U.S. patent application number 16/780076 was filed with the patent office on 2020-08-06 for compressor.
This patent application is currently assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI. The applicant listed for this patent is KABUSHIKI KAISHA TOYOTA JIDOSHOKKI. Invention is credited to Kazunari Honda, Hiroyuki Kobayashi, Ken Namiki, Kengo Sakakibara, Shinya Yamamoto.
Application Number | 20200248690 16/780076 |
Document ID | / |
Family ID | 1000004655597 |
Filed Date | 2020-08-06 |
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United States Patent
Application |
20200248690 |
Kind Code |
A1 |
Yamamoto; Shinya ; et
al. |
August 6, 2020 |
COMPRESSOR
Abstract
A compressor includes a rotary shaft, a rotating body, which
rotates together with the rotary shaft, and a fixed body, which
does not rotate together with the rotary shaft. The rotating body
has a rotating body surface, and the fixed body has a fixed body
surface facing the rotating body surface in the axial direction.
The compressor includes a vane, which is inserted in a vane groove
provided in the rotating body, and a compression chamber, which is
defined by the rotating body surface and the fixed body surface.
The vane includes a vane body, which is inserted in the vane
groove, and a tip seal, which is movable in the axial direction
relative to the vane body.
Inventors: |
Yamamoto; Shinya;
(Kariya-shi, JP) ; Honda; Kazunari; (Kariya-shi,
JP) ; Sakakibara; Kengo; (Kariya-shi, JP) ;
Kobayashi; Hiroyuki; (Kariya-shi, JP) ; Namiki;
Ken; (Kariya-shi, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
KABUSHIKI KAISHA TOYOTA JIDOSHOKKI |
Kariya-shi |
|
JP |
|
|
Assignee: |
KABUSHIKI KAISHA TOYOTA
JIDOSHOKKI
Kariya-shi
JP
|
Family ID: |
1000004655597 |
Appl. No.: |
16/780076 |
Filed: |
February 3, 2020 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04C 27/005
20130101 |
International
Class: |
F04C 27/00 20060101
F04C027/00 |
Foreign Application Data
Date |
Code |
Application Number |
Feb 6, 2019 |
JP |
2019-019647 |
Claims
1. A compressor comprising: a rotary shaft; a rotating body that is
configured to rotate together with the rotary shaft and includes a
rotating body surface, which intersects with an axial direction of
the rotary shaft, and a vane groove and; a fixed body that is
configured not to rotate together with the rotary shaft and
includes a fixed body surface, which faces the rotating body
surface in the axial direction; a vane that is inserted in the vane
groove and configured to rotate together with the rotating body
while moving in the axial direction; and a compression chamber that
is defined by the rotating body surface and the fixed body surface
and in which suction and compression of fluid is performed when the
vane rotates while moving in the axial direction, wherein the vane
includes a vane body inserted in the vane groove, and a sealing
member attached to an end face in the axial direction of the vane
body so as to be movable in the axial direction relative to the
vane body, a back pressure space is located between the sealing
member and the vane body, and the sealing member is configured to
be pressed by the back pressure space toward the fixed body surface
so as to be in contact with the fixed body surface.
2. The compressor according to claim 1, wherein the compression
chamber includes a first part chamber located on a trailing side of
the vane in a rotation direction of the rotating body, and a second
part chamber located on a leading side of the vane in the rotation
direction, the sealing member includes a seal attachment section
attached to a body attachment section located in the end face of
the vane body, and the body attachment section and the seal
attachment section face each other in a circumferential direction
of the rotary shaft.
3. The compressor according to claim 2, wherein the body attachment
section is a body attachment groove that is located in the end face
of the vane body, has a width in a thickness direction of the vane,
and extends in a radial direction of the rotary shaft, the body
attachment groove includes a first body groove side surface and a
second body groove side surface, which is on the leading side of
the first body groove side surface in the rotation direction, the
sealing member includes a seal body that is in contact with the
fixed body surface, the seal attachment section is a seal
attachment protrusion that protrudes from the seal body toward the
end face of the vane body, the seal attachment protrusion includes
a first seal protrusion side surface and a second seal protrusion
side surface, which is on the leading side of the first seal
protrusion side surface in the rotation direction, the seal
attachment protrusion is inserted in the body attachment groove so
that the sealing member is attached to the vane body, and the first
seal protrusion side surface and the first body groove side surface
face each other in the circumferential direction.
4. The compressor according to claim 3, wherein at least one of the
vane body and the sealing member has an introduction groove
configured to introduce fluid into the back pressure space from the
second part chamber.
5. The compressor according to claim 3, wherein the first body
groove side surface is tilted with respect to the axial direction
so as to be displaced gradually toward the leading side in the
rotation direction as the body attachment groove deepens, and the
first seal protrusion side surface is tilted with respect to the
axial direction so as to be displaced gradually toward the leading
side in the rotation direction from a proximal end to a distal end
of the seal attachment protrusion.
6. The compressor according to claim 3, wherein the fixed body
surface includes a fixed body contact surface that is in contact
with the rotating body surface; and two curved surfaces that are
located on opposite sides of the fixed body contact surface in the
circumferential direction and curved in the axial direction such
that a distance to the rotating body surface gradually increases as
the curved surfaces extend away from the fixed body contact surface
in the circumferential direction, and the body attachment groove
and the seal attachment protrusion are closer to the first part
chamber than to the second part chamber so that a side surface
contact area, which is an area of contact between the first seal
protrusion side surface and the first body groove side surface, is
closer to the first part chamber than to the second part
chamber.
7. The compressor according to claim 2, wherein the sealing member
is made of a material softer than the vane body, the sealing member
has a seal body that is in contact with the fixed body surface, the
seal body has a seal body bottom surface that faces the end face of
the vane body, the seal attachment section is a seal attachment
groove recessed from the seal body bottom surface, the body
attachment section is a body attachment protrusion protruding from
the end face of the vane body, and the body attachment protrusion
is inserted in the seal attachment groove so that the sealing
member is attached to the vane body.
8. The compressor according to claim 7, wherein the seal attachment
groove includes a first seal groove side surface and a second seal
groove side surface, which is located on the leading side of the
first seal groove side surface in the rotation direction, the body
attachment protrusion includes a first body protrusion side surface
and a second body protrusion side surface, which is located on the
leading side of the first body protrusion side surface in the
rotation direction, the second seal groove side surface is tilted
with respect to the axial direction so as to be displaced gradually
toward the trailing side in the rotation direction as the seal
attachment groove deepens, the second body protrusion side surface
is tilted with respect to the axial direction so as to be displaced
gradually toward the trailing side from a proximal end to a distal
end of the body attachment protrusion, and the second body
protrusion side surface and the second seal groove side surface
face each other in the circumferential direction.
Description
[0001] BACKGROUND
1. Field
[0002] The present disclosure relates to a compressor.
2. Description of Related Art
[0003] Japanese Laid-Open Patent Publication No. 2015-14250
describes an axial vane compressor that includes a rotary shaft, a
columnar rotor, which has slit grooves, vanes fitted in the slit
grooves to be allowed to swing, and side plates having cam
surfaces. Each cam surface serves as a fixed body surface provided
in the side plate, which serves as a fixed body. Rotation of the
rotary shaft and the rotor of this axial vane compressor causes the
vanes to rotate while moving in the axial direction of the rotary
shaft. This results in suction and compression of the fluid in the
compression chambers defined by the axial end faces of the rotor
and the cam surfaces.
[0004] If the vanes are spaced apart from the fixed body surfaces,
the fluid may leak through the gap between the vanes and the fixed
body surfaces. This increases the loss of the compressor and thus
lowers the efficiency.
SUMMARY
[0005] It is an objective of the present disclosure to provide a
compressor that reduces the likelihood of a gap created between the
vanes and the fixed body surfaces.
[0006] This Summary is provided to introduce a selection of
concepts in a simplified form that are further described below in
the Detailed Description. This Summary is not intended to identify
key features or essential features of the claimed subject matter,
nor is it intended to be used as an aid in determining the scope of
the claimed subject matter.
[0007] In one general aspect, a compressor is provided that
includes a rotary shaft, a rotating body, a fixed body, a vane, and
a compression chamber. The rotating body is configured to rotate
together with the rotary shaft and includes a rotating body
surface, which intersects with an axial direction of the rotary
shaft, and a vane groove. The fixed body is configured not to
rotate together with the rotary shaft and includes a fixed body
surface, which faces the rotating body surface in the axial
direction. The vane is inserted in the vane groove and configured
to rotate together with the rotating body while moving in the axial
direction. The compression chamber is defined by the rotating body
surface and the fixed body surface and in which suction and
compression of fluid is performed when the vane rotates while
moving in the axial direction. The vane includes a vane body
inserted in the vane groove and a sealing member attached to an end
face in the axial direction of the vane body so as to be movable in
the axial direction relative to the vane body. A back pressure
space is located between the sealing member and the vane body. The
sealing member is configured to be pressed by the back pressure
space toward the fixed body surface so as to be in contact with the
fixed body surface.
[0008] Other features and aspects will be apparent from the
following detailed description, the drawings, and the claims.
BRIEF DESCRIPTION OF THE DRAWINGS
[0009] FIG. 1 is a schematic diagram of a compressor according to a
first embodiment.
[0010] FIG. 2 is an exploded perspective view of the main
components of the compressor of FIG. 1.
[0011] FIG. 3 is an exploded perspective view of the main
components as viewed in the opposite direction from FIG. 2.
[0012] FIG. 4 is a cross-sectional view of the main components of
the compressor of FIG. 1.
[0013] FIG. 5 is a side view of the main components of the
compressor of FIG. 1.
[0014] FIG. 6 is a cross-sectional view taken along line 6-6 in
FIG. 4.
[0015] FIG. 7 is a cross-sectional view taken along line 7-7 in
FIG. 4.
[0016] FIG. 8 is an exploded perspective view of a front cylinder,
a front valve, and a front retainer of the compressor of FIG.
1.
[0017] FIG. 9 is an enlarged cross-sectional view of the
configuration around a vane in the compressor of FIG. 1.
[0018] FIG. 10 is a perspective view of a rotating body and vanes
of the compressor of FIG. 1.
[0019] FIG. 11 is an exploded perspective view of a vane of FIG.
10.
[0020] FIG. 12 is a cross-sectional view schematically showing how
a vane is in contact with two fixed body surfaces in the compressor
of FIG. 1.
[0021] FIG. 13 is a cross-sectional view taken along line 13-13 in
FIG. 9.
[0022] FIG. 14 is a developed view schematically showing the
rotating body, the two fixed bodies, and the vanes of the
compressor of FIG. 1.
[0023] FIG. 15 is a developed view schematically showing the
rotating body, the two fixed bodies, and the vanes at a phase
different from that in FIG. 14.
[0024] FIG. 16 is a cross-sectional view schematically showing how
a vane is in contact with two fixed body surfaces according to a
second embodiment.
[0025] FIG. 17 is a cross-sectional view schematically showing how
a vane is in contact with two fixed body surfaces according to a
third embodiment.
[0026] FIG. 18 is a cross-sectional view schematically showing how
a vane is in contact with two fixed body surfaces according to a
fourth embodiment.
[0027] FIG. 19 is a cross-sectional view schematically showing tip
seals of a modification.
[0028] FIG. 20 is a cross-sectional view schematically showing a
compressor of another modification.
[0029] Throughout the drawings and the detailed description, the
same reference numerals refer to the same elements. The drawings
may not be to scale, and the relative size, proportions, and
depiction of elements in the drawings may be exaggerated for
clarity, illustration, and convenience.
DETAILED DESCRIPTION
[0030] This description provides a comprehensive understanding of
the methods, apparatuses, and/or systems described. Modifications
and equivalents of the methods, apparatuses, and/or systems
described are apparent to one of ordinary skill in the art.
Sequences of operations are exemplary, and may be changed as
apparent to one of ordinary skill in the art, with the exception of
operations necessarily occurring in a certain order. Descriptions
of functions and constructions that are well known to one of
ordinary skill in the art may be omitted.
[0031] Exemplary embodiments may have different forms, and are not
limited to the examples described. However, the examples described
are thorough and complete, and convey the full scope of the
disclosure to one of ordinary skill in the art.
First Embodiment
[0032] Referring to the drawings, a first embodiment of a
compressor will now be described. The compressor of the present
embodiment may be used for a vehicle. Specifically, the compressor
may be mounted on a vehicle. The compressor may be used for a
vehicle air conditioner, and the fluid compressed by the compressor
may be a refrigerant containing oil. For convenience of
illustration, FIG. 1 shows a rotary shaft 12, a rotating body 60,
and two fixed bodies 90 and 110 in side views. In addition, FIGS. 6
and 7 schematically show vanes 131 in side views.
[0033] As shown in FIG. 1, the compressor 10 includes a housing 11,
a rotary shaft 12, an electric motor 13, an inverter 14, a front
cylinder 30, which serves as a cylinder portion, a rear plate 40, a
rotating body 60, a front fixed body 90, and a rear fixed body
110.
[0034] The housing 11 may be cylindrical as a whole and includes a
suction port 11a, through which fluid is drawn from outside, and a
discharge port 11b, through which the compressed fluid is
discharged. The housing 11 accommodates the rotary shaft 12, the
electric motor 13, the inverter 14, the front cylinder 30, the rear
plate 40, the rotating body 60, and the two fixed bodies 90 and
110.
