U.S. patent application number 15/741437 was filed with the patent office on 2018-07-19 for compressor.
The applicant listed for this patent is SANDEN AUTOMOTIVE COMPONENTS CORPORATION. Invention is credited to Yukihiko TAGUCHI.
Application Number | 20180202424 15/741437 |
Document ID | / |
Family ID | 57609382 |
Filed Date | 2018-07-19 |
United States Patent
Application |
20180202424 |
Kind Code |
A1 |
TAGUCHI; Yukihiko |
July 19, 2018 |
COMPRESSOR
Abstract
An oil circulation ratio OCR of a compressor is reduced with a
simple structure. A cylinder head 104 has a suction chamber 141
formed on the inside thereof in a radial direction and a discharge
chamber 142 formed on the outside thereof in the radial direction,
the suction and discharge chambers being separated by a first
annular partition wall 104d. An oil storage chamber 148 is formed
at a central portion of the cylinder head 104 by being separated
from the suction chamber 141 by a second annular partition wall
104e. A pressure release passage 146
(101c.fwdarw.101d.fwdarw.103c.fwdarw.148.fwdarw.104e1) allows a
crank chamber 140 and the suction chamber 141 to communicate with
each other. The oil storage chamber 148 forms a portion of the
pressure release passage 146, separates oil from a refrigerant
flowing through the pressure release passage 146, and stores the
oil.
Inventors: |
TAGUCHI; Yukihiko;
(Isesaki-shi, Gunma, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
SANDEN AUTOMOTIVE COMPONENTS CORPORATION |
Isesaki-shi, Gunma |
|
JP |
|
|
Family ID: |
57609382 |
Appl. No.: |
15/741437 |
Filed: |
June 2, 2016 |
PCT Filed: |
June 2, 2016 |
PCT NO: |
PCT/JP2016/066448 |
371 Date: |
January 2, 2018 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04B 27/12 20130101;
F04B 39/16 20130101; F04B 27/109 20130101; F04B 39/0223 20130101;
F04B 27/1045 20130101; F04B 39/04 20130101; F04B 27/10 20130101;
F04B 27/1081 20130101; F04B 27/1054 20130101; F04B 39/0284
20130101; F04B 27/18 20130101 |
International
Class: |
F04B 39/02 20060101
F04B039/02; F04B 27/10 20060101 F04B027/10; F04B 39/04 20060101
F04B039/04; F04B 39/16 20060101 F04B039/16 |
Foreign Application Data
Date |
Code |
Application Number |
Jul 2, 2015 |
JP |
2015-133330 |
Claims
1. A compressor that includes a cylinder block that has a plurality
of cylinder bores and has a piston mounted on each of the cylinder
bores, and a cylinder head that is disposed on one end side of the
cylinder block via a valve plate and defines a suction chamber on
the inside thereof in a radial direction and a discharge chamber on
the outside thereof in the radial direction, and in which the
piston is reciprocated by a swash plate that rotates in
synchronization with a driving shaft to draw a refrigerant into the
cylinder bore from the suction chamber and compress the refrigerant
within the cylinder bore to discharge the refrigerant to the
discharge chamber, the compressor comprising: a pressure release
passage that allows a crank chamber, in which the swash plate is
disposed, and the suction chamber to communicate with each other;
and an oil storage chamber that forms a portion of the pressure
release passage and separates oil from the refrigerant flowing
through the pressure release passage to store the oil, wherein the
oil storage chamber is defined by an annular partition wall and the
valve plate, wherein the annular partition wall is formed
integrally with the cylinder head, is provided to protrude toward
the valve plate from a bottom wall of the cylinder head, and has an
outer peripheral portion surrounded by the suction chamber.
2. The compressor according to claim 1, wherein a protruding height
of the annular partition wall is set such that a protruding-side
end portion of the annular partition wall presses the valve plate
when the cylinder block and the cylinder head are fastened to each
other.
3. The compressor according to claim 2, wherein a lower region of
the oil storage chamber in a gravitational direction communicates
with the suction chamber via an oil return passage with a throttle
straddling the annular partition wall, and wherein the oil return
passage is formed in at least one of the valve plate and an
interposed member interposed between the valve plate and the
cylinder head.
4. The compressor according to claim 1, wherein a suction passage
that allows an external refrigerant circuit and the suction chamber
to communicate with each other is formed in the cylinder head, and
wherein the suction passage has a straight path that linearly
extends from the outside of the cylinder head in the radial
direction toward the inside thereof in the radial direction, and a
constituent wall of the straight path is bulged into the oil
storage chamber.
5. The compressor according to claim 1, wherein a suction passage
that allows an external refrigerant circuit and the suction chamber
to communicate with each other is formed in the cylinder head,
wherein the suction passage has a straight path that linearly
extends from the outside of the cylinder head in the radial
direction toward the inside thereof in the radial direction, and
wherein a tubular space, which communicates with the straight path
on one end side thereof and communicates with the suction chamber
on the other end side thereof via a throttle, is formed on an
extension of the straight path, and a constituent wall of the
tubular space is bulged into the oil storage chamber.
6. The compressor according to claim 1, wherein the oil storage
chamber becomes a pressure region of the suction chamber, wherein a
suction passage that allows an external refrigerant circuit and the
suction chamber to communicate with each other is formed in the
cylinder head, wherein the suction passage has a straight path that
linearly extends from the outside of the cylinder head in the
radial direction toward the inside thereof in the radial direction,
wherein an upper region of the oil storage chamber in a
gravitational direction communicates with a connecting path that
extends from the straight path, and wherein the connecting path has
a smaller-diameter portion having a smaller diameter than the
straight path.
7. The compressor according to claim 6, wherein the connecting path
has the smaller-diameter portion, and a larger-diameter portion
that is disposed closer to the straight path than the
smaller-diameter portion and has a larger diameter than the
smaller-diameter portion.
