U.S. patent application number 13/637570 was filed with the patent office on 2013-02-28 for compressor.
This patent application is currently assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI. The applicant listed for this patent is Naofumi Kimura, Yasuhiro Kondoh, Masakatsu Kuroishi, Takahiro Moroi, Masakazu Obayashi, Kazunori Yoshida, Fumitaka Yoshizumi. Invention is credited to Naofumi Kimura, Yasuhiro Kondoh, Masakatsu Kuroishi, Takahiro Moroi, Masakazu Obayashi, Kazunori Yoshida, Fumitaka Yoshizumi.
Application Number | 20130052066 13/637570 |
Document ID | / |
Family ID | 44762773 |
Filed Date | 2013-02-28 |
United States Patent
Application |
20130052066 |
Kind Code |
A1 |
Moroi; Takahiro ; et
al. |
February 28, 2013 |
COMPRESSOR
Abstract
A compressor includes a discharge chamber, a compression
chamber, a partition wall, and a discharge reed valve. The
partition wall is arranged between the discharge chamber and the
compression chamber and includes a fixing surface that faces the
discharge chamber. The partition wall includes a discharge port
that can communicate the discharge chamber and the compression
chamber. The discharge reed valve includes a fixed portion, an
intermediate portion, and a valve portion. The partition wall
includes a supporting portion, a receiving portion, and a main
coupling portion. The supporting portion supports a central region
of the valve portion. The receiving portion receives a distal
region of the valve portion. The main coupling portion extends from
the supporting portion to couple the supporting portion and the
receiving portion in order to divide into two a distal discharging
region of the discharge port.
Inventors: |
Moroi; Takahiro;
(Kariya-shi, JP) ; Obayashi; Masakazu;
(Kariya-shi, JP) ; Kimura; Naofumi; (Kariya-shi,
JP) ; Yoshizumi; Fumitaka; (Nisshin-shi, JP) ;
Kuroishi; Masakatsu; (Seto-shi, JP) ; Kondoh;
Yasuhiro; (Nisshin-shi, JP) ; Yoshida; Kazunori;
(Nagoya-shi, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Moroi; Takahiro
Obayashi; Masakazu
Kimura; Naofumi
Yoshizumi; Fumitaka
Kuroishi; Masakatsu
Kondoh; Yasuhiro
Yoshida; Kazunori |
Kariya-shi
Kariya-shi
Kariya-shi
Nisshin-shi
Seto-shi
Nisshin-shi
Nagoya-shi |
|
JP
JP
JP
JP
JP
JP
JP |
|
|
Assignee: |
KABUSHIKI KAISHA TOYOTA
JIDOSHOKKI
Aichi-ken
JP
|
Family ID: |
44762773 |
Appl. No.: |
13/637570 |
Filed: |
March 31, 2011 |
PCT Filed: |
March 31, 2011 |
PCT NO: |
PCT/JP2011/058215 |
371 Date: |
September 26, 2012 |
Current U.S.
Class: |
417/559 |
Current CPC
Class: |
F04B 27/1009 20130101;
F04B 39/1073 20130101; F16K 15/16 20130101 |
Class at
Publication: |
417/559 |
International
Class: |
F04B 39/10 20060101
F04B039/10 |
Foreign Application Data
Date |
Code |
Application Number |
Mar 31, 2010 |
JP |
2010-083872 |
Mar 28, 2011 |
JP |
2011-070961 |
Claims
1. A compressor comprising: a discharge chamber; a compression
chamber; a partition wall arranged between the discharge chamber
and the compression chamber and including a fixing surface that
faces the discharge chamber, wherein the partition wall includes a
discharge port that can communicate the discharge chamber and the
compression chamber; and a discharge reed valve having a length
extending along a longitudinal direction, a distal end, and a basal
end, wherein the discharge reed valve includes a fixed portion
located at the basal end and fixed to the fixing surface, an
intermediate portion extending from the fixed portion toward the
distal end and being liftable relative to the fixing surface, and a
valve portion further extending from the intermediate portion
toward the distal end and being capable of opening and closing the
discharge port, wherein the partition wall includes a supporting
portion that supports a central region of the valve portion, a
receiving portion that receives a distal region of the valve
portion, and a main coupling portion that extends from the
supporting portion to couple the supporting portion and the
receiving portion in order to divide into two a distal discharging
region of the discharge port located at a distal side of the
supporting portion in the longitudinal direction, the discharge
port extends through the partition wall so as to leave the
supporting portion, the receiving portion, and the main coupling
portion in the partition wall, and the receiving portion has a
larger width than the supporting portion in a direction orthogonal
to the longitudinal direction.
2. The compressor according to claim 1, wherein the partition wall
includes a sub-coupling portion extending from the supporting
portion to divide at least into two a basal discharging region of
the discharge port located at a basal side of the supporting
portion in the longitudinal direction, and the discharge port
extends through the partition wall so as to leave the supporting
portion, the receiving portion, the main coupling portion, and the
sub-coupling portion in the partition wall.
3. The compressor according to claim 2, wherein the sub-coupling
portion extends along the longitudinal direction; and the discharge
port is divided into two port segments by the sub-coupling portion,
the supporting portion, the main coupling portion, and the
receiving portion.
4. The compressor according to claim 3, wherein the sub-coupling
portion, the supporting portion, the main coupling portion, and the
receiving portion have widths that increase toward the distal side
in the longitudinal direction.
5. The compressor according to claim 2, wherein the sub-coupling
portion includes a first sub-coupling portion, which extends along
the longitudinal direction, a second sub-coupling portion, which
extends at an angle of 90.degree. in a clockwise direction from the
main coupling portion, and a third sub-coupling portion, which
extends along at an angle of 90.degree. in a counterclockwise
direction from the main coupling portion, and the discharge port is
divided into four port segments by the first sub-coupling portion,
the second sub-coupling portion, the third sub-coupling portion,
the supporting portion, the main coupling portion, and the
receiving portion.
6. The compressor according to claim 2, wherein the sub-coupling
portion includes a first sub-coupling portion, which extends at an
angle of 120.degree. in a clockwise direction from the main
coupling portion, and a second sub-coupling portion, which extends
at an angle of 120.degree. in a counterclockwise direction from the
main coupling portion, and the discharge port is divided into three
port segments by the first sub-coupling portion, the second
sub-coupling portion, the supporting portion, the main coupling
portion, and the receiving portion.
7. The compressor according to claim 2, wherein the sub-coupling
portion, the supporting portion, the main coupling portion, and the
receiving portion are flush with the fixing surface.
8. The compressor according to claim 2, wherein the sub-coupling
portion, the supporting portion, the main coupling portion, and the
receiving portion include a recess that is recessed from the fixing
surface.
9. The compressor according to claim 8, wherein the recess extends
in a groove-shaped form along the longitudinal direction.
10. The compressor according to claim 8, wherein the recess extends
in a groove-shaped form along the lateral direction.
11. The compressor according to claim 2, wherein the sub-coupling
portion, the supporting portion, the main coupling portion, and the
receiving portion include a crowning.