[0035] The housing 11 includes a front housing member 21, a rear
housing member 22, and an inverter cover 25.
[0036] The front housing member 21 has a circumferential wall, an
end wall located at one end in the axial direction of the
circumferential wall, and an open end opening toward the rear
housing member 22. The suction port 11a may be provided in the
circumferential wall of the front housing member 21 at a position
closer to the end wall than to the open end. However, the suction
port 11a may be provided at any position.
[0037] The cylindrical rear housing member 22 includes a rear
housing end wall 23 and a rear housing circumferential wall 24
extending from the rear housing end wall 23 toward the front
housing member 21. The front housing member 21 and the rear housing
member 22 are combined as one unit with their open ends facing each
other. The discharge port 11b is provided in the rear housing
circumferential wall 24. However, the discharge port 11b may be
provided at any position.
[0038] The inverter cover 25 and the rear housing member 22 are
located on the opposite sides of the front housing member 21. The
inverter cover 25 is butted against and fixed to the end wall of
the front housing member 21. The inverter cover 25 accommodates the
inverter 14, which actuates the electric motor 13.
[0039] As shown in FIG. 1, the front cylinder 30 cooperates with
the rear plate 40 and accommodates the two fixed bodies 90 and 110
and the rotating body 60. The front cylinder 30 is cylindrical and
smaller in diameter than the circumferential wall 24 of the rear
housing member 22. The front cylinder 30 opens toward the rear
housing end wall 23.
[0040] The front cylinder 30 includes a front cylinder end wall 31
and a front cylinder circumferential wall 32 extending from the
front cylinder end wall 31 toward the rear housing end wall 23.
[0041] As shown in FIGS. 1 and 2, the front cylinder end wall 31
has steps arranged in the axial direction Z of the rotary shaft 12,
and includes a first end wall 31a, which is closer to the center,
and a second end wall 31b, which is located on the outer side of
the first end wall 31a in the radial direction R of the rotary
shaft 12. The second end wall 31b is displaced from the first end
wall 31a toward the rear housing end wall 23. The first end wall
31a has a front insertion hole 31c, which receives the rotary shaft
12.
[0042] As shown in FIG. 1, the front cylinder circumferential wall
32 is positioned inside the rear housing member 22. The front
cylinder circumferential wall 32 has a front cylinder inner
circumferential surface 33 and a front cylinder outer
circumferential surface 34, which is on the opposite side from the
front cylinder inner circumferential surface 33.
[0043] The front cylinder inner and outer circumferential surfaces
33 and 34 may be cylindrical surfaces having an axis extending in
the axial direction Z of the rotary shaft 12. The front cylinder
outer circumferential surface 34 is in contact with the inner
circumferential surface of the rear housing circumferential wall 24
in the radial direction R.
[0044] The front cylinder outer circumferential surface 34 includes
a discharge recess 35 defining a discharge chamber A1. The
discharge recess 35 is provided between the two axial ends of the
front cylinder outer circumferential surface 34 and is recessed
radially inward. The discharge recess 35 and the rear housing
circumferential wall 24 define the discharge chamber A1 containing
the compressed fluid. The discharge chamber A1 is cylindrical and
has an axis extending in the axial direction Z of the rotary shaft
12. The discharge chamber A1 is continuous with the discharge port
11b. The compressed fluid in the discharge chamber A1 is discharged
through the discharge port 11b.
[0045] The front cylinder 30 has a bulging section 36 projecting
outward in the radial direction. The bulging section 36 connects
the front cylinder end wall 31 to the front cylinder
circumferential wall 32. The bulging section 36 projects radially
outward from the front cylinder outer circumferential surface 34.
The front housing member 21 and the rear housing member 22 are
coupled to each other with the bulging section 36 sandwiched
between them. The housing members 21 and 22 limit displacement of
the front cylinder 30 in the axial direction Z.
[0046] As shown in FIG. 1, the front housing member 21 and the
front cylinder end wall 31 define a motor chamber A2 in the housing
11. The motor chamber A2 accommodates the electric motor 13. When
the electric power is supplied from the inverter 14, the electric
motor 13 rotates the rotary shaft 12 in the direction indicated by
arrow M, specifically, in the clockwise direction as viewed in the
direction from the electric motor 13 to the two fixed bodies 90 and
110.
[0047] Since the suction port 11a is provided in the front housing
member 21, which defines the motor chamber A2, the fluid entering
through the suction port 11a is drawn into the motor chamber A2 in
the housing 11. That is, the motor chamber A2 contains the fluid
drawn through the suction port 11a. The motor chamber A2 is a
suction chamber into which the fluid is drawn.
[0048] In the compressor 10 of this embodiment, the inverter 14,
the electric motor 13, the front fixed body 90, the rotating body
60, and the rear fixed body 110 are arranged in this order in the
axial direction Z. However, the positions of these components may
be changed, and the inverter 14 may be located radially outward
from the electric motor 13, for example.
[0049] The rear plate 40 is planar (has the shape of a circular
plate in the present embodiment) and accommodated in the rear
housing member 22 such that its thickness direction coincides with
the axial direction Z. The outer diameter of the rear plate 40 may
be the same as the diameter of the front cylinder outer
circumferential surface 34 (or the inner circumferential surface of
the rear housing circumferential wall 24). The rear plate 40 is
fitted into and supported by the rear housing member 22.
[0050] The rear plate 40 is separate from the front cylinder end
wall 31. The front cylinder 30 and the rear plate 40 are assembled
such that the distal end (open end) of the front cylinder
circumferential wall 32 is butted against the rear plate 40. The
rear plate 40 closes the opening of the front cylinder 30.
[0051] Specifically, the rear plate 40 has a plate recess 42 in the
position facing the distal end of the front cylinder
circumferential wall 32 in the axial direction Z. The plate recess
42 extends over the entire circumference. The front cylinder 30 is
coupled to the rear plate 40 with the distal end of the front
cylinder circumferential wall 32 fitted into the plate recess
42.
[0052] The housing 11 supports the rear plate 40. Specifically, the
rear plate 40 is held between the front cylinder 30, which is
supported by the housing 11, and the rear housing end wall 23,
which is a part of the housing 11. This may be changed as long as
the housing 11 supports the rear plate 40.
[0053] The rear plate 40 has a first plate surface 43 and a second
plate surface 44 extending orthogonal to the axial direction Z. The
first plate surface 43 faces away from the rear housing end wall
23. The second plate surface 44 faces the rear housing end wall 23
in the axial direction Z. Since the present embodiment has the
plate recess 42, the first plate surface 43 is smaller than the
second plate surface 44.
[0054] As used herein, the term "face" refers to a state where two
members face each other with a gap created between them, and also a
state where the two members are in contact with each other. For
example, the second plate surface 44 and the rear housing end wall
23 may be spaced apart from each other or in contact with each
other. The term "face" also refers to a state where two surfaces
face each other with parts of the surfaces are in contact with each
other and other parts are spaced apart from each other.
[0055] As shown in FIG. 1, the compressor 10 includes shaft
bearings 51 and 53, which support the rotary shaft 12 in a
rotatable manner.
[0056] The front shaft bearing 51 is attached to a boss 52 provided
on the end wall of the front housing member 21. The boss 52 is
ring-shaped and protrudes from the end wall of the front housing
member 21. The front shaft bearing 51 is located radially inward
from the boss 52 and supports a front shaft end 12a in a rotatable
manner. The front shaft end 12a is one of the two axial shaft ends
12a and 12b of the rotary shaft 12.
[0057] The central section of the rear plate 40 has a rear
insertion hole 41, which receives the rotary shaft 12. The diameter
of the rear insertion hole 41 is greater than or equal to the
diameter of the rear shaft end 12b. The rear shaft end 12b is
inserted in the rear insertion hole 41.
[0058] The inner wall surface defining the rear insertion hole 41
includes a rear shaft bearing 53, which supports the rear shaft end
12b in a rotatable manner. The rear shaft bearing 53 may be a
coating bearing formed by a coating layer on the inner wall surface
defining the rear insertion hole 41.
[0059] The coating layer may be changed and include a thermosetting
resin or a lubricant. Further, the rear shaft bearing 53 does not
have to be the coating bearing formed by the coating layer, and may
be other sliding bearings or rolling bearings. FIG. 1 shows the
rear shaft bearing 53 thicker than the actual size.
[0060] In the present embodiment, the two shaft bearings 51 and 53
support the shaft ends 12a and 12b in a rotatable manner. The front
shaft bearing 51 is attached to the boss 52 of the front housing
member 21, and the rear housing member 22 supports the rear plate
40 including the rear shaft bearing 53. As such, the rotary shaft
12 may be considered as being supported by the housing 11 with the
shaft bearings 51 and 53 so as to be rotatable relative to the
housing 11. In the present embodiment, the rotary shaft 12 is
columnar.
[0061] As shown in FIG. 1, the rear housing end wall 23 includes a
housing recess 54 in the position facing the rotary shaft 12 in the
axial direction Z. The housing recess 54 is circular and slightly
larger than the rear shaft end 12b, for example. A part of the rear
shaft end 12b is located in the housing recess 54.
[0062] The compressor 10 includes a ring plate 55 placed in the
housing recess 54, and the ring plate 55 limits displacement of the
rotary shaft 12 in the axial direction Z. The ring plate 55 may be
a flat ring fitted into the housing recess 54. The outer diameter
of the ring plate 55 may be equal to the inner diameter of the
housing recess 54. The ring plate 55 is arranged between the rear
shaft end 12b and the bottom surface of the housing recess 54. The
section of the rotary shaft 12 other than the front shaft end 12a
is located between the front shaft bearing 51 and the ring plate 55
in the axial direction Z. This limits movement of the rotary shaft
12 in the axial direction Z. However, to accommodate dimensional
errors, a small clearance may be provided between the ring plate 55
and the rear shaft end 12b.
[0063] As shown in FIG. 1, in the housing 11, the front cylinder 30
and the rear plate 40 define an accommodation chamber A3, which
accommodates the rotating body 60 and the two fixed bodies 90 and
110.
[0064] The motor chamber A2 and the accommodation chamber A3 are
arranged in the axial direction Z in the housing 11. The front
cylinder end wall 31 separates the motor chamber A2 from the
accommodation chamber A3 so that the fluid in the motor chamber A2
does not flow into the accommodation chamber A3. The front cylinder
end wall 31 serves as a partition wall that separates the motor
chamber A2 from the accommodation chamber A3 and limits migration
of the fluid from the motor chamber A2 to the accommodation chamber
A3. The rotary shaft 12, which extends through the front cylinder
end wall 31 serving as the partition wall, is located in both of
the motor chamber A2 and the accommodation chamber A3. The rear
plate 40 serves as a defining portion used to define the
accommodation chamber A3.
[0065] Referring to FIGS. 2 to 5, the details of the rotating body
60 will now be described. For the convenience of illustration, FIG.
5 shows the rotating body 60 in a different rotational position,
that is, at a different phase, from that in FIG. 4.
[0066] As the rotary shaft 12 rotates, the rotating body 60 rotates
in a rotation direction M. The rotational axis of the rotating body
60 placed in the housing 11 coincides with the center axis of the
rotary shaft 12. That is, the rotating body 60 is coaxial with the
rotary shaft 12. Accordingly, the compressor 10 performs concentric
motion instead of eccentric motion.
[0067] The rotating body 60 includes a rotating body tube 61, which
receives the rotary shaft 12, and a rotating body ring 70, which
extends radially outward from the rotating body tube 61.
[0068] The rotating body tube 61 is coupled to the rotary shaft 12
so as to rotate together with the rotary shaft 12. Rotation of the
rotary shaft 12 thus rotates the rotating body 60. The rotating
body tube 61 may be coupled to the rotary shaft 12 in any manner.
For example, the rotating body tube 61 may be fixed to the rotary
shaft 12 by press-fitting, or a fixing pin may extend through the
rotary shaft 12 and the rotating body tube 61 to fix the rotating
body tube 61 to the rotary shaft 12. The rotating body tube 61 may
be coupled to the rotary shaft 12 by a coupling member, such as a
key. Further, the rotating body tube 61 may be connected to the
rotary shaft 12 by the engagement between a recess provided in one
of them and a projection provided in the other.
[0069] The rotating body tube 61 is a cylindrical member having an
axis extending in the axial direction Z, for example. The rotating
body tube 61 may have an inner diameter that is greater than or
equal to the diameter of the rotary shaft 12. The inner
circumferential surface of the rotating body tube 61 faces the
outer circumferential surface of the rotary shaft 12 in the radial
direction R.
[0070] The rotating body tube 61 has a tube outer circumferential
surface 62 having an axis extending in the axial direction Z. The
tube outer circumferential surface 62 curves radially outward and
is a tubular surface in this embodiment.
[0071] As shown in FIGS. 2 to 4, the rotating body ring 70 may be
located at an arbitrary position (in the central section in the
present embodiment) between opposite rotating body ends 61a and
61b, which are axial ends of the rotating body tube 61.
[0072] The rotating body ring 70 is an annular plate having a plate
thickness in the axial direction Z. The rotating body ring 70
includes two axial end faces, a front rotating body surface 71 and
a rear rotating body surface 72. These rotating body surfaces 71
and 72 are ring-shaped. The two rotating body surfaces 71 and 72
intersect with the axial direction Z. In the present embodiment,
the rotating body surfaces 71 and 72 are flat surfaces extending
orthogonal to the axial direction Z. Thus, the inner and outer
edges of the rotating body surfaces 71 and 72 extend linearly as
viewed in the radial direction R, and the entire circumference of
each edge is located in the same position in the axial direction
Z.