8. The compressor according to claim 6, wherein the suction passage
has a first passage that directly reaches the suction chamber from
the straight path, and a second passage that reaches the suction
chamber via the connecting path and the upper region of the oil
storage chamber in the gravitational direction from the straight
path, and a minimum flow passage cross-sectional area of the second
passage is set to be smaller than a minimum flow passage
cross-sectional area of the first passage.
9. The compressor according to claim 1, wherein the oil storage
chamber becomes a pressure region of the suction chamber, wherein a
suction passage that allows an external refrigerant circuit and the
suction chamber to communicate with each other is formed in the
cylinder head, wherein the suction passage has a straight path that
linearly extends from the outside of the cylinder head in the
radial direction toward the inside thereof in the radial direction,
wherein an upper region of the oil storage chamber in a
gravitational direction communicates with a connecting path that
extends from the straight path, and wherein the connecting path
forms a portion of the pressure release passage.
10. The compressor according to claim 1, further comprising: a
pressure supply passage that allows the discharge chamber and the
crank chamber to communicate with each other; a control valve
disposed in the pressure supply passage; and a throttle disposed
upstream of the oil storage chamber of the pressure release
passage, wherein the swash plate is configured such that an
inclination angle thereof is changeable, and when the pressure of
the crank chamber increases, the inclination angle decreases and
thereby the stroke of the piston decreases.
Description
TECHNICAL FIELD
[0001] The present invention relates to a compressor that is
primarily used for air-conditioning systems for vehicles, and in
particular, relates to a technique for reducing the amount of
lubricating oil that flows out of a compressor into an external
refrigerant circuit.
BACKGROUND ART
[0002] A compressor disclosed in Patent Document 1 includes a
cylinder block that has a plurality of cylinder bores and has a
piston mounted on each of the cylinder bores, and a cylinder head
that is disposed on one end side of the cylinder block via a valve
plate and defines a suction chamber on the inside thereof in a
radial direction and a discharge chamber on the outside thereof in
the radial direction. The piston is reciprocated by a swash plate
that rotates in synchronization with a driving shaft to draw a
refrigerant into the cylinder bore from the suction chamber and
compress the refrigerant within the cylinder bore to discharge the
refrigerant to the discharge chamber.
[0003] In such a compressor, lubricating oil is mixed into a
refrigerant gas, and the lubrication of respective parts of the
compressor is performed. Here, if the lubricating oil flows out
into an external refrigerant circuit, system efficiency decreases.
Therefore, reducing the amount of the lubricating oil that flows
out of the compressor into the external refrigerant circuit, that
is, a reduction in an oil circulation ratio (OCR) has been
required.
[0004] For this reason, in the compressor disclosed in Patent
Document 1, a partition member is provided to partition the suction
chamber into a first space to which a suction passage from the
outside is connected on a bottom wall side of the cylinder head and
a second space on the valve plate side, and this partition member
is provided with a communication passage that allows the first
space and the second space to communicate with each other. Also, a
pressure release passage, which releases the pressure of a crank
chamber behind the piston in which the swash plate is disposed, to
the suction chamber, is connected to the first space.
[0005] According to the above configuration, the lubricating oil
that flows out of the crank chamber together with the refrigerant
flows into the first space and is stored therein, and the
refrigerant gas from which the lubricating oil is separated passes
through the second space, and then is compressed and discharged. As
a result, it is possible to suppress the outflow of the oil to the
external refrigerant circuit.
REFERENCE DOCUMENT LIST
Patent Document
[0006] Patent Document 1: JP 2014-095301 A
SUMMARY OF THE INVENTION
Problems to be Solved by the Invention
[0007] However, the configuration disclosed in Patent Document 1
has the following problems.
[0008] (1) Although there are advantages in that the partition
member is capable of being integrally formed with the head gasket
and an exclusive partition member becomes unnecessary, the shape of
the head gasket provided with the partition member is
complicated.
[0009] (2) Since the second space is between the valve plate and
the first space (oil storage chamber), there is a restriction on a
path that connects the pressure release passage to the first space
(oil storage chamber).
[0010] (3) The periphery of the first space (oil storage chamber)
is the discharge chamber, and the stored oil is influenced by the
transfer of heat from high-temperature discharge gas. Accordingly,
the viscosity of the oil decreases and lubrication performance
deteriorates.
[0011] An object of the present invention is to provide a
compressor capable of solving the above problems.
Means for Solving the Problems
[0012] A compressor according to the present invention includes, as
a premise, a cylinder block that has a plurality of cylinder bores
and has a piston mounted at each of the cylinder bores, and a
cylinder head that is disposed on one end side of the cylinder
block via a valve plate and defines a suction chamber on the inside
thereof in a radial direction and a discharge chamber on the
outside thereof in the radial direction. The piston is reciprocated
by a swash plate that rotates in synchronization with a driving
shaft to draw a refrigerant into the cylinder bore from the suction
chamber and compress the refrigerant within the cylinder bore to
discharge the refrigerant to the discharge chamber.
[0013] Also, the compressor according to the present invention is
characterized by including a pressure release passage that allows a
crank chamber, in which the swash plate is disposed, and the
suction chamber to communicate with each other; and an oil storage
chamber that forms a portion of the pressure release passage and
separates oil from the refrigerant flowing through the pressure
release passage to store the oil. The oil storage chamber is
defined by an annular partition wall and the valve plate. The
annular partition wall is formed integrally with the cylinder head,
is provided to protrude toward the valve plate from a bottom wall
of the cylinder head, and has an outer peripheral portion
surrounded by the suction chamber.
Effects of the Invention
[0014] According to the present invention, since the annular
partition wall that defines the oil storage chamber is formed
integrally with the cylinder head, it is possible to easily form
the oil storage chamber.
