Scroll compressor

Rotary expansible chamber devices – Working member has planetary or planetating movement – Helical working member – e.g. – scroll

Reexamination Certificate

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Details

C418S057000, C418S055400, C418S055600

Reexamination Certificate

active

06769887

ABSTRACT:

TECHNICAL FIELD
The present invention relates to a refrigerant compressor for use in refrigerating/air-conditioning equipment.
BACKGROUND ART
FIG. 7
is a longitudinal sectional view showing the construction of a conventional scroll compressor disclosed in JP-A-2000-161254.
In
FIG. 7
, numeral
1
designates a fixed scroll having its outer circumferential portion fastened to a guide frame
15
by means of bolts (not shown). Plate-like scroll teeth
1
b
are formed on one surface (lower side in
FIG. 7
) of a base plate portion
1
a
. In addition, two Oldham's guide grooves
1
c
are formed substantially in a straight line in the outer circumferential portion. A claw
9
c
of an Oldham's ring
9
is reciprocally slidably engaged with each of the Oldham's guide grooves
1
c
. Further, from a side surface of the fixed scroll
1
, a suction pipe
10
a
is press fitted through a closed vessel
10
.
Numeral
2
designates an oscillating scroll, and plate-like scroll teeth
2
b
having substantially the same shape as the plate-like scroll teeth
1
b
of the fixed scroll
1
are provided on the upper surface of a base plate portion
2
a
. Thus, a compression chamber
1
d
is formed geometrically. A hollow cylindrical boss portion
2
f
is formed in the center portion of that surface of the base plate portion
2
a
which is opposite to the plate-like scroll teeth
2
b
. An oscillating bearing
2
c
is formed on the inner surface of the boss portion
2
f
. In addition, a thrust surface
2
d
which can slide in pressure contact with a thrust bearing
3
a
of a compliant frame
3
, is formed on the same side surface as the boss portion
2
f
but on an outer side than the boss portion
2
f
. In the outer circumferential portion of the oscillating scroll base plate portion
2
a
, two Oldham's guide grooves
2
e
are formed substantially in a straight line to have a phase difference of 90 degrees with respect to the Oldham's guide grooves
1
c
of the fixed scroll
1
. A claw
9
a
of the Oldham's ring
9
is reciprocally slidably engaged with each of the Oldham's guide grooves
2
e
. An extraction hole
2
j
is also provided in the base plate portion
2
a
so as to extend from the compression chamber
1
d
through the thrust surface
2
d
. An aperture portion
2
k
of the extraction hole
2
j
on the side of the thrust surface
2
d
is located so that the circular locus of the aperture portion
2
k
always stays inside the thrust bearing surface
3
a
of the compliant frame
3
.
The compliant frame
3
has two upper and lower cylindrical surfaces
3
d
and
3
e
in its outer circumferential portion. The cylindrical surfaces
3
d
and
3
e
are supported in the radial direction of the scroll compressor by cylindrical surfaces
15
a
and
15
b
provided in the inner circumferential portion of the guide frame
15
, respectively. A main bearing
3
c
and an auxiliary main bearing
3
h
for supporting a main shaft
4
in the radial direction of the scroll compressor are formed in the center portions of the compliant frame
3
. The main shaft
4
is driven to rotate by a motor
7
. In addition, between the outside of the compliant frame
3
and the inside of the guide frame
15
, a frame space
15
f
is defined by sealing materials
16
a
and
16
b
disposed on cylindrical surfaces
15
c
and
15
d
, respectively. The frame space
15
f
communicates with the compression chamber
1
d
through a communication passageway
3
s
and the extraction hole
2
i
which are interconnected via the surface of the thrust bearing
3
a
. Thus, the frame space
15
f
is filled with refrigerant gas which is supplied from the compression chamber
1
d
and which is on the way of compression.
A regulating valve receiving space
3
p
is also formed in the compliant frame
3
. One end (lower end in
FIG. 7
) of the regulating valve receiving space
3
p
communicates with a boss portion outside space