[0073] The rotating body ring 70 has a ring outer circumferential
surface 73, which intersects with the radial direction R. The ring
outer circumferential surface 73 faces the front cylinder inner
circumferential surface 33 in the radial direction R. The ring
outer circumferential surface 73 and the front cylinder inner
circumferential surface 33 may be in contact with each other, or
may be spaced apart from each other by a small gap.
[0074] As shown in FIG. 4, the compressor 10 includes thrust
bearings 81 and 82, which support the rotating body 60 in the axial
direction Z. The thrust bearings 81 and 82 are located on the
opposite axial ends of the rotating body tube 61 and sandwich the
rotating body tube 61 in the axial direction Z.
[0075] Specifically, the front thrust bearing 81 is located in a
space created by the steps in the front cylinder end wall 31. The
front thrust bearing 81, which is supported by the front cylinder
end wall 31, supports the rotating body tube 61 (specifically, the
front rotating body end 61a) in the axial direction Z.
[0076] The rear thrust bearing 82 is located in a thrust
accommodation recess 83 provided in the rear plate 40. The thrust
accommodation recess 83 is provided in a section of the inner wall
surface defining the rear insertion hole 41 that is adjacent to the
first plate surface 43. The rear thrust bearing 82, which is
supported by the rear plate 40, supports the rotating body tube 61
(specifically, the rear rotating body end 61b) in the axial
direction Z.
[0077] The two thrust bearings 81 and 82 are shaped as circular
plates and receive the rotary shaft 12. In the present embodiment,
the inner circumference surfaces of the thrust bearings 81 and 82
are in contact with the outer circumference surface of the rotary
shaft 12. The thrust bearings 81 and 82 are in contact with the
rotary shaft 12 in the radial direction R and thus support the
rotary shaft 12. However, the thrust bearings 81 and 82 may be
spaced apart from the rotary shaft 12 in the radial direction
R.
[0078] The fixed bodies 90 and 110 are arranged on the opposite
sides of the rotating body ring 70 in the axial direction. That is,
the fixed bodies 90 and 110 are spaced apart from each other in the
axial direction Z with the rotating body ring 70 located between
them. In other words, the rotating body ring 70 is positioned
between the two fixed bodies 90 and 110.
[0079] The fixed bodies 90 and 110 are fixed to the front cylinder
30 (i.e., the housing 11) so as not to rotate together with the
rotary shaft 12. For example, the fixed bodies 90 and 110 are
fastened to the front cylinder circumferential wall 32 using
fasteners (not shown) extending through the front cylinder
circumferential wall 32. The fixed bodies 90 and 110 are thus fixed
to the front cylinder 30.
[0080] However, the two fixed bodies 90 and 110 may be fixed to the
front cylinder 30 by any method, such as press-fitting and mating.
One or more fastening sections may be provided to fasten the front
fixed body 90 to the front cylinder end wall 31, and one or more
fastening sections may be provided to fasten the rear fixed body
110 to the rear plate 40.
[0081] The structure of the two fixed bodies 90 and 110 will now be
described in detail. In this embodiment, the fixed bodies 90 and
110 have the same shape.
[0082] As shown in FIGS. 1 to 4, the front fixed body 90, which is
one of the fixed bodies 90 and 110 that is located closer to the
front cylinder end wall 31, in other words, closer to the motor
chamber A2, is ring-shaped (annular in this embodiment) and has a
front fixed body insertion hole 91, which receives the rotary shaft
12. In the present embodiment, the front fixed body insertion hole
91 is a through hole extending through the front fixed body 90 in
the axial direction Z. The front fixed body 90 is located in the
front cylinder 30 with the rotary shaft 12 inserted in the front
fixed body insertion hole 91.
[0083] The front fixed body 90 has a front fixed body outer
circumferential surface 92 facing the front cylinder inner
circumferential surface 33 in the radial direction R. In the
present embodiment, the front fixed body outer circumferential
surface 92 is in contact with the front cylinder inner
circumferential surface 33. However, the present disclosure is not
limited to this, and the front cylinder inner circumferential
surface 33 may be spaced apart from the front fixed body outer
circumferential surface 92.
[0084] The front fixed body 90 includes a front back surface 93
facing the front cylinder end wall 31 in the axial direction Z. The
front back surface 93 and the inner bottom surface 31d of the front
cylinder end wall 31 may be spaced apart from each other or in
contact with each other.
[0085] As shown in FIGS. 1 to 4, in the same manner as the front
fixed body 90, the rear fixed body 110, which is one of the fixed
bodies 90 and 110 that is located closer to the rear plate 40
serving as the defining portion, in other words, located farther
from the motor chamber A2, is ring-shaped (annular in this
embodiment) and has a rear fixed body insertion hole 111, which
receives the rotary shaft 12. In the present embodiment, the rear
fixed body insertion hole 111 is a through hole extending through
the rear fixed body 110 in the axial direction Z. The rear fixed
body 110 is located in the front cylinder 30 with the rotary shaft
12 inserted in the rear fixed body insertion hole 111. That is, in
this embodiment, the rotary shaft 12 extends through the two fixed
bodies 90 and 110 in the axial direction Z.
[0086] The rear fixed body 110 has a rear fixed body outer
circumferential surface 112 facing the front cylinder inner
circumferential surface 33 in the radial direction R. In the
present embodiment, the rear fixed body outer circumferential
surface 112 is in contact with the front cylinder inner
circumferential surface 33. However, the present disclosure is not
limited to this, and the rear fixed body outer circumferential
surface 112 may be spaced apart from the front cylinder inner
circumferential surface 33.
[0087] The rear fixed body 110 includes a rear back surface 113
that faces the first plate surface 43 of the rear plate 40 in the
axial direction Z. The rear back surface 113 and the first plate
surface 43 may be spaced apart from each other or in contact with
each other.
[0088] As shown in FIG. 4, the rotating body tube 61 is inserted in
the fixed body insertion holes 91 and 111 so that the fixed bodies
90 and 110 support the rotating body 60.
[0089] Specifically, the front rotating body end 61a of the
rotating body tube 61 is inserted in the front fixed body insertion
hole 91 and extends through the front fixed body 90.
[0090] The front fixed body insertion hole 91 is shaped and sized
corresponding to the rotating body tube 61 (specifically, the tube
outer circumferential surface 62). In the present embodiment, the
front fixed body insertion hole 91 is circular as viewed in the
axial direction Z corresponding to the circular rotating body tube
61. The front fixed body insertion hole 91 is equal to or slightly
larger than the tube outer circumferential surface 62 in diameter.
The front rotating body end 61a is supported by a front rotating
body bearing 94, which is provided in the inner wall surface
defining the front fixed body insertion hole 91, so as to be
rotatable relative to the front fixed body 90.
[0091] Likewise, the rear rotating body end 61b is inserted in the
rear fixed body insertion hole 111 and extends through the rear
fixed body 110.
[0092] The rear fixed body insertion hole 111 is shaped and sized
corresponding to the rotating body tube 61 (specifically, the tube
outer circumferential surface 62). In the present embodiment, the
rear fixed body insertion hole 111 is circular as viewed in the
axial direction Z corresponding to the circular rotating body tube
61. The rear fixed body insertion hole 111 is equal to or slightly
larger than the tube outer circumferential surface 62 in diameter.
The rear rotating body end 61b is supported by a rear rotating body
bearing 114, which is provided in the inner wall surface defining
the rear fixed body insertion hole 111, so as to be rotatable
relative to the rear fixed body 110.
[0093] The two fixed bodies 90 and 110 support the rotating body
ends 61a and 61b through the two rotating body bearings 94 and 114.
The fixed bodies 90 and 110 thus support the rotating body 60 and
limit displacement of the rotating body 60 relative to the two
fixed bodies 90 and 110.
[0094] Further, the two rotating body ends 61a and 61b are the
axial ends of the rotating body 60, so that the rotating body
bearings 94 and 114 support the axial ends of the rotating body 60.
The rotating body 60 is thus supported in a stable manner.
[0095] Further, the fixed body insertion holes 91 and 111 provided
corresponding to the rotating body tube 61 reduce or eliminate a
gap provided between the tube outer circumferential surface 62 and
the inner wall surfaces defining the fixed body insertion holes 91
and 111.
[0096] Each rotating body bearing 94, 114 may be a coating bearing
formed by a coating layer on the inner wall surface defining the
fixed body insertion hole 91, 111. FIG. 4 shows the rotating body
bearing 94, 114 thicker than the actual size. The rotating body
bearing 94, 114 does not have to be a coating bearing, and may be
other sliding bearings or rolling bearings.
[0097] The front fixed body 90 has a front fixed body surface 100,
which is a fixed body surface facing the front rotating body
surface 71 in the axial direction Z. The front fixed body surface
100 is a plate surface opposite to the front back surface 93. The
front fixed body surface 100 is ring-shaped, and annular as viewed
in the axial direction Z in the present embodiment.
[0098] As shown in FIG. 3, the front fixed body surface 100
includes a first front flat surface 101, a second front flat
surface 102, and two front curved surfaces 103. The first and
second front flat surfaces 101 and 102 intersect with the axial
direction Z (at right angles in the present embodiment). The front
curved surfaces 103 connect the two front flat surfaces 101 and
102.
[0099] As shown in FIG. 4, the two front flat surfaces 101 and 102
are displaced from each other in the axial direction Z.
Specifically, the second front flat surface 102, which serves as a
fixed body contact surface, is closer to the front rotating body
surface 71 than the first front flat surface 101 and is in contact
with the front rotating body surface 71. The section of the front
fixed body surface 100 other than the second front flat surface 102
is spaced apart from the front rotating body surface 71.
[0100] The two front flat surfaces 101 and 102 are spaced apart in
the circumferential direction of the front fixed body 90, and are
displaced from each other by 180.degree., for example. In the
present embodiment, each front flat surface 101, 102 has the shape
of a sector. In the following descriptions, the circumferential
positions in the fixed bodies 90 and 110 are also referred to as
angular positions.
[0101] Each of the two front curved surfaces 103 has the shape of a
sector. As shown in FIG. 3, the two front curved surfaces 103 are
aligned in the radial direction as viewed in the axial direction Z.
The two front curved surfaces 103 have the same shape.
[0102] Each front curved surface 103 connects the two front flat
surfaces 101 and 102. Specifically, one of the front curved
surfaces 103 connects the first ends in the circumferential
direction of the front flat surfaces 101 and 102, and the other
front curved surface 103 connects the second ends in the
circumferential direction of the front flat surfaces 101 and
102.
[0103] The angular positions of the borders between the first front
flat surface 101 and the front curved surfaces 103 are defined as
first angular positions .theta.1, and the angular positions of the
borders between the second front flat surface 102 and the front
curved surfaces 103 are defined as second angular positions
.theta.2. Although the angular positions .theta.1 and .theta.2 are
indicated by broken lines in FIG. 3, the front curved surfaces 103
and the front flat surfaces 101 and 102 are actually connected
smoothly at the borders.
[0104] The position in the axial direction Z of each front curved
surface 103 varies with circumferential position, in other words,
the angular position in the front fixed body 90. Specifically, each
front curved surface 103 is curved in the axial direction Z such
that the distance to the front rotating body surface 71 gradually
decreases from the first angular position .theta.1 to the second
angular position .theta.2. In other words, the two front curved
surfaces 103 are located on the opposite sides of the second front
flat surface 102 in the circumferential direction and curved in the
axial direction Z such that the distance to the front rotating body
surface 71 gradually increases as the front curved surfaces 103
extend away from the second front flat surface 102 in the
circumferential direction.
[0105] Each front curved surface 103 includes a front concave
surface 103a, which is curved in the axial direction Z away from
the front rotating body surface 71, and a front convex surface
103b, which is curved in the axial direction Z toward the front
rotating body surface 71.
[0106] The front concave surface 103a is closer to the first front
flat surface 101 than to the second front flat surface 102, and the
front convex surface 103b is closer to the second front flat
surface 102 than to the first front flat surface 101. The front
concave surface 103a is continuous with the front convex surface
103b. That is, the front curved surface 103 has an inflection
point.
[0107] The angular range of the front convex surface 103b and the
angular range of the front concave surface 103a may be the same or
different. Further, the position of the inflection point is
arbitrary. Since the front curved surface 103 is curved in a wave
shape, the front fixed body surface 100 may be considered as a
front wavy surface including sections that are curved in a wave
shape.
[0108] The rear fixed body 110 has a rear fixed body surface 120,
which is a fixed body surface facing the rear rotating body surface
72 in the axial direction Z. The rear fixed body surface 120 is a
plate surface opposite to the rear back surface 113. The rear fixed
body surface 120 is ring-shaped, and annular as viewed in the axial
direction Z in the present embodiment.
[0109] In the present embodiment, the rear fixed body surface 120
has the same shape as the front fixed body surface 100. As shown in
FIG. 2, the rear fixed body surface 120 includes a first rear flat
surface 121, a second rear flat surface 122, and two rear curved
surfaces 123. The first and second rear flat surfaces 121 and 122
intersect with the axial direction Z (at right angles in the
present embodiment). The rear curved surfaces 123 connect the two
rear flat surfaces 121 and 122.
[0110] As shown in FIG. 4, the two rear flat surfaces 121 and 122
are displaced from each other in the axial direction Z.
