U.S. patent application number 10/296390 was filed with the patent office on 2003-12-25 for vane structure for compressor.
Invention is credited to Ahn, Byung-Ha, Kim, Young-Jong, Sa, Bum-Dong, Sim, Jae-Sul.
Application Number | 20030235510 10/296390 |
Document ID | / |
Family ID | 26638957 |
Filed Date | 2003-12-25 |
United States Patent
Application |
20030235510 |
Kind Code |
A1 |
Kim, Young-Jong ; et
al. |
December 25, 2003 |
Vane structure for compressor
Abstract
A vane structure for a compressor comprises: a Z-plate located
in a cylinder assembly for dividing an inner space of the cylinder
assembly into a plurality of compression spaces and notated by a
driving unit to suck, compress, and discharge fluid; and vanes
undergoing reciprocating movements by being contacted to both
surfaces of the Z-plate for dividing the respective compression
space into a suction area and a compression area, wherein the vane
includes a vane roller which is rolling contacted to the Z-plate to
reduce a friction resistance between the Z-plate and the vane, and
thereby an abrasion can be minimized, a noise generation can be
reduced, life spans of components can be increased, and a
reliability of the compressor can be improved.
Inventors: |
Kim, Young-Jong; (Gimhae,
KR) ; Sa, Bum-Dong; (Changwon, KR) ; Ahn,
Byung-Ha; (Busan, KR) ; Sim, Jae-Sul; (Busan,
KR) |
Correspondence
Address: |
BIRCH STEWART KOLASCH & BIRCH
PO BOX 747
FALLS CHURCH
VA
22040-0747
US
|
Family ID: |
26638957 |
Appl. No.: |
10/296390 |
Filed: |
November 25, 2002 |
PCT Filed: |
April 10, 2002 |
PCT NO: |
PCT/KR02/00639 |
Current U.S.
Class: |
418/219 |
Current CPC
Class: |
F04C 18/3568
20130101 |
Class at
Publication: |
418/219 |
International
Class: |
F04C 018/344 |
Foreign Application Data
Date |
Code |
Application Number |
Apr 10, 2001 |
KR |
2001-0018935 |
Dec 3, 2001 |
KR |
2001-0075964 |
Claims
1. A vane structure for a compressor including a cylinder assembly
having a suction passage and a discharge passage, a Z-plate
dividing an inner space of the cylinder assembly into a plurality
of compression spaces, and sucking, compressing and discharging a
fluid while being rotated by a driving unit, and vanes being in
contact with both sides of the Z-plate to make a reciprocal
movement, and dividing each compression space into a suction area
and a compression area, wherein the vane has a vane roller being in
rolling-contact with the Z-plate.
2. The vane structure of claim 1, wherein the vane includes a vane
plate reciprocally moved along both sides of the Z-plate and a vane
roller provided at the vane plate and being in a rolling-contact
with the Z-plate.
3. The vane structure of claim 2, wherein the vane plate includes a
roller receiving hole into which the vane roller is inserted and
mounted.
4. The vane structure of claim 3, wherein the vane roller is formed
as a bar type with the same diameter wholly, and the roller
receiving hole is formed in a hole structure having the same inner
diameter.
5. The vane structure of claim 3, wherein an opened portion of the
roller receiving hole so that the vane roller comes in contact with
the Z-plate therethrough is smaller than a diameter of the vane
roller to prevent the vane roller from releasing.
6. The vane structure of claim 3, wherein at least one of both
sides of the roller receiving hole has an opened structure.
7. The vane structure of claim 3, wherein a roller support extended
from the vane plate is formed at both sides of the roller receiving
hole, and the vane roller can be rotatably supported by the roller
support.
8. The vane structure of claim 7, wherein the vane roller is
installed at the roller support through a pin member.
9. The vane structure of claim 3, wherein the vane roller is formed
in a bar structure with a tapering shape, and the roller receiving
hole is formed in a tapering hole structure.
10. The vane structure of claim 9, wherein the vane roller is
positioned such that a side with a relatively smaller diameter is
directed inward of the cylinder assembly and a side with a
relatively greater diameter is directed outward of the cylinder
assembly.