12. The compressor according to claim 1, wherein the valve portion
is enlarged in a direction that differs from the longitudinal
direction as compared with the intermediate portion.
13. The compressor according to claim 1, wherein the fixing surface
includes a first groove portion, which extends around the discharge
port, and a valve seat surface, which is located between the
discharge port and the first groove portion, the valve portion can
come into contact with the valve seat surface to close the
discharge port, and the first groove portion extends to a range
overlapping the intermediate portion when viewing the discharge
reed valve from above in a state closing the discharge port.
14. The compressor according to claim 13, wherein the first groove
portion is an annular groove that surrounds the discharge port in a
circumferential direction.
15. The compressor according to claim 13, wherein the first groove
portion has a C-shaped form and surrounds the discharge port in a
circumferential direction excluding a portion at the distal side in
the longitudinal direction.
16. The compressor according to claim 1, wherein the fixing surface
includes a second groove portion, which is located at the basal
side of the discharge port in the longitudinal direction, and a
communication groove, which is located in a range overlapped with
the intermediate portion and which extends along the longitudinal
direction, the second groove portion extends across the
intermediate portion in a lateral direction when viewing the
discharge reed valve from above in a state closing the discharge
port, and the communication groove communicates the first groove
portion and the second groove portion.
Description
TECHNICAL FIELD
[0001] The present invention relates to a compressor.
BACKGROUND ART
[0002] The following compressor is known (e.g., patent document 1).
In this compressor, a valve plate is arranged between a discharge
chamber and a compression chamber. A discharge port, which extends
through the valve plate, can communicate the discharge chamber and
the compression chamber. A discharge reed valve, which is located
in the discharge chamber, opens and closes the discharge port.
[0003] The discharge reed valve includes a fixed portion, which is
fixed to a fixing surface that is a surface of the valve plate at a
side facing the discharge chamber, an intermediate portion, which
extends toward a distal side along a longitudinal direction from
the fixed portion and can be lifted, and a valve portion, which
extends toward the distal side along the longitudinal direction
from the intermediate portion to open and close the discharge port.
An annular groove that surrounds the entire circumference of the
discharge port is arranged in the fixing surface. A portion of the
fixing surface between the discharge port and the annular groove
forms a valve seat surface that is flush with the portion of the
fixing surface outward from the annular groove. In a state in which
the discharge reed valve is closing the discharge port, a distal
part of the valve portion extends beyond the valve seat surface in
the longitudinal direction.
[0004] In this type of compressor, it is ideal that the discharge
port immediately opens at the moment the difference between the
pressure in the discharge chamber and the pressure in the
compression chamber exceeds zero. However, when lubricating oil is
present like in an actual machine, as shown in FIG. 23, an adhesive
force S acts in a direction inhibiting the opening of a discharge
reed valve 81. Thus, the discharge reed valve 81 does not open a
discharge port 82 until a force F produced by the pressure
difference prevails over the adhesive force S. In such a situation,
a bore inner pressure (pressure in the compression chamber) is as
shown in FIG. 24. Such a phenomenon in which the bore inner
pressure becomes higher than the discharging pressure is referred
to as over-compression and causes power loss. The adhesive force is
produced by the oil film pressure of the lubricating oil. The oil
film pressure is lower than the surrounding pressure when the
discharge reed valve 81 attempts to separate from the valve plate
27. The inventors refer to this effect as a "negative squeeze
effect".
PATENT DOCUMENT
[0005] Patent Document 1: Japanese Laid-Open Patent Publication No.
11-117867
DISCLOSURE OF THE INVENTION
[0006] Such power loss leads to an increase in energy consumption.
From the standpoint of reducing energy consumption, it is desirable
that the power loss be further decreased.
[0007] Further, in the compressor described above, the discharge
reed valve may be damaged, and it is desirable that the durability
be improved.
[0008] It is an object of the present invention to provide a
compressor that can further reduce power loss and exhibit higher
durability.
[0009] In order to achieve the above object, the inventors have
analyzed the conventional compressor in detail. As a result, the
inventors have taken notice of the enlargement of the discharge
port and the moment the discharge reed valve closes.
[0010] More specifically, if the discharge port has, for example, a
circular shape when viewed from above, a pressure receiving area of
the valve portion that opens and closes the discharge port
increases in proportion to the square of the diameter of the
discharge port. Thus, the force opening the discharge port
increases when the discharge port is enlarged. In this case, the
adhesive force of the lubricating oil that inhibits the valve
opening acts on the circumferential edge of the discharge port and
is thus only proportional to the diameter of the discharge port.
This decreases the adhesive force when the discharge port is
enlarged. Therefore, when the discharge port is enlarged,
over-compression can be reduced, and power loss can be
suppressed.
[0011] However, in the simulation conducted by the inventors, when
the discharge port was enlarged, a central region of the valve
portion was greatly bent into the discharge port due to the force
of inertia or the pressure difference of the compression chamber
and the discharge chamber (hereinafter referred to as "pressure
difference") during a suction stroke at the moment the discharge
reed valve closes. Thus, fatigue failure is apt to occur at the
valve portion. In particular, this tendency is stronger when the
compressor operates at high speeds. This lowers the durability of
the compressor.
[0012] In particular, in the simulation, at the valve portion, the
striking against the valve seat surface starts from the side of the
intermediate portion, and a stress wave is propagated toward the
distal side. Thus, if the valve portion of the discharge reed valve
has a circular shape when viewed from above, the valve portion
extending toward the distal side along the longitudinal direction
bends like a whip and strongly strikes the fixing surface. This is
because the mass of the discharge reed valve increases toward the
distal side along the longitudinal direction, and a large force of
inertia acts on the valve portion toward the distal side in the
longitudinal direction. This phenomenon becomes remarkable when the
intermediate portion is rectangular with its long sides extending
in the longitudinal direction and the valve portion is circular
having a diameter that is larger than or equal to the short sides
of the intermediate portion so that the discharge reed valve
greatly opens the discharge port.
[0013] In this manner, the inventors have completed the present
invention.
[0014] One aspect of the present invention provides a compressor
comprising a discharge chamber, a compression chamber, a partition
wall, and a discharge reed valve. The partition wall is arranged
between the discharge chamber and the compression chamber and
includes a fixing surface that faces the discharge chamber. The
partition wall includes a discharge port that can communicate the
discharge chamber and the compression chamber. The discharge reed
valve has a length extending along a longitudinal direction, a
distal end, and a basal end. The discharge reed valve includes a
fixed portion, an intermediate portion, and a valve portion. The
fixed portion is located at the basal end and fixed to the fixing
surface. The intermediate portion extends from the fixed portion
toward the distal end and is liftable relative to the fixing
surface. The valve portion further extends from the intermediate
portion toward the distal end and is capable of opening and closing
the discharge port. The partition wall includes a supporting
portion, a receiving portion, and a main coupling portion. The
supporting portion supports a central region of the valve portion.