Specifically, the second rear flat surface 122, which serves as a
fixed body contact surface, is closer to the rear rotating body
surface 72 than the first rear flat surface 121 and is in contact
with the rear rotating body surface 72. The section of the rear
fixed body surface 120 other than the second rear flat surface 122
is spaced apart from the rear rotating body surface 72.
[0111] The two rear flat surfaces 121 and 122 are spaced apart from
each other in the circumferential direction of the rear fixed body
110, and are displaced from each other by 180.degree., for example.
In the present embodiment, each rear flat surface 121, 122 has the
shape of a sector.
[0112] Each of the two rear curved surfaces 123 has the shape of a
sector. The two rear curved surfaces 123 face each other in the
radial direction as viewed in the axial direction Z. One of the
rear curved surfaces 123 connects the first ends in the
circumferential direction of the rear flat surfaces 121 and 122,
and the other rear curved surface 123 connects the second ends in
the circumferential direction of the rear flat surfaces 121 and
122.
[0113] The two rear curved surfaces 123 are arranged on the
opposite sides of the second rear flat surface 122 in the
circumferential direction and curved in the axial direction Z such
that the distance to the rear rotating body surface 72 gradually
increases as the curved surfaces 123 extend away from the second
rear flat surface 122 in the circumferential direction.
[0114] The two fixed body surfaces 100 and 120 face toward each
other in the axial direction Z with the rotating body ring 70
placed between them. In addition, the two fixed body surfaces 100
and 120 are arranged in angular positions that are different from
each other by 180.degree..
[0115] The distance between the two fixed body surfaces 100 and 120
in the axial direction Z is uniform at any angular positions (i.e.,
the circumferential positions). Specifically, as shown in FIG. 4,
the first front flat surface 101 and the second rear flat surface
122 face each other in the axial direction Z, and the second front
flat surface 102 and the first rear flat surface 121 face each
other in the axial direction Z. The displacement in the axial
direction Z between the two front flat surfaces 101 and 102 is
equal to the displacement between the two rear flat surfaces 121
and 122. Hereinafter, the displacement in the axial direction Z
between the two front flat surfaces 101 and 102 and the
displacement between the two rear flat surfaces 121 and 122 are
simply referred to as displacement Z1.
[0116] Further, the front curved surfaces 103 and the rear curved
surfaces 123 have the same curvatures. That is, the front curved
surfaces 103 and the rear curved surfaces 123 are curved in the
same manner so that the distance in the axial direction Z does not
vary with the angular position. The distance between the two fixed
body surfaces 100 and 120 in the axial direction Z is therefore
uniform at any angular positions.
[0117] The shapes of the first rear flat surface 121, the second
rear flat surface 122, and the two rear curved surfaces 123 are the
same as those of the first front flat surface 101, the second front
flat surface 102, and the two front curved surfaces 103 and thus
not described in detail. As with the front curved surface 103,
since the rear curved surface 123 is curved in a wave shape, the
rear fixed body surface 120 may be considered as a rear wavy
surface including sections that are curved in a wave shape.
[0118] The circumferential direction of the two fixed bodies 90 and
110 and the rotating body 60 is the same as the circumferential
direction of the rotary shaft 12. The radial direction of the two
fixed bodies 90 and 110 and the rotating body 60 is the same as the
radial direction R of the rotary shaft 12. The axial direction of
the fixed bodies 90 and 110 and the rotating body 60 is the same as
the axial direction Z of the rotary shaft 12. As such, the
circumferential direction, the radial direction R, and the axial
direction Z of the rotary shaft 12 are interchangeable with those
of the rotating body 60 and the fixed bodies 90 and 110.
[0119] As shown in FIG. 4, the compressor 10 includes compression
chambers A4 and A5, in which suction and compression of the fluid
are performed. The compression chambers A4 and A5 are provided in
the accommodation chamber A3, specifically, on the opposite sides
of the rotating body ring 70 in the axial direction Z.
[0120] The front compression chamber A4 is defined by the front
rotating body surface 71 and the front fixed body surface 100, more
specifically, by the front rotating body surface 71, the front
fixed body surface 100, the tube outer circumferential surface 62,
and the front cylinder inner circumferential surface 33.
[0121] The rear compression chamber A5 is defined by the rear
rotating body surface 72 and the rear fixed body surface 120, more
specifically, by the rear rotating body surface 72, the rear fixed
body surface 120, the tube outer circumferential surface 62, and
the front cylinder inner circumferential surface 33. In the present
embodiment, the front compression chamber A4 and the rear
compression chamber A5 are equal in size.
[0122] The compression chambers A4 and A5 face the discharge
chamber A1 in the radial direction R with the front cylinder
circumferential wall 32 located between them. That is, the
discharge chamber A1 is located on the outer side of the
compression chambers A4 and A5 in the radial direction R.
[0123] In the present embodiment, the discharge chamber A1 faces a
part of the front compression chamber A4 in the radial direction R,
and faces the entire rear compression chamber A5 in the radial
direction R. However, the present disclosure is not limited to this
configuration. Any configuration may be used as long as the
discharge chamber A1 extends in the axial direction Z so as to face
at least a part of the front compression chamber A4 and at least a
part of the rear compression chamber A5 in the radial direction
R.
[0124] As shown in FIGS. 2 to 5, the compressor 10 includes
multiple (three) vane grooves 130 provided in the rotating body 60
and multiple (three) vanes 131 inserted in the respective vane
grooves 130.
[0125] The vane grooves 130 are provided in the rotating body ring
70. The vane grooves 130 extend through the rotating body ring 70
in the axial direction Z and open at the two rotating body surfaces
71 and 72. Each vane groove 130 extends in the radial direction R,
has a width in a direction orthogonal to both of the axial
direction Z and the radial direction R, and opens radially outward.
The rotating body tube 61 does not have a vane groove 130. Each
vane groove 130 has two side surfaces that face each other and are
spaced apart from each other in the circumferential direction.
[0126] The rotating body ring 70 is a section positioned radially
outward from the rotating body tube 61. As such, the rotating body
tube 61 is located radially inward from the rotating body ring 70.
That is, the rotating body ring 70 is a section that is positioned
on the tube outer circumferential surface 62 and protrudes radially
outward from the tube outer circumferential surface 62.
[0127] Each vane 131 is generally a rectangular plate having plate
surfaces that intersect with (extend orthogonal to) the
circumferential direction of the rotary shaft 12. The vane 131 is
located between the two fixed bodies 90 and 110 (i.e., the two
fixed body surfaces 100 and 120). The vane 131 is a plate having a
thickness in the width direction of the vane groove 130, in other
words, in a direction orthogonal to both of the axial direction Z
and the radial direction R.
[0128] The two plate surfaces of the vane 131 face the respective
side surfaces of the vane groove 130 in the circumferential
direction (i.e., the width direction of the vane groove 130). The
width of the vane groove 130 (i.e., the distance between the two
side surfaces of the vane groove 130) is the same as or slightly
wider than the plate thickness of the vane 131. The vane 131
inserted in the vane groove 130 is sandwiched between the two side
surfaces of the vane groove 130. The vane 131 can move in the axial
direction Z along the vane groove 130. In the present embodiment,
the vane 131, specifically, the two axial ends of the vane 131, is
in contact with the fixed body surfaces 100 and 120.
[0129] The vane grooves 130 are arranged at regular intervals in
the circumferential direction, specifically, at intervals of
120.degree.. The vanes 131 are arranged accordingly at regular
intervals in the circumferential direction.
[0130] Rotation of the rotating body 60 rotates the vanes 131 in
the rotation direction M. At the same time, the vanes 131, which
are in contact with the fixed body surfaces 100 and 120, move
(swing) in the axial direction Z along the curved fixed body
surfaces 100 and 120. That is, the vanes 131 rotate while moving in
the axial direction Z. As a result, the vanes 131 move into the
front compression chamber A4 and the rear compression chamber A5.
That is, the vane grooves 130 rotate and place the vanes 131 in the
compression chambers A4 and A5 as the rotating body 60 rotates.
[0131] The moving distance (in other words, the swinging distance)
of the vanes 131 in the axial direction Z is the difference between
the positions of the front flat surfaces 101 and 102 (or between
the rear flat surfaces 121 and 122) in the axial direction Z, that
is, the displacement Z1. The vanes 131 are continuously in contact
with the two fixed body surfaces 100 and 120 while the rotating
body 60 rotates. The vanes 131 are thus unlikely to intermittently
come into contact, or more specifically, come into and out of
contact repeatedly, with the fixed body surfaces 100 and 120.
[0132] As shown in FIG. 6, the three vanes 131 partition the front
compression chamber A4 into three part chambers, a first front
compression chamber A4a, a second front compression chamber A4b,
and a third front compression chamber A4c.
[0133] For convenience of description, of the three part chambers,
the part chamber located on the leading side of the second front
flat surface 102 in the rotation direction M is referred to as the
first front compression chamber A4a.
[0134] Of the three part chambers, the part chamber located on the
trailing side of the first front compression chamber A4a in the
rotation direction M is referred to as the second front compression
chamber A4b. At least a part of the second front compression
chamber A4b is located on the trailing side of the second front
flat surface 102 in the rotation direction M.
[0135] Of the three part chambers, the part chamber located between
the first front compression chamber A4a and the second front
compression chamber A4b in the circumferential direction is
referred to as the third front compression chamber A4c. In the
rotation direction M, the third front compression chamber A4c is
located on the leading side of the first front compression chamber
A4a and located on the trailing side of the second front
compression chamber A4b.
[0136] In the following description, the leading side in the
rotation direction M and the trailing side in the rotation
direction M may simply be referred to as the leading side and the
trailing side, respectively.
[0137] Each of the front compression chambers A4a to A4c spans over
an angular range of 120.degree.. That is, each of the front
compression chambers A4a to A4c extends in the circumferential
direction, and the length of each chamber in the circumferential
direction corresponds to an angular range of 120.degree..
[0138] Specifically, when one of the vanes 131 is in contact with
the second front flat surface 102, this vane 131 is not positioned
within the front compression chamber A4. At this time, the spaces
at opposite sides in the circumferential direction of the vane 131
that is in contact with the second front flat surface 102 are
separated from each other by the section where the front rotating
body surface 71 is in contact with the second front flat surface
102. The spaces are not continuous with each other. Thus, even when
one of the vanes 131 is in contact with the second front flat
surface 102, the front compression chamber A4 is partitioned into
three part chambers. In the present embodiment, for convenience of
description, even when one of the vanes 131 is in contact with the
second front flat surface 102, the front compression chamber A4 is
considered to be partitioned by the three vanes 131 into the front
compression chambers A4a to A4c.
[0139] As shown in FIG. 7, in the same manner as the front
compression chamber A4, the three vanes 131 partition the rear
compression chamber A5 into a first rear compression chamber A5a, a
second rear compression chamber A5b, which is on the trailing side
of the first rear compression chamber A5a, and a third rear
compression chamber A5c located between the first rear compression
chamber A5a and the second rear compression chamber A5b in the
circumferential direction. The first to third rear compression
chambers A5a, A5b and A5c are the same as the first to third front
compression chambers A4a, A4b and A4c and thus not described in
detail.
[0140] The configuration relating to the suction of fluid into the
compression chambers A4 and A5 and the discharging of compressed
fluid will now be described. FIG. 4 schematically shows a front
suction port 141 and a rear suction port 142.
[0141] As shown in FIGS. 2 to 4 and 6, the compressor 10 includes a
front suction port 141 through which fluid is drawn into the front
compression chamber A4. The front suction port 141 may be provided
in the front cylinder 30. Specifically, the front suction port 141
extends in the front cylinder end wall 31 and the front cylinder
circumferential wall 32 in the axial direction Z.
[0142] In addition, the front suction port 141 extends in the
circumferential direction along the front cylinder circumferential
wall 32 and is formed in an arc shape as viewed in the axial
direction Z. At least a part of the front suction port 141 is
located radially outward from the first front compression chamber
A4a. In other words, the first front compression chamber A4a
includes a part of or the entire cavity located radially inward
from the front suction port 141.
[0143] The front suction port 141 opens to the motor chamber A2 and
also to the front compression chamber A4. The front suction port
141 thus connects the motor chamber A2 and the front compression
chamber A4 to each other.
[0144] Specifically, as shown in FIG. 6, the front suction port 141
has a front suction opening 141a, which is positioned to be
continuous with the first front compression chamber A4a. The front
suction opening 141a extends in the front cylinder inner
circumferential surface 33 in the rotation direction M from a
position corresponding to the circumferential center of the second
front flat surface 102. The extending length of the front suction
opening 141a may be substantially the same as the circumferential
length of each of the front compression chambers A4a to A4c, for
example. That is, the front suction opening 141a may extend in the
front cylinder inner circumferential surface 33 in the
circumferential direction from a position corresponding to the
circumferential center of the second front flat surface 102 by
substantially the same length as the circumferential interval
between the vanes 131.
[0145] When the angular position of the circumferential center of
the second front flat surface 102 is defined as 0.degree. and the
angle increases from this 0.degree. angular position in the
rotation direction M, the front suction opening 141a preferably
extends at least from the leading edge in the rotation direction M
of the second front flat surface 102 to the 120.degree. angular
position.
[0146] As shown in FIGS. 6 and 8, the compressor 10 includes front
discharge ports 151, which discharge the fluid compressed in the
front compression chamber A4, a front valve 152, which opens and
closes the front discharge ports 151, and a front retainer 153,
which adjusts the opening degree of the front valve 152.