Description
TECHNICAL FIELD
[0001] The present invention relates a vane structure for a
compressor in which a vane is in contact with a Z-plate, a rotation
member, so that a fluid can be compressed in a compression chamber
and discharged therefrom
BACKGROUND ART
[0002] Generally, compressors convert a mechanical energy into a
compression energy of an compressible fluid, of which a freezing
compressor is classified into a reciprocating compressor, a scroll
type compress, a centrifugal type compressor and rotary type
compressor depending on a compression method.
[0003] The present applicant has developed a compressor with a
novel concept, which can be classified into the rotary compressor,
and filed an application for the invention to the Korean Industrial
Patent Office (Application No. 10-1999-0042381, Application date:
Oct. 1, 1999), which has been laid open May 7, 2001 with
a-publication number 2001-0035687.
[0004] The former application invention of the same applicant will
now be described with reference to FIG. 1.
[0005] FIG. 1 is a vertical sectional view showing a compressor of
the former application invention of the present invention.
[0006] As shown in FIG. 1, a compressor of the former application
invention of the present invention includes: a electric mechanism
unit 4 consisting of a stator and a rotor 3 inside a casing 1 and
generating a rotational force; and a compression mechanism unit 10
for compressing a fluid by a rotational force generated from the
rotor 3 of the electric mechanism unit 4 and discharging it.
[0007] FIG. 2 is a partial cut-out perspective view showing the
compression mechanism unit 10.
[0008] With reference to FIGS. 1 and 2, the compression mechanism
unit. 10 includes: a cylinder 11 fixed at a lower portion of the
casing 1; a first bearing plate 13 and a second bearing plate 14
fixed at an upper surface and a lower surface of the cylinder 11
and forming a compression space (V) together with the cylinder 11;
a rotational shaft 12 for transmitting a rotational driving force
generated from the rotor 3 of the electric mechanism unit 4 to the
compression mechanism unit; a Z-plate 15 coupled at the rotational
shaft 12 and rotated, and dividing the compression space (V) of the
cylinder 11 into a first space (V1) and a second space (V2); and a
first vane 17 and a second vane 18 each being in contact with the
upper surface and lower surface of the Z-plate and dividing the
spaces V1 and V2 into suction areas (V1s and V2s) and compression
area (V1p and V2p) when the Z-plate is rotated.
[0009] The cylinder 11, the first bearing plate 13 and the second
bearing plate 14 are cylinder assembly forming the compression
space (V).
[0010] In FIG. 1, reference number 5 denotes a suction pipe through
which a fluid is sucked into the casing 1, and 6 denotes a
discharge pipe through which a fluid is discharged.
[0011] Reference numerals 11a and 11b denote suction passages
through which a fluid is sucked into the compression space (V) of
the cylinder 11, 13a and 14a denote discharge passages for
discharging a compressed fluid, and 13b and 14b denote discharge
valves.
[0012] Reference numerals 19 and 20 denote discharge mufflers for
reducing a discharge noise, and 19a and 20a denote discharge holes
formed at the discharge mufflers 19 and 20, through which a
compressed fluid is discharged.
[0013] Primary construction elements of the compressor will now be
described in detail.
[0014] The Z-plate 15 is formed as disk type when projected on
plane so that its outer circumference face can slidably contact an
inner circumferential face of the cylinder 11, and its side is
formed with a cam surface of a sine wave curve which has the same
thickness from the inner circumferential face to the outer
cicumferential face in its development, so that its upper dead
point (R1) is in contact with the lower surface of the first
bearing plate 13 and rotated, and a lower dead point (R2) is
closely adhered to the upper surface of the second bearing plate 14
and rotated.
[0015] As shown in FIG. 3, the first vane 17 and the second vane 18
are formed in square plate shape with a certain thickness,
penetrating each bearing plate 13 and 14, so that when the
rotational shaft 12 is rotated the first vane 17 and the second
vane 18 linearly and reciprocally moved in the axial direction
along the cam surface of the Z-plate 17 while being in contact with
the upper surface and lower surface of the Z-plate 15,
respectively.
