Compressor with reduced pressure pulsation and noise
TECHNICAL FIELD The present invention relates to a compressor capable of reducing
pressure pulsation and discharge noise by preventing over-compression of a
fluid.
BACKGROUND ART In general, a compressor is an apparatus converting mechanical
energy into compression energy of a fluid, and is largely classified into a
reciprocating compressor, a scroll compressor, a centrifugal compressor and
a rotary compressor.
Among those compressors, the rotary compressor is a compressor in
which a rotational body is rotated in a state that an internal space of a
cylinder is divided into a suction region and a compression region by
inserting a vane into the rotational body so that the suction region and the
compression region are sequentially converted into one another, sucking,
compressing and discharging a compressible fluid.
Hereinafter, the rotary compressor as above will be described. FigJ is a longitudinal sectional view illustrating a main part of a
compressor according to the conventional art, Fig.2 is a perspective view
illustrating a partially cut compression part of a compressor according to the
conventional art, and Fig.3 is a plane view illustrating a compression part of a
compressor according to the conventional art.
As shown in FigsJ and 2, a conventional compressor largely includes
a hermetic casing 110 communicating with a suction pipe 135 and with a
discharge pipe (not shown); a driving force generating unit 112 disposed
inside the hermetic casing 110, and for generating a rotational force; a
compression part 114 disposed inside the hermetic casing 110 to be isolated
from the driving force generating unit 112 at a predetermined interval
therebetween, and for sucking, compressing and discharging a fluid by the
rotational force generated from the driving force generating unit 112. Like a general electric motor, the driving force generating unit 112
includes a stator 116 adhesively fixed to an inner circumferential surface of
the hermetic casing 110; and a rotor 118 disposed maintaining a certain air
gap from an inner circumferential surface of the stator 116, and for
generating a rotational force by an electromagnetic interaction between itself
and the stator 116.
The compression part 114 includes a cylinder assembly 131 disposed
inside the hermetic casing 110, and forming a compression space (V) where
a fluid which is sucked from the outside is compressed; a rotational shaft 120
rotatably fixed to the cylinder assembly 131 , and also adhesively fixed to an
inner circumferential surface of the rotor 118 to be rotated with the rotor 118
when the rotor 118 is rotated 118; a compression member 123 coupled to the
rotational shaft 120 to be rotated therewith, and dividing the compression
space (V) in the cylinder assembly 131 into a first space (V1) and a second
space (V2); and a first vane 160 and a second vane 170 which are in contact
with an upper surface and a lower surface of the compression member 123
respectively, and thus reciprocating in an inward/outward direction of the
compression space (V) along the upper surface and the lower surface of the
compression member 123 when the compression member 123 is rotated,
dividing the first and second spaces (V1), (V2) into suction regions (Via),
(V2a) and compression regions (V1b), (V2b) respectively.
The cylinder assembly 131 includes a cylinder 130 formed in a
cylindrical shape, and having one side where a suction path 136
communicating with the suction pipe 135 and thus through which a fluid is
sucked to the first space (V1) and the second space (V2) is formed; and a
first bearing plate 140 and a second bearing plate 150 fixed to both sides of
the cylinder 130, forming the compression space together with the cylinder
130, and supporting the rotating shaft. As shown in Fig.3, the first and second bearing plates 140,150 are
formed in a disc form with a predetermined thickness and an area, and
include journal portions 142, 152 extended from their centers with having a
predetermined height and an outer diameter, and whose insides are
penetrated so that the rotational shaft 120 is rotatably inserted therein; a first
vane slot 144 and a second vane slot 154 formed penetrating the first and
second bearing plates 140, 150 at one side of the journal portions 142, 152
so that the first and second vanes 160, 170 are inserted therein respectively;
discharge paths 146, 156 formed at one side of the first and second vane
slots 144, 154 respectively, and through which a compressed fluid is
discharged from the compression space (V) of the cylinder assembly 131 ;
and an opening/closing member 180 mounted toward an outlet of the
discharge paths 146, 156, and for opening/closing the discharge paths 146.