[0147] As shown in FIG. 6, the front discharge ports 151 may be
placed in a position of the front cylinder circumferential wall 32
that is radially outward from the front compression chamber A4 and
on the trailing side of the second front flat surface 102.
[0148] Specifically, the curved front cylinder outer
circumferential surface 34 has a front seat surface 154, which is a
recessed surface in the front cylinder outer circumferential
surface 34. The front seat surface 154 is provided in a section of
the front cylinder outer circumferential surface 34 that is located
between the front compression chamber A4 and the discharge chamber
A1 and on the trailing side of the second front flat surface 102.
The front seat surface 154 is a flat surface extending orthogonal
to the radial direction R.
[0149] As shown in FIG. 6, the front discharge ports 151 are
provided in the front seat surface 154. The front discharge ports
151 extend through the front cylinder circumferential wall 32 in
the radial direction R, thereby connecting the second front
compression chamber A4b and the discharge chamber A1 to each
other.
[0150] The front discharge ports 151 are arranged in the
circumferential direction. Each front discharge port 151 is
circular. However, the number and shape of the front discharge
ports 151 may be changed. For example, the front seat surface 154
may include only one front discharge port 151. The front discharge
port 151 may be oval. When front discharge ports 151 are provided,
the sizes of the front discharge ports 151 may be the same or
different from one another.
[0151] At least a part of each front discharge port 151 is located
radially outward from the second front compression chamber A4b. In
other words, the second front compression chamber A4b includes a
part of or the entire cavity located radially inward from the front
discharge ports 151.
[0152] The front suction port 141 and the front discharge ports 151
are spaced apart from each other in the circumferential direction.
A section of the front cylinder circumferential wall 32 that is
located radially outward from the second front flat surface 102 is
present between these ports 141 and 151.
[0153] That is, the first front compression chamber A4a is
configured to be continuous with the front suction port 141 but not
with the front discharge ports 151.
[0154] The second front compression chamber A4b is continuous with
the front discharge ports 151. However, since the second front
compression chamber A4b has a longer circumferential length than
the second front flat surface 102, depending on the angular
position of the vanes 131, the second front compression chamber A4b
may be located radially inward from the front suction port 141 and
radially inward from the front discharge ports 151 simultaneously.
Nevertheless, in the present embodiment, the area of contact
between the front rotating body surface 71 and the second front
flat surface 102 is present between the space radially inward from
the front suction port 141 and the space radially inward from the
front discharge ports 151. As such, regardless of the angular
position of the vanes 131, this contact area disconnects these two
spaces from each other. Thus, the front suction port 141 is not
continuous with the front discharge ports 151. That is, the contact
area partitions the second front compression chamber A4b further
into a space for suction and a space for compression.
[0155] As the rotating body 60 rotates, the third front compression
chamber A4c moves from a position where the chamber A4c is not
continuous with the front discharge ports 151 to a position where
it is continuous with the front discharge ports 151.
[0156] As shown in FIG. 8, the front valve 152 and the front
retainer 153 are provided on the front seat surface 154. The front
seat surface 154 has screw holes 154a. The front valve 152 and the
front retainer 153 are fixed to the front seat surface 154 by bolts
B, which extend through the front retainer 153 and the front valve
152 and engage the screw holes 154a.
[0157] The front valve 152 normally closes the front discharge
ports 151. When the pressure in the front compression chamber A4
(specifically, the second front compression chamber A4b) exceeds
the threshold, the front valve 152 moves from a position that
closes the front discharge ports 151 to a position that opens the
front discharge ports 151. The fluid compressed in the front
compression chamber A4 is thus discharged into the discharge
chamber A1. The front retainer 153 limits the opening angle of the
front valve 152.
[0158] As shown in FIGS. 2 to 4 and 7, the compressor 10 includes a
rear suction port 142 through which the fluid is drawn into the
rear compression chamber A5. The rear suction port 142 may be
formed in the front cylinder 30. Specifically, the rear suction
port 142 extends in the front cylinder end wall 31 and the front
cylinder circumferential wall 32 in the axial direction Z.
[0159] In addition, the rear suction port 142 extends in the
circumferential direction along the front cylinder circumferential
wall 32 and is formed in an arc shape as viewed in the axial
direction Z. At least a part of the rear suction port 142 is
located radially outward from the first rear compression chamber
A5a. In other words, the first rear compression chamber A5a
includes a part of or the entire cavity located radially inward
from the rear suction port 142.
[0160] The rear suction port 142 opens to the motor chamber A2 and
also to the rear compression chamber A5. The rear suction port 142
thus connects the motor chamber A2 and the rear compression chamber
A5 to each other.
[0161] Specifically, as shown in FIG. 7, the rear suction port 142
has a rear suction opening 142a, which is positioned to be
continuous with the first rear compression chamber A5a. The rear
suction opening 142a extends in the front cylinder inner
circumferential surface 33 in the rotation direction M from a
position corresponding to the circumferential center of the second
rear flat surface 122.
[0162] The rear suction port 142 and the rear suction opening 142a
extend in the rotation direction M from the position corresponding
to the circumferential center of the second rear flat surface 122
to an extent that does not interferes with the front discharge
ports 151, the front valve 152, or the front retainer 153.
[0163] However, the present disclosure is not limited to this, and
the rear suction port 142 and the rear suction opening 142a may
have the same circumferential length as the front suction port 141
and the front suction opening 141a. In this case, to prevent the
rear suction port 142 and the rear suction opening 142a from
interfering with the front discharge ports 151 or other parts, the
axial length of the front valve 152 may be shortened, the front
discharge ports 151 may be displaced, or the angular range of the
second front flat surface 102 may be reduced.
[0164] The present embodiment has two suction ports 141 and 142
corresponding to the two compression chambers A4 and A5. The front
suction port 141 and the rear suction port 142 are displaced from
each other in the circumferential direction so as not to be
continuous with each other. Specifically, these ports 141 and 142
are displaced from each other by 180.degree.. As a result, the
suction of fluid into one of the compression chambers A4 and A5 is
less likely to reduce the amount of the fluid drawn into the other
compression chamber, which would otherwise occur if the two suction
ports 141 and 142 are continuous with each other.
[0165] As shown in FIG. 7, the compressor 10 includes rear
discharge ports 161, which discharge the fluid compressed in the
rear compression chamber A5, a rear valve 162, which opens and
closes the rear discharge ports 161, and a rear retainer 163, which
adjusts the opening degree of the rear valve 162.
[0166] The rear discharge ports 161 may be placed in a position of
the front cylinder circumferential wall 32 that is radially outward
from the rear compression chamber A5 and on the trailing side of
the second rear flat surface 122.
[0167] In accordance with the second front flat surface 102 and the
second rear flat surface 122, which are displaced from each other
by 180.degree., the rear discharge ports 161 are displaced from the
front discharge ports 151 by 180.degree. in the circumferential
direction. Further, in accordance with the front compression
chamber A4 and the rear compression chamber A5, which are displaced
from each other in the axial direction Z, the rear discharge ports
161 are displaced from the front discharge ports 151 in the axial
direction Z.
[0168] The specific configurations of the rear discharge ports 161,
the rear valve 162, and the rear retainer 163 are substantially the
same as those of the front discharge ports 151, the front valve
152, and the front retainer 153 except for their positions, and
thus not described in detail. The term "front" in the description
of the front discharge ports 151, the front valve 152, and the
front retainer 153 may be replaced with "rear." The discharge ports
151 and 161 may be considered as discharge passages.
[0169] The vanes 131 will now be described. In the following
description, of the two part chambers separated by a vane 131, the
part chamber on the trailing side of the vane 131 is referred to as
a first part chamber Ax, and the part chamber located on the
leading side of the vane 131 is referred to as a second part
chamber Ay. For the vane 131 separating the first front compression
chamber A4a from the third front compression chamber A4c, the first
part chamber Ax is the first front compression chamber A4a, and the
second part chamber Ay is the third front compression chamber A4c.
For the vane 131 separating the third front compression chamber A4c
from the second front compression chamber A4b, the first part
chamber Ax is the third front compression chamber A4c, and the
second part chamber Ay is the second front compression chamber A4b.
For the vane 131 separating the second front compression chamber
A4b from the first front compression chamber A4a, the first part
chamber Ax is the second front compression chamber A4b, and the
second part chamber Ay is the first front compression chamber A4a.
The same applies to the rear compression chamber A5.
[0170] The pressure in each of the front compression chambers A4a
to A4c tends to be higher if the chamber is located on the leading
side in the rotation direction M. Specifically, the pressure tends
to be the highest in the second front compression chamber A4b (in
particular, the space on the trailing side of the area of contact
between the front rotating body surface 71 and the second front
flat surface 102), followed by the third front compression chamber
A4c and the first front compression chamber A4a. For this reason,
the pressure of the second part chamber Ay on the leading side of a
vane 131 tends to be higher than the pressure of the first part
chamber Ax on the trailing side of the vane 131.
[0171] As shown in FIGS. 9 to 13, each vane 131 consists of
multiple parts. Specifically, the vane 131 includes a vane body
170, which is inserted in a vane groove 130, and two tip seals 180
and 190, which are arranged on the opposite end faces 171, 172 in
the axial direction Z of the vane body 170. The tip seals 180 and
190 form the axial ends of the vane 131 and are in contact with the
fixed body surfaces 100 and 120, respectively.
[0172] The vane body 170 is made of the same material as the
rotating body 60 and the fixed bodies 90 and 110. In one example,
the vane body 170 is made of metal. The vane body 170 is planar and
inserted in a vane groove 130 with its thickness direction
extending in the width direction of the vane groove 130. The vane
body 170 extends in the axial direction Z and the radial direction
R. The vane body 170 is a rectangular plate in the present
embodiment, but the vane body 170 may be a plate of any shape. The
vane body 170 is received in the vane groove 130 regardless of the
movement of the vane 131 in the axial direction Z.
[0173] The vane body 170 has two end faces 171 and 172 including
body attachment grooves 173 and 174, respectively, which serve as
body attachment sections. The body attachment grooves 173 and 174
have a width in the thickness direction of the vane 131, extend in
the radial direction R, and open to the inner and outer sides in
the radial direction R.
[0174] Each body attachment groove 173, 174 has a body groove
bottom surface 173a, 174a and a first body groove side surface
173b, 174b and a second body groove side surface 173c, 174c, which
extend from the body groove bottom surface 173a, 174a. The first
body groove side surface 173b, 174b and the second body groove side
surface 173c, 174c intersect with the circumferential direction (in
other words, a direction orthogonal to both of the axial direction
Z and the radial direction R). These two surfaces face each other
and spaced apart from each other in the circumferential direction.
The second body groove side surface 173c, 174c is on the leading
side of the first body groove side surface 173b, 174b in the
rotation direction M. That is, the first body groove side surface
173b, 174b is the side surface on the trailing side of the body
attachment groove 173, 174, and the second body groove side surface
173c, 174c is the side surface on the leading side of the body
attachment groove 173, 174.
[0175] The tip seals 180 and 190 are made of a material that
differs from the material of the vane body 170, such as a material
that is easier to deform (i.e., softer) than the vane body 170. For
example, the tip seals 180 and 190 are made from resin. Each tip
seal 180, 190 is in contact with the fixed body surface 100, 120,
so that the two part chambers Ax and Ay on the opposite sides in
the circumferential direction of the vane 131 are not continuous
with each other. In this embodiment, the two tip seals 180 and 190
have the same shape. The areas of contact between the tip seals 180
and 190 and the fixed body surfaces 100 and 120 are referred to as
distal end contact areas Pa1 and Pa2, respectively.
[0176] As shown in FIGS. 9 to 11, the tip seal 180, 190 may be
elongated and extend in the radial direction R. Each tip seal 180,
190 may include a seal body 181, 191, which is in contact with the
fixed body surface 100, 120, and a seal attachment protrusion 182,
192, which serves as a seal attachment section attached to the vane
body 170.
[0177] As shown in FIG. 12, each seal body 181, 191 has a width
that is substantially the same as the thickness of the vane body
170 and is sandwiched by the end face 171, 172 of the vane body 170
and the fixed body surface 100, 120 in the axial direction Z. In
other words, the seal body 181, 191 is located between the end face
171, 172 of the vane body 170 and the fixed body surface 100,
120.
[0178] As shown in FIGS. 11 and 12, each seal body 181, 191
includes a seal surface 181a, 191a, which is a convex surface
curved toward the fixed body surface 100, 120, and a seal body
bottom surface 181b, 191b, which faces the end face 171, 172 of the
vane body 170 in the axial direction Z.
[0179] The seal surface 181a, 191a faces the fixed body surface
100, 120 in the axial direction Z. The seal surface 181a, 191a is
in contact with the fixed body surface 100, 120. The curvature of
the seal surface 181a, 191a is flatter than that of a configuration
in which the seal body 181, 191 is semicircular. Specifically, the
curvature radius of the seal surface 181a, 191a is greater than
half the thickness of the vane 131. However, the present disclosure
is not limited to this, and the seal surface 181a, 191a may have
any curvature.
[0180] The seal surface 181a, 191a extends in the radial direction
R and is in contact with the fixed body surface 100, 120 along its
entire length in the radial direction R. However, the present
disclosure is not limited to this, and the seal body 181, 191 may
be in contact with the fixed body surface 100, 120 only partially
along its length in the radial direction R.