[0015] Additionally, since the oil storage chamber is defined by
the valve plate, it is possible to easily connect the pressure
release passage to the oil storage chamber.
[0016] Additionally, the periphery of the oil storage chamber is
the suction chamber, and is separated from the discharge chamber.
Therefore, the oil that flows out of the crank chamber into the oil
storage chamber and is stored therein is cooled by a drawn in
refrigerant. Hence, it is possible to reduce a decrease in the
viscosity of the oil and it is possible to maintain excellent
lubrication performance.
BRIEF DESCRIPTION OF THE DRAWINGS
[0017] FIG. 1 is a sectional view of a compressor according to a
first embodiment of the present invention.
[0018] FIG. 2 is an enlarged sectional view of the main part
(cylinder head portion) of the above first embodiment.
[0019] FIG. 3 is a sectional view of a cylinder head portion
according to a second embodiment.
[0020] FIG. 4 is a sectional view of a cylinder head portion
according to a third embodiment.
[0021] FIG. 5 is a sectional view of a cylinder head portion
according to a fourth embodiment.
[0022] FIG. 6 is a sectional view of a cylinder head portion
according to a fifth embodiment.
[0023] FIG. 7 is a sectional view of a cylinder head portion
according to a sixth embodiment.
MODE FOR CARRYING OUT THE INVENTION
[0024] Hereinbelow, an embodiment of the present invention will be
described in detail.
[0025] FIG. 1 is a sectional view of a compressor according to a
first embodiment of the present invention, and FIG. 2 is an
enlarged sectional view of the main part (cylinder head portion) of
the first embodiment.
[0026] A basic configuration of a compressor (in particular, a
variable displacement compressor) 100 illustrated in FIG. 1 will be
described.
[0027] The variable displacement compressor 100 is capable of a
discharge displacement zero operation and therefore is a clutchless
compressor.
[0028] The variable displacement compressor 100 includes a cylinder
block 101 provided with a plurality of cylinder bores 101a, a
cylinder head 104 provided on one end side of the cylinder block
101 via a valve plate 103, and a front housing 102 provided on the
other end side of the cylinder block 101.
[0029] A driving shaft 110 is provided across the inside of a crank
chamber 140 defined by the cylinder block 101 and the front housing
102, and a swash plate 111 is disposed at a periphery of an
intermediate portion in a longitudinal direction of the driving
shaft 110. The swash plate 111 is coupled to a rotor 112 fixed to
the driving shaft 110 via a link mechanism 120, and the inclination
angle thereof is changeable along the driving shaft 110.
[0030] The link mechanism 120 includes a first arm 112a provided to
protrude from the rotor 112, a second arm 111a provided to protrude
from the swash plate 111, and a link arm 121, one end of which is
rotatably connected to the first arm 112a via a first connecting
pin 122, and the other end of which is rotatably connected to the
second arm 111a via a second connecting pin 123.
[0031] A through-hole 111b of the swash plate 111 is formed to
allow the swash plate 111 to incline in a range of a maximum
inclination angle and a minimum inclination angle, and a minimum
inclination angle restricting portion coming into contact with the
driving shaft 110 is formed in the through-hole 111b. In a case in
which the inclination angle of the swash plate when the swash plate
111 is orthogonal to the driving shaft 110 is 0.degree., the
minimum inclination angle restricting portion of the through-hole
111b is formed such that the swash plate 111 is capable of being
inclined up to about 0.degree.. In addition, the maximum
inclination angle of the swash plate is restricted when the swash
plate 111 comes into contact with the rotor 112.
[0032] An inclination angle reducing spring 114 that biases the
swash plate 111 until reaching the minimum inclination angle toward
the minimum inclination angle is mounted between the rotor 112 and
the swash plate 111, and an inclination angle increasing spring 115
that biases the swash plate 111 in a direction in which the
inclination angle of the swatch plate is increased is mounted
between the swash plate 111 and a spring supporting member 116.
Since the biasing force of the inclination angle increasing spring
115 at the minimum inclination angle is set to be greater than the
biasing force of the inclination angle reducing spring 114, the
swash plate 111 is located at an inclination angle at which the
biasing forces of the inclination angle reducing spring 114 and the
inclination angle increasing spring 115 are balanced with each
other when the driving shaft 110 is not rotating.
[0033] One end of the driving shaft 110 extends through the inside
of a boss 102a protruding to the outside of the front housing 102
and extends to the outside, and is coupled to a power transmission
device (not illustrated). In addition, a shaft seal device 130 is
inserted between the driving shaft 110 and the boss 102a to cut off
the inside and the outside.
[0034] An integral structure of the driving shaft 110 and the rotor
112 is supported by bearings 131 and 132 in a radial direction, and
is supported by a bearing 133 and a thrust plate 134 in a thrust
direction. In addition, a gap between an end face of the driving
shaft 110, which faces the thrust plate 134, and the thrust plate
134 is adjusted to a predetermined gap by an adjusting screw
135.
[0035] Therefore, the power from an external driving source is
transmitted to the power transmission device, and the driving shaft
110 is rotatable in synchronization with the power transmission
device.
[0036] A piston 136 is disposed within each cylinder bore 101a, an
outer peripheral portion of the swash plate 111 is accommodated in
an inner space of an end portion protruding to the crank chamber
140 of the piston 136, and the swash plate 111 is configured to
interlock with the piston 136 via a pair of shoes 137. Therefore,
the piston 136 is reciprocable within the cylinder bore 101a by the
rotation of the swash plate 111.
[0037] A suction chamber 141 is disposed on the inside of the
cylinder head 104 in the radial direction, and a discharge chamber
142 is defined so as to annularly surround the outside of the
suction chamber 141 in the radial direction. In addition, an oil
storage chamber 148 is disposed, as will be described below, at a
central portion (a region in which an axis O of the driving shaft
110 extends) of the cylinder head 104, and the suction chamber 141
is defined so as to surround the outside of the oil storage chamber
148 in the radial direction.
