a ball bearing. Moreover, a lip seal
(sealing device) 30 is disposed between the small-diameter shaft
part 24b and the small-diameter inner peripheral surface 4d of the
front housing 4. The outer periphery side of the lip seal 30 is
mounted to the small-diameter inner peripheral surface 4d, and
functions as a sealing device by the lip part located on the inner
periphery side coming into contact with the small-diameter shaft
part 24b during rotation, to partition the inside of the front
housing 4 in an airtight manner.
[0032] The small-diameter shaft part 24b of the rotary shaft 24
protrudes from the front housing 4, and this protruding end is
interconnected with a drive pulley 32 having an electromagnetic
clutch built-in. The drive pulley 32 is rotatably supported on the
front housing 4 via a bearing 34 which is a ball bearing. The drive
pulley 32 is connected to an output pulley on the side of the
engine of the vehicle via a belt, and receives the power of the
engine, thereby being rotated.
[0033] On the other hand, a crankpin 24c is protruded toward the
movable scroll 10 from the large-diameter shaft part 24a of the
rotary shaft 24. The crankpin 24c, which is provided at a position
eccentric from the axial center of the rotary shaft 24, is inserted
and fitted into a crankpin hole 38 drilled in an eccentric bush 36.
The crankpin 24c supports the eccentric bush 36 by its base end
part 24c1. Moreover, the eccentric bush 36 supports a boss 41 of
the movable scroll 10 via a bearing 40 which is a needle
bearing.
[0034] Moreover, a counterweight 42 is attached to the crankpin 24c
so as to be interposed between the eccentric bush 36 and the
large-diameter shaft part 24a. The counterweight 42, which is made
up by superposing a plurality of large and small arc-shaped plates
42a in an axial direction of the rotary shaft 24, cancels
centrifugal force acting on the rotary shaft 24 as the movable
scroll 10 orbits, thereby balancing the orbiting of the movable
scroll 10.
[0035] In this way, a crank mechanism 44 which converts rotary
motion of the rotary shaft 24 into orbiting motion of the movable
scroll 10 and transfers the orbiting motion, is made up of the
above described crankpin 24c, eccentric bush 36, boss 41, and
counterweight 42.
[0036] Moreover, a rotation prevention mechanism 46 of a ball
coupling type is disposed between an end plate 10a of the movable
scroll 10 and an opening end 4a of the front housing 4. The
rotation prevention mechanism 46 prevents the rotation of the
movable scroll 10 without hindering the orbiting motion of the
movable scroll 10 with respect to the fixed scroll 8.
[0037] In the compressor 1 as thus configured, when an
electromagnetic clutch in the drive pulley 32 is ON-operated during
driving of engine, and the rotary shaft 24 is rotated together with
the drive pulley 32, the eccentric bush 36 into which the crankpin
24c is fitted rotates. As a result, orbiting motion is imparted to
the movable scroll 10 via the boss 41 with rotation being prevented
by the rotation prevention mechanism 46.
[0038] When the movable scroll 10 undergoes orbiting motion with
respect to the fixed scroll 8, the refrigerant sucked from the
refrigerant circulation passage via the suction port 22 is
introduced into the scroll unit 6, and the fixed scroll 8 and the
movable scroll 10 cooperate. As a result, a compression chamber 18
of refrigerant including lubricating oil is partitioned and formed
between the fixed spiral body 8b and the movable spiral body 10b.
In the compression chamber 18, the volume thereof is reduced while
the movable spiral body 10b is moved toward the center of the fixed
spiral body 8b by the orbiting motion of the movable scroll 10 with
respect to the fixed scroll 8, and thus the refrigerant is
compressed. The compressed refrigerant is ejected to the ejection
chamber 12 via the ejection hole 14, and fed to the refrigerant
circulation passage from the ejection port 20.
[0039] Here, a crank chamber 48 is partitioned inside a
large-diameter inner peripheral surface 4b in the front housing 4.
The crank chamber 48 is a space in the front housing 4, in which
the crank mechanism 44 is positioned, and smooth orbiting of the
counterweight 42 is allowed as the rotary shaft 24 rotates.
