U.S. patent application number 14/409289 was filed with the patent office on 2015-06-25 for rotary compressor.
The applicant listed for this patent is DENSO CORPORATION. Invention is credited to Akira Inagaki, Hiroki Ishii, Yoshinori Murase.
Application Number | 20150176583 14/409289 |
Document ID | / |
Family ID | 49783201 |
Filed Date | 2015-06-25 |
United States Patent
Application |
20150176583 |
Kind Code |
A1 |
Murase; Yoshinori ; et
al. |
June 25, 2015 |
ROTARY COMPRESSOR
Abstract
A rotary compression mechanism is provided with a rotor which
can rotate about the axis of a shaft mounted to a casing, a
cylinder which can rotate about a rotation center eccentric from
the shaft, and a drive plate which is installed so as to be capable
of swinging relative to one of the cylinder and the rotor and to be
capable of sliding relative to the other of the cylinder and the
rotor and which rotationally connects the cylinder and the rotor.
Spaces which are separated from each other by both a partition
point and the drive plate and which are located between the inner
surface of the cylinder and the outer periphery of the rotor are
operating chambers for performing compression or suction.
Inventors: |
Murase; Yoshinori;
(Kariya-shi, JP) ; Inagaki; Akira; (Toyohashi-shi,
JP) ; Ishii; Hiroki; (Kariya-shi, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
DENSO CORPORATION |
Kariya-city, Aichi-pref. |
|
JP |
|
|
Family ID: |
49783201 |
Appl. No.: |
14/409289 |
Filed: |
June 26, 2013 |
PCT Filed: |
June 26, 2013 |
PCT NO: |
PCT/JP2013/067528 |
371 Date: |
December 18, 2014 |
Current U.S.
Class: |
418/54 |
Current CPC
Class: |
F04C 23/02 20130101;
F04C 23/008 20130101; F04C 18/22 20130101; F04C 29/12 20130101;
F04C 18/332 20130101 |
International
Class: |
F04C 18/22 20060101
F04C018/22; F04C 29/12 20060101 F04C029/12 |
Foreign Application Data
Date |
Code |
Application Number |
Jun 26, 2012 |
JP |
2012-142867 |
Claims
1. A rotary compressor which is provided with a rotor which can
rotate about an axial center of a shaft which is attached to a
casing, a cylinder which can rotate about a center of rotation
which is eccentric from said shaft, and a drive plate which can
swing with respect to either said cylinder or said rotor and can
slide with respect to the other and which connects said cylinder
and said rotor to be able to rotate, and a side plate which forms a
side part of said drive cylinder, wherein, an inner surface of said
cylinder and an outer circumference of said rotor are made to
contact at a partition point by making the center of rotation of
said cylinder eccentric from the axial center of said shaft, and
the space between an inner surface of said cylinder and an outer
circumference of said rotor, which is partitioned off by said
partition point and said drive plate, forms working chambers for
compression or suction. a suction passage is provided at said shaft
and said rotor for suction into the working chamber which performs
suction and a discharge valve part is provided for discharge at a
side plate which forms a side part of said cylinder.
2. The rotary compressor according to claim 1, which drives said
cylinder to rotate.
3. The rotary compressor according to claim 2, which connects a
motor rotor of an electric motor to an outer circumference of said
cylinder.
4. The rotary compressor according to claim 1, which drives said
rotor to rotate.
5. (canceled)
6. (canceled)
7. The rotary compressor according to claim 1, wherein a swinging
side of said drive plate is configured by a cylindrical
surface.
8. The rotary compressor according to claim 1, wherein said drive
plate is configured by a flat plate and wherein a swinging side of
said drive plate is sandwiched between two shoes with single sides
which are configured by cylindrical surfaces.
Description
TECHNICAL FIELD
[0001] The present invention relates to a rotary compressor, more
particularly to one which is high in efficiency and reliability in
compression of a refrigerant in an air-conditioner etc. and which
can be reduced in size while achieving both high efficiency and
reliability.
