U.S. patent application number 11/154730 was filed with the patent office on 2006-03-16 for multi-cylinder rotary type compressor.
This patent application is currently assigned to SAMSUNG ELECTRONICS CO., LTD.. Invention is credited to Jin Woo Lee, Valeri Lenchine, Jong Won Seok.
Application Number | 20060056988 11/154730 |
Document ID | / |
Family ID | 36162549 |
Filed Date | 2006-03-16 |
United States Patent
Application |
20060056988 |
Kind Code |
A1 |
Seok; Jong Won ; et
al. |
March 16, 2006 |
Multi-cylinder rotary type compressor
Abstract
A multi-cylinder rotary type compressor designed to reduce
intake loss and noise. The multi-cylinder compressor includes first
and second compressing compartments partitioned from each other;
first and second intake ports communicated with the first and
second compressing compartments, respectively; and a communication
hole located adjacent to the first and second intake ports to
communicate the first compressing compartment with the second
compressing compartment.
Inventors: |
Seok; Jong Won; (Suwon-Si,
KR) ; Lenchine; Valeri; (Suwon-Si, KR) ; Lee;
Jin Woo; (Suwon-Si, KR) |
Correspondence
Address: |
SUGHRUE MION, PLLC
2100 PENNSYLVANIA AVENUE, N.W.
SUITE 800
WASHINGTON
DC
20037
US
|
Assignee: |
SAMSUNG ELECTRONICS CO.,
LTD.
|
Family ID: |
36162549 |
Appl. No.: |
11/154730 |
Filed: |
June 17, 2005 |
Current U.S.
Class: |
417/273 ;
417/410.1 |
Current CPC
Class: |
F04C 18/3562 20130101;
F04C 23/008 20130101; F04C 29/068 20130101; F04C 29/061 20130101;
F04B 39/0055 20130101; F04C 23/001 20130101 |
Class at
Publication: |
417/273 ;
417/410.1 |
International
Class: |
F04B 1/04 20060101
F04B001/04; F04B 35/04 20060101 F04B035/04 |
Foreign Application Data
Date |
Code |
Application Number |
Sep 15, 2004 |
KR |
2004-73807 |
Claims
1. A multi-cylinder rotary type compressor, comprising: first and
second compressing compartments partitioned from each other; first
and second intake ports communicated with the first and second
compressing compartments, respectively; and a communication hole
located adjacent to the first and second intake ports to
communicate the first compressing compartment with the second
compressing compartment.
2. The compressor according to claim 1, further comprising: first
and second cavities recessed a predetermined depth on an inner
surface of the respective first and second compressing compartments
so as to be adjacent to the communication hole.
3. The compressor according to claim 2, wherein the first and
second cavities are located opposite to the communication hole.
4. The compressor according to claim 3, further comprising: first
and second cylinder bodies constituting the first and second
compressing compartments, respectively; first and second
compressing devices disposed within the first and second
compressing compartments, respectively; a rotational shaft
penetrating through the first and second compressing compartments
to drive the first and second compressing devices; a partition
plate disposed between the first and second cylinder bodies; and
first and second shaft supporting members provided opposite to the
partition plate to close openings of the first and second
compressing compartments, respectively, while supporting the
rotational shaft.
5. The compressor according to claim 4, wherein the communication
hole is formed through the partition plate, and the first and
second cavities are formed on inner surfaces of the first and
second shaft supporting members, respectively, so as to be opposite
to the communication hole.
6. The compressor according to claim 5, wherein the first and
second compressing devices comprise first and second eccentric
portions provided to the rotational shaft within the first and
second compressing compartments so as to be eccentric in opposite
directions to the rotational shaft, respectively; first and second
ring pistons coupled to outer surfaces of the first and second
eccentric portions within the first and second compressing
compartments, respectively; and first and second vanes to partition
an inner space of the first and second compressing compartments
while linearly traveling in a radial direction according to
rotation of the ring pistons, respectively.
7. The compressor according to claim 6, wherein the communication
hole, and the first and second cavities have a maximum width less
than a thickness of the ring pistons in the radial direction.