Further, in the crank chamber 48, an annulus-shaped base surface
48a which substantially intersects at right angles with the axis of
the rotary shaft 24 is formed as a stepped surface between the
large-diameter inner peripheral surface 4b and the
intermediate-diameter inner peripheral surface 4c of the front
housing 4, and an arc-shaped plate 42a of the counterweight 42 is
positioned in proximity to the base surface 48a.
[0040] On the other hand, in the front housing 4, a seal chamber 50
is partitioned from inner side of the intermediate-diameter inner
peripheral surface 4c to the inner side of the small-diameter inner
peripheral surface 4d. The seal chamber 50 is a space in which a
lip part of the lip seal 30 is positioned, and an annulus-shaped
base surface 50a which substantially intersects at right angles
with the axis of the rotary shaft 24 is formed as a stepped surface
between the intermediate-diameter inner peripheral surface 4c and
the small-diameter inner peripheral surface 4d of the front housing
4, and a bearing 26 mounted to the intermediate-diameter inner
peripheral surface 4c is positioned in proximity to the base
surface 50a.
[0041] FIG. 2 is an enlarged cross-sectional view of parts of the
crank chamber 48 and the seal chamber 50, and FIG. 3 is a plan view
of the front housing 4 as viewed from the opening end 4a side
thereof. As shown in FIGS. 2 and 3, in the present embodiment, two
communication holes 52 which communicate the crank chamber 48 with
the seal chamber 50 are penetrated through in the front housing 4
at symmetric positions on one diagonal line interposing the rotary
shaft 24. Each communication hole 52 is formed at a position to
extend linearly inclined with respect to the axis of the rotary
shaft 24 and along the radial direction of the rotary shaft 24, to
be opened in the base surface 48a in the crank chamber 48, and to
be intermittently covered by the arc-shaped plate 42a as the
counterweight 42 circles.
[0042] On the other hand, in the seal chamber 50, each
communication hole 52 is opened in the vicinity of the base surface
50a of the intermediate-diameter inner peripheral surface 4c. The
openings on the crank chamber 48 side and the seal chamber 50 side
of each communication hole 52 are substantially positioned on a
diameter line of the rotary shaft 24. Further, a guide groove
(first guide groove) 54 is concaved from the communication hole 52
opened in the intermediate-diameter inner peripheral surface 4c to
the vicinity of the lip part of the lip seal 30 in the base surface
50a which is an inner wall of the seal chamber 50. The guide groove
54, which is formed so as to have a bottom which is inclined in an
arc shape with respect to the axis of the rotary shaft 24, extends
linearly along the radial direction of the rotary shaft 24 from the
communication hole 52 opened in the intermediate-diameter inner
peripheral surface 4c to the vicinity of the lip part of the lip
seal 30.
[0043] Here, when the refrigerant flows from the suction port 22
toward the compression chamber 18 side as the movable scroll 10
undergoes orbiting motion, refrigerant including lubricating oil
will also flow to the back surface 10c side of the end plate 10a of
the movable scroll 10. Moreover, the lubricating oil which has
flown into the crank chamber 48 with the refrigerant lubricates the
rotation prevention mechanism 46, the bearing 40, the bearing 26,
and the lip seal 30.
[0044] Specifically, as shown by solid arrows in FIGS. 2 and 3, the
refrigerant that has flown into the crank chamber 48 is temporarily
compressed in a minute gap formed between the arc-shaped plate 42a
and the base surface 48a proximal to the arc-shaped plate 42a as a
result of the counterweight 42 circling in the two-dot-chain line
arrow direction. The refrigerant that has been compressed in the
crank chamber 48 is pushed out by differential pressure from the
communication hole 52 into the seal chamber 50 in which pressure
will be lower.
[0045] The refrigerant that has flown into seal chamber 50 from the
crank chamber 48 through the communication hole 52 is guided to the
lip seal 30 passing through the guide groove 54, and in this
occasion, the lip seal 30 is appropriately lubricated by the
lubricating oil contained in the refrigerant. On the other hand, as
shown by a broken line in FIGS. 2 and 3, the refrigerant that has
flown into the seal chamber 50 is returned to the crank chamber 48
through the bearing 26, and in that occasion, the bearing 26 is
appropriately lubricated by the lubricating oil contained in the
refrigerant. Thus, a lubricating oil recirculation passage is
formed between the crank chamber 48 and the seal chamber 50.