BACKGROUND ART
[0002] From the viewpoint of lower cost and easier mountability in
a vehicle etc., it has become necessary for compressors to be
reduced in size. As a means for reducing size, arrangement of the
compression part inside of a drive motor is effective for achieving
greater compactness. Such a configuration in which a compression
part is arranged inside of a motor is disclosed in PLT 1. In this
prior art, an elliptical shaped cylinder 8, which is formed
integrally with a rotor of a motor, is configured to rotate with
respect to a stationary state piston 17 which is contrary to a
usual rolling piston. This basically can still be said to be a
usual rolling piston type rotory compressor, so there is a vane
nose. Further, the springs and vanes are arranged at the rotating
cylinder part, so centrifugal force acts on them at the time of
high speed rotation. If overcoming the spring force, clearance is
formed between the vane nose and rotor (the vane is separate from
the rotor.) and no compression operation occurs, so the drop in
performance becomes a problem. Therefore this was unsuited for high
speed rotation. Further, if increasing the spring force so as to
overcome the centrifugal force, the sliding action occurs in the
state where the pressing force between the vane nose and the rotor
becomes excessive, and the vane nose part would seize up by
adhesive wear or other problems would arise in reliability.
[0003] On the other hand, PLT 2 discloses forming a compression
chamber by a vane part 13 (partition plate) between a cylinder 8
which is formed integrally with a rotor of an electric motor, and a
stationary type piston 11 which is set at an eccentric position
with respect to the cylinder 8. This prior art can also still
basically be called a usual rolling piston, so the above-mentioned
problems arose.
CITATIONS LIST
Patent Literature
[0004] PLT 1: Japanese Examined Patent Publication No.
53-043682B2
[0005] PLT 2: Japanese Examined Patent Publication No.
01-054560B2
SUMMARY OF INVENTION
Technical Problem
[0006] The present invention, in view of the above problems,
provides a rotary compressor which is high in efficiency and
reliability and can be reduced in size while achieving both high
efficiency and reliability.
Solution to Problem
[0007] To solve the above problem, the aspect of the invention of
claim 1 provides a rotary compressor which is provided with a rotor
(11) which can rotate about an axial center (O1) of a shaft (12)
which is attached to a casing (1), a cylinder (8) which can rotate
about a center of rotation (O2) which is eccentric from the shaft
(12), and a drive plate (13) which can swing with respect to either
the cylinder (8) or the rotor (11) and can slide with respect to
the other and which connects the cylinder (8) and the rotor (11) to
be able to rotate, in which rotary compressor, an inner surface of
the cylinder (8) and an outer circumference of the rotor (11) are
made to contact at a partition point (C) by making the center of
rotation (O2) of the cylinder (8) eccentric from the axial center
(O1) of the shaft (12), and the space between an inner surface of
the cylinder (8) and an outer circumference of the rotor (11) which
is partitioned off by the partition point (C) and the drive plate
(13) forms working chambers (9, 10) for compression or suction.
[0008] Note that the reference signs which are attached to the
above are examples which show the correspondence with specific
examples which are described in the later mentioned
embodiments.
BRIEF DESCRIPTION OF DRAWINGS
[0009] FIG. 1 is a cross-sectional view which shows a first
embodiment of the present invention.
[0010] FIG. 2 is a detailed partial cross-sectional view which
shows the first embodiment of the present invention.
[0011] FIG. 3 is an explanatory view which shows the operation of
the first embodiment of the present invention.
[0012] FIG. 4 is a cross-sectional view which shows the first
embodiment of the present invention.
[0013] FIG. 5 is a cross-sectional view which shows a second
embodiment of the present invention.
[0014] FIG. 6 is a cross-sectional view which shows a third
embodiment of the present invention.
[0015] FIG. 7 is a cross-sectional view which shows a fourth
embodiment of the present invention.
DESCRIPTION OF EMBODIMENTS
[0016] Below, referring to the figures, embodiments of the present
invention will be explained. In the embodiments, parts of the same
configuration will be assigned the same reference signs and
explanations will be omitted. In the following explanation of the
embodiments, compression of a refrigerant for a vehicular
air-conditioning system will be used as an example, but the
invention is not necessarily limited to this. The present invention
can be applied to a broad range of home or industrial use
compressors.