8. The compressor according to claim 1, further comprising: first
and second cylinder bodies to constitute the first and second
cylindrical compressing compartments, respectively; first and
second compressing devices installed within the first and second
compressing compartments, respectively; and a rotational shaft
installed to penetrate through the first and second compressing
compartments in order to operate the first and second compressing
devices; and a partition plate disposed between the first and
second cylinder bodies, wherein the communication hole is formed
through the partition plate so as to be adjacent to the intake
ports.
9. The compressor according to claim 8, wherein the first and
second compressing devices comprise first and second eccentric
portions provided to the rotational shaft within the first and
second compressing compartments so as to be eccentric in opposite
directions to the rotational shaft, respectively; first and second
ring pistons coupled to outer surfaces of the first and second
eccentric portions within the first and second compressing
compartments, respectively; and first and second vanes to partition
an inner space of the first and second compressing compartments
while linearly traveling in a radial direction according to
rotation of the ring pistons, respectively.
10. The compressor according to claim 9, wherein the communication
hole, and the first and second cavities have a maximum width less
than a thickness of the ring pistons in the radial direction.
11. A multi-cylinder rotary type compressor, comprising: first and
second compressing compartments partitioned from each other; first
and second compressing devices to perform compressing operation in
a state of being eccentric in opposite directions within the first
and second compressing compartments, respectively; first and second
intake ports communicated with the first and second compressing
compartments, respectively; and a communication hole located
adjacent to the first and second intake ports to communicate the
first compressing compartment with the second compressing
compartment.
12. The compressor according to claim 11, further comprising: a
partition plate disposed between the first and second compressing
compartments, wherein the communication hole is formed through the
partition plate.
13. The compressor according to claim 12, further comprising: first
and second cavities recessed a predetermined depth on an inner
surface of the respective first and second compressing compartments
so as to be adjacent to the communication hole.
14. The compressor according to claim 13, wherein the first and
second cavities are located opposite to the communication hole.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] This application claims priority from Korean Patent
Application No. 2004-73807, filed on Sep. 15, 2004 in the Korean
Intellectual Property Office, the disclosure of which is
incorporated herein by reference.
BACKGROUND OF THE INVENTION
[0002] 1. Field of the Invention
[0003] The present invention relates to a multi-cylinder rotary
type compressor and, more particularly, to a multi-cylinder rotary
type compressor, designed to reduce intake loss and noise caused by
intake of a refrigerant.
[0004] 2. Description of the Related Art
[0005] Generally, as for rotary type compressors comprising only
one compressing compartment, since a ring piston inside the
compressing compartment is rotated in a state of being eccentric
against the center of a rotational shaft, there occurs a problem of
severe vibration caused by severe variation in rotational torque
and disequilibrium of mass during compression of gas. Accordingly,
in order to solve the problem, multi-cylinder rotary type
compressors are provided, which comprise separate compressing
compartments provided at upper and lower portions of the
compressor, and ring pistons to rotate in opposite dispositions
within the respective compressing compartments, thereby minimizing
the variation of the rotational torque, and the disequilibrium of
mass.
[0006] One example of such a multi-cylinder rotary type compressor
is disclosed in Japanese Patent Laid-open Publication No.
2001-153079 (Laid-open Date: Jun. 5, 2001). The compressor
comprises a first cylinder body provided at an upper portion
thereof and having a cylindrical first compressing compartment
formed in the first cylinder body, a second cylinder body provided
at a lower portion and having a cylindrical second compressing
compartment formed in the second cylinder body, and a partition
plate between the compressing compartments. The compressor further
comprises first and second ring pistons to compress a refrigerant
gas while eccentrically rotating in a state of maintaining opposite
dispositions within the respective compressing compartments upon
rotation of the rotational shaft, and first and second intake ports
communicated with inner portions of the respective compressing
compartments to intake the refrigerant gas into the compressing
compartments.
[0007] In such a multi-cylinder rotary type compressor, the first
and second cylinder bodies respectively constituting the
compressing compartments have a lower height than that of the
single cylinder compressor having the same capability as that of
the multi-cylinder rotary type compressor, whereby the diameters of
the first and second intake ports of the respective compressing
compartments are limited. Accordingly, since the multi-cylinder
rotary type compressor has a large resistance against the intake
flow due to a small cross-sectional area of each intake port, it
has a problem of enlarged intake loss and intake noise due to
insufficient intake amount of gas through the respective intake
ports when intake volumes of the respective compressing
compartments are rapidly increased (that is, when intake amounts of
the gas are rapidly increased).