The receiving portion receives a distal region of the valve
portion. The main coupling portion extends from the supporting
portion to couple the supporting portion and the receiving portion
in order to divide into two a distal discharging region of the
discharge port located at a distal side of the supporting portion
in the longitudinal direction. The discharge port extends through
the partition wall so as to leave the supporting portion, the
receiving portion, and the main coupling portion in the partition
wall. The receiving portion has a larger width than the supporting
portion in a direction orthogonal to the longitudinal
direction.
[0015] In the compressor of the present invention, when the force
of inertia or the pressure difference acts to greatly bend the
central region of the valve portion into the discharge port at the
moment the discharge reed valve closes the central region of the
valve portion, the supporting portion supports the central region
of the valve portion. Further, in a preferred manner, the
supporting portion, the main coupling portion, and the receiving
portion support the valve portion, which strikes the fixing surface
while bending like a whip toward the distal side along the
longitudinal direction. This prevents fatigue failure at the valve
portion.
[0016] Further, in the compressor of the present invention, the
receiving portion has a larger width than the supporting portion in
a direction orthogonal to the longitudinal direction. Thus, when
the valve portion of the discharge reed valve strikes the receiving
portion, the lubricating oil on the receiving portion reduces the
striking force due to the squeeze film effect so that only a small
stress acts on the valve portion, and a large stress is not
produced at the distal region of the valve portion. This further
prevents fatigue failure at the discharge reed valve, and the
compressor can exhibit high durability. With the squeeze film
effect, when a gap between parallel surfaces decreases at the
velocity V, due to the viscosity of the fluid, the fluid resists
being pushed out of the gap and generates pressure (proportional to
viscosity coefficient and velocity V).
[0017] In the compressor, due to the operations described above,
the pressure receiving area of the valve portion is increased, the
force that opens the discharge port is increased by increasing the
port diameter, while the increase of the adhesive force of the
lubricating oil inhibiting valve opening is limited. Thus,
over-compression can be decreased and power loss can be
suppressed.
[0018] Accordingly, the compressor can further reduce power loss
and exhibit higher durability.
[0019] Further, in the compressor, discharging pulsation can be
reduced by limiting the opening delay of the discharge reed valve.
This improves the quietness of the compressor. Further, in the
compressor, over-compression is decreased by increasing the port
diameter. Thus, exciting force, bearing load, piston side force
(lateral force), and the like have a tendency of decreasing. This
reduces mechanical loss and suppresses wear. As a result, power
consumption can be decreased, and reliability can be improved.
[0020] Japanese Laid-Open Patent Publication No. 2009-235913
discloses a compressor including a supporting portion that divides
an entire suction port into two. However, in regard with the
disclosed technique of the publication, the present invention has a
significant advantage in that superior effects are obtained at the
discharge side, which requires capacities that can endure harsher
conditions.
[0021] When the widths of the supporting portion, the main coupling
portion, and the receiving portion are increased, fatigue failure
of the valve portion can be prevented. In contrast, when the areas
of the supporting portion, the main coupling portion, and the
receiving portion are increased, the area of the discharge port is
decreased. Further, an increase in the contact area of the
supporting portion, the main coupling portion, and the receiving
portion increases adhesive force, and the discharge port thus
cannot easily open. To resolve these contradicting problems, the
present invention allows for selection of the suitable size and
shape of the supporting portion, the main coupling portion, and the
receiving portion.
[0022] Preferably, the partition wall includes a sub-coupling
portion extending from the supporting portion to divide at least
into two a basal discharging region of the discharge port located
at a basal side of the supporting portion in the longitudinal
direction. The discharge port extends through the partition wall so
as to leave the supporting portion, the receiving portion, the main
coupling portion, and the sub-coupling portion in the partition
wall.
[0023] In this case, the discharge port is divided into two or more
port segments by the supporting portion, the receiving portion,
main coupling portion, and the sub-coupling portion. This increases
the strength of the supporting portion, and the valve portion that
bends like a whip can easily be supported sequentially from the
basal side toward the distal side in the longitudinal direction.
Further, fatigue failure is effectively prevented at the valve
portion.
[0024] Preferably, the sub-coupling portion extends along the
longitudinal direction. The discharge port is divided into two port
segments by the sub-coupling portion, the supporting portion, the
main coupling portion, and the receiving portion.
[0025] In this case, the advantages in which fatigue failure at the
valve portion is prevented and the discharge port easily opens are
obtained.
[0026] Preferably, the sub-coupling portion, the supporting
portion, the main coupling portion, and the receiving portion have
widths that increase toward the distal side in the longitudinal
direction.
[0027] In this case, the discharge port easily opens at a basal
discharging region, the receiving portion receives a distal region
of the valve portion in a preferred manner, and fatigue failure at
the valve portion can be further prevented.
[0028] Preferably, the sub-coupling portion includes a first
sub-coupling portion, which extends along the longitudinal
direction, a second sub-coupling portion, which extends at an angle
of 90.degree. in a clockwise direction from the main coupling
portion, and a third sub-coupling portion, which extends along at
an angle of 90.degree. in a counterclockwise direction from the
main coupling portion. The discharge port is divided into four port
segments by the first sub-coupling portion, the second sub-coupling
portion, the third sub-coupling portion, the supporting portion,
the main coupling portion, and the receiving portion.
[0029] This also easily obtains the advantages in which fatigue
failure of the valve portion is prevented and the discharge port
easily opens.
[0030] Preferably, the sub-coupling portion includes a first
sub-coupling portion, which extends at an angle of 120.degree. in a
clockwise direction from the main coupling portion, and a second
sub-coupling portion, which extends at an angle of 120.degree. in a
counterclockwise direction from the main coupling portion. The
discharge port is divided into three port segments by the first
sub-coupling portion, the second sub-coupling portion, the
supporting portion, the main coupling portion, and the receiving
portion.
[0031] This also easily obtains the advantages in which fatigue
failure of the valve portion is prevented and the discharge port
easily opens.
[0032] Preferably, the sub-coupling portion, the supporting
portion, the main coupling portion, and the receiving portion are
flush with the fixing surface.
[0033] This reduces machining costs.
[0034] Preferably, the sub-coupling portion, the supporting
portion, the main coupling portion, and the receiving portion
include a recess that is recessed from the fixing surface.
[0035] In this case, the contact area of the valve portion of the
discharge reed valve and the sub-coupling portion, the supporting
portion, the main coupling portion, and the receiving portion
decreases, the adhesive force decreases, and the valve easily
opens.
[0036] Preferably, the recess extends in a groove-shaped form along
the longitudinal direction.
[0037] In this case, the contact area is decreased. Further, the
adhesive force produced by the negative squeeze effect when the
valve opens is decreased, and the valve easily opens.
[0038] Preferably, the recess extends in a groove-shaped form along
the lateral direction.
[0039] This decreases the contact area. Further, the amount of oil
supplied from the fixing surface to the sub-coupling portion, the
supporting portion, the main coupling portion, and the receiving
portion decreases, the adhesive force decreases, and the valve
easily opens.