First Embodiment
[0017] As shown in FIGS. 1 and 2, a stator 2 of an electric motor
is fit and fastened at an inner surface of a casing 1. The casing 1
has a lid 4 attached to it by fastening bolts etc. A rotor 3 (motor
rotor) of the electric motor is fastened to an outer circumference
of a drive cylinder 8 (cylinder 8), so the drive cylinder 8 is made
to rotate about a shaft 12 by the motor rotor 3. The drive cylinder
8 comprises a tubular shaped cylinder and side plates 27 and 27
which are attached to the two sides of the tubular shaped cylinder
by fastening bolts 41 etc. The tubular shaped cylinder and the side
plates together configure the drive cylinder 8. The shaft 12 is
press fit into the casing 1 at the right end in FIG. 1. The left
end part of the shaft 12 is inserted or press fit into the lid 4,
so the shaft 12 is designed not to rotate.
[0018] The motor rotor 3 and the drive cylinder 8 are formed
integrally each other around this stationary shaft 12 and are able
to rotate with respect to an eccentric part 12' of the shaft 12
through bearings 42. As shown in FIG. 2, a rotor 11 which acts as a
compressor is turned along with the drive cylinder 8 by a drive
plate 13. Here, the axial center O1 of the shaft 12 is eccentric
from the center of rotation O2 of the motor rotor 3 of the electric
motor. These center of rotation O2 and axial center O1 are
non-moving points. The rotor 11 of the compressor is arranged so
that the rotor 11 can rotate around the shaft 12. The rotor 11 can
rotate about the non-moving axial center O1 and is turned along
with the drive cylinder 8 by the drive plate 13. Note that, as the
drive motor of the present embodiment, an electric motor is used,
but the invention can also be applied to the case of a belt
transmission.
[0019] One end of the drive plate 13 is set at the drive cylinder 8
so as to be able to swing, while the other end of the drive plate
13 is inserted into a sliding groove 24 of the rotor 11 of the
compressor. Rotation of the drive cylinder 8 is transmitted by the
drive plate 13 to the rotor 11 whereby the rotor 11 rotates. The
drive cylinder 8 and the rotor 11 contact each other at the
partition part (contact point) C at all times during rotation. Note
that, one end of the drive plate 13 may be set at the rotor 11 so
as to be able to swing, while the other end of the drive plate 13
may be inserted into a sliding groove 24 of the drive cylinder
8.
[0020] The refrigerant gas to be compressed or other compression
medium, as shown in FIGS. 1 and 2, is introduced from a suction
port 16, passes through a suction passage 17, and is introduced
from a shaft opening 18 and rotor passage 20 to a suction side
working chamber (suction chamber) 10. The shaft opening 18 and the
rotor passage 20 are communicated at all times at all angles. At
the outlet of the shaft opening 18, a groove 19 is formed across
the entire circumference in the circumferential direction of part
of the shaft 12.
[0021] At the side plate 27 which is fastened to one side of the
drive cylinder 8, a compression chamber discharge port 21 is
provided. At the outside, a reed valve 22 (discharge valve part) is
set. Instead of a reed valve, another valve (poppet valve etc.) may
also be used. Of course, it is also possible to provide the port 21
at the outer circumference of the tubular shaped cylinder of the
drive cylinder 8, but it is necessary to consider the effects of
centrifugal force. The compression chamber discharge port 21 and
reed valve 22 rotate while discharging compressed gas to the space
inside of the casing along with rotation of the drive cylinder 8.
After that, the gas is discharged outside from a casing discharge
port 23.
[0022] Next, the drive plate 13 will be explained. The drive plate
13 is a member which corresponds to a "vane" in a rolling piston of
the prior art. That is, in the present embodiment, the drive plate
13 is a member which partitions a space into a compression chamber
(compression side working chamber) 9 and a suction chamber 10. The
drive plate 13 also has the function as a connecting member for
making the rotor 11 of the compressor be turned along with the
drive cylinder 8. To perform the function as a connecting member, a
head part 131 of the drive plate 13 forms a cylindrical surface.