[0038] The suction chamber 141 communicates with the cylinder bore
101a via a suction hole 103a provided in the valve plate 103, and a
suction valve (not illustrated) formed in a suction valve forming
sheet 152 (FIG. 2). The discharge chamber 142 communicates with the
cylinder bore 101a via a discharge valve (not illustrated) formed
in a discharge valve forming sheet 138 (FIG. 2) and a discharge
hole 103b provided in the valve plate 103.
[0039] The front housing 102, a center gasket 150, the cylinder
block 101, a cylinder gasket 151 (FIG. 2), the suction valve
forming sheet 152 (FIG. 2), the valve plate 103, the discharge
valve forming sheet 138 (FIG. 2), a head gasket 139 (FIG. 2), and
the cylinder head 104 are fastened together by a plurality of
through bolts 105 to form a compressor housing.
[0040] A suction passage 104a that allows a suction-side
refrigerant circuit of an air-conditioning system and the suction
chamber 141 to communicate with each other is formed in the
cylinder head 104. The suction passage 104a has a straight path
104a1 that linearly extends from the outside of the cylinder head
104 in the radial direction toward the inside thereof in the radial
direction, and a communication passage 104a2 that allows the
straight path 104a1 and the suction chamber 141 to communicate with
each other.
[0041] Additionally, an upper portion of the cylinder block 101 in
FIG. 1 is provided with a muffler, and the muffler is formed by a
muffler forming wall 101b defined by the upper portion of the
cylinder block 101 and a lid member 106 being fastened together via
a seal member (not illustrated) with bolts. A check valve 200 is
disposed in a muffler space 143. The check valve 200 is disposed at
a connecting portion between a communication passage 144 formed
over the cylinder head 104, the valve plate 103, and the cylinder
block 101, and the muffler space 143, operates in response to a
pressure difference between the communication passage 144 (upstream
side) and the muffler space 143 (downstream side), cuts off the
communication passage 144 in a case in which a pressure difference
is smaller than a predetermined value, and releases the
communication passage 144 in a case in which the pressure
difference is greater than the predetermined value. Therefore, the
discharge chamber 142 is connected to a discharge-side refrigerant
circuit of the air-conditioning system via a discharge passage,
which includes the communication passage 144, the check valve 200,
the muffler space 143, and a discharge port 106a.
[0042] The cylinder head 104 is further provided with a control
valve 300.
[0043] The control valve 300 adjusts the opening degree of a
pressure supply passage 145, which allows the discharge chamber 142
and the crank chamber 140 to communicate with each other, in
response to the pressure of the suction chamber 141 introduced via
a pressure introduction passage 147, and an electromagnetic force
generated by an electric current that flows into a solenoid, and
controls the amount of discharge gas to be introduced into the
crank chamber 140. Blowby gas leaking out from a gap between the
piston 136 and the cylinder bore 101a when the piston 136
compresses refrigerant gas, and discharge gas passing through via
the control valve 300 flow into the crank chamber 140. The
refrigerant within the crank chamber 140 flows into the suction
chamber 141 via a pressure release passage 146, which includes a
communication passage 101c, a space 101d, a throttle 103c, the oil
storage chamber 148, and a communication passage 104e1.
[0044] The space 101d is formed between the cylinder block 101 and
the valve plate 103 by recessing a central portion of the cylinder
block 101. The communication passage 101c is bored in the cylinder
block 101 so as to allow the crank chamber 140 and the space 101d
to communicate with each other.
[0045] The throttle 103c is bored in the valve plate 103 so as to
allow the space 101d on the cylinder block 101 side and the oil
storage chamber 148 on the cylinder head 104 side to communicate
with each other, and defines a minimum flow passage cross-sectional
area of the pressure release passage 146.
[0046] The oil storage chamber 148 is a space for forming a portion
of the pressure release passage 146 and for separating and storing
oil from the refrigerant that flows through the pressure release
passage 146. The communication passage 104e1 allows the oil storage
chamber 148 and the suction chamber 141 to communicate with each
other. The oil storage chamber 148 and the communication passage
104e1 will be described below in detail.
[0047] Therefore, by including the pressure supply passage 145 that
allows the discharge chamber 142 and the crank chamber 140 to
communicate with each other, the control valve 300 disposed in the
pressure supply passage 145, the pressure release passage 146 that
allows the crank chamber 140 and the suction chamber 141 to
communicate with each other, and the throttle 103c disposed in the
pressure release passage 146, the pressure of the crank chamber 140
is capable of being changed by the control valve 300, and the
inclination angle of the swash plate 111, that is, the stroke of
the piston 136, is capable of being changed. Specifically, if the
pressure of the crank chamber 140 is increased, the inclination
angle of the swash plate 111 decreases, and thereby, it is possible
to reduce the stroke of the piston 136. Accordingly, the discharge
displacement of the variable displacement compressor 100 is capable
of being variably controlled.
[0048] During the operation of an air-conditioner, that is, in the
operating state of the variable displacement compressor 100, the
energization amount of the solenoid of the control valve 300 is
adjusted by a control device based on an external signal, and the
discharge displacement is variably controlled such that the
pressure of the suction chamber 141 reaches the predetermined
value. Therefore, the control valve 300 is capable of optimally
controlling the pressure of the suction chamber 141 according to an
external environment.
[0049] Additionally, when the air-conditioner is not operated, that
is, when the variable displacement compressor 100 is in a
non-operating state, by turning off the energization of the
solenoid and bringing the pressure supply passage 145 into a fully
open state, the pressure of the crank chamber 140 is controlled to
the maximum, and the discharge displacement of the variable
displacement compressor 100 is controlled to the minimum.