SUMMARY OF THE INVENTION
[0008] The present invention has been made in view of the above and
other problems, and an aspect of the present invention is to
provide a multi-cylinder rotary type compressor, designed to reduce
intake loss in respective compressing compartments without
increasing cross-sectional areas of intake ports of the respective
compressing compartments.
[0009] It is another aspect of the present invention to provide a
multi-cylinder rotary type compressor, designed to reduce intake
noise of the compressor.
[0010] Additional aspects and/or advantages of the invention will
be set forth in part in the description which follows and, in part,
will be apparent from the description, or may be learned by
practice of the invention.
[0011] In accordance with one aspect, a multi-cylinder rotary type
compressor is provided comprising: first and second compressing
compartments partitioned from each other; first and second intake
ports communicated with the first and second compressing
compartments, respectively; and a communication hole located
adjacent to the first and second intake ports to communicate the
first compressing compartment with the second compressing
compartment.
[0012] The multi-cylinder compressor may further comprise first and
second cavities recessed a predetermined depth on inner surfaces of
the respective first and second compressing compartments so as to
be adjacent to the communication hole.
[0013] The first and second cavities may be located opposite to the
communication hole.
[0014] The multi-cylinder compressor may further comprise: first
and second cylinder bodies constituting the first and second
compressing compartments, respectively; first and second
compressing devices disposed within the first and second
compressing compartments, respectively; a rotational shaft
penetrating through the first and second compressing compartments
to drive the first and second compressing devices; a partition
plate disposed between the first and second cylinder bodies; and
first and second shaft supporting members provided opposite to the
partition plate to close openings of the first and second
compressing compartments, respectively, while supporting the
rotational shaft.
[0015] The communication hole may be formed through the partition
plate.
[0016] The first and second cavities may be formed on the inner
surfaces of the first and second shaft supporting members,
respectively, so as to be opposite to the communication hole.
[0017] The first and second compressing devices may comprise first
and second eccentric portions provided to the rotational shaft
within the first and second compressing compartments so as to be
eccentric in opposite directions to the rotational shaft,
respectively; first and second ring pistons coupled to outer
surfaces of the first and second eccentric portions within the
first and second compressing compartments, respectively; and first
and second vanes to partition an inner space of the first and
second compressing compartments while linearly traveling in a
radial direction according to rotation of the ring pistons,
respectively.
[0018] The communication hole, and the first and second cavities
may have a maximum width less than a thickness of the ring pistons
in the radial direction.
[0019] In accordance with another aspect, a multi-cylinder rotary
type compressor is provided comprising: first and second
compressing compartments partitioned from each other; first and
second compressing devices to perform compressing operation in a
state of being eccentric in opposite directions within the first
and second compressing compartments, respectively; first and second
intake ports communicated with the first and second compressing
compartments, respectively; and a communication hole located
adjacent to the first and second intake ports to communicate the
first compressing compartment with the second compressing
compartment.
BRIEF DESCRIPTION OF THE DRAWINGS
[0020] These and/or other aspects and advantages of the invention
will become apparent and more readily appreciated from the
following description of the exemplary embodiments, taken in
conjunction with the accompanying drawings, in which:
[0021] FIG. 1 is a cross-sectional view illustrating the
construction of a multi-cylinder rotary type compressor in
accordance with one embodiment of the present invention;
[0022] FIG. 2 is a cross-sectional view taken along line II-II' of
FIG. 1;
[0023] FIG. 3 is a cross-sectional view taken along line III-III'
of FIG. 1;
[0024] FIG. 4 is a detail view of circle IV of FIG. 1;
[0025] FIG. 5 is a perspective view illustrating the construction
of communication hole, and first and second cavities of the
multi-cylinder rotary type compressor in accordance with the
embodiment of the present invention;
[0026] FIG. 6 is a view illustrating the cavity of a ring piston of
the multi-cylinder rotary type compressor in a state of being
partially closed in accordance with the embodiment of the present
invention; and
[0027] FIG. 7 is a cross-sectional view illustrating the
construction of a multi-cylinder rotary type compressor in
accordance with another embodiment of the present invention.