156. In addition, a first discharge muffler 145 and a second discharge
muffler 155 covers an upper part of the first bearing plate 140 and a lower
part of the second bearing plate 150 respectively so as to reduce discharge
noise generated when the compressed fluid is discharged.
- The rotational shaft 120 includes a shaft portion 121 formed so as to
have a certain outer diameter and a predetermined length, and inserted in
the journal portions 142, 152 of the first and second bearing plates 140, 150;
and a support portion 122 integrally formed at a circumference of the shaft
portion 121 , coupled with the compression member 123 in the cylinder
assembly 131 , and supported on inner surfaces of the first and second
bearing plates 140, 150. Herein, the support portion 122 of the rotational
shaft 120 is concentric with the shaft portion 121 the rotational shaft 120, and
an oil path 125 is formed penetrating the shaft portion 121 so that oil within a
lower portion of the hermetic casing 11 can be upwardly supplied. The compression member 123 is formed in a disc shape in a plane
view so that its outer circumferential surface slidably contacts with the inner
circumferential surface of the cylinder 130. And also, the compression
member 123 is formed to have a cam surface with a sinuous curve having a
predetermined thickness from the inner circumferential surface thereof to its
outer circumferential surface in a laterally projective view. Thus, a surface D1
having the top dead point is rotated sliding on a lower surface of the first
bearing plate 140, and a surface D2 having the bottom dead point is rotated
sliding on an upper surface of the second bearing plate 150.
The first vane 160 and the second vane 170 are formed into a
rectangular board shape, and are adhered to the cam surface of the
compression member 123 in the compression space (V) of the cylinder
assembly 131. So, when the compression member 123 is rotated, the first
vane 160 and the second vane 170 vertically reciprocate along the curve of
cam surface of the compression member 123, dividing the compression
spaces (V1), (V2) into suction regions (Via), (V2a) and compression regions
(V1b), (V2b).
In addition, the first and second vanes 160, 170 are elastically
supported by elastically supporting members 190 installed at the first and
second bearing plates 140, 150.
Operations of the compressor according to the conventional art
constructed as above will now be described.
First, when the rotational shaft 120 is rotated by a driving force of the
driving force generating unit 112, the compression member 123 coupled to
the rotational shaft 120 in the cylinder assembly 131 is simultaneously
rotated.
At this time, the first space (V1) positioned at an upper portion of the
compression member 123 is divided into a suction region Via and a
compression region V1b on the basis of the top dead point (D1) of the
compression member 123 and the first vane 160. And, the second space
(V2) positioned at an lower portion of the compression member 123 is
divided into a suction region (V2a) and a compression region (V2b on the
basis of the bottom dead point (D2) of the compression member 123 and the
second vane 170.
In such a state, the top dead point (D1) and the bottom dead point
(D2) of the compression member 123 are moved by the rotation of the
compression member 123, varying volumes of the suction regions (Via),
(V2a) and the compression region (V1b), (V2b) of the first and second
spaces (V1), (V2). At this time, the first vane 160 and the second vane 170
reciprocate in directions opposite to each other on the basis of the
compression member 123. Accordingly, the fluid is sucked into each suction region (Via), (V2a)
of the first space (V1) and the second space (V2) through the suction path
136, and gradually compressed. Then, at the moment when the pressure of
the fluid in the compression regions (V1b), (V2b) reaches discharge pressure,
the compressed fluid is discharged outside the cylinder assembly 131
through discharge paths 146, 156 of each compression space (V1), (V2).
And, the fluid discharged outside the cylinder assembly 131 is
discharged outside the hermetic casing through the discharge pipe (not
shown) via the first and second mufflers 145, 155 and the inside of the
hermetic casing 110.
In the compressor according to the conventional art constructed and
operating as above, the pressure of the fluid in the compression regions
(V1b), (V2b) is gradually increased by the rotation of the compression
member 123, and then at the moment of reaching the discharge pressure,
the fluid is discharged through the discharge paths 146, 156 with pushing the
opening/closing member 180. But, at the moment when the pressure of the
fluid in the compression regions (V1b), (V2b) reaches the discharge pressure,
the fluid is over-compressed, thereby generating pressure pulsation and
discharge noise, and degrading the compression performance of the
compressor.