[0050] Next, an OCR-reducing structure including the oil storage
chamber 148 will be described with reference to FIG. 2.
[0051] The cylinder head 104 has an outer peripheral wall 104b, an
end wall (bottom wall) 104c, the first annular partition wall 104d
that defines the suction chamber 141 and the discharge chamber 142,
and a second annular partition wall 104e disposed on the inside of
the first annular partition wall 104d in the radial direction, and
these are integrally formed by aluminum casting. The outer
peripheral wall 104b, the first annular partition wall 104d, and
the second annular partition wall 104e are concentrically formed
about the axis O of the driving shaft 110.
[0052] The second annular partition wall 104e is provided to
protrude toward the valve plate 103 from the end wall (bottom wall)
104c. The height of the second annular partition wall 104e relative
to the outer peripheral wall 104b and the first annular partition
wall 104d is set such that a tip of the second annular partition
wall 104e presses the valve plate 103 together with a tip of the
outer peripheral wall 104b and a tip of the first annular partition
wall 104d with the head gasket 139 and the discharge valve forming
sheet 138 interposed therebetween when the through bolts 105 are
fastened to constitute the compressor housing. The second annular
partition wall 104e also has the function as pressing means for
holding down the floating of the valve plate 103 when the pressure
within a cylinder bore 101a reaches a high pressure in the
compression stroke of the piston 136.
[0053] The tip of the second annular partition wall 104e is brought
into contact with the head gasket 139, and a space surrounded by
the second annular partition wall 104e has its opening side blocked
by the head gasket 139 to form the oil storage chamber 148.
[0054] In addition, this space may be directly blocked by the valve
plate 103 by cutting out a portion of the head gasket 139 and the
discharge valve forming sheet 138 equivalent to an opening of the
space surrounded by the second annular partition wall 104e.
[0055] Therefore, the discharge chamber 142, the suction chamber
141, and the oil storage chamber 148 are formed from the outside of
the cylinder head 104 in the radial direction toward the inside
(central portion side) thereof in the radial direction by being
separated from each other by the first annular partition wall 104d
and the second annular partition wall 104e that are concentric with
each other.
[0056] The oil storage chamber 148 is capable of being easily
disposed at a central portion of the cylinder head 104 by the
second annular partition wall 104e and the valve plate 103.
[0057] A throttle 103c formed in the valve plate 103 is open in the
oil storage chamber 148. Also, the groove-shaped (cut-out)
communication passage 104e1 that allows the oil storage chamber 148
and the suction chamber 141 to communicate with each other is
formed at the tip of the second annular partition wall 104e that
separates the oil storage chamber 148 and the suction chamber 141
from each other.
[0058] Therefore, as already described, the crank chamber 140 and
the suction chamber 141 communicate with each other via the
communication passage 101c, the space 101d, the throttle 103c, the
oil storage chamber 148, and the communication passage 104e1, and
the communication passage 101c, the space 101d, the throttle 103c,
the oil storage chamber 148, and the communication passage 104e1
form the pressure release passage 146.
[0059] Here, the oil storage chamber 148 is disposed on the
pressure release passage 146 that allows the crank chamber 140 and
the suction chamber 141 to communicate with each other, and the
throttle 103c is disposed on the upstream side (crank chamber 140
side) of the oil storage chamber 148. Therefore, the oil storage
chamber 148 becomes a pressure region (a region with the same
pressure as that of the suction chamber 141) of the suction chamber
141.
[0060] Since the throttle 103c is formed in the valve plate 103
that defines the oil storage chamber 148, formation also including
the adjustment of opening area is easy. However, the throttle 103c
may be formed in the suction valve forming sheet 152, the discharge
valve forming sheet 138, or the like. Additionally, the
communication passage 104e1 may be, for example, a through-hole
that passes through the second annular partition wall 104e instead
of the groove.
[0061] The oil storage chamber 148 is disposed on the pressure
release passage 146 that allows the crank chamber 140 and the
suction chamber 141 to communicate with each other as described
above, and separates and stores oil from the refrigerant that flows
through the pressure release passage 146 depending on a difference
in weight (density difference).
[0062] The throttle 103c that is an inlet for the refrigerant to
the oil storage chamber 148, and the communication passage 104e1
that is an outlet for the refrigerant from the oil storage chamber
148 are formed in a relatively upper portion of the oil storage
chamber 148, and the refrigerant flows through the upper portion of
the oil storage chamber 148. Since the refrigerant is light and the
oil mixed into this refrigerant is heavy, the oil can be separated
within the oil storage chamber 148, and the oil can be stored at a
bottom portion of the oil storage chamber 148.
[0063] Therefore, the space within the oil storage chamber 148 is
divided into an upper gas space that forms the pressure release
passage 146, and a lower oil storage space in which the separated
oil is stored.
[0064] Here, in order to secure a sufficient oil storage space, it
is desirable that the throttle 103c and the communication passage
104e1 are disposed so as to communicate with an upper space of the
oil storage chamber 148 in the gravitational direction.
[0065] In addition, if the oil stored in the oil storage chamber
148 rises up to the height of the communication passage 104e1, the
stored oil flows out of the communication passage 104e1 into the
suction chamber 141. Therefore, the maximum amount of the oil
stored in the oil storage chamber 148 is determined depending on
the position of the communication passage 104e1. Therefore, it is
desirable that the throttle 103c be disposed above the
communication passage 104e1 in the gravitational direction.
[0066] The opening of the throttle 103c on the oil storage chamber
148 side faces a bather 104e2 formed integrally with the second
annular partition wall 104e, and configured such that a refrigerant
stream that flows out of the throttle 103c into the oil storage
chamber 148 collides against the barrier 104e2, and oil separation
is promoted.
[0067] The periphery of the second annular partition wall 104e
becomes the suction chamber 141, the oil stored in the oil storage
chamber 148 is cooled by a drawn in refrigerant and is not
influenced by the direct heat transfer from the discharge chamber
142.
