U.S. patent application number 15/442905 was filed with the patent office on 2017-10-05 for compressor.
This patent application is currently assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI. The applicant listed for this patent is KABUSHIKI KAISHA TOYOTA JIDOSHOKKI. Invention is credited to Yuya HATTORI, Kunihisa MATSUDA, Tatsushi MORI, Hiroki NAGANO.
Application Number | 20170284397 15/442905 |
Document ID | / |
Family ID | 59886072 |
Filed Date | 2017-10-05 |
United States Patent
Application |
20170284397 |
Kind Code |
A1 |
NAGANO; Hiroki ; et
al. |
October 5, 2017 |
COMPRESSOR
Abstract
A compressor according to the present invention includes an oil
separation mechanism and an oil supply mechanism. The oil
separation mechanism includes an oil separation chamber and an oil
drain path. The oil supply mechanism includes an oil supply port.
The oil drain path includes a first flow path formed by penetrating
a second partition of a housing and configured to open toward a
first partition of a housing from the oil separation chamber, and a
second flow path recessed in at least one of the first partition
and the second partition and formed by the cooperation of the first
partition and the second partition so as to get communicated with
the first flow path. An outlet of the second flow path is located
at a higher level in a vertical direction than an inlet of the
second flow path while avoiding a direction facing the oil supply
port.
Inventors: |
NAGANO; Hiroki; (Kariya-shi,
JP) ; MATSUDA; Kunihisa; (Kariya-shi, JP) ;
HATTORI; Yuya; (Kariya-shi, JP) ; MORI; Tatsushi;
(Kariya-shi, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
KABUSHIKI KAISHA TOYOTA JIDOSHOKKI |
Kariya-shi |
|
JP |
|
|
Assignee: |
KABUSHIKI KAISHA TOYOTA
JIDOSHOKKI
Kariya-shi
JP
|
Family ID: |
59886072 |
Appl. No.: |
15/442905 |
Filed: |
February 27, 2017 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04C 29/026 20130101;
F04C 27/003 20130101; F04C 2240/20 20130101; F04C 27/008 20130101;
F04C 18/3441 20130101; F04C 2240/30 20130101 |
International
Class: |
F04C 29/02 20060101
F04C029/02; F04C 27/00 20060101 F04C027/00; F04C 18/344 20060101
F04C018/344 |
Foreign Application Data
Date |
Code |
Application Number |
Mar 30, 2016 |
JP |
2016-068499 |
Claims
1. A compressor comprising: a housing; a compression mechanism
accommodated in the housing, forming a suction chamber, a discharge
chamber, and a compression chamber in conjunction with the housing,
and adapted to suck refrigerant into the compression chamber from
the suction chamber, compress the refrigerant, and discharge the
refrigerant to the discharge chamber; an oil separation mechanism
provided in the discharge chamber and adapted to separate
lubricating oil from the refrigerant and store the lubricating oil
in the discharge chamber; and an oil supply mechanism adapted to
lead the lubricating oil in the discharge chamber to the
compression mechanism, wherein the housing comprises a housing body
provided with an inner circumferential surface extending in a
circumferential direction, a first partition provided in the
housing body and adapted to separate the compression chamber and
the discharge chamber from each other, and a second partition
coupled to the first partition and provided with the oil separation
mechanism, the oil separation mechanism comprises an oil separation
chamber formed in the second partition and adapted to separate the
lubricating oil from the refrigerant led from the compression
chamber, and an oil drain path adapted to communicate the oil
separation chamber with the discharge chamber, the oil supply
mechanism comprises an oil supply port formed in the second
partition and configured to open vertically downward to take in the
lubricating oil from the discharge chamber, the oil drain path
comprises a first flow path formed by penetrating the second
partition and configured to open toward the first partition from
the oil separation chamber and a second flow path recessed in at
least one of the first partition and the second partition and
formed by the cooperation of the first partition and the second
partition so as to be communicated with the first flow path, and an
outlet of the second flow path is located at a higher level in a
vertical direction than an inlet of the second flow path while
avoiding a direction facing the oil supply port.
2. The compressor according to claim 1, wherein the outlet of the
second flow path is placed face-to-face with the inner
circumferential surface of the housing body.
3. The compressor according to claim 1, wherein if a normal is
defined at a position where the outlet of the second flow path
comes face-to-face with the inner circumferential surface of the
housing body, the second flow path intersects the normal at an
acute angle.
