Rotary expansible chamber devices – Working member has planetary or planetating movement – With relatively movable partition member
Reexamination Certificate
2000-03-15
2001-06-05
Denion, Thomas (Department: 3748)
Rotary expansible chamber devices
Working member has planetary or planetating movement
With relatively movable partition member
C418S181000, C418S079000, C418S075000
Reexamination Certificate
active
06241496
ABSTRACT:
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to a hermetic rotary compressor and, in particular, to a hermetic rotary compressor which is capable of improving the effect of reducing noise due to pressure pulsation generated during a gas suction and discharge process, and at the same time improving the compressing efficiency of the compressor by reducing compressive driving force.
2. Description of the Prior Art
Generally, a rotary compressor is an apparatus for compressing gas, and there are many kinds of compressors depending on its method of compressing the gas including a rotary compressor, a reciprocating compressor, a scroll compressor, etc.
Each of these compressor includes a hermetic vessel having a certain space portion, an motor unit mounted on the hermetic vessel for thereby generating driving force, and a compression unit which receives the driving force from the motor unit for thereby compressing gas.
As an example of the above-mentioned compressors, a hermetic rotary compressor will be described as follows with reference to
FIGS. 1 and 2
.
FIG. 1
is a front cross-sectional view illustrating a general rotary compressor, and
FIG. 2
is a horizontal cross-sectional view illustrating a general rotary compressor.
As illustrated therein, the motor unit is mounted on one side portion of the hermetic vessel
1
, and the compression unit is mounted on the other side portion of the hermetic vessel at a certain distance from the motor unit.
The motor unit includes a stator
2
fixedly connected to the inner surface of the hermetic vessel
1
, and a rotator
3
connected to be rotatable in the stator
2
.
And, the compression unit includes a crankshaft
4
which is press-fitted to the inner diameter of the rotator
3
and has an eccentric portion
4
a
formed at one end of the crankshaft
4
, and a cylinder
5
in which the eccentric portion
4
a
of the shaft
4
is inserted into a space portion
11
at which gas is sucked and compressed are mounted on the hermetic vessel.
In addition, the compression unit includes upper and lower bearings
7
and
8
which is bolted to the upper and lower surfaces of the cylinder
5
for thereby supporting the crankshaft
4
and enclosing the space portion
11
of the cylinder
5
, a rolling piston positioned in the space portion
11
of the cylinder
5
, revolving according to the rotation of the crankshaft
4
, an eccentric portion
4
a
of the crankshaft
4
being inserted into the rolling piston
9
, a vane
10
which is inserted into one side of the cylinder
5
in order to linearly reciprocate in a radius direction of the cylinder
5
as one end of the vane
10
contacts the outer surface of the rolling piston
9
during the rotation of the rolling piston
9
, whereby the space portion formed by the inner surface of the cylinder
5
and the outer surface of the rolling piston
9
is partitioned into a suction area
11
a
and a compression area
11
b.
And, a suction hole
5
a
through which gas is sucked into the cylinder
5
is formed in the suction area
11
a
of the cylinder
5
, more specifically, at one side of the cylinder
5
neighboring the vane
10
. A discharge port
5
b
through which compressed gas is discharged is formed in the compression area
11
b
of the cylinder
5
, that is, at the other side of the cylinder
5
neighboring the vane
10
. The above discharge port
5
b
is communicated with a discharge hole
7
a
formed at the upper bearing
7
, and the discharge hole
7
a
can be formed at the lower bearing
8
connected to the lower surface of the cylinder
5
.
A inlet pipe
12
through which gas is sucked is connected to a side wall of the hermetic vessel
1
, a outlet pipe
13
through which gas is discharged is connected to the upper side of the hermetic vessel
1
, and oil(not shown) is filled in the bottom of the hermetic vessel
1
.
In the drawings, reference numeral
14
denotes a discharge valve,
15
denotes a retainer,
16
denotes a muffler, and
17
denotes an accumulator.
The operation of the above general hermetic rotary compressor will be described as follows.
When the crankshaft
4
is rotated by an applied current, along with the rotator
3
, the rolling piston
9
connected to the eccentric portion
4
a
of the crankshaft
4
is revolved around the crankshaft
4
in the cylinder space portion
11
while being in contact with the vane
10
.
Due to the volume change of the space portion
11
formed by the inner surface of the cylinder
5
and the outer surface of the rolling piston
9
by the revolution of the rolling piston
9
, a gaseous refrigerant of low temperature and pressure is sucked into the space portion
11
of the cylinder
5
through the inlet pipe
12
and the suction hole
5
a
to thereafter be compressed into gas of high temperature and pressure, and the compressed gaseous refrigerant of high temperature and pressure is discharged through the discharge port
5
b
, the discharge hole
7
a
, and the discharge valve
14
.
Herein, the process in which gaseous refrigerant is sucked, compressed, and then discharged according to the rotation of the crankshaft
4
will be described in more detail with reference to
FIGS. 3
,
4
, and
5
.
FIGS. 3
,
4
, and
5
are horizontal cross-sectional views illustrating the operational process of the rotary compressor.
First, as shown in
FIG. 3
, when the semimajor axial front end (A) of the eccentric portion
4
a
of the crankshaft
4
is in contact with the vane
10
, the discharge stroke is terminated and at the same time the suction stroke is terminated.
And, as the crankshaft
4
is rotated, and thereby the space portion
11
is converted to the suction area
11
a
and the compression area
11
b
by the vane
10
at a position that the semimajor axial front end of the eccentric portion
4
a
is displaced from the vane by 180 degrees as illustrated in
FIG. 4
, gaseous refrigerant is sucked into the suction area
11
a
and at the same time the volume of the compression area
11
a
is reduced, whereby the gas is progressively compressed.
And, when the crankshaft
4
is rotated, and thereby the semimajor axial front end of the eccentric portion
4
a
passes an angle of 180 degrees and then moves to the discharge port
5
b
, the amount of gaseous refrigerant sucked into the suction area
11
a
and the pressure of the compression area
11
b
is increased at the same time, whereby the pressure of the compression area
11
b
becomes higher compared to discharged gas. In this case, the discharge valve
14
is opened, and compressed gas is discharged through the discharge port
5
b
and the discharge hole
7
a.
Meantime, when the rolling piston
9
continues to repeat the process of sucking, compressing, and discharging gaseous refrigerant while revolving during the operation of the above compressor, noises due to pressure pulsation are generated. In this regard, many studies for reducing noises due to pressure pulsation is in progress in order to obtain an resonance effect at the space portion
11
of the cylinder
5
.
With reference to
FIGS. 6 and 7
illustrating an embodiment of a conventional noise reduction structure in order to reduce the above-mentioned pressure pulsation, a surge recess
18
, an unpierced hole having a certain diameter and depth, is formed between 150 and 270 degrees from the vane
10
in a rotational direction of the crankshaft
4
.
With respect to the position at which the above surge recess
18
is formed, there arises a malfunction that compressed gas flows back to the suction side at every angles at which the surge recess
18
is formed. When the angle is increased, the loss of re-expansion is increased as much, while the compression work(compressive driving force) of the compressor according to the surge recess
18
is decreased, thereby obtaining a gain of compressive driving force.
In regard to compression efficiency, when the performance of the compressor is analyzed based on a P-V diagram in
FIG. 8
, there arises a difference between a re-expansion loss and a compressive dr
Byun Sang Myung
Kim Kwang Ho
Ku Se Jin
Lee Yun Won
Seo Hong Seok
Denion Thomas
LG Electronics Inc.
Ostrolenk Faber Gerb & Soffen, LLP
Trieu Theresa
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