[0040] Preferably, the sub-coupling portion, the supporting
portion, the main coupling portion, and the receiving portion
include a crowning.
[0041] In this case, the contact area of the valve portion of the
discharge reed valve and the sub-coupling portion, the supporting
portion, the main coupling portion, and the receiving portion
decreases, the adhesive force decreases, and the valve easily
opens.
[0042] Preferably, the valve portion is enlarged in a direction
that differs from the longitudinal direction as compared with the
intermediate portion.
[0043] In this case, enlargement of the discharge port and an
increase in the pressure receiving area of the valve portion can
easily be realized. Thus, the force that opens the discharge port
can be further increased, and an increase in the adhesive force of
lubricating oil that hinders valve opening at the intermediate
portion can be avoided. As a result, over-compression can be
further reduced, and power loss can be suppressed. Further, in this
case, the distal region of the valve portion can further easily
bend like a whip and strongly strikes the fixing surface. Thus, the
advantages of the supporting portion, the main coupling portion,
and the receiving portion become further prominent.
[0044] Preferably, the fixing surface includes a first groove
portion, which extends around the discharge port, and a valve seat
surface, which is located between the discharge port and the first
groove portion. The valve portion can come into contact with the
valve seat surface to close the discharge port. The first groove
portion extends to a range overlapping the intermediate portion
when viewing the discharge reed valve from above in a state closing
the discharge port.
[0045] In this case, the valve portion seals the discharge port
with the valve seat surface in a preferred manner.
[0046] Preferably, the first groove portion is an annular groove
that surrounds the discharge port in a circumferential
direction.
[0047] In this case, in a state in which the discharge reed valve
closes the discharge port, the intermediate portion is overlapped
with an arc portion in the annular groove facing the basal side in
the longitudinal direction over a larger area. Thus, the area in
which the fixing surface adheres to the intermediate portion is
decreased by an amount corresponding to the overlapping area.
[0048] Preferably, the first groove portion has a C-shaped form and
surrounds the discharge port in a circumferential direction
excluding a portion at the distal side in the longitudinal
direction.
[0049] In this case, the distance between the two ends of the
C-shaped groove at the distal side in the longitudinal direction
can be increased to easily form the receiving portion between the
two ends. Thus, when the valve portion of the discharge reed valve
strikes the receiving portion, the lubricating oil on the receiving
portion reduces the striking force. Thus, only a small stress acts
on the valve portion, and a large stress is not produced at the
distal region of the valve portion. As a result, the compressor
effectively prevents damage to the discharge reed valve and has a
superior durability.
[0050] Preferably, the fixing surface includes a second groove
portion, which is located at the basal side of the discharge port
in the longitudinal direction, and a communication groove, which is
located in a range overlapped with the intermediate portion and
which extends along the longitudinal direction. The second groove
portion extends across the intermediate portion in a lateral
direction when viewing the discharge reed valve from above in a
state closing the discharge port. The communication groove
communicates the first groove portion and the second groove
portion.
[0051] Portions in the fixing surface other than the communication
groove may be a contact portion that contacts the discharge reed
valve.
[0052] In this case, foreign substances are prevented from being
caught by the intermediate portion in a state in which the
discharge reed valve closes the discharge port. Further, when the
discharge reed valve opens, a multiphase jet flow including gas and
lubricating oil blows away the lubricating oil, which exists
between the intermediate portion and the fixing surface and thereby
removes the oil film. The jet flow is discharged outward in the
lateral direction of the discharge reed valve through the
communication groove and the second groove portion from the first
groove portion. This blows away the lubricating oil collected in
the first groove portion, the lubricating oil collected between the
fixing surface and the intermediate portion and the lubricating oil
collected in the second groove portion. Further, the communication
groove decreases the area of contact between the fixing surface and
the intermediate portion. Thus, the compressor advances the timing
at which the fixing surface and the intermediate portion separate
from each other. This suppresses over-compression of the gas.
BRIEF DESCRIPTION OF THE DRAWINGS
[0053] FIG. 1 is a cross-sectional view of a compressor according
to a first embodiment of the present invention.
[0054] FIG. 2 is an enlarged cross-sectional view showing a state
in which a discharge reed valve opens a discharge port in the
compressor of FIG. 1. FIG. 3 is a plan view showing a valve plate
and a discharge valve plate, which includes a plurality of
discharge reed valves, in the compressor of FIG. 1.
[0055] FIG. 4 is an enlarged plan view showing a state in which the
discharge reed valve closes the discharge port in the compressor of
FIG. 1.
[0056] FIG. 5 is an enlarged cross-sectional view taken along line
Z-Z of FIG. 4 showing a state in which the discharge reed valve
closes the discharge port in the compressor of FIG. 1.
[0057] FIG. 6 shows the compressor of FIG. 1, in which part (A)
shows a plan view of the discharge port, and the like, part (B)
shows a plan view of a discharging region, and part (C) shows a
cross-sectional view of a supporting portion.
[0058] FIG. 7 is a plan view of a discharge port and the like in a
compressor according to a second embodiment of the present
invention.
[0059] FIG. 8 is a plan view of a discharge port and the like in a
compressor according to a third embodiment of the present
invention.
[0060] FIG. 9 is a plan view of a discharge port and the like in a
compressor according to a fourth embodiment of the present
invention.
[0061] FIG. 10 is a cross-sectional view of a supporting portion
corresponding to line A-A of FIG. 6 in a compressor according to a
fifth embodiment of the present invention.
[0062] FIG. 11 is a cross-sectional view of a supporting portion
corresponding to line B-B of FIG. 6 in a compressor according to a
sixth embodiment of the present invention.
[0063] FIG. 12 is a cross-sectional view of a supporting portion
corresponding to line B-B of FIG. 6 in a compressor according to a
seventh embodiment of the present invention.
[0064] FIG. 13 is a cross-sectional view of a supporting portion
corresponding to line A-A of FIG. 6 in a compressor according to an
eighth embodiment of the present invention.
[0065] FIG. 14 is a cross-sectional view of a supporting portion
corresponding to line A-A of FIG. 6 in a compressor according to a
ninth embodiment of the present invention.
[0066] FIG. 15 is a cross-sectional view of a supporting portion
corresponding to line B-B of FIG. 6 in the compressor according to
the ninth embodiment of the present invention.
[0067] FIG. 16 shows a compressor according to a tenth embodiment
of the present invention, in which part (A) shows a plan view of a
discharge port and the like, and part (B) shows a cross-sectional
view of a supporting portion.
[0068] FIG. 17 is an enlarged plan view showing a state in which a
discharge reed valve closes a discharge port in a compressor
according to an eleventh embodiment of the present invention.
[0069] FIG. 18 is an enlarged cross-sectional view taken along line
Y-Y of FIG. 17 showing a state in which the discharge reed valve
closes the discharge port in the compressor of FIG. 17.
[0070] FIG. 19 is an enlarged plan view showing a state in which a
discharge reed valve closes a discharge port in a compressor
according to a twelfth embodiment of the present invention.