[0016] The first vane 17 and the second vane 18 receives an elastic
force from springs 21 and 22 supplied by the bearing plates 13 and
14 at their rear portion 17a (refer to FIG. 1). An outer side 17b
of each vane 17 and 18 is in contact with the inner circumferential
face of the cylinder 11, and an inner side of each vane 17 and 18
is in contact with the outer circumferential face of the rotational
shaft 12. A front end portion 17d of each vane 17 and 18 slidably
contacts the upper surface and the lower surface of the Z-plate 15
(reference to FIG. 2).
[0017] The operation process of the compressor of the former
application invention constructed as described above will now be
explained.
[0018] When the rotational shaft 12 is rotated by a driving force
of the electric mechanism unit 4, the Z-plate 15 coupled at the
rotational shaft 12 is simultaneously rotated in the cylinder 11,
thereby sucking, compressing and discharging a fluid.
[0019] Namely, with reference to FIG. 2, the first space V1
positioned at an upper portion of the Z-plate 15 is divided into a
suction area V1s and a compression area V1p by taking the upper
dead point (R1) and the first vane 17 as a boundary, and the second
space V2 positioned at the lower portion of the Z-plate 15 is
divided into a suction area (V2s) and a compression area (V2p) by
taking the lower dead point (R2) and the second vane 18 as a
boundary.
[0020] In this state, as the Z-plate 15 is rotated, the upper dead
point (R1) and the lower dead point (R2) of the Z-plate 15 are
moved to vary a volume of the suction area and the compression area
of each space.
[0021] At this time, the first vane 17 and the second vane 18 are
reciprocally moved in the mutually opposite direction up to as high
as the cam face of the Z-plate.
[0022] Accordingly, a fresh fluid is simultaneously sucked into
each suction area (V1s, V2s) through each suction passage 11a and
11b of the first space V1 and the second space V2 and gradually
compressed, and then, when the upper dead point R1 or the lower
dead point R2 of the Z-plate reaches a discharge initiation point,
the fluid is simultaneously discharged outwardly of the compression
space (V) through the discharge passages 13a and 14a of each space
V1 and V2.
[0023] However, in the compressor of the former application
invention, as the vanes which are linearly and reciprocally moved
are in contact with the upper surface and the lower surface of the
Z-plate 15, a sliding friction takes place at the contact side
between the vanes 17 and 18 and the Z-plate 15.
[0024] Accordingly, a driving force loss is increased due to the
friction resistance between the vanes 17 and 18 and the Z-plate 15,
and a friction noise is generated.
[0025] In addition, as the friction face between the vanes 17 and
18 and the Z-plate 15 is abraded t shorten a life span of the
parts, and especially, as the fluid at the side of the compression
area is leaked toward the suction area, so that a compression
efficiency is degraded.
[0026] Technical Gist of the Pesent Invention
[0027] Therefore, an object of the present invention is to provide
a vane structure of a compressor that is capable of heightening an
efficiency and a reliability of a compressor by reducing a friction
loss and abrasion between a vane and a Z-plate.
DETAILED DESCRIPTION OF THE INVENTION
[0028] In order to achieve the above objects, there is provided a
vane structure for a compressor including a cylinder assembly
having a suction passage and a discharge passage, a Z-plate
dividing an inner space of the cylinder assembly into a plurality
of compression spaces, and sucking, compressing and discharging a
fluid while being rotated by a driving unit, and vanes being in
contact with both sides of the Z-plate to make a reciprocal
movement, and dividing each compression space into a suction area
and a compression area, wherein the vane has a vane roller being in
rolling-contact with the Z-plate.
[0029] The vane includes a vane plate reciprocally moved along both
sides of the Z-plate and a vane roller provided at the vane plate
and being in a rolling-contact with the Z-plate.
[0030] The vane plate includes a roller receiving hole into which
the vane roller is inserted and mounted.
[0031] In one embodiment of the present invention, the vane roller
is formed having a bar structure with the same diameter on the
whole, and the roller receiving hole is formed in a hole structure
having the same inner diameter.