[0068] An appropriate amount of the oil stored in the oil storage
chamber 148 flows back to the suction chamber 141 via an oil return
passage 149 formed over a lower side of the second annular
partition wall 104e in the gravitational direction, and contributes
to the lubrication of the inside of the compressor 100.
[0069] The oil return passage 149 includes: a communication hole
138a that is formed in the discharge valve forming sheet 138, is
open to the oil storage chamber 148, and functions as the throttle;
a communication hole 138b that is formed in the discharge valve
forming sheet 138 and is open to the suction chamber 141; and a
groove 103d that communicates with the communication hole 138a on
one end side thereof, communicates with the communication hole 138b
on the other end side thereof, and is formed in the valve plate
103.
[0070] In addition, either the communication hole 138b or the
groove 103d may be the throttle. Additionally, a filter may be
disposed at an inlet (oil storage chamber 148 side) of the
communication hole 138a. Moreover, the oil return passage 149 may
be directly formed in the second annular partition wall 104e, that
is, a groove or a hole may be provided and formed in the second
annular partition wall 104e.
[0071] According to the present embodiment, since the second
annular partition wall 104e that defines the oil storage chamber
148 is formed integrally with the cylinder head 104, the oil
storage chamber 148 can be easily formed.
[0072] Additionally, since the oil storage chamber 148 is defined
by the valve plate 103, the pressure release passage 146 can be
easily connected to the oil storage chamber 148.
[0073] Additionally, the periphery of the oil storage chamber 148
is the suction chamber 141, and is separated from the discharge
chamber 142. Therefore, the oil that flows out of the crank chamber
140 into the oil storage chamber 148 and is stored therein is
cooled by the drawn in refrigerant. Hence, a decrease in the
viscosity of the oil is suppressed and it is possible to maintain
excellent lubrication performance.
[0074] Additionally, according to the present embodiment, the
protruding height of the second annular partition wall 104e is set
such that a protruding-side end portion of the second annular
partition wall 104e presses the valve plate 103 when the cylinder
block 101 and the cylinder head 104 are fastened together.
Therefore, since the second annular partition wall 104e has a
function as the pressing means for holding down the floating of the
valve plate 103, it becomes unnecessary to provide exclusive
pressing means.
[0075] Additionally, according to the present embodiment, the lower
region of the oil storage chamber 148 in the gravitational
direction communicates with the suction chamber 141 via the oil
return passage 149 with a throttle straddling the second annular
partition wall 104e, and the oil return passage 149 is formed in at
least one of the valve plate 103 and interposed members (138, 139)
interposed between the valve plate 103 and the cylinder head 104.
Therefore, the oil return passage 149 with a throttle can be easily
formed.
[0076] Next, a second embodiment of the present invention will be
described with reference to FIG. 3.
[0077] In the embodiment of FIG. 3, the straight path 104a1 of the
suction passage 104a is formed to extend, and a constituent wall of
an extending portion 140a1' is bulged into the oil storage chamber
148. In other words, the extending portion 104a1' of the straight
path 104a1 is located behind a wall portion of the oil storage
chamber 148.
[0078] Moreover, the extending portion 104a1' of the straight path
104a1 is made to be directly open to a lower region of the suction
chamber 141. Therefore, the suction passage 104a communicates with
the suction chamber 141 at two points, that is, at the
communication passage 104a2 and the extending portion 104a1'.
[0079] Particularly, according to the present embodiment, the
suction passage 104a has a straight path (the straight path 104a1
and its extending portion 104a1') that linearly extends from the
outside of the cylinder head 104 in the radial direction toward the
inside thereof in the radial direction, and a constituent wall of
the straight path is bulged into the oil storage chamber 148.
Therefore, the oil stored in the oil storage chamber 148 can be
more easily cooled by the drawn in refrigerant, and the cooling
effect of the oil can be improved.
[0080] In addition, in the present embodiment, the suction passage
104a is allowed to communicate with the suction chamber 141 at two
points of the communication passage 104a2 and the extending portion
104a1'. However, the communication passage 104a2 may be eliminated,
and the suction passage 104a may be allowed to communicate with the
suction chamber 141 only via the extending portion 104a1'.
[0081] Next, a third embodiment of the present invention will be
described with reference to FIG. 4.
[0082] In the embodiment of FIG. 4, a tubular space 104g, which
communicates with the straight path 104a1 on one end side thereof
and communicates with the suction chamber 141 on the other end side
thereof via a throttle 104f, is formed on an extension of the
straight path 104a1 of the suction passage 104a, and a constituent
wall of the tubular space 104g is bulged into the oil storage
chamber 148.
[0083] According to the present embodiment, the refrigerant that is
drawn in, which has flowed into the suction passage 104a from an
external refrigerant circuit, can be separated into a refrigerant
and oil in the process of passing through the straight path 104a1,
and the oil separated from the drawn in refrigerant can be stored
in the tubular space 104g separate from the oil storage chamber
148. Additionally, since the constituent wall of the tubular space
104g is bulged into the oil storage chamber 148, the oil stored in
the oil storage chamber 148 can be more easily cooled with the oil
separated from the drawn in refrigerant and stored in the tubular
space 104g, and the cooling effect of the oil can be improved. This
is because the oil separated from the drawn in refrigerant has a
temperature lower than the oil separated from the refrigerant that
flows through the pressure release passage 146.
[0084] Next, a fourth embodiment of the present invention will be
described with reference to FIG. 5.
[0085] In the embodiment of FIG. 5, the straight path 104a1 of the
suction passage 104a and the oil storage chamber 148 communicate
with each other via a connecting path 104h.