[0071] FIG. 20 is an enlarged plan view showing a state in which
the discharge reed valve closes the discharge port in a compressor
according to a thirteenth embodiment of the present invention.
[0072] FIG. 21 is an enlarged plan view showing a state in which a
discharge reed valve closes a discharge port in a compressor
according to a fourteenth embodiment of the present invention.
[0073] FIG. 22 is an enlarged plan view showing a state in which a
discharge reed valve closes a discharge port in a compressor
according to a fifteenth embodiment of the present invention.
[0074] FIG. 23 is a cross-sectional view illustrating the adhesive
force and the like that act on the discharge reed valve.
[0075] FIG. 24 is a graph showing the relationship of the time and
the bore inner pressure in a compressor.
DETAILED DESCRPTION OF THE PREFERRED EMBODIMENTS
[0076] First to fifteenth embodiments of the present invention will
now be described with reference to the drawings.
First Embodiment
[0077] A compressor of a first embodiment is a variable
displacement type swash plate compressor. As shown in FIG. 1, the
compressor is provided with a cylinder block 1 including a
plurality of cylinder bores 1a. The cylinder bores 1a are
concentrically arranged at equal angular intervals and extended
parallel to each other. The cylinder block 1 is held between a
front housing 3, which is located in the front, and a rear housing
5, which is located in the rear, and fastened by a plurality of
bolts 7 in this state. A crank chamber 9 is formed in the cylinder
block 1 and the front housing 3. The rear housing 5 includes a
suction chamber 5a and a discharge chamber 5b.
[0078] The front housing 3 includes a shaft hole 3a, and the
cylinder block 1 includes a shaft hole 1b. A drive shaft 11 is
supported in a rotatable manner by a shaft seal 9a and radial
bearings 9b and 9c in the shaft holes 3a and 1b. A pulley or an
electromagnetic clutch (not shown) is arranged on the drive shaft
11. A belt (not shown), which is driven by an engine of a vehicle,
runs about the pulley or an electromagnetic clutch pulley.
[0079] The drive shaft 11 is press-fitted to a lug plate 13, which
is arranged in the crank chamber 9. A thrust bearing 15 is arranged
between the lug plate 13 and the front housing 3. The drive shaft
11 is inserted through a swash plate 17, which is arranged in the
crank chamber 9, to support the swash plate 17. A link mechanism
19, which supports the swash plate 17 in a tiltable manner, couples
the lug plate 13 and the swash plate 17.
[0080] Each cylinder bore 1a accommodates a piston 21, which can
reciprocate in the bore 1a. A valve unit 23 is arranged between the
cylinder block 1 and the rear housing 5. As shown in the enlarged
view of FIG. 2, the valve unit 23 includes a suction valve plate
25, which is in contact with a rear end face of the cylinder block
1, a valve plate 27, which is in contact with the suction valve
plate 25, a discharge valve plate 29, which is in contact with the
valve plate 27, and a retainer plate 31, which is in contact with
the discharge valve plate 29. The retainer plate 31 also functions
as a gasket. The suction valve plate 25, the valve plate 27, the
discharge valve plate 29, and the retainer plate 31 are stacked in
this order to form the valve unit 23.
[0081] As shown in FIG. 1, front and rear shoes 33a and 33b, which
form a pair, are arranged between the swash plate 17 and each
piston 21. Each pair of the shoes 33a and 33b convert the wobbling
movement of the swash plate 17 into a reciprocating movement of the
piston 21.
[0082] The crank chamber 9 and the suction chamber 5a are connected
by a bleed passage 35a, and the crank chamber 9 and the discharge
chamber 5b are connected by an air supply passage (not shown). A
displacement control valve (not shown) is arranged in the air
supply passage. The displacement control valve is formed so that it
can vary the open degree of the air supply passage in accordance
with the suction pressure. A condenser is connected by a pipe to
the discharge chamber 5b. The condenser is connected by a pipe to
an evaporator via an expansion valve, and the evaporator is
connected by a pipe to the suction chamber 5a of the compressor.
The cylinder bores 1a, the pistons 21, and the valve unit 23 form
compression chambers 24.
[0083] A plurality of suction ports 23a are formed in the valve
plate 27, the discharge valve plate 29, and the retainer plate 31
to communicate the suction chamber 5a and the compression chambers
24. The suction valve plate 25 includes a plurality of suction reed
valves 25a that open and close the suction ports 23a.
[0084] As shown in FIGS. 2 to 5, a plurality of discharge ports 23b
are formed in the suction valve plate 25 and the valve plate 27 to
communicate the compression chambers 24 and the discharge chamber
5b.
[0085] As shown in part (A) of FIG. 6, the discharge port 23b for
each cylinder bore la is divided into two port segments 231 and 232
by a supporting portion 27t, a receiving portion 27h, a main
coupling portion 27v, and a sub-coupling portion 27w, which will be
described later.
[0086] As shown in FIG. 2, a plurality of discharge reed valves 29a
are formed in the discharge valve plate 29 to open and close the
port segments 231 and 232. The retainer plate 31 includes a
retainer 31a that restricts the lift length of each discharge reed
valve 29a. In the present example, as shown in FIG. 3, the
discharge valve plate 29 includes a circular portion and a
plurality of (six in the present embodiment) extended portions,
which extend radially outward in the radial direction from the
circular portion. The extended portions form the discharge reed
valves 29a that open and close the discharge ports 23b.
[0087] As shown in FIGS. 4 to 6, a ring-shaped annular groove 27a,
which surrounds the entire circumference of the discharge port 23b,
is arranged in a fixing surface 27f, which is the surface of the
valve plate 27 at the side facing the discharge chamber 5b. The
annular groove 27a serves as a first groove portion of the present
invention. In the fixing surface 27f, a ring-shaped region located
between the discharge port 23b and the annular groove 27a forms a
valve seat surface (also referred to as eyeglass portion) 27b that
is flush with a portion of the fixing surface 27f located outward
from the annular groove 27a. In the compressor, the suction valve
plate 25 and the valve plate 27 serve as a partition wall.
[0088] As shown in FIGS. 2 to 5, each of the six discharge reed
valves 29a has a basal end and a distal end and includes a fixed
portion 291a, which is positioned at the basal end and fixed to the
fixing surface 27f of the valve plate 27, an intermediate portion
292a, which extends toward the distal end along the longitudinal
direction of the discharge reed valve 29a from the fixed portion
291a and can be lifted, and a valve portion 293a, which extends
toward the distal end along the longitudinal direction from the
intermediate portion 292a to open and close the discharge port 23b.
In the present embodiment, the longitudinal direction is a
direction that is parallel to the fixing surface 27f and that
extends in the radial direction of the drive shaft 11. In FIG. 4,
in particular, the longitudinal direction from the basal end toward
the distal end of each discharge reed valve 29a is indicated by
reference character D1, and the longitudinal direction from the
distal end toward the basal end of each discharge reed valve 29a is
indicated by reference character D2.