DISCLOSURE OF THE INVENTION Therefore, it is an object of the present invention to provide a
compressor capable of reducing pressure pulsation and discharge noise
generated when a compressed fluid is discharged, and improving its
performance by reducing a loss due to over-compression of a fluid.
To achieve the above object, there is provided a compressor including
a cylinder disposed inside a hermetic casing, and having a compression
space therein; a compression member disposed inside the compression
space of the cylinder, and rotated with varying a volume of the compression
space; a rotational shaft fixed to a driving force generating unit, and
transmitting a driving force generated at the driving force generating unit to
the compression member; a bearing plate on which axial-directional and
radial-directional loads of the rotational shaft are supported, and having a
discharge path through which a compressed fluid is discharged; a vane
reciprocating in an inward/outward direction of the cylinder along a surface of
the compression member in rotation of the compression member, and
dividing the compression space into a suction region and a compression
region; a cavity formed at the rotational shaft so as to have a predetermined
volume; and a communication path formed at the bearing plate, and for
making the compression region and the cavity temporarily communicate with
each other
BRIEF DESCRIPTION OF THE DRAWINGS Fig.1 is a longitudinal sectional view illustrating a main part of a
compressor according to the conventional art; Fig.2 is a perspective view illustrating a partially cut compression part
of a compressor according to the conventional art;
Fig.3 is a plane view illustrating a compression part of a compressor
according to the conventional art;
Fig.4 is a longitudinal sectional view illustrating a main part of a
compressor according to the present invention;
Fig.5 is a perspective view illustrating a partially cut compression part
of a compressor according to the present invention;
Fig.6 is a plane view illustrating a compression part of a compressor
according to the present invention;
Fig.7 is a longitudinal sectional view illustrating a compression part of
a compressor according to the present invention; and
Figs.δA to 8C are operational state views illustrating an operation
process of a compressor according to the present invention.
MODES FOR CARRYING OUT THE PREFERRED EMBODIMENTS Hereinafter, a preferred embodiment according to the present
invention will now be described with reference to accompanying drawings. Fig.4 is a longitudinal sectional view illustrating a main part of a
compressor according to the present invention, Fig.5 is a perspective view
illustrating a partially cut compression part of a compressor according to the
present invention, Fig.6 is a plane view illustrating a compression part of a
compressor according to the present invention, and Fig.7 is a longitudinal
sectional view illustrating a compression part of a compressor according to
the present invention. As shown therein, the compressor according to the
present invention largely includes a hermetic casing 10 communicating with a
suction pipe 35 and with a discharge pipe (not shown); a driving force
generating unit 12 disposed inside the hermetic casing 10, and for generating
a rotational force; and a compression part 14 disposed inside the hermetic
casing 10 to be isolated from the driving force generating unit 12 at a
predetermined interval therebetween, and for sucking, compressing and
discharging a compressible fluid by the rotational force generated from the
driving force generating unit 12.
Like a general electric motor, the driving force generating unit 12
includes a stator 16 adhesively fixed to an inner circumferential surface of the
hermetic casing 10; and a rotor 18 disposed maintaining a certain air gap
from an inner circumferential surface of the stator 16, and for generating a
rotational force by an electromagnetic interaction between itself and the
stator 16.
The compression part 14 includes a cylinder assembly 31 disposed
inside the hermetic casing 10, and forming a compression space (V) where
the fluid sucked from the outside is compressed; a rotational shaft 20
rotatably fixed to the cylinder assembly 31 , and adhesively fixed to an inner
circumferential surface of the rotor 18 to be rotated therewith when the rotor
18 is rotated; a compression member 23 coupled to the rotational shaft 20 to
be rotated, and dividing the compression space (V) in the cylinder assembly
31 into a first space (V1) and a second space (V2); and a first vane 60 and a
second vane 70 which are in contact with an upper surface and a lower
surface of the compression member 23 respectively and reciprocate in an
inward/outward direction of the compression space (V) along the upper
surface and the lower surface of the compression member 23 when the
compression member 23 is rotated, dividing the first and second spaces (V1),
(V2) into suction regions (Via), (V2a) and compression regions (V1b), (V2b)
respectively.
