Pumps – With muffler acting on pump fluid
Reexamination Certificate
2001-09-10
2004-02-17
Walberg, Teresa (Department: 3742)
Pumps
With muffler acting on pump fluid
Reexamination Certificate
active
06692238
ABSTRACT:
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to a muffler of a compressor and particularly to a muffler of a compressor in which flow of refrigerant gas is smooth and pulsation flow can be decreased.
2. Description of the Background Art
Generally, a muffler applied to a compressor is installed at a suction side or discharge side of a compressor so as to attenuate suction noise occurred when sucking fluid or discharge noise occurred when discharging fluid.
A muffler installed at the suction side is called as a suction muffler and a muffler installed at the discharge side is called as a discharge muffler.
A suction muffler and a discharge muffler decrease pulsation phenomenon occurred periodically when sucking and discharging fluid.
Also, a suction muffler and a discharge muffler attenuate compressor noise by blocking valve noise occurred when sucking and discharging fluid and flow noise of fluid.
Hereinafter, a suction muffler applied to a reciprocating type compressor will be described.
FIG. 1
is a longitudinal cross-sectional view showing an example of a reciprocating compressor having a conventional muffler of a compressor.
As shown in
FIG. 1
, a conventional reciprocating compressor is comprised of a casing
1
which is filled with oil, a electric motor unit which is installed in the inner lower part of the compressor to generate driving force by power supply from the outside of the compressor, and a compression unit which is installed in the upper part of the electric motor unit receiving driving force of the electric motor unit to suck and compress gas.
The compression unit includes a frame
2
which is fixed inside of the casing
1
in the horizontal direction, a cylinder
3
which is fixed at one side of the frame
2
, a driving shaft
5
which penetrates the center of the frame
2
and is pressed-fitted to a rotor
4
B of the electric motor unit, a connecting rod
6
which is connected with the upper eccentric part of the driving shaft
5
to change a rotational motion to a reciprocating motion, a piston
7
which is connected with the connecting rod
6
and which performs a reciprocating motion in the cylinder
3
, a valve assembly
8
assembled to the cylinder
3
to control the suction and discharge of refrigerant gas, a head cover
9
which is combined to the valve assembly
8
having a certain discharge space (DS), a suction muffler
10
which is connected to one side of the head cover
9
so that the muffler
10
is connected to the valve assembly
8
and a discharge muffler (DM) which is installed in the cylinder
3
to be connected to the discharge side of the valve assembly
8
.
The suction muffler
10
as shown in
FIG. 2A
, comprises an inlet port
11
which is connected to the refrigerant suction channel SP (shown in
FIG. 1
) which penetrates the inner part of the casing
1
or the casing
1
itself, an outlet port
12
which is connected to the suction side of the valve assembly
8
to lead the refrigerant gas flown through the inlet port
11
to a compression space of the cylinder
3
(shown in FIG.
1
), first compartment
13
and second compartment
14
for dividing the inner volume between the inlet port
11
and the outlet port
12
to first, second and third extended spaces S
1
, S
2
and S
3
, first passage pipe
15
for connecting the first extended space S
1
and the second extended space S
2
by penetrating the first compartment
13
vertically, second passage pipe
16
for connecting the second extended space S
2
to the outlet port
12
, and a resonance hole
17
for connecting the third extended space S
3
to the outlet port
12
so that the second passage pipe
16
is formed penetrating the peripheral wall at a center of the second passage pipe
16
and forming a Helmholtz Reservoir together with the third extended space S
3
.
In
FIG. 1
, reference numeral
4
A designates a stator,
18
designates an oil drain hole, C designates a support spring, O designates an oil feeder and SP designates a compressor suction channel.
A conventional reciprocating compressor having the above structure is operated as follows.
Firstly, power is supplied to the electric motor unit and the rotor
4
B rotates by the interaction of the stator
4
A and the rotor
4
B.
The rotor
4
B rotates together with the driving shaft
5
and the rotational motion is changed to a linear reciprocating motion by the connecting rod
6
which is combined to the eccentric part of the driving shaft
5
and the linear reciprocating motion is transmitted to the piston
7
.
The piston
7
sucks, compresses and discharges the refrigerant gas performing a reciprocating motion in the cylinder
3
and pulsating pressure and noise occurred during the process, flow in the opposite direction of the flow direction of refrigerant gas and are attenuated by the suction muffler
10
.
This operation will be described in more detail as follows.
In case of a suction stroke in which the piston
7
moves from a top dead point to a bottom dead point, the refrigerant gas filled in the second extended space S
2
opens the suction valve (not shown). Then the refrigerant gas is sucked to the compression space of the cylinder
3
and at the same time, new refrigerant gas is flown to the second extended space S
2
through the refrigerant inlet port
11
, the first extended space S
1
and the first passage pipe
15
.
On the other hand, in case of a compression stroke in which the piston
7
moves from a bottom dead point to a top dead point, the discharge valve (reference numeral is not shown) is opened at the same time as the suction valve (reference numeral is not shown) is closed and the compressed gas is discharged to the discharge space DS of the head cover
9
through the discharge valve.
At this time, repeated pulsating pressure is occurred continuously in the suction muffler
10
and the head cover
9
in the repeating process of suction and discharge of the refrigerant gas.
This pulsating pressure having phase difference is transmitted through each channel of the suction muffler
10
. However, consequently the pulsating pressure greatly decreases at the inlet port
11
and the refrigerant gas flows smoothly since the pulsating pressure is attenuated gradually and almost removed.
Meanwhile, the noise occurred during suction of the refrigerant gas is converted to a heat energy by diffusion and dissipation and attenuated passing through the respective passage pipes
15
and
16
, and extended spaces S
1
and S
2
, and at the same time, the noise having a certain frequency is attenuated by the Helmholtz's Effect at the Helmholtz resonance portion which comprises a resonance hole of the second passage pipe
16
and the third extended space S
3
. Accordingly, the whole noise decreases.
However, in the above conventional suction muffler, the inlet port
11
which forms a suction channel, the first passage pipe
15
, and the second passage pipe
16
are positioned in parallel to each other and accordingly, the refrigerant gas flows in zigzags.
Therefore, by the flow of the refrigerant gas in zigzags, a smooth flow of the refrigerant gas is interrupted and the refrigerant gas flown from the inlet port
11
, the first passage pipe
15
, and the second passage pipe
16
collides with the walls of the respective extended spaces S
1
, S
2
and S
3
. Accordingly, the speed energy of the refrigerant gas is converted to a collision energy and thus to cause flow loss.
Also, in another conventional suction muffler as shown in
FIG. 2B
, first passage pipe
21
(inlet port in drawings) and second passage pipe
22
form a right angle each other, or in the other conventional suction muffler as shown in
FIG. 2C
, first passage pipe
31
is positioned on a straight line with the second passage pipe
32
thus to improve flow of refrigerant gas.
However, in the suction muffler shown in
FIG. 2B
, the refrigerant gas sucked through the first passage pipe
21
is collided in an extended space
23
and then flown to the second passage
22
. Accordingly, flow loss by collision still
Lee In Seop
Myung Hwan Joo
Patel Vinod D.
Walberg Teresa
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