[0032] An opened portion of the roller receiving hole so that the
vane roller comes in contact with the Z-plate therethrough is
smaller than a diameter of the vane roller to prevent the vane
roller from releasing.
[0033] At least one of both sides of the roller receiving hole has
an opened structure.
[0034] In another embodiment of the present invention, a roller
support extended from the vane plate is formed at both sides of the
roller receiving hole, and the vane roller can be rotatably
supported by the roller support.
[0035] The vane roller is installed at the roller support through a
pin member.
[0036] In still another embodiment of the present invention, the
vane roller is formed in a bar structure with a tapering shape, and
the roller receiving hole is formed in a tapering hole
structure.
[0037] The vane roller is positioned such that a side with a
relatively smaller diameter is directed inward of the cylinder
assembly and a side with a relatively greater diameter is directed
outward of the cylinder assembly.
[0038] The vane structure for a compressor of the present invention
has effects that by mounting the vane roller being in rotatably
contact with the Z-plate in the vane, a friction resistance between
the Z-plate and the vane can be reduced when a compressor is
operated, according to which a friction between the Z-plate and the
vane can be minimized, a noise is restrained from generating, a
durability of parts can be lengthened, and a reliability of the
compressor can be heightened.
BRIEF DESCRIPTION OF THE DRAWINGS
[0039] FIG. 1 is a vertical-sectional view showing a compressor of
a former application invention of the present invention;
[0040] FIG. 2 is a partial cut-out perspective view showing a
compression mechanism unit of a compressor of the former
application invention of the present invention;
[0041] FIG. 3 is a perspective view of a vane of the compressor of
the former application invention of the present invention;
[0042] FIG. 4 is a vertical-sectional view showing a compression
mechanism unit of a compressor in accordance with the present
invention;
[0043] FIGS. 5 and 6 are a perspective view and an exploded
perspective view showing a vane structure in accordance with a
first embodiment of the present invention;
[0044] FIGS. 7 and 8 are a perspective view and an exploded
perspective view showing a vane structure in accordance with a
second embodiment of the present invention;
[0045] FIG. 9 is an exploded perspective view showing a vane
structure and a vane installation structure in accordance with a
third embodiment of the present invention; and
[0046] FIG. 10 and FIG. 11 are explanatory side views showing a
vane operation state of the third embodiment of the present
invention.
MODE FOR CARRYING OUT THE PREFERRED EMBODIMENTS
[0047] The present invention will now be described with reference
to accompanying drawings.
[0048] FIG. 4 is a vertical-sectional view showing a compression
mechanism unit of a compressor in accordance with the present
invention, and FIGS. 5 and 6 are a perspective view and an exploded
perspective view showing a vane structure in accordance with a
first embodiment of the present invention.
[0049] The same reference numerals are given to the same and
similar parts as in the former application invention as described
above in the following descriptions.
[0050] A compression mechanism unit 10 of a compressor where vanes
are installed includes: a rotational shaft 12 coupled at a rotor of
an electric mechanism unit provided inside a casing 1; a Z-plate 15
dividing the inner space of the cylinder assembly including the
cylinder 11 coupled with the rotational shaft 12 into a first space
V1 and a second space V2; and a first vane 50 and a second vane 55
respectively inserted into the first and second bearing plates 13
and 14 and linearly and reciprocally moved along the cam face of
the Z-plate 15.
[0051] Especially, each vane 50 and 55 include vane rollers 52 and
57 at their front end portion so as to be in rolling-contact with
the Z-plate 15.
[0052] In FIG. 4, reference number 5 is suction pipes through which
a fluid is sucked into the casing 1, 19 and 20 denote discharge
mufflers for reducing a discharge noise, and 19a and 20a denote
discharge holes formed at the discharge mufflers 19 and 20, through
which a compressed fluid is discharged.
[0053] Major constructional elements of the compression mechanism
unit 10 will now be described.
[0054] The first and second bearing plats 13 and 14 are
respectively mounted at an upper side and a lower side of the
cylinder 11, which form a compression space of the cylinder
assembly together with the cylinder 11.