4. The compressor according to claim 1, wherein: the housing
comprises a cylinder block in which a cylinder chamber is formed,
the housing body configured to surround the cylinder block, the
first partition configured to form the discharge chamber between
the cylinder block and the housing body, and the second partition;
the compression mechanism comprises a rotor installed in the
cylinder chamber rotatably around a rotational axis with a
plurality of vane grooves formed therein and vanes installed
advanceably/retractably in the respective vane grooves; the
compression mechanism forms the compression chamber defined by one
face of the cylinder chamber, an inner circumferential surface of
the cylinder chamber, another face of the cylinder chamber, an
outer circumferential surface of the rotor, and the respective
vanes; a back pressure chamber is provided between each of the
vanes and the corresponding one of the vane grooves; and the oil
supply port is communicated with the back pressure chambers through
a back pressure flow path.
5. The compressor according to claim 4, wherein the first partition
includes a side plate configured to form one face of the cylinder
chamber.
6. The compressor according to claim 4, wherein the first partition
includes a gasket.
Description
TECHNICAL FIELD
[0001] The present invention relates to a compressor.
BACKGROUND ART
[0002] A conventional vane compressor is disclosed in Japanese
Patent Laid-Open No. 7-12072. In the compressor, a cylinder block
is accommodated in a housing, and a front side plate and a rear
side plate are joined and fixed to opposite ends of the cylinder
block. An oil storage chamber, which is a discharge chamber, is
formed between the rear side plate and the housing. The rear side
plate is provided with an oil separator. The oil separator is
formed of a casing and an oil separation cylinder fixed to upper
part of an oil separation chamber formed in the casing.
[0003] In the oil separation chamber, lubricating oil is separated
from refrigerant. The refrigerant with the lubricating oil
separated therefrom is discharged from a discharge chamber to a
refrigerating circuit outside. The lubricating oil in the oil
separation chamber is stored in the oil storage chamber via an oil
drain path. The lubricating oil in the oil storage chamber is
supplied to a vane groove serving as a back pressure chamber, or a
sliding portion such as a bearing, through an oil feed passage
communicated with the oil storage chamber, where the back pressure
chamber produces back pressure to press a vane.
[0004] However, with the compressor, in which the oil drain path
interconnects the oil separation chamber and the oil storage
chamber linearly, flow velocity of the lubricating oil is less
prone to fall, and consequently when a large amount of lubricating
oil is stored in the oil storage chamber, the lubricating oil in
the oil storage chamber tends to be blown or disturbed by the
lubricating oil discharged through the oil drain path. Therefore,
the refrigerant in the discharge chamber tends to get mixed with
the lubricating oil in the oil storage chamber again, and the
lubricating oil mixed with the refrigerant tends to be supplied to
the vane groove or the bearing through an opening of the oil feed
passage. In this case, the sliding portion is not lubricated
sufficiently, which raises concerns that noise and vibration may be
produced, breaking quiet and that durability may be spoiled.
[0005] To resolve these concerns, for example, as described in
Japanese Patent Laid-Open No. 2010-31757, it is conceivable to
define a space in the casing of the oil separator in the discharge
room to store lubricating oil. In this case, it is considered that
lubricating oil drained in sequence from the oil drain path and the
separated refrigerant gas are less prone to get mixed with each
other, which will make it possible to supply lubricating oil not
mixed much with refrigerant to the vane groove and the sliding
portion and achieve higher quiet and durability.
[0006] However, if a space for use to store lubricating oil is
provided in the casing of the oil separator as described above, the
oil separator will increase in size or become troublesome in
producing. If the oil separator increases in size, volume of the
discharge chamber will decrease, making discharge pulsation liable
to occur, and the entire compressor grows in size, impairing
mountability on a vehicle or the like. Also, troublesome producing
will result in escalation of production costs.
[0007] The present invention has been made in view of the
conventional circumstances described above and an object of the
invention is to provide a compressor which can be lubricated
sufficiently, is less prone to discharge pulsation, and is capable
of achieving downsizing and production cost reductions.