[0046] As so far described, according to the present embodiment, in
the case of a structure in which a suction port 22 is provided on
the outer peripheral side of the scroll unit 6 as in the compressor
1, since the refrigerant introduced from the suction port 22 will
be able to be sucked into the scroll unit 6 immediately,
improvement in compression efficiency of refrigerant can be
expected. On the other hand, in the compressor 1 of such a
structure, the flow rate of the refrigerant flowing into a portion
apart from the suction port 22 in the front housing 4 is reduced,
and in particular, deterioration of lubrication of the lip seal 30
has conventionally been a concern.
[0047] Even in such a case, as a result of forming the
communication hole 52 and the guide groove 54 in the front housing
4, thereby forming a lubricating oil circulation passage between
the crank chamber 48 and the seal chamber 50, it is made possible
to actively guide the lubricating oil to the lip seal 30.
Therefore, it is possible to significantly reduce wear of the lip
seal 30 while improving compression efficiency of the compressor 1,
and by extension, to ensure a residual fastening margin of the lip
seal 30 with respect to the small-diameter shaft part 24b, thereby
maintaining the sealing performance of the compressor 1 over a long
period of time. Note that the numbers of the communication hole 52
and the guide grooves 54 are not particularly limited, and for
example, as shown in FIG. 4, two sets of the communication hole 52
and the guide groove 54 may be formed at symmetrical positions
interposing the rotary shaft 24 on the two diagonal lines, or as
shown in FIG. 5, only one set of the communication hole 52 and the
guide groove 54 may be formed.
Second Embodiment
[0048] FIG. 6 is an enlarged cross-sectional view of parts of the
crank chamber 48 and the seal chamber 50 according to a second
embodiment of the present invention, and FIG. 7 is a plan view of
the front housing 4 of FIG. 6 as viewed from its opening end 4a
side. Note that regarding the same components as those of the first
embodiment, description thereof may be omitted by giving them the
same names and the reference symbols in the specification or the
drawings.
[0049] As shown in FIGS. 6 and 7, in the base surface 48a of the
front housing 4 of the present embodiment, two guide grooves
(second guide grooves) 56 are concaved at positions interposing the
rotary shaft 24 on the same diagonal line as that with the guide
groove 54 of the base surface 50a. Each guide groove 56 extends
linearly along the radial direction of the rotary shaft 24 from the
vicinity of the large-diameter inner peripheral surface 4b to the
vicinity of the intermediate-diameter inner peripheral surface 4c,
and the communication hole 52 is formed in the bottom of the guide
groove 56.
[0050] Thus, in the present embodiment, as a result of forming the
guide groove 56 similar to the guide groove 54 of the base surface
50a at the opening position of the communication hole 52 in the
base surface 48a, it is possible to effectively guide the
lubricating oil adhered to the base surface 48a from the guide
groove 56 to the communication hole 52, as shown by solid arrows in
FIGS. 6 and 7, thus further actively guiding the lubricating oil to
the lip seal 30. Therefore, it is possible to realize significant
reduction of wear of the lip seal 30 and ensure a residual
fastening margin of the lip seal 30 while improving the compression
efficiency of the compressor 1, thereby maintaining the sealing
performance of the compressor 1 over a long period of time.
Third Embodiment
[0051] FIG. 8 is a plan view of a front housing 4 according to a
third embodiment of the present invention as viewed from its
opening end 4a side. Note that the present embodiment will be
described as a variant of FIG. 5 shown in the first embodiment, and
regarding the same components as those of the first embodiment,
description thereof may be omitted by giving them the same names
and the reference symbols in the specification or the drawings.
[0052] As shown in FIG. 8, a communication hole 58 that
communicates the crank chamber 48 with the seal chamber 50 is
formed in the front housing 4. This communication hole 58 extends
linearly inclined with respect to both the axis and radial
directions of the rotary shaft 24 as shown by broken lines.