[0055] The suction passages 11a and 11b are respectively formed at
the cylinder 11, communicating with the first space V1 and the
second space V2, in order to suck a fluid from outside. Discharge
passages 13a and 14a are formed at each bearing plate 13 and 14,
which respectively include discharge valves 13b and 14b.
[0056] The Z-plate 15 is formed as a disk type when viewed from
plane projection so that its outer circumferential surface can
slidably contact the inner circumferential surface of the cylinder
11, and the circumferential side is formed as a cam face of a sine
wave curve having the same thickness from the inner circumferential
face to the outer circumference face when the side is opened.
[0057] In the first embodiment of the present invention, as shown
in FIGS. 5 and 6, the first vane 50 and the second vane 55 include
a vane plate 51 formed in a square plate structure with a certain
thickness and area; and a vane roller 52 rotatably mounted at a
front end portion of the vane plate 51 and being in rolling-contact
with the upper surface and the lower surface of the Z-plate 15.
[0058] The vane plate 51 is supplied by springs 21 and 22 at its
rear portion 51a, and both sides 51b and 51c are respectively in
contact with the inner circumferential face of the cylinder and the
outer circumferential face of the rotational shaft 12.
[0059] A long circular roller receiving hole 51e is formed at a
front end portion 51d of the vane plat 51, into which the vane
roller 52 is inserted and mounted.
[0060] The roller receiving hole 51e has a certain inner diameter
as large as the vane roller 51 can be inserted. The roller
receiving hole 51e is preferably formed in such a structure that
both sides of the vane plate 51 are all opened, but according to a
designing condition, either one side may be opened or both sides
may not be opened.
[0061] The vane roller 52 is formed in a circular bar structure
with an outer diameter and length corresponding to the inner
diameter and length of the roller receiving hole 51e and is in
rolling-contact with the cam face constituted by upper and lower
sides of the Z-plate 15.
[0062] The vane roller 52 is inserted and mounted in the roller
receiving hole 51e, and at this time, the both end portions of the
vane roller 52 may be mounted exposed outwardly of the roller
receiving hole 51e.
[0063] The vanes 50 and 55 are respectively inserted into the vane
slots of the first and second bearing plates 13 and 14, so that the
vane roller 52 of the front end portion 51d is in rolling-contact
at the upper surface and the lower surface of the Z-plate, and the
both sides 51b and 51c of the vane plate 51 are respectively in
contact with the inner circumferential surface of the cylinder 11
and the outer circumferential surface of the rotational shaft
12.
[0064] At this time, the vanes 50 and 55 are positioned in a radial
direction, directing to the center of the Z-plate, and positioned
perpendicular to the rotational shaft 12.
[0065] The roller receiving hole 51e is formed such that a center
of the circular section thereof is positioned at a rather inner
side than the front end portion 51d of the vane plate 51 so that
the vane rollers 52 and 57 are not released therefrom.
[0066] That is, as shown in FIG. 5, the roller receiving hole 51e
has a space (L) between both ends smaller than the diameter (D) of
the vane rollers 52 and 57.
[0067] The operation and effect of the compressor having such a
vane structure in accordance with the first embodiment of the
present invention will now be described.
[0068] When power is applied to the electric mechanism unit, the
Z-plate 15 is rotated together with the rotational shaft 12, and
vanes 50 and 55 are vertically and reciprocally moved in the
mutually opposite direction according to the height of the cam face
of the Z-plate 15.
[0069] At this time, as for the vanes 50 and 55 being in contact
with the upper and lower can face of the Z-plate 15, the vane
rollers 52 and 57 provided at the front end portion roratably
contact along the cam face of the Z-plate 15 when the vane rollers
52 and 57 are rotated, so that a friction resistance between the
Z-plate 15 and the vanes 50 and 55 can be considerably reduced.