The cylinder assembly 31 includes a cylinder 30 formed in a
cylindrical shape, and having one side where a suction path 36
communicating with the suction pipe 35, and through a fluid is sucked into
the first space (V1) and the second space (V2) is formed; and a first bearing
plate 40 and a second bearing plate 50 fixed at both sides of the cylinder 30,
forming the compression space together with the cylinder 30, and supporting
an axial-directional load of the rotational shaft 20 and a radial-directional load
thereof.
As shown in Fig.6, the first and second bearing plates 40, 50 are
formed in a disc shape with a certain thickness and an area, and include
journal portions 42, 52 extended from their centers to have a predetermined
height and an outer diameter, and whose inside are penetrated so that the
rotational shaft 20 is rotatably inserted therein; a first vane slot 44 and a
second vane slot 54 formed penetrating the first and second bearing plates
40, 50 at one side of the journal portions 42, 52 so that the first and second
vanes 60, 70 are inserted therein; discharge paths 46, 56 formed at one side
of the first and second vane slot 44, 54, and through which the compressed
fluid is discharged from the compression space (V) of the cylinder assembly
31 ; and an opening/closing member 80 mounted toward an outlet of the
discharge paths 46, 56, and for opening/closing the discharge paths 46, 56. In addition, a first discharge muffler 45 and a second discharge
muffler 55 covers an upper portion of the first bearing plate 40 and a lower
portion of the second bearing plate 50 respectively so as to reduce discharge
noise generated when the compressed fluid is discharged.
The rotational shaft 20 includes a shaft portion 21 having a certain
diameter and a predetermined length, and inserted at the journal portions 42,
52 of the first and second bearing plates 40, 50; and a support portion 22
integrally formed at a circumference of the shaft portion 21 , coupled with the
compression member 23 inside the cylinder assembly 31 , and supported on
the inner surfaces of the first and second bearing plates 40, 50. That is, a
radial-directional load of the rotational shaft 20 is supported on radial bearing
surfaces (R) of the journal portions 42, 52 of the first and second bearing
plates 40, 50. And, an axial-directional load of the rotational shaft 20 is
supported by thrust bearing surfaces (T) of inner surfaces of the first and
second bearing plates 40, 50. The support portion 22 of the rotational shaft
20 is concentric with the shaft portion 21 of the rotational shaft 20, and an oil
path 25 is formed penetrating the shaft portion 21 so as to upwardly provide
oil within a lower portion of the hermetic casing 10. The compression member 23 is formed in a disc shape in a plane
view so that its outer circumferential surface slidably contacts with the inner
circumferential surface of the cylinder 30. And also, the compression member
23 is formed to have a cam surface with a sinuous curve having a
predetermined thickness from its inner circumferential surface to its outer
circumferential surface in a laterally projective view. Thus, a surface D1
having the top dead point is rotated sliding on a lower surface of the first
bearing plate 40, and a surface D2 having the bottom dead point is rotated
sliding on an upper surface of the second bearing plate 50.
The first vane 60 and the second vane 70 are formed in a rectangular
board shape, and are adhered to a cam surface of the compression member
23 in the compression space (V) of the cylinder assembly 31. So, when the
compression member 23 is rotated, the first vane 60 and the second vane 70
reciprocate in an inward/outward direction of the cylinder assembly 31 along
the curve of the cam surface of the compression member 23, dividing the
compression spaces (V1), (V2) into suction regions (Via), (V2a) and
compression regions (V1 b), (V2b). In addition, the first and second vanes 60,
70 are elastically supported by elastically supporting members 90 installed at
the first and second bearing plates 40, 50 respectively.