[0181] Each seal attachment protrusion 182, 192 is a ridge that
protrudes from the seal body 181, 191 toward the vane body 170, has
a width in the thickness direction of the vane 131, and extends in
the radial direction R. The seal attachment protrusion 182, 192
includes an attachment distal end face 182a, 192a, a first seal
protrusion side surface 182b, 192b, and a second seal protrusion
side surface 182c, 192c located on the leading side of the first
seal protrusion side surface 182b, 192b. The first seal protrusion
side surface 182b, 192b and the second seal protrusion side surface
182c, 192c intersect with the circumferential direction. The first
seal protrusion side surface 182b, 192b is the side surface on the
trailing side of the seal attachment protrusion 182, 192, and the
second seal protrusion side surface 182c, 192c is the side surface
on the leading side of the seal attachment protrusion 182, 192.
[0182] The seal attachment protrusion 182, 192 is inserted in the
body attachment groove 173, 174 so that the tip seal 180, 190 is
attached to the vane body 170. The body attachment groove 173, 174,
which is a body attachment section, and the seal attachment
protrusion 182, 192 face each other in the circumferential
direction (i.e., the width direction of the vane groove 130).
Specifically, the first body groove side surface 173b, 174b and the
first seal protrusion side surface 182b, 192b face each other in
the circumferential direction, and the second body groove side
surface 173c, 174c and the second seal protrusion side surface
182c, 192c face each other in the circumferential direction. The
tip seals 180 and 190 can move toward and away from the vane body
170 in the axial direction Z. That is, the tip seals 180 and 190
are attached to the vane body 170 so as to be movable in the axial
direction Z relative to the vane body 170.
[0183] The tip seals 180 and 190 are movable in the axial direction
Z relative to the vane body 170, and the vane 131 includes the vane
body 170 and the tip seals 180 and 190. As such, the vane 131 may
be considered as extendable in the axial direction Z.
[0184] As shown in FIGS. 11 and 12, a back pressure space 183, 193,
which is provided between the vane body 170 and the tip seal 180,
190, pushes the tip seal 180, 190 toward the fixed body surface
100, 120.
[0185] The front back pressure space 183 is defined by the front
attachment distal end face 182a, the front body groove bottom
surface 173a, the front first body groove side surface 173b, and
the front second body groove side surface 173c. The width of the
front seal attachment protrusion 182 is the same as or slightly
smaller than the width of the front body attachment groove 173.
Thus, the gap between the front seal attachment protrusion 182 and
the front body attachment groove 173 allows the fluid to enter the
front back pressure space 183. The same applies to the rear back
pressure space 193.
[0186] As shown in FIGS. 11 and 12, the compressor 10 has
introduction grooves 184 and 194 that introduce the fluid into the
back pressure spaces 183 and 193 from the second part chamber
Ay.
[0187] Each tip seal 180, 190 has introduction grooves 184, 194.
The tip seal 180, 190 includes multiple (two in this embodiment)
introduction grooves 184, 194, which are spaced apart from each
other in the radial direction R. However, the number of the
introduction grooves 184, 194 is arbitrary, and may be one or three
or more.
[0188] As shown in FIG. 12, the introduction grooves 184, 194
extend along the seal body 181, 191 and the seal attachment
protrusion 182, 192. Specifically, each introduction groove 184,
194 extends along the second seal protrusion side surface 182c,
192c and a section of the seal body bottom surface 181b, 191b
located on the leading side of the seal attachment protrusion 182,
192.
[0189] Each front introduction groove 184 is provided on the
leading side of the front tip seal 180 and opens to the second part
chamber Ay, which is located on the leading side. Likewise, each
rear introduction groove 194 is provided on the leading side of the
rear tip seal 190 and opens to the second part chamber Ay. This
allows the fluid in the second part chamber Ay to flow easily into
the back pressure spaces 183 and 193 through the introduction
grooves 184 and 194.
[0190] In this configuration, the fluid in each back pressure space
183, 193 pushes the tip seal 180, 190 toward the fixed body surface
100, 120, reducing the likelihood of a gap created between the tip
seal 180, 190 and the fixed body surface 100, 120.
[0191] Specifically, even in a configuration in which the rotating
body 60 is supported by the two fixed bodies 90 and 110 with the
rotating body tube 61, dimensional or assembly errors in the
manufacturing of the rotating body 60 and the fixed bodies 90 and
110 can result in a gap created between a vane 131 and at least one
of the two fixed body surfaces 100 and 120. Such a gap can be
created over the entire angular range in which the vane 131
rotates, or only in a specific angular range.
[0192] In the present embodiment, as shown in FIG. 12, when the
vane bodies 170 rotate together with the rotating body 60, the vane
bodies 170 push the tip seals 180 and 190 in the rotation direction
M. This brings each first seal protrusion side surface 182b, 192b,
which is the side surface on the trailing side of the seal
attachment protrusion 182, 192, into contact with the first body
groove side surface 173b, 174b, which is the side surface on the
trailing side of the body attachment groove 173, 174, in the
circumferential direction. This area of contact (hereinafter
referred to as a "side surface contact area Pb1, Pb2") provides
sealing, thereby reducing the possibility that the fluid moves
through between each tip seal 180, 190 and the vane body 170 and
thus between the two part chambers Ax and Ay.
[0193] In particular, each side surface contact area Pb1, Pb2 of
the present embodiment extends in the axial direction Z. This helps
to maintain the contact between the first seal protrusion side
surface 182b, 192b and the first body groove side surface 173b,
174b even when the tip seal 180, 190 moves in the axial direction Z
relative to the vane body 170.
[0194] Since the body attachment groove 173, 174 forms the body
attachment section, the side surface contact area Pb1, Pb2 may be
considered as an area of contact between the body attachment
section and the seal attachment protrusion 182, 192.
[0195] On the other hand, a clearance is provided on the leading
side in the rotation direction M. Specifically, a clearance is
provided between each second seal protrusion side surface 182c,
192c and the second body groove side surface 173c, 174c. As
indicated by the long dashed double-short dashed lines in FIG. 12,
the clearance introduces the fluid into the back pressure space
183, 193 from the second part chamber Ay. In particular, in the
present embodiment, the introduction grooves 184, 194 facilitate
the flow of fluid from the second part chamber Ay into the back
pressure space 183, 193.
[0196] The fluid flowing into the back pressure space 183, 193
pushes the tip seal 180, 190 toward the fixed body surface 100,
120. This maintains the contact and thus the sealing between the
tip seal 180, 190 (specifically, the seal surface 181a, 191a) and
the fixed body surface 100, 120. A gap is therefore unlikely to be
created between the tip seal 180, 190 and the fixed body surface
100, 120.
[0197] The depth of the body attachment groove 173, 174 may be
greater than the protruding amount of the seal attachment
protrusion 182, 192. This maintains the back pressure space 183,
193 even when the seal body bottom surface 181b, 191b is in contact
with the end face 171, 172, aspaceing the problem that the back
pressure space 183, 193 disappears. However, the depth of the body
attachment groove 173, 174 is not limited to this, and may be less
than or equal to the protruding amount of the seal attachment
protrusion 182, 192.
[0198] As shown in FIGS. 9 and 13, each vane 131 includes a vane
outer end face 201 and a vane inner end face 202, which are the two
end faces in the radial direction R. Of the two end faces in the
radial direction R, the vane outer end face 201 is on the outer
side in the radial direction R (located radially outward), and the
vane inner end face 202 is on the inner side in the radial
direction R (located radially inward).
[0199] The vane outer end face 201 includes the outer end face of
the vane body 170 and the outer end faces of the two tip seals 180
and 190. The outer end face of the vane body 170 and the outer end
faces of the two tip seals 180 and 190 are continuous in the axial
direction Z and flush with one another. The vane outer end face 201
is thus a single plane.
[0200] The vane outer end face 201 is in contact with the front
cylinder inner circumferential surface 33 regardless of the
movement of the vane 131. That is, the front cylinder inner
circumferential surface 33 is longer in the axial direction Z than
the moving range of the vane 131 so as to maintain the contact with
the vane outer end face 201 regardless of the movement of the vane
131.
[0201] As shown in FIG. 13, the vane outer end face 201 may be a
convex surface curved radially outward so as to be continuous with
the ring outer circumferential surface 73 in the circumferential
direction. The curvature of the vane outer end face 201 is
preferably the same as that of the front cylinder inner
circumferential surface 33. That is, the vane outer end face 201 is
preferably in planar contact with the front cylinder inner
circumferential surface 33. However, the vane outer end face 201
may have other shapes.
[0202] In the same manner as the vane outer end face 201, each vane
inner end face 202 includes the inner end face of the vane body 170
and the inner end faces of the two tip seals 180 and 190. The inner
end face of the vane body 170 and the inner end faces of the two
tip seals 180 and 190 are continuous in the axial direction Z and
flush with one another. The vane inner end face 202 is thus a
single plane.
[0203] As shown in FIG. 13, the vane inner end face 202 is a
concave surface curved radially outward. The curvature of the vane
inner end face 202 is preferably the same as that of the tube outer
circumferential surface 62. That is, the vane inner end face 202 is
preferably in planar contact with the tube outer circumferential
surface 62. However, the vane inner end face 202 may have other
shapes.
[0204] Referring to FIGS. 14 and 15, the sequence of operations of
the compressor 10 will now be described. FIGS. 14 and 15 are
developed views schematically showing the rotating body 60, the
fixed bodies 90 and 110, and the vanes 131. FIGS. 14 and 15 show
the rotating body 60 and the vanes 131 at different phases. The
ports 141, 142, 151 and 161 are shown schematically in FIGS. 14 and
15.
[0205] As shown in FIGS. 14 and 15, when the electric motor 13
rotates the rotary shaft 12, the rotating body 60 rotates
accordingly. The vanes 131 thus rotate while moving in the axial
direction Z along the fixed body surfaces 100 and 120 and
maintaining the positional relationship between one another in the
circumferential direction. As viewed in FIGS. 14 and 15, the vanes
131 move downward while moving in the left-right direction. This
changes the volumes of the front compression chambers A4a to A4c
and the rear compression chambers A5a to A5c, allowing for suction,
compression and expansion of the fluid. That is, the rotation and
movement in the axial direction Z of the vanes 131 perform the
suction and compression of fluid in the compression chambers A4 and
A5.
[0206] Specifically, the first front compression chamber A4a and
the space in the second front compression chamber A4b that is
located on the leading side of the second front flat surface 102
increase in volume and perform suction of fluid through the front
suction port 141.
[0207] In contrast, the third front compression chamber A4c and the
space in the second front compression chamber A4b that is located
on the trailing side of the second front flat surface 102 (the
trailing space) decrease in volume as the rotating body 60 rotates
and perform compression of the fluid. Specifically, the fluid is
compressed in the third front compression chamber A4c, and the
fluid compressed in the third front compression chamber A4c is
further compressed in the trailing space of the second front
compression chamber A4b.
[0208] When the pressure in the trailing space of the second front
compression chamber A4b exceeds the threshold, the front valve 152
opens allowing the fluid compressed in the second front compression
chamber A4b to be discharged into the discharge chamber A1 through
the front discharge ports 151. The same applies to the rear
compression chamber A5.
[0209] As described above, the rotation of the rotating body 60 and
the vanes 131 results in one cycle of suction and compression,
which corresponds to 480.degree., repeated in the three part
chambers in each of the compression chambers A4 and A5.
Specifically, in each compression chamber A4, A5, the fluid is
drawn and expanded in the phase between 0.degree. and 240.degree.,
and the fluid is compressed in the phase between 240.degree. and
480.degree..
[0210] For example, it is assumed that the angular position of the
circumferential center of the second front flat surface 102 is
0.degree., and the first vane 131 is located at this
circumferential center. Additionally, it is assumed that the angle
increases in the rotation direction M from this 0.degree. angular
position. In this case, while the first vane 131 moves from the
0.degree. angular position to the 240.degree. angular position, the
fluid is drawn into the part chamber located on the trailing side
of the first vane 131.
[0211] In particular, since the front suction opening 141a extends
at least from the leading edge of the second front flat surface 102
to the 120.degree. angular position, the suction of the fluid
continues until the first vane 131 reaches the 240.degree. angular
position. This limits expansion of the fluid in this part chamber,
thereby improving the efficiency.
[0212] While the second vane 131, which is on the trailing side of
the first vane 131, moves from the 120.degree. angular position to
the 360.degree. angular position, the fluid is compressed in the
part chamber on the leading side of the second vane 131.
[0213] The three front compression chambers A4a to A4c are at
different phases. That is, the space defined by the front rotating
body surface 71, the front fixed body surface 100, the tube outer
circumferential surface 62, and the front cylinder inner
circumferential surface 33 is partitioned by the vanes 131 into
three compression chambers at different phases. In the present
embodiment, while the rotating body 60 rotates 480.degree., the
suction and compression of fluid take place in each of the three
front compression chambers and the three rear compression
chambers.
[0214] In the above description, the three front compression
chambers A4a to A4c separated by the vanes 131 are defined in terms
of the positional relationship with the front suction port 141 and
the front discharge ports 151. However, the front compression
chambers A4a to A4c may be described from another viewpoint. For
example, the following description focuses on one cycle in one
compression chamber.
[0215] As the first vane 131 moves to the leading side of the
second front flat surface 102, a compression chamber continuous
with the front suction port 141 is provided on the trailing side of
the first vane 131. This compression chamber increases in volume as
the vane 131 rotates, while maintained to be continuous with the
front suction port 141. The fluid is thus drawn into this
compression chamber.