[0070] That is, the Z-plate 15 makes a rotational motion centering
around the rotational shaft 12, whereas the vanes 50 and 55 make a
linear motion in an axial direction of the rotational shaft 12
while being in contact at the cam face of the Z-plate. Accordingly
the motion direction of the Z-plate 15 and the vanes 50 and 55
makes 90.degree., causing a problem of generation of a severe
friction at the mutual contact side.
[0071] Comparatively, however, in the present invention, the vane
rollers 52 and 57 are provided at the vanes 50 and 55, to make a
rolling motion between the vanes 50 and 55 and the Z-plate 15,
agreeing with the rotation direction of the Z-plate 15. Thus, a
friction resistance between the Z-plate 15 and the vanes 50 and 55
can be minimized.
[0072] In order to mount the vane rollers 52 and 57, the vane
rollers 52 and 57 are pushed from the side and inserted into the
roller receiving hole 51e formed at each vane plate 51. Therefore,
less number of parts are required to mount the vane rollers 52 and
57 and its assembly work is easy, so that a productivity
degradation can be prevented.
[0073] In addition, since the center of the roller receiving hole
51e for receiving the vane rollers 52 and 57 is formed at the inner
side of the contact end of the front end portion, so that the vane
rollers 52 and 57 can be prevented from releasing during
operation.
[0074] FIGS. 7 and 8 are a perspective view and an exploded
perspective view showing a vane structure in accordance with a
second embodiment of the present invention.
[0075] Compared to the construction of the first embodiment of the
present invention in which only the vane rollers are inserted into
the roller receiving hole, the second embodiment of the present
invention proposes a structure that both sides of vanes 60 and 65
are rotatably supported by vane plates 61 and 66.
[0076] That is, in the vane plates 61 and 66, roller receiving
holes 61e and 66e are formed at a front end portion being in
contact with the Z-plate, of which both sides are not opened, and
roller supports 61b and 66b are formed to rotatably support the
vane rollers 62 and 67 by means of pin members 63 and 68.
[0077] Pin through holes 62a, 67a, 61c and 66c are formed at the
vane rollers 62 and 67 and at the roller supports 61b and 66b, into
which the pin members 63 and 68 are inserted.
[0078] It is preferred that the size of the roller supports 61b and
66b is adjusted such that they are formed less protruded than the
vane rollers 62 and 67 so as not directly to be in contact with the
Z-plate.
[0079] Meanwhile, though not presented in the drawings, protrusions
may be formed at both ends of the vane rollers 62 and 67 and
inserted and mounted into grooves of the roller supports 61b and
66b, without installing pin members.
[0080] FIG. 9 is an exploded perspective view showing a vane
structure and a vane installation structure in accordance with a
third embodiment of the present invention, and FIG. 10 and FIG. 11
are explanatory side views showing a vane operation state of the
third embodiment of the present invention.
[0081] Unlike the vane rollers which are formed in a cylindrical
structure with the same diameter as in the first and second
embodiments as described above, a vane roller 72 in the third
embodiment has a structure that it is tapering off.
[0082] That is, a roller receiving hole 71e of a vane plate 71 is
form in a conical shape, for which the vane roller 72 inserted into
the roller receiving hole 71e is also formed in a conical bar shape
corresponding to the roller receiving hole 71e. The conical vane
roller 72 is in rolling-contact with the Z-plate 15.
[0083] The vane roller 72 has a length corresponding to the length
of the roller receiving hole 71e and different diameters at both
end portions as it tapers off to form a conical bar shape.
[0084] The roller receiving hole 71e is formed in a conical shape
with different inner diameters at both ends, of which lower surface
being in contact with the Z-plate is opened.
[0085] The roller receiving hole 71e is preferably formed from the
side being in contact with an outer circumference of the rotational
shaft 12 to the side being in contact with an inner wall of the
cylinder 11.
[0086] Namely, the roller receiving hole 71e is preferably formed
penetrating both sides of the vane plate 71. In this respect,
however, one side of the roller receiving hole 71e may penetrate
one side of the vane plate 71 with some portion of the other side
remaining, or otherwise, a roller support may be formed at both
sides likewise in the second embodiment of the present
invention.