DETAILED DESCRIPTION OF THE ILLUSTRATIVE, NON-LIMITING EMBODIMENTS
OF THE INVENTION
[0028] Reference will now be made in detail to illustrative,
non-limiting embodiments of the invention, examples of which are
illustrated in the accompanying drawings, wherein like reference
numerals refer to the like elements throughout the drawings. The
embodiments are described below to explain the invention by
referring to the figures.
[0029] Referring to FIG. 1, a multi-cylinder rotary type compressor
in accordance with one embodiment of the invention comprises a
motor 20 disposed at an upper portion inside a closed container 10
to generate a rotational force, and a compressing part 30 disposed
at a lower portion inside the closed container 10 while being
connected to the motor 20 through a rotational shaft 21.
[0030] The motor 20 includes a cylindrical stator 22 fixed to an
inner surface of the closed container 10, and a rotor 23 rotatably
installed inside the stator 22 while being coupled at the center of
the rotor 23 to the rotational shaft 21.
[0031] As shown in FIGS. 1 to 3, the compressing part 30 includes a
first cylinder body 33 provided at an upper portion thereof and
having a first cylindrical compressing compartment 31 formed in the
first cylinder body 33, a second cylinder body 34 provided at a
lower portion and having a second cylindrical compressing
compartment 32 formed in the second cylinder body 34, and first and
second compressing devices 40 and 50 installed within the first and
second compressing compartments 31 and 32 to compress a gas,
respectively. The rotational shaft 21 extended from the motor 20 is
installed to penetrate though the center of the first and second
compressing compartments 31 and 32 so as to operate the first and
second compressing devices 40 and 50 within the first and second
compressing compartments 31 and 32.
[0032] The compressing part 30 includes a partition plate 35
disposed between the first and second cylinder bodies 33 and 34 in
order to partition the first compressing compartment 31 provided at
the upper portion of the compressing part from the second
compressing compartment 32 provided at the lower portion of the
compressing part, and first and second shaft supporting members 36
and 37 mounted on an upper side of the first cylinder body 33 and a
lower side of the second cylinder body 34, respectively, so as to
close upper and lower openings of the first and second compressing
compartments 31 and 32, respectively, while supporting the
rotational shaft 21.
[0033] The first and second compressing devices 40 and 50
respectively installed within the first and second compartments 31
and 32 include first and second eccentric portions 41 and 51
provided on outer surfaces of the rotational shaft 21 in the
compressing compartments 31 and 32, first and second ring pistons
42 and 52 rotatably coupled to outer surfaces of the first and
second eccentric portion 41 and 51 with outer surfaces of the ring
pistons 42 and 52 in contact with inner surfaces of the compressing
compartments 31 and 32 to allow the first and second eccentric
portions 41 and 51 to rotate, first and second vanes 43 and 53 to
partition the inner space of the compressing compartments 31 and 32
into an intake side and a discharge side while linearly traveling
in a radial direction within the respective compressing
compartments 31 and 32 according to rotation of the respective ring
pistons 42 and 52 (see FIGS. 2 and 3). At this time, the first and
second eccentric portions 41 and 51 are disposed on the outer
surfaces of the rotational shaft 21 to be eccentric in opposite
directions. This construction is provided for the purpose of
minimizing variation in rotational torque and reducing vibration
upon compressing operation by maintaining balance between opposite
sides of the rotational shaft.
[0034] The first and second cylinder bodies 33 and 34 have first
and second intake ports 61 and 62 connected to first and second
intake pipes 63 and 64, respectively, such that the gas flows in
first and second cylinder bodies 33 and 34 therethrough. The first
and second supporting members 36 and 37 have first and second
discharge ports 65 and 66 in order to discharge a compressed gas
(see FIGS. 2 and 3). In FIG. 1, reference numeral 13 denotes an
accumulator installed within a refrigerant intake pipe 11, and
reference numeral 12 denotes a discharge pipe to guide the
compressed refrigerant inside the closed container 10 to the
outside.
[0035] In such a multi-cylinder rotary type compressor, as the
first and second eccentric portions 41 and 51 within the first and
second compressing compartments 31 and 32 are rotated in a
direction of arrow A by virtue of driving of the motor 20 while
maintaining opposite disposition within the compressor, the first
and second ring pistons 42 and 52 intake the gas from the first and
second intake ports 61 and 62, and discharge the compressed gas
towards the first and second discharge ports 65 and 66 while
eccentrically rotating within the first and second compressing
compartment 31 and 32, respectively, thereby performing a
compressing operation.