SUMMARY OF THE INVENTION
[0008] A compressor according to the present invention comprises: a
housing; a compression mechanism accommodated in the housing,
forming a suction chamber, a discharge chamber, and a compression
chamber in conjunction with the housing, and adapted to suck
refrigerant into the compression chamber from the suction chamber,
compress the refrigerant, and discharge the refrigerant to the
discharge chamber; an oil separation mechanism provided in the
discharge chamber and adapted to separate lubricating oil from the
refrigerant and store the lubricating oil in the discharge chamber;
and an oil supply mechanism adapted to lead the lubricating oil in
the discharge chamber to the compression mechanism. The housing
comprises a housing body provided with an inner circumferential
surface extending in a circumferential direction, a first partition
provided in the housing body and adapted to separate the
compression chamber and the discharge chamber from each other, and
a second partition coupled to the first partition and provided with
the oil separation mechanism. The oil separation mechanism
comprises an oil separation chamber formed in the second partition
and adapted to separate the lubricating oil from the refrigerant
led from the compression chamber, and an oil drain path adapted to
communicate the oil separation chamber with the discharge chamber.
The oil supply mechanism comprises an oil supply port formed in the
second partition and configured to open vertically downward to take
in the lubricating oil from the discharge chamber. The oil drain
path comprises a first flow path formed by penetrating the second
partition and configured to open toward the first partition from
the oil separation chamber and a second flow path recessed in at
least one of the first partition and the second partition and
formed by the cooperation of the first partition and the second
partition so as to get communicated with the first flow path. An
outlet of the second flow path is located at a higher level in a
vertical direction than an inlet of the second flow path while
avoiding a direction facing the oil supply port.
[0009] Other aspects and advantages of the invention will be
apparent from embodiments disclosed in the attached drawings,
illustrations exemplified therein, and the concept of the
invention.
BRIEF DESCRIPTION OF THE DRAWINGS
[0010] FIG. 1 is a sectional view of a vane compressor according to
Embodiment 1.
[0011] FIG. 2 is a sectional arrow view of the vane compressor
according to Embodiment 1, taken in the direction of line II-II in
FIG. 1.
[0012] FIG. 3 is an expanded sectional view of principal part of
the vane compressor of FIG. 1 according to Embodiment 1.
[0013] FIG. 4 is a sectional arrow view of the vane compressor
according to Embodiment 1, taken in the direction of line IV-IV in
FIG. 3.
[0014] FIG. 5 is a sectional arrow view of the vane compressor
according to Embodiment 1, taken in the direction of line V-V in
FIG. 1.
[0015] FIG. 6 is a back view of a gasket in the vane compressor
according to Embodiment 1.
[0016] FIG. 7 is a back view of a cover plate in the vane
compressor according to Embodiment 1.
[0017] FIG. 8 is a partial sectional view similar to FIG. 4,
showing a vane compressor according to Embodiment 2.
[0018] FIG. 9 is a partial sectional view similar to FIG. 4,
showing a vane compressor according to Embodiment 3.
DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS
[0019] Embodiments 1 to 3 which embody the present invention will
be described below with reference to the drawings. In the following
description, it is assumed that the left side of FIG. 1 corresponds
to the front side of the compressor while the right side of FIG. 1
corresponds to the rear side of the compressor. Also, it is assumed
that the top side of FIG. 1 corresponds to the top side of the
compressor while the bottom side of FIG. 1 corresponds to the
bottom side of the compressor. Then, in FIG. 2 and subsequent
figures, the front, rear, top, and bottom directions are designated
with reference to FIG. 1. The front-and-rear direction and
top-and-bottom direction in Embodiments 1 to 3 indicate the
directions of a compressor according to the present invention when
the compressor is mounted on a vehicle, where the top-and-bottom
direction corresponds to a vertical direction, but mounting
attitude of the compressor according to the present invention is
changed as appropriate depending on the vehicle on which the
compressor is mounted, and the front-and-rear direction and
top-and-bottom direction in Embodiments 1 to 3 are exemplary and
not restrictive.
Embodiment 1
[0020] An electric vane compressor (hereinafter referred to simply
as a "compressor") according to Embodiment 1 shown in FIG. 1 is an
example of a concrete form of the compressor according to the
present invention. The compressor includes a housing 1, a motor
mechanism 3, a compression mechanism 5, an oil separation mechanism
7, and an oil supply mechanism 9. The motor mechanism 3 drives the
compression mechanism 5 by being accommodated in the housing 1. By
being accommodated in the housing 1, the compression mechanism 5
forms a suction chamber 11, a discharge chamber 13, and compression
chambers 15 in conjunction with the housing 1. Then, the
compression mechanism 5 sucks refrigerant from the suction chamber
11 into the compression chambers 15, compresses the refrigerant and
discharges the compressed refrigerant to the discharge chamber 13.