[0089] As shown in FIG. 4, when viewing the intermediate portion
292a and the valve portion 293a from above, the intermediate
portion 292a has a rectangular shape in which the long sides extend
toward the distal side in the longitudinal direction D1. The valve
portion 293a is a circle concentric with the annular groove 27a
having the short side of the intermediate portion 292a as the
diameter. A diameter of the valve portion 293a in a direction
orthogonal to the longitudinal direction D1 is greater than the
diameter of the valve seat surface 27b in the longitudinal
direction D1.
[0090] As shown in FIGS. 4 and 6, the valve plate 27 includes the
supporting portion 27t, which receives the central region of the
valve portion 293a, the receiving portion 27h, which receives the
distal region of the valve portion 293a, the main coupling portion
27v, which couples the supporting portion 27t and the receiving
portion 27h, and the sub-coupling portion 27w, which extends from
the supporting portion 27t. The valve portion 293a is circular, and
the central region of the valve portion 293a is thus a fixed range
including the center of the valve portion 293a. The distal region
of the valve portion 293a is a fixed range located at the distal
side of the central region. As shown in part (B) of FIG. 6, the
valve plate 27 includes a discharging region A, through which the
discharge port 23b extends. The discharging region A includes a
semicircular distal discharging region A1 located at the distal
side in the longitudinal direction D1 and a semicircular basal
discharging region A2 located at the basal side in the longitudinal
direction D1. As shown in part (A) of FIG. 6, the supporting
portion 27t is a fixed range including the center O of the
discharging region A. The supporting portion 27t is arranged to
receive the central region of the valve portion 293a, and the
discharge port 23b is located at the left and right of the distal
side and the left and right of the basal side in the longitudinal
direction D1 as viewed from the supporting portion 27t. The main
coupling portion 27v extends from the supporting portion 27t to
divide the distal discharging region A1 into two. The sub-coupling
portion 27w divides the basal discharging region A2 into two. The
discharge port 23b extends through the valve plate 27 so as to
leave the supporting portion 27t, the receiving portion 27h, the
main coupling portion 27v, and the sub-coupling portion 27w in the
valve plate 27. The supporting portion 27t, the receiving portion
27h, the main coupling portion 27v, and the sub-coupling portion
27w are arranged in the valve plate 27 and thereby divide the
discharge port 23b into two port segments 231 and 232.
[0091] The sub-coupling portion 27w, the supporting portion 27t,
the main coupling portion 27v, and the receiving portion 27h are in
an I-shaped form extending toward the distal side in the
longitudinal direction D1. As shown in part (C) of FIG. 6, the
supporting portion 27t, the receiving portion 27h, the main
coupling portion 27v, and the sub-coupling portion 27w are flush
with the fixing surface 27f. The supporting portion 27t, the
receiving portion 27h, the main coupling portion 27v, and the
sub-coupling portion 27w are located between the port segments 231
and 232. The port segments 231 and 232, which are shaped in such a
manner, are formed, for example, by punching and pressing the valve
plate 27.
[0092] As shown in part (A) of FIG. 6, the supporting portion 27t,
the main coupling portion 27v, and the sub-coupling portion 27w
have the same width in a direction orthogonal to the longitudinal
direction D1. However, the receiving portion 27h has a larger width
than the supporting portion 27t, the main coupling portion 27v, and
the sub-coupling portion 27w. The port segments 231 and 232 have
corners that are not pointed but slightly rounded due to accuracy
limitations of the punching and pressing or the like.
[0093] As shown in FIGS. 2 to 5, a long groove 27c is arranged in
the fixing surface 27f at the basal side of the discharge port 23b
in the longitudinal direction D1 extending across the intermediate
portion 292a in its lateral direction. The long groove 27c serves
as a second groove portion of the present invention. As shown in
FIG. 4, when viewing the long groove 27c from above, the shape of
the long groove 27c is an oblong ellipse that is orthogonal to the
longitudinal direction D1. The long groove 27c is deeper than the
annular groove 27a.
[0094] In the above compressor, when the drive shaft 11 is driven
and rotated, the lug plate 13 and the swash plate 17 are
synchronously rotated with the drive shaft 11, and the pistons 21
are reciprocated in the cylinder bores 1a with a stroke
corresponding to the tilt angle of the swash plate 17. Thus,
refrigerant gas is drawn from the suction chamber 5a into each
compression chamber 24 and compressed. Then, the refrigerant gas is
discharged to the discharge chamber 5b. The refrigerant gas that
undergoes compression in the compressor contains lubricating oil in
the form of a mist. The lubricating oil collects on sliding and
moving parts such as the pistons 21, the shoes 33a and 33b, the
swash plate 17, and the like to suppress wear. The lubricating oil
is also collected in the annular grooves 27a and the long grooves
27c.
[0095] In this state, as shown in FIG. 2, the discharge reed valve
29a is elastically deformed at the intermediate portion 292a due to
the difference between the pressure in the discharge chamber 5b and
the pressure in the compression chamber 24. This opens the
discharge port 23b at the valve portion 293a. As shown in FIG. 5,
the valve portion 293a does not open the discharge port 23b until
the pressure difference prevails over the adhesive force of the
intermediate portion 292a.
[0096] In this compressor, when the force of inertia or pressure
difference acts to greatly bend the central region of the valve
portion 293a into the discharge port 23b at the moment the
discharge reed valve 29a closes the discharge port 23b, the
supporting portion 27t supports the central region of the valve
portion 293a. The sub-coupling portion 27w, the supporting portion
27t, the main coupling portion 27v, and the receiving portion 27h
are in an I-shaped form extending along the longitudinal direction
D1. This increases the strength of the supporting portion 27t, and
the valve portion 293a that strikes the fixing surface 27f while
bending like a whip toward the distal side along the longitudinal
direction D1 can easily be supported sequentially from the basal
side toward the distal side in the longitudinal direction D1. This
prevents fatigue failure at the valve portion 293a.
[0097] In this compressor, in particular, when the valve portion
293a of the discharge reed valve 29a strikes the receiving portion
27h, the lubricating oil on the receiving portion 27h reduces the
striking force due to the squeeze film effect so that only a small
stress acts on the valve portion 293a, and a large stress is not
produced at the distal end of the valve portion 293a. This further
prevents fatigue failure at the discharge reed valve 29a, and the
compressor can exhibit high durability.
[0098] In the compressor, due to the operations described above,
the pressure receiving area of the valve portion 293a is increased,
the force that opens the discharge port 23b is increased, and the
adhesive force of the lubricating oil inhibiting valve opening is
reduced. Thus, over-compression can be decreased and power loss can
be suppressed.
[0099] Accordingly, the compressor can further reduce power loss
and exhibit higher durability.
[0100] In the compressor, discharging pulsation can be reduced by
suppressing the opening delay of the discharge reed valve 29a. This
improves the quietness of the compressor. Further, in the
compressor, the peak pressure in the compression chamber 24 can be
lowered. Thus, the maximum compression load can be reduced, and the
reliability can be increased for the thrust bearing 15, the
surfaces of contact of the shoes 33a and 33b and the pistons 21,
the sliding surfaces of the shoes 33a and 33b and the swash plate
17, and the like.