[0216] Then, the second vane 131 moves to the leading side of the
second front flat surface 102, so that the compression chamber is
defined by the first and second vanes 131. The fluid is drawn into
this compression chamber until the second vane 131 reaches the
leading end of the front suction opening 141a.
[0217] The second vane 131 continues to move beyond the leading end
of the front suction opening 141a to the leading side, so that the
compression chamber is no longer continuous with the front suction
port 141. As the rotating body 60 rotates further, the compression
chamber becomes continuous with the front discharge ports 151. In
this stage, the volume of the compression chamber decreases as the
rotating body 60 rotates, thereby compressing the fluid in the
compression chamber. Then, when the second vane 131 reaches a
position where it comes into contact with the second front flat
surface 102, the volume of the compression chamber becomes 0, and
one cycle of suction and compression in the compression chamber is
completed.
[0218] The present embodiment has the following advantages.
[0219] (1-1) The compressor 10 includes the rotary shaft 12, the
rotating body 60, which rotates together with the rotary shaft 12,
the fixed bodies 90 and 110, which do not rotate together with the
rotary shaft 12, and the vanes 131, which are inserted in the vane
grooves 130 provided in the rotating body 60 and rotate while
moving in the axial direction Z as the rotating body 60 rotates.
The rotating body 60 has the rotating body surfaces 71 and 72
intersecting with the axial direction Z. The fixed bodies 90 and
110 have the fixed body surfaces 100 and 120, which face the
respective rotating body surfaces 71 and 72 in the axial direction
Z. The compressor 10 includes the compression chambers A4 and A5
defined by the rotating body surfaces 71 and 72 and the fixed body
surfaces 100 and 120. The vanes 131 rotate while moving in the
axial direction Z, causing the suction and compression of fluid in
the compression chambers A4 and A5.
[0220] Each vane 131 includes the vane body 170, which is inserted
in a vane groove 130, and the tip seals (sealing members) 180 and
190, which are attached to the respective end faces 171, 172 of the
vane body 170 in the axial direction Z so as to be movable in the
axial direction Z relative to the vane body 170. The fluid
(pressure) in each back pressure space 183, 193, which is provided
between the vane body 170 and the tip seal 180, 190, pushes the tip
seal 180, 190 toward the fixed body surface 100, 120 so that the
tip seal 180, 190 is in contact with the fixed body surface 100,
120.
[0221] The tip seal 180, 190, which is pressed by the fluid
(pressure) in the back pressure space 183, 193 and thus in contact
with the fixed body surface 100, 120, ensures the sealing between
the vane 131 and the fixed body surface 100, 120. A gap is
therefore unlikely to be created between the vane 131 and each
fixed body surface 100, 120.
[0222] (1-2) The front compression chamber A4 includes the first
part chamber Ax and the second part chamber Ay located on the
opposite sides of each vane 131 in the circumferential direction.
The first part chamber Ax is located on the trailing side of the
vane 131, and the second part chamber Ay is located on the leading
side of the vane 131. Each end face 171, 172 of the vane body 170
has the body attachment groove 173, 174, which is a body attachment
section. Each tip seal 180, 190 includes the seal attachment
protrusion 182, 192, which is attached to the body attachment
groove 173, 174. The seal attachment protrusion 182, 192 and the
body attachment groove 173, 174 (specifically, the first body
groove side surface 173b, 174b) face each other in the
circumferential direction of the rotary shaft 12.
[0223] In this configuration, when the vane 131 (specifically, the
vane body 170) rotates together with the rotating body 60, the seal
attachment protrusion 182, 192 comes into contact with the body
attachment groove 173, 174 in the circumferential direction. This
area of contact, which is the side surface contact area Pb1, Pb2,
ensures the sealing between the vane body 170 and the tip seal 180,
190, thereby limiting movement of fluid between the two part
chambers Ax and Ay through the back pressure space 183, 193.
[0224] (1-3) The present embodiment uses the body attachment
grooves 173 and 174, which are provided in the end faces 171 and
172 of the vane body 170, as body attachment sections. Each body
attachment groove 173, 174 includes the first body groove side
surface 173b, 174b, which is on the trailing side, and the second
body groove side surface 173c, 174c, which is on the leading
side.
[0225] Each tip seal 180, 190 has the seal body 181, 191, which is
in contact with the fixed body surface 100, 120. The seal
attachment protrusion 182, 192 protrudes from the seal body 181,
191 toward the end face 171, 172 of the vane body 170. The seal
attachment protrusion 182, 192 includes the first seal protrusion
side surface 182b, 192b, which is on the trailing side, and the
second seal protrusion side surface 182c, 192c, which is on the
leading side.
[0226] The tip seal 180, 190 is attached to the vane body 170 by
inserting the seal attachment protrusion 182, 192 into the body
attachment groove 173, 174. The first seal protrusion side surface
182b, 192b and the first body groove side surface 173b, 174b face
each other in the circumferential direction.
[0227] In this configuration, the seal attachment protrusion 182,
192 is inserted in the body attachment groove 173, 174 so that the
tip seal 180, 190 is attached to the vane body 170. As such, the
rotation of the vane 131 (specifically, the vane body 170) brings
the first seal protrusion side surface 182b, 192b into contact with
the first body groove side surface 173b, 174b in the
circumferential direction. This area of contact, which is the side
surface contact area Pb1, Pb2, ensures the sealing between the vane
body 170 and the tip seal 180, 190.
[0228] In the present embodiment, each side surface contact area
Pb1, Pb2 extends in the axial direction Z. Thus, the contact
between the first seal protrusion side surface 182b, 192b and the
first body groove side surface 173b, 174b is likely to be
maintained even when the tip seal 180, 190 moves toward the fixed
body surface 100, 120. This limits leakage of fluid through the
back pressure spaces 183 and 193 and removal of the tip seals 180
and 190.
[0229] (1-4) The contact between the first seal protrusion side
surface 182b, 192b and the first body groove side surface 173b,
174b increases the likelihood that a clearance will separate the
second seal protrusion side surface 182c, 192c from the second body
groove side surface 173c, 174c. This clearance facilitates the flow
of fluid into the back pressure space 183, 193 from the second part
chamber Ay. The fluid in the second part chamber Ay tends to have a
higher pressure than the fluid in the first part chamber Ax. For
example, as for the vane 131 separating the third front compression
chamber A4c from the second front compression chamber A4b, the
second front compression chamber A4b has a higher pressure. This
increases the force of the fluid pushing the tip seals 180 and 190
in the back pressure spaces 183 and 193. The sealing between the
vane 131 and the fixed body surfaces 100 and 120 is thus
enhanced.
[0230] (1-5) Each tip seal 180, 190 includes the introduction
grooves 184, 194 for introducing the fluid into the back pressure
space 183, 193 from the second part chamber Ay.
[0231] In this configuration, the introduction grooves 184 and 194
facilitate the introduction of the fluid into the back pressure
spaces 183 and 193 from the second part chamber Ay. As such, the
fluid in the second part chamber Ay, which tends to have a
relatively high pressure, pushes each tip seal 180, 190 toward the
fixed body surface 100, 120. This further enhances the sealing
between the vane 131 and the fixed body surfaces 100 and 120.
[0232] (1-6) The introduction grooves 184, 194 are located closer
to the second part chamber Ay than the side surface contact area
Pb1, Pb2. The side surface contact area Pb1, Pb2 limits leakage of
the fluid in the back pressure space 183, 193, which is introduced
through the introduction grooves 184, 194, into the first part
chamber Ax. This helps to solve the problem that the introduction
grooves 184, 194 can cause leakage of fluid from the second part
chamber Ay into the first part chamber Ax.
[0233] (1-7) Each introduction groove 184, 194 extends along the
second seal protrusion side surface 182c, 192c and a section of the
seal body bottom surface 181b, 191b that is on the leading side of
the seal attachment protrusion 182, 192.
[0234] In this configuration, even if the seal body bottom surface
181b, 191b is in contact with the end face 171, 172 of the vane
body 170, the fluid in the second part chamber Ay can still flow
into the back pressure space 183, 193.
Second Embodiment
[0235] As shown in FIG. 16, in this embodiment, the first body
groove side surfaces 212 and 215 and the second body groove side
surfaces 213 and 216 are tilted with respect to the axial direction
Z such that the body attachment grooves 211 and 214 become
gradually narrower as they deepen. In the present embodiment, each
first body groove side surface 212, 215 is displaced gradually
toward the leading side in the rotation direction M as the body
attachment groove 211, 214 deepens from the end face 171, 172 of
the vane body 170 (in other words, as it extends toward the body
groove bottom surface 173a, 174a).
[0236] In accordance with the body attachment groove 211, 214
becoming gradually narrower as it deepens, the seal attachment
protrusion 221, 224 becomes gradually narrower from the proximal
end to the distal end. Specifically, in accordance with the
inclination of the first body groove side surface 212, 215 and the
second body groove side surface 213, 216, the first seal protrusion
side surface 222, 225 and the second seal protrusion side surface
223, 226 are tilted with respect to the axial direction Z. The
first seal protrusion side surface 222, 225 is displaced gradually
toward the leading side in the rotation direction M from the
proximal end to the distal end.
[0237] The first seal protrusion side surface 222, 225 and the
first body groove side surface 212, 215 face each other in the
circumferential direction. In this embodiment, these side surfaces
are inclined at the same angle. Likewise, the second seal
protrusion side surface 223, 226 and the second body groove side
surface 213, 216 face each other in the circumferential direction.
In this embodiment, these side surfaces are inclined at the same
angle.
[0238] In this configuration, when the vane 131 (specifically, the
vane body 170) rotates together with the rotating body 60, each
first seal protrusion side surface 222, 225 is brought into contact
with the first body groove side surface 212, 215 in the
circumferential direction. Accordingly, the side surface contact
area Pb1, Pb2 is tilted with respect to the axial direction Z.
[0239] In the same manner as the first embodiment, the back
pressure space 183, 193 is created between the tip seal 180, 190
and the vane body 170. The back pressure space 183, 193 pushes the
tip seal 180, 190 toward the fixed body surface 100, 120.
[0240] The present embodiment has the following advantages.
[0241] (2-1) Each first body groove side surface 212, 215 is tilted
with respect to the axial direction Z so as to be displaced
gradually toward the leading side in the rotation direction M as
the body attachment groove 211, 214 deepens. The first seal
protrusion side surface 222, 225 is tilted with respect to the
axial direction Z so as to be displaced gradually toward the
leading side in the rotation direction M from the proximal end to
the distal end. The first body groove side surface 212, 215 and the
first seal protrusion side surface 222, 225 face each other in the
circumferential direction.
[0242] In this configuration, when the vane body 170 rotates
together with the rotating body 60, the first seal protrusion side
surface 222, 225 is brought into contact with the first body groove
side surface 212, 215, and the area of contact, which is the side
surface contact area Pb1, Pb2, receives a pushing force F1, F2
acting in a direction orthogonal to the side surface contact area
Pb1, Pb2.
[0243] The side surface contact area Pb1, Pb2 is tilted with
respect to the axial direction Z so as to be displaced gradually
toward the leading side in the rotation direction M as it extends
away from the fixed body surface 100, 120. As such, the pushing
force F1, F2 includes a component in the axial direction Z,
specifically, a component in the direction toward the fixed body
surface 100, 120. This pushes the tip seal 180, 190 toward the
fixed body surface 100, 120, thereby enhancing the sealing at the
distal end contact area Pa1, Pa2.
[0244] In the present embodiment, the second seal protrusion side
surface 223, 226 and the second body groove side surface 213, 216
are tilted with respect to the axial direction Z, but these
surfaces may be inclined in the same direction and at the same
angle as the first seal protrusion side surface 222, 225 and the
first body groove side surface 212, 215. In this case, the width of
the body attachment groove 211, 214 and the width of the seal
attachment protrusion 221, 224 are uniform. The second seal
protrusion side surface 223, 226 and the second body groove side
surface 213, 216 may be parallel to the axial direction Z. That is,
the second seal protrusion side surface 223, 226 and the second
body groove side surface 213, 216 may have any configurations.
Third Embodiment
[0245] As shown in FIG. 17, in this embodiment, the seal attachment
protrusions 182 and 192 and the body attachment grooves 173 and 174
are closer to the first part chamber Ax than to the second part
chamber Ay. Specifically, the center line passing through the
circumferential center of the seal attachment protrusion 182, 192
and the body attachment groove 173, 174 is at a position displaced
from the center line passing through the circumferential center of
the tip seal 180, 190 toward the first part chamber Ax (in other
words, at a position displaced toward the trailing side). In the
present embodiment, the side surface contact area Pb1, Pb2
corresponds to the "area of contact between two attachment
sections."
[0246] The operation of the present embodiment will now be
described.
[0247] As shown in FIG. 17, each tip seal 180, 190 receives a first
pushing force Ff1, Fr1, which is applied by the fluid in the first
part chamber Ax, and a second pushing force Ff2, Fr2, which is
applied by the fluid in the second part chamber Ay. The first
pushing force Ff1, Fr1 acts in a direction orthogonal to the line
connecting the distal end contact area Pa1, Pa2 to the edge of the
side surface contact area Pb1, Pb2 that is closer to the seal body
bottom surface 181b, 191b. The second pushing force Ff2, Fr2 acts
in a direction orthogonal to the line connecting the distal end
contact area Pa1, Pa2 to the edge of the side surface contact area
Pb1, Pb2 that is closer to the body groove bottom surface 173a,
174a. The second pushing force Ff2, Fr2 is likely to be larger than
the first pushing force Ff1, Fr1.