[0036] Upon the compression of the gas, since the first and second
eccentric portions 41 and 51 are eccentric in opposite directions
to each other, the compressing compartments 31 and 32 always
provide different intake volumes from each other, one of which is
alternatively higher than the other, and this phenomenon is
repeated with a phase difference of 180 degrees within the
compressing compartments 31 and 32. That is, in the case where the
first compressing compartment 31 has an increased intake volume as
shown in FIG. 2, the second compressing compartment 32 has a
reduced intake volume as shown in FIG. 3. In this state, when the
rotational shaft 21 is rotated 180.degree. more in a direction of
arrow A, the intake volume of the second compressing compartment 32
is increased, whereas the intake volume of the first compressing
compartment 31 is reduced. As such, since the intake volumes of the
respective compressing compartments 31 and 32 operate in opposite
fashions, if one of the compressing compartments 31 and 32 has an
increased intake requirement for the gas due to an increased intake
volume, the intake volume of the other compressing compartment is
reduced, thereby providing a reduced intake requirement for the
gas.
[0037] Meanwhile, a rapid increase in intake volume within the
respective compressing compartments 31 and 32 is accompanied with a
rapid increase in intake requirement for the gas through the first
and second intake ports 61 and 62. However, since the size of the
respective intake ports 61 and 62 is limited, an intake amount of
the gas is insufficient, causing intake loss. In order to solve
this problem, as shown in FIGS. 4 and 5, the present invention has
a communication hole 71 formed adjacent to the intake ports 61 and
62 through the partition plate 35 such that the first and second
compressing compartments 31 and 32 are communicated with each other
via the communication hole 71.
[0038] As a result, when one of the compressing compartments is
increased in intake volume and then has an increased intake
requirement for the gas, the construction described above can allow
the gas within the compressing compartment, which has a reduced
intake requirement for the gas due to a reduced intake volume of
the compressing compartment, to be supplied to the compressing
compartment, which has a higher intake requirement (or intake
volume) for the gas due to an increased intake volume of the
compressing compartment through the communication hole 71, thereby
preventing the intake loss. That is, even though the size of the
intake ports 61 and 62 of the respective compressing compartments
31 and 32 is limited, the communication hole 71 allows the gas
supplied through the intake ports 61 and 62 into the compressing
compartments 31 and 32 to be shared by the compressing compartments
31 and 32 through the communication hole 71, so that, when the
intake requirement for the gas is maximized in one of the
compressing compartments 31 and 32, the gas can be sufficiently
supplied into an associated compressing compartment 31 or 32,
thereby preventing the intake loss.
[0039] For instance, in the case of a rapid increase in intake
requirement for the gas due to an increase of the intake volume of
the first compressing compartment 31, not only the gas supplied to
the first compressing compartment 31 through the first intake port
61, but also some portion of the gas supplied to the second
compressing compartment 32 through the second intake port 62 are
supplied to the intake side of the first compressing compartment 31
through the communication hole 71, so that the intake loss can be
prevented. On the contrary, when the second compressing compartment
32 has an increased intake volume, some portion of the gas supplied
to the first compressing compartment 31 through the first intake
port 61 is additionally supplied to the second compressing
compartment 32 through the communication hole 71, so that the
intake loss can be prevented.
[0040] In this case, in the present embodiment, the first and
second compressing compartments 31 and 32 are, as shown in FIGS. 4
and 5, communicated with each other through the communication hole
71 formed adjacent to the first and second intake ports 61 and 62
through the partition plate 35 within the first and second
compressing compartments 31 and 32. Meanwhile, as shown in FIG. 7,
if a communication hole 72 is formed through an inner wall of the
first and second compressing compartments 31 and 32 of the cylinder
bodies 33 and 34 as well as the partition plate 35 to allow exits
of the intake ports 61 and 62 to be communicated with each other,
the same effect as that of the present embodiment can also be
realized. However, in order to provide the construction shown in
FIG. 7, the communication holes are drilled through not only the
partition plate 35, but also the cylinder bodies 33 and 34,
complicating the manufacturing process. Accordingly, it is
desirable that the communication hole 71 is formed through the
partition plate 35 such that the inner portions of the compressing
compartments are directly communicated with each other via the
partition plate 35, as shown in FIG. 4.