Being installed in the discharge chamber 13, the oil separation
mechanism 7 separates lubricating oil from the refrigerant and
stores the separated lubricating oil in the discharge chamber 13.
The oil supply mechanism 9 leads the lubricating oil in the
discharge chamber 13 to the compression mechanism 5.
[0021] Specifically, the housing 1 includes a motor housing 17, a
gasket 43, a compressor housing 19, a first side plate 21, a
cylinder block 23, a second side plate 25, a gasket 59, and a cover
plate 27. The compressor housing 19 corresponds to a housing body
according to the present invention, the second side plate 25 and
the gasket 59 correspond to a first partition according to the
present invention, and the cover plate 27 corresponds to the second
partition according to the present invention.
[0022] A cylindrical circumferential wall 17a of the motor housing
17 extends in an axial direction from a front end side to a rear
end side. The circumferential wall 17a is closed on the front end
side by a front wall 17b and provided with an opening 17c on the
rear end side. The suction chamber 11 serving also as a motor
chamber is formed inside the motor housing 17. An inlet port 17d
communicated with the suction chamber 11 is formed in the
circumferential wall 17a. A bearing 29 is provided on the front
wall 17b and a rotating shaft 31 is installed in the bearing 29
rotatably around a rotational axis X1. The inlet port 17d is
connected with an evaporator via a non-illustrated pipe. The
compressor, a condenser, an expansion valve, and the evaporator
form an air-conditioning apparatus of the vehicle. The refrigerant
passing through the evaporator is sucked into the suction chamber
11 through the inlet port 17d.
[0023] A stator 33 is fixed to an inner side of the circumferential
wall 17a of the motor housing 17, and a motor rotor 35 is fixed to
the rotating shaft 31. The motor rotor 35 is placed in the stator
33. A connection terminal 37 is fixed to the front wall 17b, and
the connection terminal 37 is provided with lead wires 39 extending
to the stator 33 in the suction chamber 11 from outside. The lead
wires 39 are provided with a cluster block 41 within the
circumferential wall 17a. The stator 33, the motor rotor 35, the
connection terminal 37, the lead wires 39, and the cluster block 41
form the motor mechanism 3.
[0024] The compressor housing 19 is fixed to a rear end of the
motor housing 17 by plural non-illustrated bolts. A circumferential
wall 19a in a cylindrical shape extends in the axial direction from
a front end side to a rear end side of the compressor housing 19.
The circumferential wall 19a is closed on a rear end side by a rear
wall 19b and provided with an opening on the front end side. The
circumferential wall 19a has an inner circumferential surface 19d
extending in a circumferential direction. The inner circumferential
surface 19d is coaxial with the rotational axis X1.
[0025] An opening 19c of the compressor housing 19 is coupled to
the opening 17c of the motor housing 17, closing both the motor
housing 17 and the compressor housing 19. The gasket 43 is provided
between the opening 17c of the motor housing 17 and the opening 19c
of the compressor housing 19. Also, the first side plate 21 is
fixed to the compressor housing 19 together with the motor housing
17 on the side of the opening 19c. The first side plate 21 defines
the suction chamber 11 between the motor housing 17 and the
cylinder block 23 by extending in a radial direction, and separates
the compression chamber 15 and the suction chamber 11 from each
other. An O-ring 45 is provided between the first side plate 21 and
the compressor housing 19. A shaft hole 21a is formed in the first
side plate 21 coaxially with the bearing 29. The rotating shaft 31
is passed through the shaft hole 21a.
[0026] The cylinder block 23, the second sideplate 25, and the
cover plate 27 are accommodated in the compressor housing 19. The
cylinder block 23 and the second side plate 25 are assembled on a
rear face of the first side plate 21 by plural bolts 47 as shown in
FIG. 2. The cylinder block 23 is sandwiched from front and rear by
the first side plate 21 and the second side plate 25 as shown in
FIG. 1. The second side plate 25 is fitted in the inner
circumferential surface 19d of the compressor housing 19. An O-ring
48 is provided between the second side plate 25 and the inner
circumferential surface 19d. A shaft hole 25a is formed in the
second side plate 25 coaxially with the bearing 29 and the shaft
hole 21a. The rotating shaft 31 is passed also through the shaft
hole 25a.