[0086] That is, the suction passage 104a has the straight path
104a1 that linearly extends from the outside of the cylinder head
104 in the radial direction toward the inside thereof in the radial
direction on the upper side in the gravitational direction, and the
upper region of the oil storage chamber 148 in the gravitational
direction communicates with the connecting path 104h that extends
from the straight path 104a1. In addition, in the present
embodiment, the straight path 104a1 serving as the suction passage
104a indicates up to a portion connected to the communication
passage 104a2.
[0087] The connecting path 104h has a smaller-diameter portion
104h1 disposed on the oil storage chamber 148 side, and a
larger-diameter portion 104h2 disposed on the straight path 104a1
side. The smaller-diameter portion 104h1 has a smaller diameter
than the larger-diameter portion 104h2.
[0088] The straight path 104a1 of the suction passage 104a and the
suction chamber 141 communicate with each other via the
communication passage 104a2, and communicate with each other via
the connecting path 104h, the upper region of the oil storage
chamber 148 in the gravitational direction, and the communication
passage 104e1. Therefore, the connecting path 104h, the upper
region of the oil storage chamber 148 in the gravitational
direction, and the communication passage 104e1 form a portion of
the suction passage 104a.
[0089] In addition, since the flow passage cross-sectional area of
the smaller-diameter portion 104h1 is set to be smaller than the
minimum flow passage cross-sectional area of the straight path
104a1 and the communication passage 104a2, a mainstream of the
drawn in refrigerant flows through the communication passage
104a2.
[0090] Therefore, in the oil storage chamber 148, oil is separated
due to a difference in weight (density difference) from a
refrigerant gas flow that flows toward the suction chamber 141 from
the crank chamber 140, the separated oil is stored in the lower
region of the oil storage chamber 148, and the refrigerant gas
reaches the suction chamber 141 via the communication passage
104e1.
[0091] Additionally, although the refrigerant that circulates
through the external refrigerant circuit flows into the suction
chamber 141 from the suction passage 104a, the oil that circulates
with the drawn in refrigerant also flows into the suction chamber.
Since the oil storage chamber 148 is on the extension of the
straight path 104a1, the oil separated from the drawn in
refrigerant due to the difference in weight is collected in the
larger-diameter portion 104h2 of the connecting path 104h, and
flows into the oil storage chamber 148 via the smaller-diameter
portion 104h1. Since the refrigerant flowing into the oil storage
chamber 148 is suppressed by the smaller-diameter portion 104h1, it
is possible to prevent the stored oil from being stirred.
[0092] In the present embodiment, the oil storage chamber 148 can
not only separate and store oil from the refrigerant that flows
into the suction chamber 141 from the crank chamber 140, but can
also store the oil separated from the refrigerant that flows
through the suction passage 104a.
[0093] Additionally, since the connecting path 104h can be formed
integrally with the straight path 104a1, there is little effect on
cost.
[0094] According to the present embodiment, the suction passage
104a has the straight path 104a1 that linearly extends from the
outside of the cylinder head 104 in the radial direction toward the
inside thereof in the radial direction, the upper region of the oil
storage chamber 148 in the gravitational direction communicates
with the connecting path 104h that extends from the straight path
104a1, and the connecting path 104h has the smaller-diameter
portion 104h1 having a smaller diameter than the straight path
104a1. Therefore, the oil separated from the drawn in refrigerant
can also be stored in the oil storage chamber 148. Since the
connecting path 104h has the smaller-diameter portion 104h1, it is
possible to prevent the inflow of the drawn in refrigerant into the
oil storage chamber 148, and it is possible to prevent the stored
oil from being stiffed.
[0095] Additionally, according to the present embodiment, the
connecting path 104h has the larger-diameter portion 104h2 that is
disposed closer to the straight path 104a1 than the
smaller-diameter portion 104h1 and has a larger diameter than the
smaller-diameter portion 104h1. Therefore, since the
larger-diameter portion 104h2 becomes an oil storage space, the oil
separated from the drawn in refrigerant due to the difference in
weight can be effectively guided to the oil storage chamber
148.
[0096] Additionally, according to the present embodiment, the
suction passage 104a has a first passage (communication passage
104a2) that directly reaches the suction chamber 141 from the
straight path 104a1, and a second passage (communication passage
104e1) that reaches the suction chamber 141 via the connecting path
104h and the upper region of the oil storage chamber 148 in the
gravitational direction from the straight path 104a1, and the
minimum flow passage cross-sectional area (the cross-sectional area
of the smaller-diameter portion 104h1) of the second passage is set
to be smaller than the minimum flow passage cross-sectional area of
the first passage. Therefore, the oil separated from the drawn in
refrigerant can easily flow into the oil storage chamber 148 from
the connecting path 104h.
[0097] Next, a fifth embodiment of the present invention will be
described with reference to FIG. 6.
[0098] In the embodiment of FIG. 6, the communication passage 104e1
(refer to FIGS. 1 to 5) that allows the oil storage chamber 148 and
the suction chamber 141 to directly communicate with each other is
eliminated. Also, the straight path 104a1 of the suction passage
104a and the oil storage chamber 148 communicate with each other
via the connecting path 104h, and the connecting path 104h is
configured to form a portion of the pressure release passage
146.
[0099] That is, the suction passage 104a has the straight path
104a1 that linearly extends from the outside of the cylinder head
104 in the radial direction toward the inside thereof in the radial
direction on the upper side in the gravitational direction, and the
upper region of the oil storage chamber 148 in the gravitational
direction communicates with the connecting path 104h that extends
from the straight path 104a1. In addition, in the present
embodiment, the straight path 104a1 serving as the suction passage
104a indicates up to a portion connected to the communication
passage 104a2.
[0100] The connecting path 104h also serves as a portion of the
pressure release passage 146 that allows the oil storage chamber
148 and the suction chamber 141 to communicate with each other, and
the flow passage cross-sectional area of the connecting path 104h
is set to be greater than the flow passage cross-sectional area of
the throttle 103c.