[0041] Moreover, as shown in FIG. 4, the communication hole 71 has
a maximum width less than the thickness of the first and second
ring pistons 42 and 52 in the radial direction. This is attributed
to the fact that, if the width of the communication hole 71 is
larger than the thickness of the ring pistons 42 and 52,
compressing efficiency can be lowered because the compressed gas
can flow from the respective compressing compartments 31 and 32 to
the inner spaces of the respective ring pistons 42 and 52 through
the communication hole 71, when the ring pistons 42 and 52 are
located on the communication hole 71.
[0042] Moreover, the multi-cylinder rotary type compressor
consistent with the invention has first and second cavities 73 and
74 recessed a predetermined depth on inner surfaces of the
respective compressing compartments 31 and 32 in order to reduce
the intake noise. The first and second cavities 73 and 74 are
formed on the inner surfaces of the first and second shaft
supporting members 36 and 37 at locations adjacent to the
respective intake ports 61 and 62 while being opposite to the
communication hole 71.
[0043] This construction can allow the first and second cavities 73
and 74 to act as a Helmholtz resonator upon generation of noise due
to flow resistance of the intake gas at an initial stage of intake
of the respective compressing compartments 31 and 32, thereby
reducing intake noise of the gas. A typical Helmholtz resonator
comprises a cavity with a small entrance, and reduces noise and
vibration using a principle that, when an incidence wave within a
specific frequency band comes into the cavity through the small
entrance, a new reflection wave having a waveform opposite to that
of the incidence wave is generated, and extinguishes the incidence
wave as it comes out of the cavity.
[0044] In the present invention, the first and second cavities 73
and 74 act as the Helmholtz resonator described above. For example,
when the second ring piston 52 passes the second cavity 74 as shown
in FIG. 6, an entrance 74a of the second cavity 74 is partially
opened in a state of being screened by the second ring piston 52.
At this time, the partially opened entrance 74a of the second
cavity 74 acts as the small entrance of the Helmholtz resonator,
and an inner space 74b of the second cavity 74 acts as the cavity
of the Helmholtz resonator, so that the second cavity 74 can reduce
the intake noise of the second compressing compartment 32 while
acting as the Helmholtz resonator. The first cavity 73 also reduces
the intake noise of the first compressing compartment 31 with the
principle described above.
[0045] Under such a principle, it can be considered that, even
though the first and second cavities 73 and 74 are not necessarily
adjacent to the intake ports 61 and 62, respectively, these can act
to reduce the noise generated from the compressing compartments 31
and 32. However, the noise related to intake of the gas in the
rotary type compressor frequently occurs at the respective intake
ports 61 and 62 having the maximum intake flow resistance. In
particular, since the rotary type compressor of the invention has a
large fluctuation in gas flow through the respective intake ports
61 and 62 at the moment that the compressor starts the intake
operation, the intake noise is also increased at an initial time of
the intake operation. Accordingly, in order to enhance the noise
reduction effect of the intake gas, it is desirable that the first
and second cavities 73 and 74 are located adjacent to the first and
second intake ports 61 and 62, respectively, as illustrated in the
present embodiments.
[0046] As apparent from the above description, in spite of the
limited size of the intake ports, the multi-cylinder compressor of
the present invention allows the gas, which is supplied to the
respective compressing compartments through the respective intake
ports, to be shared by the compressing compartments through the
communication hole, so that, even when the intake requirement of
any of the compressing compartments reaches the maximum point, the
amount of the gas supplied to the associated compressing
compartment is sufficiently secured, thereby preventing the intake
loss.
[0047] Additionally, the gas supply into the compressing
compartments can be smoothly performed, so that the intake noise
caused by the intake flow resistance at the intake ports is
minimized.
[0048] Furthermore, the first and second cavities are respectively
provided on the inner surfaces of the compressing compartments so
as to be adjacent to the intake ports, and act as a Helmholtz
resonator, so that the intake noise can be further reduced.
[0049] Although exemplary embodiments of the invention have been
disclosed for illustrative purposes, those skilled in the art will
appreciate that various modifications, additions and substitutions
are possible, without departing from the scope and spirit of the
invention as disclosed in the accompanying claims.
* * * * *