[0027] A cylinder chamber 23a is formed in the cylinder block 23 as
shown in FIG. 2. The cylinder chamber 23a is closed by the rear
face of the first side plate 21 and a front face of the second side
plate 25 as shown in FIG. 1. A rotor 49 is fixed integrally to the
rotating shaft 31 between the first side plate 21 and the second
side plate 25. The rotor 49 is configured to be rotatable around
the rotational axis X1 in the cylinder chamber 23a. Plural vane
grooves 49a are formed in the rotor 49 as shown in FIG. 2. Vanes 51
are installed advanceably/retractably in the respective vane
grooves 49a.
[0028] Also, a suction passage 23b and a suction port 23c are
formed in the cylinder block 23. The suction passage 23b extends in
the front-and-rear direction parallel to the rotational axis X1.
The suction passage 23b is communicated with the cylinder chamber
23a through the suction port 23c. Furthermore, a discharge space
23d is formed in the cylinder block 23 in conjunction with the
inner circumferential surface 19d of the compressor housing 19. The
discharge space 23d is communicated with the cylinder chamber 23a
through a discharge port 23e. A discharge reed valve 53 adapted to
open and close the discharge port 23e and a discharge retainer 55
adapted to restrict an opening degree of the discharge reed valve
53 are provided in the discharge space 23d. The discharge reed
valve 53 and the discharge retainer 55 are fixed to the cylinder
block 23 by a bolt 57.
[0029] As shown in FIG. 1, a suction passage 21c adapted to
communicate the suction chamber 11 and the suction passage 23b with
each other is formed by penetrating the first side plate 21. The
gasket 59 is provided between the second side plate 25 and the
cover plate 27. The second side plate 25, gasket 59, and the cover
plate 27 are assembled and fixed by plural bolts 76 as shown in
FIGS. 3 to 5. The second side plate 25, gasket 59, and the cover
plate 27 form the discharge chamber 13 between the cylinder block
23 and the compressor housing 19 by extending in the radial
direction and separates the compression chamber 15 and the
discharge chamber 13 from each other.
[0030] An introduction passage 25b adapted to communicate the
discharge space 23d with an oil separation chamber 65 described
later is formed by penetrating the second side plate 25, gasket 59,
and the cover plate 27. The first side plate 21, the cylinder block
23, the second side plate 25, the rotor 49, the vanes 51, the
discharge reed valve 53, the discharge retainer 55, and the bolt 57
form the compression mechanism 5. The compression mechanism 5 forms
the compression chamber 15 defined by the front face of the
cylinder chamber 23a, an inner circumferential surface of the
cylinder chamber 23a, the rear face of the cylinder chamber 23a,
the outer circumferential surface of the rotor 49, and the vanes
51. Aback pressure chamber 61 is provided between each vane groove
49a and the corresponding vane 51.
[0031] As shown in FIG. 5, the second side plate 25 and the cover
plate 27 are coupled together in an annular coupling region 73 via
the gasket 59. An intermediate pressure chamber 69 is formed
between the second side plate 25 and the cover plate 27, being
located closer to the side of the rotational axis X1 than to the
coupling region 73 is. As shown in FIGS. 3 and 4, the intermediate
pressure chamber 69 makes part of the second side plate 25 and part
of the cover plate 27 spaced away from each other in a direction of
the rotational axis X1. When viewed in the direction of the
rotational axis X1, the intermediate pressure chamber 69 is placed
so as to overlap at least part of the rear face of the cylinder
chamber 23a.
[0032] As shown in FIGS. 3 to 5, the oil separation mechanism 7 is
provided on the cover plate 27. The oil separation mechanism 7
includes a cylindrical member 63, the oil separation chamber 65,
and an oil drain path 71. As shown in FIG. 3, the oil separation
chamber 65 includes an upper chamber 65a scooped out in a columnar
manner and a lower chamber 65b communicated with the upper chamber
65a on an underside of the upper chamber 65a, scooped out in a
columnar manner coaxially with the upper chamber 65a, and
configured to be a little smaller in diameter than the upper
chamber 65a. As shown in FIG. 5, the upper chamber 65a and the
lower chamber 65b are formed with upper part inclined slightly
inward with respect to a top-and-bottom direction slightly on the
left side of the cover plate 27 in FIG. 5.