[0101] In the compressor, the annular groove 27a is arranged in the
fixing surface 27f, as shown in FIG. 4. Thus, the intermediate
portion 292a and an arc portion 27g (shown in FIG. 4) of the
annular groove 27a are overlapped over a wide range in a state in
which the discharge reed valve 29a closes the discharge port 23b.
The overlapping area reduces the area of contact between the fixing
surface 27f and the intermediate portion 292a. This shortens
opening delays of the discharge reed valve 29a.
[0102] Further, in the compressor, the long groove 27c is arranged
in the fixing surface 27f. Thus, foreign substances are prevented
from being caught by the intermediate portion 292a in a state in
which the discharge reed valve 29a closes the discharge port
23b.
Second Embodiment
[0103] As shown in FIG. 7, in a compressor of a second embodiment,
four triangular port segments 231 to 234 having a center angle of
approximately 90 degrees are combined to form the discharge port
23b.
[0104] The supporting portion 27d, the main coupling portion 27v,
the receiving portion 27h, and first to third sub-coupling portions
27w1 to 27w3 are formed in the valve plate 27. The first
sub-coupling portion 27w1 extends along the longitudinal direction
D1. The second sub-coupling portion 27w2 extends at an angle of
90.degree. in the clockwise direction from the main coupling
portion 27v. The third sub-coupling portion 27w3 extends at an
angle of 90.degree. in the counterclockwise direction from the main
coupling portion 27v. The first to third sub-coupling portions 27w1
to 27w3 are arranged between the port segments 231 to 234. The
other parts are the same as the compressor of the first
embodiment.
[0105] This compressor also has the same advantages as the
compressor of the first embodiment.
Third Embodiment
[0106] As shown in FIG. 8, in a compressor of a third embodiment,
three triangular port segments 231 to 233 having a center angle of
approximately 120 degrees are combined to form the discharge port
23b.
[0107] A supporting portion 27e, the main coupling portion 27v, the
receiving portion 27h, and the first and second sub-coupling
portions 27w1, 27w2 are formed in the valve plate 27. The first
sub-coupling portion 27w1 extends at an angle of 120.degree. in the
clockwise direction from the main coupling portion 27v. The second
sub-coupling portion 27w2 extends at an angle of 120.degree. in the
counterclockwise direction from the main coupling portion 27v. The
supporting portion 27e, the main coupling portion 27v, the
receiving portion 27h, and the first and second sub-coupling
portions 27w1 and 27w2 are arranged between the port segments 231
to 233. The other parts are the same as the compressor of the first
embodiment.
[0108] This compressor also has the same advantages as the
compressor of the first embodiment.
Fourth Embodiment
[0109] As shown in FIG. 9, a compressor of a fourth embodiment
includes half-moon shaped port segments 231 and 232. The
sub-coupling portion 27w, a supporting portion 27i, the main
coupling portion 27v, and a receiving portion 27j have widths that
increase toward the distal side in the longitudinal direction D1.
The other parts are the same as the compressor of the first
embodiment.
[0110] This compressor also has the same advantages as the
compressor of the first embodiment.
[0111] The present invention drastically suppresses large bending
of the central region of the valve portion 293a into the discharge
port 23b. Thus, the valve portion 293a does not have to entirely
contact the supporting portion, the receiving portion, the main
coupling portion, and the sub-coupling portion. This allows the
forms of fifth to tenth embodiments described below to be
adopted.
Fifth Embodiment
[0112] As shown in FIG. 10, in a compressor of a fifth embodiment,
a recess 27k is formed in a surface of the supporting portion 27t
or the like. The recess 27k is formed to be groove-shaped at the
two lateral ends of the supporting portion 27t or the like. The
other parts are the same as the compressor of the first
embodiment.
[0113] In this compressor, the contact area of the valve portion
293a and the supporting portion 27t and the like is small. This
reduces the adhesive force and facilitates valve opening. In this
structure, the supporting portion 27t or the like has a width that
suppresses the contact area, and further, the adhesive force while
maintaining the strength. The other advantages are the same as the
first embodiment.
Sixth Embodiment
[0114] As shown in FIG. 11, in a compressor of a sixth embodiment,
a recess 28a is formed in a surface of the supporting portion 27t
or the like. The recess 28a is formed to groove-shaped along the
longitudinal direction of the supporting portion 27t or the like.
The other parts are the same as the compressor of the first
embodiment.
[0115] In this compressor, the contact area is reduced and the
adhesive force produced by the negative squeeze effect is reduced
during valve opening. This facilitates valve opening. The other
advantages are the same as the first embodiment.
Seventh Embodiment
[0116] As shown in FIG. 12, in a compressor of a seventh
embodiment, narrow groove-like recesses 27m are formed in the two
longitudinal ends of the supporting portion 27t or the like. The
recesses 27m extends along the lateral direction of the supporting
portion 27t or the like. The other parts are the same as the
compressor of the first embodiment.
[0117] In this compressor, the movement of lubricating oil is
blocked between the valve seat surface 27b and the supporting
portion 27t or the like by the recesses 27m. This stops the supply
of lubricating oil from the valve seat surface 27b to the
supporting portion 27t or the like, reduces the adhesive force that
acts between the supporting portion 27t or the like and the valve
portion 293a, and facilitates valve opening. The other advantages
are the same as the first embodiment.
Eighth Embodiment
[0118] As shown in FIG. 13, in a compressor of an eighth
embodiment, three narrow groove-like recesses 27n are located
between recesses 27s, which are arranged at the two ends, in the
supporting portion 27t or the like. The other parts are the same as
the compressor of the sixth embodiment.
[0119] In this compressor, the contact area of the supporting
portion 27t or the like and the valve portion 293a is reduced and
the adhesive force is reduced. This facilitates valve opening. The
other advantages are the same as the first embodiment.
Ninth Embodiment
[0120] As shown in FIG. 14 or 15, in a compressor of a ninth
embodiment, a crowning 27p is formed on the supporting portion 27t
or the like. The other parts are the same as the compressor of the
first embodiment.
[0121] In this compressor, the contact area of the valve portion
293a and the supporting portion 27t or the like is reduced, the
adhesive force is reduced, and valve opening is facilitated. The
other advantages are the same as the first embodiment.
Tenth Embodiment
[0122] As shown in FIG. 16, in a compressor of a tenth embodiment,
a plurality of recesses 27q are formed by coining and then grinding
the supporting portion 27t or the like. The other parts are the
same as the compressor of the first embodiment. This compressor
also has the same advantages as the compressor of the sixth
embodiment.
Eleventh Embodiment
[0123] As shown in FIGS. 17 and 18, in a compressor of an eleventh
embodiment, a communication groove 27r, which extends toward the
distal side in the longitudinal direction D1, is formed in the
fixing surface 27f to communicate the annular groove 27a and the
long groove 27c. Portions of the fixing surface 27f other than the
communication groove 27r form a contact portion 27s that comes into
contact with the discharge reed valve 29a. The contact portion 27s
is located at the two laterals sides of the communication groove
27r in the fixing surface 27f. Further, the contact portion 27s is
overlapped with the intermediate portion 292a when the discharge
reed valve 29a is in state of closing the discharge port 23b as
viewed from above. In the present example, the width of the
communication groove 27r is about 50% to 75% the width of the
intermediate portion 292a. This ensures that the contact portion
27s supports the intermediate portion 292a.