At surfaces of the support portion 22 of the rotational shaft 20, which
is in contact with the thrust bearing surfaces (T) of the first and second
bearing plates 40, 50, cavities 48, 58 with a predetermined width and a
length are formed. At this time, in order to prevent generation of a dead
volume during compressing operation, preferably, the cavities 48, 58 are
formed so as not to communicate with the compression space (V1), (V2) of
the cylinder assembly 31.
At the first and second bearing plates 40, 50, communication paths
49, 59 are formed respectively so that the compression regions (V1b), (V2b)
and the cavities 48, 59 temporarily communicate with each other when the
pressure of the fluid in the compression regions (V1b), (V2b) reaches
predetermined pressure. The communication paths 49, 59 are formed in a
groove shape which is extended from one side of the discharge paths 46, 56
in an inward direction of the rotational shaft 20.
Accordingly, positions of the cavities 48, 58 are changed by the
rotation of the rotational shaft 20 on the basis of a central axis of the
rotational shaft 20, and then, at the moment when the pressure of the fluid in
the compression regions (V1b), (V2b) reaches predetermined pressure by
the rotation of the compression member 23, the cavities 48, 58 temporarily
communicate with the compression regions (V1b), (V2b) through the
communication paths 48, 58. Thusly, a part of the compressed fluid in the
compression regions (V1b), (V2b) is flowed into the cavities 48, 58, therefore
by the effect of dispersing the pressure, the over-compression of a fluid is
prevented, and pressure pulsation and discharge noise is reduced.
Herein, a point of time when the cavities 48,58 and the compression
regions (V1b), (V2b) temporarily communicate with each other can be set so
as to communicate with each other just before the pressure of the fluid in the
compression regions (V1b), (V2b) reaches the discharge pressure, that is,
just before the compressed fluid is discharged. And also, the point of time
when the cavities 48, 58 and the compression regions (V1b), (V2b)
temporarily communicate with each other can be set so as to communicate
with each other at a point when the pressure of the fluid in the compression
regions (V1b), (V2b) reaches the discharge pressure, that is, when the
compressed fluid is discharged outside the cylinder assembly 31 with
pushing the opening/closing member 80. The point of time is varied
according to a radial-directional distance between the cavities 48, 58 and a
top dead point (D1) and a bottom dead point (D2) of the compression
member 23, and is selected and planned properly according to a fluid
capacity of a compressor and discharge pressure. In addition, volumes of the
cavities 48, 58 and the communication paths 49, 59 are selected and
planned properly according to the capacity of the compressor. Preferably,
cross-sectional areas of the communication paths 49, 59 are formed to be
smaller than horizontal-directional cross-sectional areas of the cavities 48, 58.
In a preferred embodiment of the present invention, the communication paths
49, 59 are extended from one side of the discharge paths 46, 56 in an inward
direction of the rotational shaft 20, but not limited thereto. So, the
communication paths 49, 59 can be formed at a position close to the
discharge paths 46, 56.
With reference to Figs.δA to 8C, the compressor according to the
present invention constructed as above will now be described. First, as shown in Fig.8A, when the rotational shaft 20 is rotated by a
driving force of the driving force generating unit 12, the compressor member
23 which is coupled to the support portion 22 of the rotational shaft 20 in the
cylinder assembly 31 is simultaneously rotated.
At this time, a first space (V1) positioned at an upper portion of the
compression member 23 is divided into a suction region (Via) to which a
fluid is sucked and a compression region (V1b) in which a fluid is
compressed, on the basis of a top dead point (D1) of the compression
member 23 and the first vane 60. And also, a second space (V2) positioned
at a lower portion of the compression member 23 is divided into a suction
region (V2a) and a compression region (V2b) on the basis of a bottom dead
point (D2) of the compression member 123 and the second vane 70.
And, the positions of the top dead point (D1) and the bottom dead
point (D2) of the compression member 23 are changed by rotation of the
compression member 23, varying volumes of the suction regions (Via),
(V2a) and the compression regions (V1b), (V2b) of the first and second
spaces (V1), (V2). At this time, the first vane 60 and the second vane 70
reciprocate in directions opposite to each other on the basis of the
compression member 23.