[0033] The cylindrical member 63 cylindrical in shape is fixed to
an upper end of the upper chamber 65a. As shown in FIG. 3, the
cylindrical member 63 is formed of a large diameter portion 63a and
a small diameter portion 63b, where the large diameter portion 63a
is configured to be large in diameter and press-fitted in the upper
chamber 65a while the small diameter portion 63b is formed
integrally and coaxially with the large diameter portion 63a under
the large diameter portion 63a and configured to be a little
smaller in diameter than the large diameter portion 63a. The
refrigerant led to the oil separation chamber 65 from the discharge
space 23d through the introduction passage 25b circles in an
annular space formed by the small diameter portion 63b and an inner
circumferential surface of the upper chamber 65a. Consequently, a
centrifugal force acts on the refrigerant, causing the lubricating
oil contained in the refrigerant to separate, drip off the inner
circumferential surface of the upper chamber 65a, and move to the
lower chamber 65b.
[0034] As shown in FIG. 1, an outlet port 19e is formed in the
circumferential wall 19a of the compressor housing 19. The outlet
port 19e is connected with a condenser via a non-illustrated pipe.
The refrigerant with lubricating oil separated therefrom in the oil
separation chamber 65 is discharged to the condenser through the
outlet port 19e.
[0035] As shown in FIG. 4, a through-hole 71a is formed in the
cover plate 27, at a lower end of the lower chamber 65b, extending,
at right angles, to an end face of the gasket 59, which is the
coupling region 73. The through-hole 71a extends in a tangential
direction from a direction in which the refrigerant circles in the
lower chamber 65b. As shown in FIG. 6, the gasket 59 has a flat end
face configured to come face-to-face to the through-hole 71a of the
cover plate 27. The through-hole 71a is a first flow path. Also, as
shown in FIGS. 4 and 7, a linear groove 71c is recessed, in the
cover plate 27, being communicated with the through-hole 71a and
extending linearly to an outer circumferential side. The linear
groove 71c is a recessed portion. Surfaces are joined together such
that an end face of the cover plate 27 with the linear groove 71c
formed therein and an end face of the gasket 59 will face each
other, and the linear groove 71c makes up a second flow path
according to the present invention.
[0036] One end of the linear groove 71c is an inlet 71b
communicated with the through-hole 71a, and another end is an
outlet 71d opening to the discharge chamber 13. As shown in FIG. 7,
the outlet 71d is located at a higher level in the vertical
direction than the inlet 71b. That is, the linear groove 71c
extends, being inclined at an angle of .theta..degree. with respect
to a horizontal direction when the compressor is mounted on the
vehicle. Consequently, as shown in FIG. 5, the linear groove 71c
extends in a direction away from an oil supply port 75c described
later. Also, as shown in FIGS. 4 and 5, the outlet 71d of the
linear groove 71c is placed face-to-face with the inner
circumferential surface 19d of the compressor housing 19, being
spaced away only by about a few millimeters. More specifically, as
shown in FIG. 5, if a normal L is defined at a position where the
outlet 71d comes face-to-face with the inner circumferential
surface 19d, the linear groove 71c intersects the normal L at an
acute angle. The through-hole 71a and the linear groove 71c form
the oil drain path 71.
[0037] Also, first and second oil flow paths 75a and 75b are formed
in the cover plate 27. The first oil flow path 75a is communicated
with a bottom of the discharge chamber 13 through the oil supply
port 75c at a lower end, and extends upward, approaching the
rotational axis X1. The second oil flow path 75b extends to the
intermediate pressure chamber 69 while being continuous with the
upper end of the first oil flow path 75a. Consequently, the
lubricating oil in the discharge chamber 13 is taken into the first
and second oil flow paths 75a and 75b through the oil supply port
75c, and led to the intermediate pressure chamber 69. In so doing,
the first and second oil flow paths 75a and 75b function as
throttle channels and leads the lubricating oil to the intermediate
pressure chamber 69 such that pressure in the intermediate pressure
chamber 69 will be lower than in the discharge chamber 13, but
higher than in the suction chamber 11.