2
h
. The boss portion outside space
2
h
is constituted by the inner circumference of the compliant frame
3
and the thrust surface
2
d
of the oscillating scroll
2
. On the other hand, the other end (upper end in
FIG. 7
) of the regulating valve receiving space
3
p
is made open to a suction pressure atmosphere space
1
g
. An intermediate pressure regulating valve
3
i
is reciprocally movably received in the lower portion of the regulating valve receiving space
3
p
. On the other hand, received in the upper portion of the regulating valve receiving space
3
p
is an intermediate pressure regulating spring retainer
3
t
fixedly attached to the compliant frame
3
. Between the intermediate pressure regulating valve
3
i
and the intermediate pressure regulating spring retainer
3
t
, an intermediate pressure regulating spring
3
m
is received in such a manner that the spring
3
m
is made shorter than its natural length.
An outer circumferential surface
15
g
of the guide frame
15
is fixedly attached to the closed vessel
10
by shrink-fitting, welding, or the like. However, a channel is ensured by a notch portion
15
h
provided in the outer circumferential portion of the guide frame
15
. Thus, high pressure refrigerant gas discharged from a discharge port
1
f
of the fixed scroll
1
is directed through the channel to a discharge pipe
10
b
provided on the motor side.
Numeral
4
designates a main shaft and an oscillating shaft
4
b
is formed in the upper end portion of the main shaft
4
. The oscillating shaft
4
b
is rotatably engaged with the oscillating bearing
2
c
of the oscillating scroll
2
. A main shaft balancer
4
e
is shrink-fitted in the lower portion of the oscillating shaft
4
b
. Further, under the main shaft balancer
4
e
, a main shaft portion
4
c
is formed so as to be rotatably engaged with the main bearing
3
c
and the auxiliary main bearing
3
h
of the compliant frame
3
. In addition, an auxiliary shaft portion
4
d
is formed in the lower portion of the main shaft
4
so as to be rotatably engaged with an auxiliary bearing
6
a
of a sub-frame
6
. A rotor
8
is shrink-fitted between the auxiliary shaft portion
4
d
and the main shaft portion
4
c.
An upper balancer
8
a
is fixed to the upper end surface of the rotor
8
and a lower balancer
8
b
is fixed to the lower end surface of the rotor
8
. Static balance and dynamic balance are ensured by the total of three balancers including the upper and lower balancers
8
a
and
8
b
in addition to the above-mentioned main shaft balancer
4
e
. Further, an oil pipe
4
f
is force fitted into the lower end of the main shaft
4
. Thus, refrigerating machine oil
10
e
retained in the bottom portion of the closed vessel
10
is sucked up through the oil pipe
4
f.
A glass terminal board
10
f
is provided at the side surface of the closed vessel
10
. The motor
7
is connected with the glass terminal board
10
f
through lead wires.
Next, description will be made about the basic operation of the conventional scroll compressor.
A sucked refrigerant of low pressure enters the compression chamber
1
d
through the suction pipe
10
a
. The compression chamber id is defined by the plate-like scroll teeth of the fixed scroll
1
and the plate-like scroll teeth of the oscillating scroll
2
. The oscillating scroll
2
driven by the motor
7
makes an eccentric turning motion while reducing the volume of the compression chamber
1
d
. On this compression stroke, the sucked refrigerant becomes high in pressure. Thus, the sucked refrigerant is discharged into the closed vessel
10
through the discharge port if of the fixed scroll
1
.
On the other hand, the refrigerant gas of intermediate pressure on the way of compression on the above-mentioned compression stroke is directed from the extraction hole
2
j
of the oscillating scroll
2
to the frame space
15
f
through the communication passageway
3
s
of the compliant frame
3
, so that the intermediate pressure atmosphere in this space is maintained.
The discharged gas of the high pressure fills the closed vessel
10
with the high pressure at

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