The drive plate 13 is designed to be able to swing with respect to
a center axis of the head part 131 due to the provision of a
clearance 132 at the drive cylinder 8. At the rotor 11 of the
compressor, as the drive cylinder 8 rotates, the drive plate 13
slides inside the sliding groove 24. Due to this, when turned
along, rotation is possible without restriction in spite of the
eccentricity of the center of rotation O2 of the drive cylinder 8
and the axial center O1 of the rotor 11.
[0023] The compressor part comprises the rotor 11 which can rotate
about the axial center O1 of the shaft 12 which is fastened to the
casing 1, the drive cylinder 8 which can freely rotate about the
center of rotation O2 which is eccentric from the shaft 12, and the
drive plate 13 which connects the drive cylinder 8 and the rotor
11. The space between the rotor 11 and the drive cylinder 8 forms
working chambers. The working chambers are formed by the drive
plate 13 splitting the space, whereby the compression chamber 9 and
the suction chamber 10 are formed. The electric motor 2, 3 which
drives rotation of the drive cylinder 8 is used to make the drive
cylinder 8 rotate so that, among the working chambers which are
formed between the drive cylinder 8 and the rotor 11, the
compression chamber 9 at the front of the drive plate 13 in the
direction of rotation compresses the suction gas. The working
chambers which are formed between the drive cylinder 8 and the
rotor 11 are partitioned by the drive plate 13 and the partition
point C of the contact point of the drive cylinder 8 and the rotor
11. At the front of the drive plate 13 in the direction of
rotation, the compression chamber 9 is formed, while at the rear,
the suction chamber 10 is formed.
[0024] Next, the above-mentioned compression process and suction
process will be explained referring to FIG. 3 for each 90.degree.
of rotational angle .theta. of the drive cylinder (position of
drive plate 13). Here, to facilitate understanding, the angles will
be made 720.degree. for the explanation. The explanation will be
given in the order from (1) .theta.=0.degree. of FIG. 3 to again
(1) .theta.=720.degree.. At (1) .theta.=0.degree., the suction has
been completed. The drive plate 13 and the partition point C match,
so the suction chamber 10 and the compression chamber 9 are
combined. As the rotational angle .theta. of the drive cylinder 8
increases from .theta.=0.degree., as shown in (2) to (4), the span
between the front side of the drive plate 13 in the direction of
rotation and the partition point C is closed and a compression
operation proceeds in the compression chamber 9.
[0025] At (5) .theta.=360.degree., the compression chamber 9
disappears. At this time, the suction chamber 10 is formed between
the rear of the drive plate 13 in the direction of rotate and the
partition point C. Suction proceeds from (5).fwdarw.(1) whereupon
the compression process and suction process are repeated. Above,
720.degree. was used for the explanation, but the actual
compression stroke and suction stroke are simultaneously performed
in one rotation of 360.degree.. In (1) to (5) of FIG. 3, it will be
understood that compression proceeds at the compression chamber 9
between the front side of the drive plate 13 in the direction of
rotation and the partition point C and, simultaneously, suction
proceeds in the suction chamber 10 between the rear of the drive
plate 13 in the direction of rotation and the partition point C. At
(1) and (5), the drive plate 13 and partition point C match, so the
suction chamber 10 and the compression chamber 9 are combined.
[0026] As explained above, to perform the compression operation by
rotation of the drive cylinder 8, the drive cylinder 8 is arranged
inside of the motor rotor 3 of the electric motor. Therefore, it is
possible to make the compressor smaller in size. The shaft 12 does
not rotate, so the shaft 12 may have a suction port 16 set at it to
suck in the gas. Further, at a side plate 27 where there is a
little effect of centrifugal force at the time of rotation, a
compression chamber discharge port 21 and reed valve 22 are
provided. In the present embodiment, there is no vane nose sliding
part, so there is no detachment or seizing (by adhesive wear) of
the vane nose sliding part like in the prior art and both
performance and reliability can be secured from a low rotation to
high rotation operation and it is possible to provide a small sized
compressor which is built into an electric motor rotor.