[0038] As shown in FIGS. 1 and 3, a communicating path 77 adapted
to communicate the intermediate pressure chamber 69 and the back
pressure chamber 61 with each other is formed by penetrating the
second side plate 25. Also, an oil groove 25c annular in shape and
coaxial with the rotational axis X1 is formed in the second side
plate 25. Furthermore, as shown in FIG. 1, an oil groove 21b
annular in shape and coaxial with the rotational axis X1 is formed
in the first side plate 21. The oil grooves 21b and 25c are
communicated with a bottom of each vane groove 49a regardless of
rotation of the rotor 49. The oil supply port 75c, the first and
second oil flow paths 75a and 75b, the intermediate pressure
chamber 69, the communicating path 77, and the oil groove 25c make
up a back pressure flow path. The oil supply port 75c, the first
and second oil flow paths 75a and 75b, the intermediate pressure
chamber 69, the communicating path 77, the oil groove 25c, the back
pressure chamber 61, and the oil groove 21b make up the oil supply
mechanism 9.
[0039] In the compressor, when electric power is supplied to the
stator 33 shown in FIG. 1, the motor mechanism 3 operates, causing
the rotating shaft 31 to rotate around the rotational axis X1.
Consequently, the compression mechanism 5 operates and the rotor 49
rotates in the cylinder chamber 23a. In doing so, in the cylinder
chamber 23a, the vanes 51 advance and retract into/from the
respective vane grooves 49a along with the rotation of the rotor
49. Consequently, the refrigerant in the suction chamber 11 is
sucked into the compression chamber 15, compressed in the
compression chamber 15, and discharged to the discharge chamber
13.
[0040] In doing so, the lubricating oil is separated from the
refrigerant in the oil separation chamber 65 of the oil separation
mechanism 7. The refrigerant from which the lubricating oil has
been separated is supplied to the condenser outside through the
discharge chamber 13 and the outlet port 19e. The lubricating oil
in the oil separation chamber 65 is stored in lower part of the
discharge chamber 13 by passing through the oil drain path 71.
[0041] Meanwhile, in the compressor, the second side plate 25 and
the cover plate 27 remain coupled together in the coupling region
73, and the oil drain path 71 is formed of the through-hole 71a and
the linear groove 71c. The through-hole 71a is formed by
penetrating the cover plate 27 and extends from the lower chamber
65b of the oil separation chamber 65 to the end face of the gasket
59, which is the coupling region 73. Consequently, the lubricating
oil discharged in sequence from the lower chamber 65b of the oil
separation chamber collides with the end face of the gasket 59
first of all, thereby having its flow direction changed and having
its force weakened.
[0042] Also, the linear groove 71c is recessed in the coupling
region 73 of the cover plate 27. The outlet 71d of the linear
groove 71c is located at a higher level in the vertical direction
than the inlet 71b. Consequently, the linear groove 71c is
communicated with the through-hole 71a and extends such that the
outlet 71d opens in a direction different from a direction toward
the oil supply port 75c. The lubricating oil discharged from the
linear groove 71c in sequence is discharged into the discharge
chamber 13 in such a way as to move away from the oil supply port
75c. With the present compressor, in particular, because the outlet
71d of the linear groove 71c is placed face-to-face with the inner
circumferential surface 19d of the compressor housing 19, the
lubricating oil discharged in sequence from the linear groove 71c
collides also with the inner circumferential surface 19d. That is,
the lubricating oil flowing through the oil drain path 71 has its
flow changed by passing through a bent path before being stored in
the discharge chamber 13 and has its flow weakened by colliding
with wall surfaces at least twice. Also, since the linear groove
71c intersects the normal L at an acute angle, the lubricating oil
discharged in sequence from the linear groove 71c is guided along
the inner circumferential surface 19d.