Inclination with respect to the radial direction of the rotary
shaft 24 is the direction along the circling direction of the
counterweight 42. That is, the openings of the crank chamber 48
side and the seal chamber 50 side of the communication hole 58 are
positioned included with respect to the diameter line of the rotary
shaft 24.
[0053] Thus, in the present embodiment, as a result of forming a
communication hole 58 having a different shape from those of the
communication holes 52 of the first and second embodiments, as
shown solid arrows in FIG. 8, it is possible to guide lubricating
oil to the lip seal 30 further effectively and quickly by
exploiting force in the circling direction of the counterweight 42
which acts on the refrigerant and the lubricating oil which have
flown into the communication hole 58. Therefore, it is possible to
realize significant reduction of wear of the lip seal 30 and ensure
a residual fastening margin of the lip seal 30 while improving the
compression efficiency of the compressor 1, thereby maintaining the
sealing performance of the compressor 1 over a long period of
time.
Fourth Embodiment
[0054] FIG. 9 is a side view showing a counterweight 60 according
to a fourth embodiment of the present invention in a state of being
mounted to the rotary shaft 24. Note that regarding the same
components as those of any of the first to the third embodiments,
description thereof may be omitted by giving them the same names
and the reference symbols in the specification or the drawings.
[0055] As shown in FIG. 9, the counterweight 60 of the present
embodiment is configured such that a radial end surface 60a1 of
each arc-shaped plate 60a is inclined with respect to the axis of
the rotary shaft 24 and forms a flush inclined surface 62. This
inclined surface 62, which is inclined in a closing direction to
the axis from the crankpin 24c side toward the large-diameter shaft
part 24a, guides the lubricating oil adhered to the radial end
surface 60a1 of each arc-shaped plate 60a toward the communication
hole 52 or the communication hole 58 as shown solid arrows, as the
counterweight 60 circles.
[0056] As a result of the counterweight 60 being provided with the
inclined surface 62 in the present embodiment, it is possible to
effectively guide the lubricating oil adhered to the radial end
surface 60a1 of each arc-shaped plate 60a into the communication
hole 52 or the communication hole 58, and more actively guide the
lubricating oil to the lip seal 30. Therefore, it is possible to
realize significant reduction of wear of the lip seal 30 and ensure
a residual fastening margin of the lip seal 30 while improving the
compression efficiency of the compressor 1, thereby maintaining the
sealing performance of the compressor 1 over a long period of
time.
[0057] Note that, without being limited to the above described one,
for example as shown in FIG. 10, an inclined surface 64 in which
only the radial end surface 60a1 of the arc-shaped plate 60a
closest to the large-diameter shaft part 24a is inclined may be
formed. Moreover, as shown in FIG. 11, a stepped surface 66 may be
formed from the radial end surface 60a1 of each arc-shaped plate
60a by causing one of the each arc-shaped plate 60a to protrude in
the radial direction of the rotary shaft 24. In such cases, as
shown by solid arrows in FIGS. 10 and 11, it is possible to
effectively guide the lubricating oil adhered to the counterweight
60 to flow or drip into the communication hole 52 or the
communication hole 58.
[0058] The present invention will not be limited to each embodiment
described above, and various modifications can be made thereto.
[0059] For example, in each embodiment described above, an
engine-driven scroll compressor 1 which is incorporated in an air
conditioner for vehicles has been described. However, the present
invention can be applied to integrated electric-motor-driven scroll
compressors and general scroll compressors in various fields which
use various working fluids.
Explanation of Reference Signs
[0060] 1 Scroll compressor [0061] 2 Rear housing (housing) [0062]
2b Outer peripheral wall [0063] 4 Front housing (housing) [0064] 6
Scroll unit [0065] 8 Fixed scroll [0066] 10 Movable scroll [0067]
22 Suction port [0068] 24 Rotary shaft [0069] 30 Lip seal (sealing
device) [0070] 42, 60 Counterweight [0071] 44 Crank mechanism
[0072] 48 Crank chamber [0073] 50 Seal chamber [0074] 52
Communication hole [0075] 54 Guide groove (first guide groove)
[0076] 56 Guide groove (second guide groove) [0077] 62, 64 Inclined
surface [0078] 66 Stepped surface
* * * * *