Furthermore, in the prior art like a rolling piston rotory
compressor, it was necessary to make the rotor (of the compressor)
engage in eccentric motion so as to form a compression chamber and
this invited deterioration of the compressor due to vibration by
eccentric motion at the time of high speed operation, but in the
present embodiment, the rotor 11 of the compressor only engages in
revolving motion at the non-moving axial center O1, so
deterioration of the compressor due to vibration by eccentric
motion can be prevented.
[0027] In the present embodiment, the head part 131 of the drive
plate 13 forms a cylindrical surface. The drive plate 13 is
configured to be able to swing with respect to the center axis of
the head part 131. As opposed to this, as shown in FIG. 4, it is
also possible to make the drive plate 13 a flat plate with no head
part. In this case, two shoes 133 with single sides which are
configured by cylindrical surfaces are set so as to sandwich the
end part of the drive plate 13. The rest is configured the same as
in FIGS. 1 and 2. The edge part of the front end face of the drive
plate 13, which is inserted into the sliding groove 24 which is
formed at the rotor 11, is formed with a rounded shape. Further,
the edge part of the opening part of the sliding groove 24, which
is formed at the circumferential surface of the rotor 11, is formed
with a rounded shape. The head part 131 of the drive plate 13, as
shown in FIGS. 1 and 2, can be provided at the drive cylinder 8 or
can be provided at the rotor 11.
Second and Third Embodiments
[0028] The second embodiment of the present invention, as shown in
FIG. 5, is the case where the shaft 12 (axial center O1) is
attached so as to rotate with respect to the casing 1 and the
cylinder 8 is driven to rotate from the rotor 11 of the compressor
through the drive plate 13. The motor rotor 3 is connected with the
shaft 12. Further, in the present embodiment, the rotor 11 of the
compressor and the shaft 12 are formed integrally. The shaft 12 is
provided with an off-centered eccentric part 12', so the cylinder 8
can rotate by the drive plate 13 around the center of rotation O2
of this eccentric part 12. The rest is the same as in the first
embodiment.
[0029] Regarding the third embodiment as well, as shown in FIG. 6,
the shaft 12 (axial center O1) is attached so as to rotate with
respect to the casing 1 and the cylinder 8 is driven to rotate from
the rotor 11 side through the drive plate 13. In this case, an
electric motor of a type where, unlike a normal motor, the stator 2
is at the inside is used. The motor rotor 3 is formed integrally
with the shaft 12 (axial center O1) together with the rotor 11 of
the compressor. Since the shaft 12 has the off-centered eccentric
part 12' set at the shaft 12, the cylinder 8 can rotate by the
drive plate 13 around the center of rotation O2 of this eccentric
part 12'. The rest is the same as in the first embodiment.
Fourth Embodiment
[0030] The fourth embodiment is an embodiment in which the suction
and discharge of the first embodiment are reversed. In this case,
the suction port 16 is set at the position of reference sign 23 in
FIG. 1. The part 21 of the side plate 27 becomes the compression
chamber suction port 21' (reed valve unnecessary). As shown in FIG.
7, at the front of the drive plate 13 in the direction of rotation,
a compression chamber 9 is formed, while at the rear, a suction
chamber 10 is formed, so at the front of the drive plate 13 in the
direction of rotation, part of the discharge passage constituted by
the rotor passage 20 is formed, while at the rear of the drive
plate 13 in the direction of rotation, a compression chamber
suction port 21' is provided. Reference signs 17 and 16 of FIG. 1
show the discharge passage in this embodiment. At any position of
the discharge passage, a discharge valve part (reed valve etc.) is
set. In this embodiment, the inside of the casing 1 becomes a
suction chamber, so the temperature becomes low and the electric
motor is improved in motor efficiency by cooling. The other effects
are the same as in the first embodiment.
REFERENCE SIGNS LIST
[0031] 1 casing [0032] 8 drive cylinder, cylinder [0033] 11 rotor
[0034] 12 shaft [0035] 13 drive plate
* * * * *