[0101] Therefore, in the oil storage chamber 148, oil is separated
due to a difference in weight (density difference) from a
refrigerant gas flow that flows toward the suction chamber 141 from
the crank chamber 140, the separated oil is stored in the lower
region of the oil storage chamber 148, and the refrigerant gas
reaches the suction chamber 141 via the connecting path 104h, the
straight path 104a1, and the communication passage 104a2.
[0102] Additionally, although the refrigerant that circulates
through the external refrigerant circuit flows into the suction
chamber 141 from the suction passage 104a, the oil that circulates
with the drawn in refrigerant also flows into the suction chamber.
Since the oil storage chamber 148 is on the extension of the
straight path 104a1, the oil separated from the drawn in
refrigerant due to the difference in weight flows into the oil
storage chamber 148 from the connecting path 104h and is stored
therein.
[0103] In the present embodiment, there is no need for providing
the communication passage 104e1 (refer to FIGS. 1 to 5) in the
second annular partition wall 104e, and it is possible to simplify
a passage configuration.
[0104] According to the present embodiment, the suction passage
104a has the straight path 104a1 that linearly extends from the
outside of the cylinder head 104 in the radial direction toward the
inside thereof in the radial direction, the upper region of the oil
storage chamber 148 in the gravitational direction communicates
with the connecting path 104h that extends from the straight path
104a1, and the connecting path 104h forms a portion of the pressure
release passage 146. Therefore, since the connecting path 104h
serves as the pressure release passage 146, it is possible to
simplify passage formation.
[0105] Next, a sixth embodiment of the present invention will be
described with reference to FIG. 7.
[0106] In the embodiment of FIG. 7, the straight path 104a1, the
upper region of the oil storage chamber 148 in the gravitational
direction, and the communication passage 104e1 are configured so as
to become the suction passage 104a.
[0107] Additionally, although the refrigerant that circulates
through the external refrigerant circuit flows into the oil storage
chamber 148 from the straight path 104a1, the oil that circulates
with the drawn in refrigerant also flows into the oil storage
chamber. The opening of the straight path 104a1 on the oil storage
chamber 148 side faces a barrier 104i that extends from the end
wall (bottom wall) 104c of the cylinder head 104. Therefore, the
drawn in refrigerant is collided against the barrier 104i to
promote the separation of the oil, the separated oil is stored in
the lower region of the oil storage chamber 148, and the
refrigerant gas flows into the suction chamber 141 from the
communication passage 104e1. Therefore, the same effects as those
of the aforementioned embodiments can be obtained.
[0108] In addition, it goes without saying that the illustrated
embodiments merely illustrate the present invention, and the
present invention includes various improvements and modifications
made by those skilled in the art within the scope of the claims in
addition to those directly illustrated in the described
embodiments.
[0109] For example, in the above embodiments, the oil storage
chamber 148 is the pressure region (the region having the same
pressure as that of the suction chamber 141) of the suction chamber
141 by disposing the throttle 103c of the pressure release passage
146 upstream of the oil storage chamber 148. However, the oil
storage chamber 148 may be the pressure region (the region having
the same pressure as that of the crank chamber 140) of the crank
chamber 140 by disposing the throttle of the pressure release
passage 146 downstream of the oil storage chamber 148, and the oil
stored in the oil storage chamber 148 may be returned to the crank
chamber 140 via the throttle.
[0110] Additionally, in the above embodiments, the present
invention is applied to the variable displacement compressor.
However, the present invention is applicable to all reciprocating
compressors including a fixed-displacement compressor.
REFERENCE SYMBOL LIST
[0111] 100 variable displacement compressor [0112] 101 cylinder
block [0113] 101a cylinder bore [0114] 101b muffler forming wall
[0115] 101c communication passage [0116] 101d space [0117] 102
front housing [0118] 102a boss [0119] 103 valve plate [0120] 103a
suction hole [0121] 103b discharge hole [0122] 103c throttle [0123]
103d groove [0124] 104 cylinder head [0125] 104a suction passage
[0126] 104a1 straight path [0127] 104a2 communication passage
[0128] 104a1' extending portion of straight path [0129] 104b outer
peripheral wall [0130] 104c end wall [0131] 104d first annular
partition wall [0132] 104e second annular partition wall [0133]
104e1 communication passage [0134] 104e2 barrier [0135] 104f
throttle [0136] 104g tubular space [0137] 104h connecting path
[0138] 104h1 smaller-diameter portion [0139] 104h2 larger-diameter
portion [0140] 104i barrier [0141] 105 through bolt [0142] 106 lid
member [0143] 106a discharge port [0144] 110 driving shaft [0145]
111 swash plate [0146] 111a second arm [0147] 111b through-hole
[0148] 112 rotor [0149] 112a first arm [0150] 114 inclination angle
reducing spring [0151] 115 inclination angle increasing spring
[0152] 116 spring supporting member [0153] 120 link mechanism
[0154] 121 link arm [0155] 122 first connecting pin [0156] 123
second connecting pin [0157] 130 shaft seal device [0158] 131, 132
bearing [0159] 133 bearing [0160] 134 thrust plate [0161] 135
adjusting screw [0162] 136 piston [0163] 137 shoe [0164] 138
discharge valve forming sheet [0165] 138a, 138b communication hole
[0166] 139 head gasket [0167] 140 crank chamber [0168] 141 suction
chamber [0169] 142 discharge chamber [0170] 143 muffler space
[0171] 144 communication passage [0172] 145 pressure supply passage
[0173] 146 pressure release passage [0174] 147 pressure
introduction passage [0175] 148 oil storage chamber [0176] 149 oil
return passage [0177] 150 center gasket [0178] 151 cylinder gasket
[0179] 152 suction valve forming sheet [0180] 200 check valve
[0181] 300 control valve
* * * * *