[0124] In the compressor, when the discharge reed valve 29a opens,
some of a multiphase jet flow including the refrigerant gas and the
lubricating oil blows away the lubricating oil, which exists
between the intermediate portion 292a and the fixing surface 27f,
and thereby the multiphase jet flow removes the oil film. The jet
flow is discharged outward in the lateral direction of the
discharge reed valve 29a through the communication groove 27r and
the long groove 27c from the annular groove 27a. This blows away
the lubricating oil collected in the annular groove 27a, the
lubricating oil accumulated between the fixing surface 27f and the
intermediate portion 292a, and the lubricating oil collected in the
long groove 27c. The communication groove 27r decreases the area of
contact between the fixing surface 27f and the intermediate portion
292a. Thus, the compressor further advances the timing at which the
fixing surface 27f and the intermediate portion 292a separate from
each other. This suppresses over-compression of the refrigerant
gas. The other advantages are the same as the first embodiment.
Twelfth Embodiment
[0125] As shown in FIG. 19, in a compressor of a twelfth
embodiment, the valve portion 293a has a circular shape having a
diameter that is greater than or equal to the short sides of the
intermediate portion 292a. In other words, the valve portion 293a
is enlarged with respect to the intermediate portion 292a in a
direction differing from the longitudinal direction D1. The other
parts are the same as the first embodiment.
[0126] In this case, enlargement of the discharge port 23b and an
increase in the pressure receiving area of the valve portion 293a
can be easily realized. This further increases the force that opens
the discharge port 23b, and the adhesive force of the lubricating
oil that inhibits the valve opening in the intermediate portion
292a is prevented from being increased. As a result,
over-compression can be further reduced, and power loss can be
suppressed in an ensured manner. In this case, the distal end
toward the distal side in the longitudinal direction D1 of the
valve portion 293a is more easily bent like a whip and thus
strongly strikes the fixing surface 27f. Thus, the advantages of
the supporting portion 27t or the like become more prominent. The
other advantages are the same as the first embodiment.
Thirteenth Embodiment
[0127] As shown in FIG. 20, in a compressor of a thirteenth
embodiment, the supporting portion 27i or the like of the fourth
embodiment is used in lieu of the supporting portion 27t or the
like of the first embodiment, and a C-shaped groove 27y is used in
lieu of the annular groove 27a of the first embodiment. The
C-shaped groove 27y also serves as the first groove portion of the
present invention. The C-shaped groove 27y, which has an arcuate
shape concentric with the center O, is formed in the fixing surface
27f and surrounds the discharge port 23b in the circumferential
direction excluding the distal side in the longitudinal direction
D1. A region of the fixing surface 27f sandwiched by the opposing
ends of the C-shaped groove 27y defines a receiving portion 27j and
a receiving portion 27z. The other parts are the same as the first
embodiment.
[0128] In this case, the distance between the opposing ends of the
C-shaped groove 27y can be increased to facilitate formation of the
receiving portions 27j and 27z that are enlarged in the lateral
direction of the supporting portion 27i as compared with other
parts of the supporting portion 27i (parts of the supporting
portion 27i other than the receiving portions 27j and 27z). Thus,
when the valve portion 293a strikes the receiving portions 27j and
27z, the lubricating oil on the large receiving portions 27j and
27z ensure that the striking force is decreased. Thus, only a small
stress acts on the valve portion 293a, and a large stress is not
produced at the distal end of the valve portion 293a. As a result,
this compressor also effectively prevents damage to the discharge
reed valve 29a and obtains superior durability. The other
advantages are the same as the first embodiment.
Fourteenth Embodiment
[0129] As shown in FIG. 21, in a compressor of a fourteenth
embodiment, the supporting portion 27i or the like of the fourth
embodiment is used in lieu of the supporting portion 27t or the
like of the first embodiment, and two first groove portions 27x are
used in lieu of the annular groove 27a of the first embodiment. The
first groove portions 27x, which are arc-shaped and concentric with
the center O, are formed in the fixing surface 27f and surround the
discharge port 23b from the left and the right excluding the distal
side and the basal side in the longitudinal direction D1. A region
sandwiched by the opposing ends on the distal side in the
longitudinal direction D1 in the first groove portions 27x define a
receiving portion 27j and a receiving portion 27z in the fixing
surface 27f. A region sandwiched by the opposing ends at the basal
side in the longitudinal direction D1 in the first groove portions
27x defines a basal side receiving portion 274 in the fixing
surface 27f. The other parts are the same as the first
embodiment.
[0130] In this case, the distance between the opposing ends of the
first groove portions 27x at the distal side in the longitudinal
direction D1 is increased to facilitate formation of the receiving
portions 27j and 27z that are larger than other portions. Thus, in
the same manner as the compressor of the thirteenth embodiment, a
large stress is not produced at the distal end of the valve portion
293a. Further, in the compressor, when the intermediate portion
292a of the discharge reed valve 29a strikes the basal side
receiving portion 274, only a small stress acts on the intermediate
portion 292a due to the large basal side receiving portion 274. As
a result, this compressor also effectively prevents damages to the
discharge reed valve 29a and obtains superior durability. The other
advantages are the same as the first embodiment.
Fifteenth Embodiment
[0131] As shown in FIG. 22, in a compressor of a fifteenth
embodiment, only a supporting portion 27u, the main coupling
portion 27v, and the receiving portion 27h are arranged in the
valve plate 27, and a U-shaped discharge port 23b is used. Thus,
the supporting portion 27u can receive the central region of the
valve portion 293a in the same manner as the supporting portion 27t
of the first embodiment. The other parts are the same as the first
embodiment.
[0132] In this case as well, the same advantages as the first
embodiment are obtained.
[0133] The present invention has been described with the first to
fifteenth embodiments. However, the present invention is not
limited to the first to fifteenth embodiments and may be modified
within the scope of the invention.
[0134] For instance, the supporting portion or the like may be
formed in the valve plate 27 or by a discrete member such as a
damping steel plate or the like.
[0135] The long groove 27c is deeper than the annular groove 27a in
the first embodiment, and the annular groove 27a, the long groove
27c, and the communication groove 27r are formed with the same
depth in the eleventh embodiment. However, the depths are not
limited in such a manner.
[0136] The recesses 27k, 27a, 27m, 27s, and 27q and the crowning
27p described in the fifth to tenth embodiments may be arranged in
only the supporting portion 27t or may be arranged extending across
the supporting portion 27t, the main coupling portion 27v, and the
sub-coupling portions 27w, and 27w1 to 27w3.
INDUSTRIAL APPLICABILITY
[0137] The present invention may be applied to a vehicle air
conditioning system.
* * * * *