[0043] Consequently, with the present compressor, even when a large
amount of lubricating oil is stored in the discharge chamber 13,
the lubricating oil discharged in sequence from the oil separation
chamber 65 is less prone to blow or disturb the lubricating oil in
the discharge chamber 13. This makes the refrigerant in the
discharge chamber 13 less prone to get mixed with the lubricating
oil in the discharge chamber 13 again. In particular, since the
outlet 71d of the linear groove 71c is not directed toward the oil
supply port 75c, the lubricating oil discharged from the outlet 71d
is kept from disturbing the refrigerant gas and the lubricating oil
around the oil supply port 75c. Consequently, the lubricating oil
just as stored in the discharge chamber 13 almost without being
mixed with refrigerant tends to be supplied to the compression
mechanism 5 through the oil supply port 75c. Specifically, the
lubricating oil taken in through the oil supply port 75c reaches
the intermediate pressure chamber 69 through the first and second
oil flow paths 75a and 75b, and is supplied from the intermediate
pressure chamber 69 to the back pressure chambers 61 through the
oil groove 25c and the communicating path 77. The lubricating oil
in the back pressure chambers 61 lubricates the sliding portions
between the respective vane grooves 49a and vanes 51 as well as
sliding portions between the respective vanes 51 and the cylinder
chamber 23a. Also, the lubricating oil in the back pressure
chambers 61 lubricates the shaft holes 21a and 25a by passing
through the oil grooves 21b and 25c. In this way, the present
compressor allows the compression mechanism 5 to be lubricated
sufficiently. Thus, the compressor is less prone to noise and
vibration, and exhibits high durability as well as high quiet.
Also, compared to when refrigerant gas is mixed in, each vane 51
can be pressed stably by hydraulic pressure, making it possible to
prevent chattering of the vane 51 and improve the quiet of the
compressor.
[0044] Also, in the present compressor, since an end face of the
cover plate 27 provided with the linear groove 71c and an end face
of the gasket 59 are placed facing each other and the second flow
path is formed by joining together the end faces, the cover plate
27 does not increase in size and is easy to produce. Thus, the
compressor makes it easy to prevent discharge pulsation by allowing
the discharge chamber 13 to have a large volume and makes it
possible to downsize the entire compressor and achieve a high
mountability on a vehicle or the like. Also, the compressor, which
is easy to produce, can reduce production costs.
[0045] Thus, the compressor can be lubricated sufficiently, is less
prone to discharge pulsation, and is capable of achieving
downsizing and production cost reductions.
Embodiment 2
[0046] In the compressor according to Embodiment 2, the cover plate
27 has a flat end face on an outer circumferential side of the
through-hole 71a as shown in FIG. 8. Also, a through-hole 71e
matching the through-hole 71a in the cover plate 27 is formed by
penetrating the gasket 59. A linear groove 71f linear in shape is
formed in the second side plate 25 by being communicated with the
through-holes 71a and 71e. Surfaces are joined together such that
the end face of the gasket 59 with the through-hole 71e formed
therein and an end face of the second side plate 25 with the linear
groove 71f formed therein will face each other. The through-hole
71e and the linear groove 71f make up the second flow path
according to the present invention. The through-hole 71a, the
through-hole 71e, and the linear groove 71c make up the oil drain
path 71.
[0047] The rest of the configuration is similar to Embodiment 1.
The present compressor achieves functions and effects similar to
those of Embodiment 1.
Embodiment 3
[0048] In the compressor according to Embodiment 3, the cover plate
27 has a flat end face on an outer circumferential side of the
through-hole 71a as shown in FIG. 9. Besides, the second sideplate
25 also has a flat end face on an outer circumferential side. A
linear notch 71g is formed in the gasket 59, being communicated
with the through-hole 71a in the cover plate 27. Surfaces are
joined together such that an end face of the cover plate 27 and an
end face of the second side plate 25 will face two end faces,
respectively, of the gasket 59 in which the notch 71g is formed.
The notch 71g corresponds to the second flow path according to the
present invention. The through-hole 71a and the notch 71g make up
the oil drain path 71.
[0049] The rest of the configuration is similar to Embodiment 1.
The present compressor also achieves functions and effects similar
to those of Embodiment 1.
[0050] Although the present invention has been described above in
line with Embodiments 1 to 3, it is needless to say that the
invention is not limited to the above-described embodiments 1 to 3,
but may be appropriately modified in application without departing
from the gist of the invention.
[0051] For example, whereas the second flow path is formed into a
linear shape from the linear groove 71c, the linear groove 71f, or
the notch 71g linear in shape in Embodiments 1 to 3, the second
flow path may be formed into a bent or curved shape.
[0052] Also, whereas three vanes are provided in the compressors
according to Embodiments 1 to 3, the number of vanes is not limited
to three, and may be, for example, two or four.
[0053] Also, whereas the present invention is embodied as a vane
compressor in Embodiments 1 to 3, the present invention can also be
embodied as a scroll compressor or the like.
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