[0248] Since the second pushing force Ff2, Fr2 differs from the
first pushing force Ff1, Fr1 in magnitude and direction, there is
an imbalance between these forces. Each tip seal 180, 190 receives
the resultant of the first pushing force Ff1, Fr1 and the second
pushing force Ff2, Fr2.
[0249] With this configuration, the inventors of the present
application have found that each tip seal 180, 190 receives a
pushing force acting in a direction away from the fixed body
surface 100, 120 when the distal end contact area Pa1, Pa2, which
is the area of contact between the seal surface 181a, 191a and the
fixed body surface 100, 120, is closer to the first part chamber Ax
than the side surface contact area Pb1, Pb2, in other words, when
the distal end contact area Pa1, Pa2 is on the trailing side of the
side surface contact area Pb1, Pb2 in the rotation direction M.
[0250] For example, as shown in the front part of FIG. 17, when the
front tip seal 180 is in contact with the front curved surface 103
inclined upward with respect to the rotation direction M, the front
distal end contact area Pa1 is likely to be positioned on the
leading side in the rotation direction M of the front side surface
contact area Pb1. Accordingly, the resultant of the front first
pushing force Ff1 and the front second pushing force Ff2 is likely
to act in the direction toward the front fixed body surface 100.
This helps to push the front tip seal 180 toward the front fixed
body surface 100, enhancing the sealing at the front distal end
contact area P1a.
[0251] In contrast, at the rear side, the rear tip seal 190 is in
contact with the rear curved surface 123 inclined downward with
respect to the rotation direction M. Consequently, the rear distal
end contact area Pa2 is likely to be positioned on the trailing
side of the center in the width direction of the rear seal surface
191a. For this reason, the rear distal end contact area Pa2 can be
positioned on the trailing side of the rear side surface contact
area Pb2. In this case, the resultant of the first rear pushing
force Fr1 and the second rear pushing force Fr2 is likely to act in
a direction away from the rear fixed body surface 120.
[0252] In this respect, as shown in FIG. 17, the rear seal
attachment protrusion 192 and the rear body attachment groove 174
of the present embodiment are arranged to be closer to the first
part chamber Ax, so that the rear side surface contact area Pb2 is
positioned near the first part chamber Ax. Accordingly, the rear
distal end contact area Pa2 is less likely to be positioned on the
trailing side of the rear side surface contact area Pb2, reducing
the likelihood that the component in the axial direction Z in the
resultant of the first rear pushing force Fr1 and the second rear
pushing force Fr2 will act in a direction away from the rear fixed
body surface 120. Further, even if the rear distal end contact area
Pa2 is positioned on the trailing side of rear side surface contact
area Pb2, the distance between these areas in the circumferential
direction and therefore the component of the force acting in a
direction away from the rear fixed body surface 120 would be small.
This limits separation of the rear tip seal 190 from the rear fixed
body surface 120.
[0253] The present embodiment has the following advantages.
[0254] (3-1) Each fixed body surface 100, 120 is a ring-shaped
surface and includes the second flat surface 102, 122, which is a
fixed body contact surface in contact with the rotating body
surface 71, 72, and the two curved surfaces 103, 123 located on the
opposite sides in the circumferential direction of the second flat
surface 102, 122. The two curved surfaces 103, 123 are curved in
the axial direction Z such that the distance to the rotating body
surface 71, 72 gradually increases as the curved surfaces 103, 123
extend away from the second flat surface 102, 122 in the
circumferential direction. The seal attachment protrusion 182, 192
and the body attachment groove 173, 174 are closer to the first
part chamber Ax than to the second part chamber Ay. In other words,
the seal attachment protrusion 182, 192 and the body attachment
groove 173, 174 are displaced from the circumferential center of
the tip seal 180, 190 toward the trailing side.
[0255] As such, the side surface contact area Pb1, Pb2 is displaced
toward the trailing side, reducing the likelihood that the distal
end contact area Pa1, Pa2 will be located on the trailing side of
the side surface contact area Pb1, Pb2. Further, even if the distal
end contact area Pa1, Pa2 is positioned on the trailing side of the
side surface contact area Pb1, Pb2, the distance between these
contact areas would be small. This prevents or reduces the force
acting on the tip seal 180, 190 in a direction away from the fixed
body surface 100, 120. Accordingly, when the tip seal 180, 190
moves along the curved surface 103, 123 inclined downward with
respect to the rotation direction M, the sealing at the distal end
contact area Pa1, Pa2 is less likely to decrease.
Fourth Embodiment
[0256] The fourth embodiment will now be described. The fourth
embodiment differs from the first embodiment in the attachment
configuration between the vane body and the tip seal.
[0257] As shown in FIG. 18, in this embodiment, each seal body 181,
191 has a seal attachment groove 231, 234, which is recessed toward
the fixed body surface 100, 120 from the seal body bottom surface
181b, 191b. The seal attachment groove 231, 234, which serves as a
seal attachment section, may have a width in the thickness
direction of the vane 131 and extend in the radial direction R.
Each seal attachment groove 231, 234 has a first seal groove side
surface 232, 235, which is on the trailing side in the rotation
direction M, and a second seal groove side surface 233, 236, which
is on the leading side in the rotation direction M. The second seal
groove side surface 233, 236 is tilted with respect to the axial
direction Z so as to be displaced gradually toward the trailing
side as the seal attachment groove 231, 234 deepens.
[0258] Each vane body 170 has body attachment protrusions 241 and
244 protruding from the respective end faces 171 and 172 of the
vane body 170 toward the fixed body surfaces 100 and 120. Each body
attachment protrusion 241, 244, which serves as a body attachment
section, may be a ridge that has a width in the thickness direction
of the vane 131 and extends in the radial direction R. The body
attachment protrusion 241, 244 has a first body protrusion side
surface 242, 245, which is on the trailing side in the rotation
direction M, and a second body protrusion side surface 243, 246,
which is on the leading side in the rotation direction M.
[0259] The second body protrusion side surface 243, 246 is tilted
with respect to the axial direction Z so as to be displaced
gradually toward the trailing side from the proximal end to the
distal end of the body attachment protrusion 241, 244.
[0260] The body attachment protrusion 241, 244 is a part of the
vane body 170. The body attachment protrusion 241, 244 is made of a
material harder than the tip seal 180, 190, such as metal.
[0261] In this configuration, each body attachment protrusion 241,
244 is inserted in the seal attachment groove 231, 234 so that the
tip seal 180, 190 is attached to the vane body 170. The first seal
groove side surface 232, 235 and the first body protrusion side
surface 242, 245 face each other in the circumferential direction,
and the second seal groove side surface 233, 236 and the second
body protrusion side surface 243, 246 face each other in the
circumferential direction. Consequently, when the vane body 170
rotates together with the rotating body 60, the second body
protrusion side surface 243, 246, which is the side surface on the
leading side of the body attachment protrusion 241, 244, is brought
into contact with the second seal groove side surface 233, 236,
which is the side surface on the leading side of the seal
attachment groove 231, 234, in the circumferential direction. This
area of contact (specifically, the side surface contact area Pb1,
Pb2) provides sealing and blocks the fluid.
[0262] In the same manner as the first embodiment, the back
pressure space 183, 193 is created between each tip seal 180, 190
and the vane body 170. The back pressure space 183, 193 pushes the
tip seal 180, 190 to the fixed body surface 100, 120.
[0263] The present embodiment has the following advantages.
[0264] (4-1) The tip seals 180 and 190 are made of a softer
material than the vane body 170. Each tip seal 180, 190 has the
seal body 181, 191, which is in contact with the fixed body surface
100, 120. The seal body 181, 191 has the seal body bottom surface
181b, 191b, which faces the end face 171, 172 of the vane body 170.
Further, the tip seal 180, 190 has the seal attachment groove 231,
234, which is recessed from the seal body bottom surface 181b,
191b. The vane body 170 has the body attachment protrusion 241, 244
protruding from each end face 171, 172 of the vane body 170. The
body attachment protrusion 241, 244 is inserted in the seal
attachment groove 231, 234 so that the tip seal 180, 190 is
attached to the vane body 170.
[0265] In this configuration, the body attachment protrusion 241,
244 is inserted in the seal attachment groove 231, 234 so that the
tip seal 180, 190 is attached to the vane body 170. This
configuration reduces removal of the tip seals 180 and 190, as
compared to the first embodiment in which the seal attachment
protrusions 182 and 192 are inserted in the respective body
attachment grooves 173 and 174.
[0266] Specifically, in a configuration in which each seal
attachment protrusion 182, 192 is inserted in the body attachment
groove 173, 174 as in the first embodiment, the seal attachment
protrusion 182, 192 may fail to have a high rigidity and thus
deform, resulting in removal of the tip seal 180, 190 from the vane
body 170.
[0267] The tip seal 180, 190, which serves as a sealing member, is
made of a soft material that easily deforms to increase the sealing
performance. For this reason, the tip seal 180, 190 is likely to
have a low rigidity, which may result in the removal.
[0268] In contrast, the present embodiment inserts each body
attachment protrusion 241, 244 of the vane body 170 into the seal
attachment groove 231, 234. The body attachment protrusion 241, 244
is a part of the vane body 170, which is harder than the tip seals
180 and 190, and thus resists deformation as compared to the tip
seals 180 and 190 (the seal attachment protrusions 182 and 192).
Further, as compared to the configuration including the seal
attachment protrusions 182 and 192, the configuration including the
seal attachment grooves 231 and 234 allows the tip seals 180 and
190 to have a higher rigidity. This reduces the problem that the
tip seals 180 and 190 are deformed and removed from the vane body
170.
[0269] (4-2) Each seal attachment groove 231, 234 has the first
seal groove side surface 232, 235 on the trailing side and the
second seal groove side surface 233, 236 on the leading side. Each
body attachment protrusion 241, 244 has the first body protrusion
side surface 242, 245 on the trailing side and the second body
protrusion side surface 243, 246 on the leading side. The second
body protrusion side surface 243, 246 and the second seal groove
side surface 233, 236 face each other in the circumferential
direction.
[0270] The second seal groove side surface 233, 236 is tilted with
respect to the axial direction Z so as to be displaced gradually
toward the trailing side as the seal attachment groove 231, 234
deepens. The second body protrusion side surface 243, 246 is tilted
with respect to the axial direction Z so as to be displaced
gradually toward the trailing side from the proximal end to the
distal end of the body attachment protrusion 241, 244.
[0271] In this configuration, when the vane body 170 rotates
together with the rotating body 60, each second body protrusion
side surface 243, 246 is brought into contact with the second seal
groove side surface 233, 236. Through this area of contact, which
is the side surface contact area PM, Pb2, the tip seal 180, 190
receives the pushing force F1, F2 including a component acting in
the direction toward the fixed body surface 100, 120. The pushing
force F1, F2 pushes the tip seal 180, 190 against the fixed body
surface 100, 120, thereby enhancing the sealing at the distal end
contact area Pa1, Pa2.
[0272] The embodiments described above may be modified as follows.
The embodiments and the following modifications may be combined to
the extent that does not cause technical contradiction.
[0273] As shown in FIG. 19, in the configuration in which each body
attachment groove 173, 174 is provided at the circumferential
center (the center in the width direction) of the vane body 170,
the width D1, D2 of the body attachment groove 173, 174 may be
greater than half the vane width D0, which is the width of the vane
131. In this case, the width of the seal attachment protrusion 182,
192 may be increased according to the body attachment groove 173,
174.
[0274] In this configuration, the increased width D1, D2 of the
body attachment groove 173, 174 allows the side surface contact
area Pb1, Pb2 to be closer to the first part chamber Ax
accordingly. This configuration thus has Advantage (3-1) described
above.
[0275] The introduction grooves 184 and 194 may be provided in the
vane body 170 instead of the tip seals 180 and 190, or may be
provided in both of the tip seals 180 and 190 and the vane body
170. That is, any configuration may be used as long as an
introduction groove 184, 194 is provided in at least one of the tip
seal 180, 190 and the vane body 170.
[0276] The introduction grooves 184 and 194 may be omitted.
[0277] The shape and the position of the tip seals 180 and 190 may
be changed freely as long as they are attached to the vane body 170
so as to be movable in the axial direction Z.
[0278] One of the tip seals 180 and 190 may be omitted. That is,
the tip seal may be provided only on one of the front side and the
rear side. In this case, the end of the vane body 170 that does not
include a tip seal preferably has a seal surface that is in contact
with a fixed body surface. That is, the vane 131 may be composed of
two parts of a vane body and one tip seal.
[0279] As long as the seal attachment protrusion 182, 192 and the
body attachment groove 173, 174 face each other, they may be in
contact with each other in the circumferential direction or spaced
apart from each other when the rotating body 60 is not rotating.
The same applies to the body attachment protrusions 241 and 244 and
the seal attachment grooves 231 and 234.
[0280] The rotating body surfaces 71 and 72 may be tilted with
respect to the axial direction Z. In this case, the front flat
surfaces 101 and 102 and the rear flat surfaces 121 and 122 may be
orthogonal to the axial direction Z, or inclined at the same angle
as the rotating body surfaces 71 and 72 so as to be in planar
contact with the rotating body surfaces 71 and 72.
[0281] The rotating body tube 61 may include a cutout section or a
protrusion. In the embodiments d