At this time, the shaft portion 21 of the rotational shaft 20 is inserted
at journal portions 42, 52 of the first and second bearing plates 40, 50 and is
rotated, making a radial-directional load of the rotational shaft 20 supported
by radial bearing surfaces (R) of the journal portions. Both sides of the
support portion 22 of the rotational shaft 20 is rotated, making an axial-
directional load of the rotational shaft 20 supported by thrust bearing surfaces
(T) of the first and second bearing plates 40, 50. And, positions of the cavities
48, 58 formed at the support portions 22 of the rotational shaft 20 are
changed in a state of being isolated from the first and second space (V1),
(V2).
Accordingly, a fluid is sucked into each suction region (Via), (V2a) of
the first space (V1) and the second space (V2) through the suction path 36,
and then gradually compressed.
As shown in Fig.δB, when the top dead point (D1) and the bottom
dead point (D2) of the compression member 23 are moved, the cavities 48,
58 formed at the support portion 22 of the rotational shaft 20 and the
discharge paths 46, 56 communicate with each other through the
communication paths 49, 59 formed at the first and second bearing plates 40,
50 just before the pressure of the compression regions (V1b), (V2b) reaches
discharge pressure, or at a point when the pressure of the fluid in the
compression regions (V1b), (V2b) reaches discharge pressure, that is, when
the compressed fluid is discharged outside the cylinder assembly 31 with
pushing the opening/closing member 60. Thusly, a part of the compressed
fluid in the compression regions (V1b), (V2b) is flowed into the cavities 46, 56
through the communication paths 49, 59. Accordingly, over-compression of
the fluid is prevented, and pressure pulsation and generation of noise due to
over-compression of the fluid are prevented. As shown in Fig.δC, as the positions of the top dead point (D1) and
the bottom dead point (D2) of the compression member 23 are continuously
changed, the compressed fluid in the compression regions (V1b), (V2b) is
discharged outside the cylinder assembly 31 through the discharge paths 46,
56 with pushing the opening/closing member δ0. The compressed fluid
discharged outside the cylinder assembly 31 is discharged outside the
hermetic casing 10 through the discharge pipe (not shown) via the first and
second discharge mufflers 45, 55 and the inside of the hermetic casing 10.
Such operations are sequentially performed, performing a cycle of suction,
compression and discharge of the fluid.
In the compressor according to the present invention constructed and
operating as above, the cavities 43, 5δ formed at the support portion 22 of
the rotational shaft 20 and the compression regions (V1b), (V2b) temporarily
communicate with each other right before the pressure of the fluid in the
compression regions (V1b), (V2b) reaches the discharge pressure, or at a
point of reaching the discharge pressure. Therefore, a part of the
compressed fluid in the compression regions (V1 b), (V2b) is flowed into the
cavity 4δ, 58, thereby preventing over-compression of the fluid in the
compression region (V1b), (V2b), and reducing pressure pulsation and
discharge noise. Also, as the cavities 48, 58 and the discharge paths 46, 56
only temporarily communicate with each other by the rotation of the rotational
shaft 20, the cavities 48, 58 do not serve as the dead volume and so, forming
the cavities 48, 58 has a very small effect on the performance of the
compressor.
As so far described, the compressor according to the present
invention is planned so that the cavity formed at the rotational shaft and with
a predetermined volume and the compression region temporarily
communicate with each other through the communication path right before
the pressure of the fluid in the compression region where the fluid is
compressed, reaches the discharge pressure, or at a point when the
pressure of the fluid in the compression region reaches the discharge
pressure, that is, when the compressed fluid is discharged outside the
cylinder assembly through the discharge path. Therefore, a part of the
compressed fluid in the compression region is flowed into the cavity, thereby
preventing over-compression of the fluid in the compression region, and
reducing pressure pulsation and discharge noise. It will be apparent to those skilled in the art that various modifications
and variations can be made in the present invention without departing from
the spirit or scope of the invention. Thus, it is intended that the present
invention cover modifications and variations of this invention provided they
come within the scope of the appended claims and their equivalents.