[0087] The center of the roller receiving hole 71e is to be formed
inclined against the front end side of the vane plate 71. The
reason for this is to allow the contact surface of the tapering
vane roller 72 inserted into the roller receiving hole 71e to
tightly adhered onto the upper surface or the lower surface of the
Z-plate 15, being level therein without a gap.
[0088] The tapering vane roller 72 is inserted such that the side
with smaller diameter is positioned at the side of the rotational
shaft 12 and the side with a larger diameter is positioned at the
side of the inner wall of the cylinder 11.
[0089] As vane 70 is inserted into the vane slot 13a formed at the
bearing plate 13, the tapering vane roller 72 is in rolling-contact
with the Z-plate and both sides of the vane plate 71 are
respectively in contact with the outer circumferential face of the
rotational shaft 12 and the inner circumferential face of the
cylinder 11.
[0090] At this time, the vane 70 is positioned in a radial
direction toward the center of the Z-plate 15 and positioned
perpendicular to the rotational shaft 12.
[0091] The vane 70 is elastically supported by a spring coupled at
one side of the bearing plate 13. Accordingly, the vane 70 makes a
rolling movement as the tapering vane roller is in line-contact
with the Z-plate with an elastic force constantly.
[0092] The vane slot 13a, into which the vane 70 is inserted, is
penetratingly formed at the bearing plate 13, having a width
corresponding to the thickness of the vane 70 and a length
corresponding to the length of the vane 70.
[0093] That is, the vane slot 13a has the same section and shape
with the vane plate 71 of the vane 70.
[0094] The operation and effect of the vane structure in accordance
with the third embodiment of the present invention will now be
described.
[0095] When a rotational shaft 12 is rotated upon receiving a
driving force from the electric mechanism unit, the Z-plate 15 is
rotated along with the rotational shaft 12, to respectively and
successively change the first and second spaces within the cylinder
assembly into a suction area and a compression area together with
vanes 70, to suck and compress and discharge a fluid.
[0096] In the above process, as the Z-plate 15 is rotated, vanes 70
being in contact with the waveform cam surface of the Z-plate are
vertically moved along the cam surface, and at this time, the vane
roller 72 of the vane 70 is rotated in a state of being in
line-contact with the waveform curved surface of the Z-plate
15.
[0097] According to the rotation of the Z-plate 15, the vane roller
72 of the vane 70 makes a rolling movement in a state of being in
line-contact with the Z-plate 15, changing the first and second
space within the cylinder assembly consisting of the cylinder 11
and the bearing plate to each suction area and compression area.
Hence, a friction resistance between the Z-plate 15 and the vane 70
can be minimized and movement of the vane 70 can be smoothly
made.
[0098] With reference to FIG. 10, there is a difference between a
curvature of an inner curved line (a) of the Z-plate 15, that is,
the curved line where the rotational shaft 12 and the Z-plate 15
meet, and the inner diameter, and a curvature of an outer curved
line (b) of the Z-plate 15 and the outer diameter. In this
connection, if the vane roller 72 of the vane 70 is formed in a bar
structure wholly having the same diameter, an infinitesimal gap may
occur due to the curvature difference between the inner curved line
(a) and the outer curved line (b) of the Z-plate 15. Then, an
infinitesimal pressure leakage may occur between the suction area
and the compression are.
[0099] However, if the vane roller 72 of the vane 70 is formed in a
tapering bar shape, as shown in FIG. 11, such an infinitesimal gap
possibly caused due to the curvature difference between the inner
curved line (a) and the outer curved line (b) of the Z-plate 15 can
be prevented from occurrence. Therefore, a friction resistance can
be minimized and a pressure leakage can be prevented.
INDUSTRIAL APPLICABILITY
[0100] As so far described, according to the vane structure for a
compressor of the present invention, by mounting the vane roller
being in rotatably contact with the Z-plate in the vane, a friction
resistance between the Z-plate and the vane can be reduced when the
compressor is operated. Thus, abrasion between the Z-plate and the
vane can be minimized, a noise occurrence can be restrained,
durability of parts can be lengthened, and accordingly, a
reliability of the compressor can be heightened.
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