U.S. patent application number 14/127683 was filed with the patent office on 2014-04-24 for vane compressor.
This patent application is currently assigned to CALSONIC KANSEI CORPORATION. The applicant listed for this patent is Kouji Hirono, Toshikatsu Miyaji, Tatsuya Osaki, Hirotada Shimaguchi, Masahiro Tsuda. Invention is credited to Kouji Hirono, Toshikatsu Miyaji, Tatsuya Osaki, Hirotada Shimaguchi, Masahiro Tsuda.
Application Number | 20140112817 14/127683 |
Document ID | / |
Family ID | 47423877 |
Filed Date | 2014-04-24 |
United States Patent
Application |
20140112817 |
Kind Code |
A1 |
Osaki; Tatsuya ; et
al. |
April 24, 2014 |
VANE COMPRESSOR
Abstract
A rotor of a vane compressor includes vanes that reciprocates in
vane slots, coil springs that urge the vanes, and guide members
each having a press-in end pressed into the vane and an
accommodated end and inserted into the coil spring. When an outer
diameter of the guide member is a, an inner diameter of the coil
spring is b1, an outer diameter thereof is b2, and an inner
diameter an accommodation hole for the coil spring is c,
(b1-a)<(c-b2) is satisfied. A diameter of an end (a first
contact portion) of the coil spring on a side of the accommodated
end is larger than a diameter of another end (a second contact
portion) thereof on a side of the press-in end. According to the
compressor, contacts between the accommodation hole and the guide
member can be prevented without high accuracy forming of the
accommodation hole.
Inventors: |
Osaki; Tatsuya;
(Saitama-shi, JP) ; Tsuda; Masahiro; (Saitama-shi,
JP) ; Shimaguchi; Hirotada; (Saitama-shi, JP)
; Miyaji; Toshikatsu; (Saitama-shi, JP) ; Hirono;
Kouji; (Saitama-shi, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Osaki; Tatsuya
Tsuda; Masahiro
Shimaguchi; Hirotada
Miyaji; Toshikatsu
Hirono; Kouji |
Saitama-shi
Saitama-shi
Saitama-shi
Saitama-shi
Saitama-shi |
|
JP
JP
JP
JP
JP |
|
|
Assignee: |
CALSONIC KANSEI CORPORATION
|
Family ID: |
47423877 |
Appl. No.: |
14/127683 |
Filed: |
May 31, 2012 |
PCT Filed: |
May 31, 2012 |
PCT NO: |
PCT/JP2012/064155 |
371 Date: |
December 19, 2013 |
Current U.S.
Class: |
418/266 |
Current CPC
Class: |
F16F 1/047 20130101;
F04C 29/045 20130101; F01C 21/0881 20130101; F01C 21/0845 20130101;
F04C 18/344 20130101; F04C 2240/20 20130101; F16F 1/123 20130101;
F16F 1/08 20130101 |
Class at
Publication: |
418/266 |
International
Class: |
F04C 18/344 20060101
F04C018/344 |
Foreign Application Data
Date |
Code |
Application Number |
Jun 28, 2011 |
JP |
2011-142876 |
Feb 17, 2012 |
JP |
2012-032549 |
Claims
1. A vane compressor comprising: a cylinder block in which a
cylinder chamber having an oval inner wall on an inner surface
thereof is formed; and a rotor rotatably provided in the cylinder
chamber, wherein the rotor includes a rotor main body that rotates
in the cylinder chamber, a plurality of vanes whose base ends are
supported by a plurality of vane slots formed in the rotor main
body and that are provided so as to be able to protrude from the
rotor main body, coil springs disposed between bottoms of the vane
slots and the vanes to urge the vanes toward the oval inner wall,
and guide members each of which has a press-in end that is pressed
into a bottom of one of the vane and the vane slot and an
accommodated end that is to be accommodated in an escape hole
provided on a bottom of another of the vane and the vane slot, and
is inserted into the coil spring to prevent the coil spring from
bending, when an outer diameter of the guide member is denoted by
a, an inner diameter of the coil spring is denoted by b1, an outer
diameter of the coil spring is denoted by b2, and an inner diameter
or an inner width of an accommodation portion for the coil spring
is denoted by c, an inequality (b1-a)<(c-b2) is satisfied, and a
first seating diameter of a first contact portion at an end of the
coil spring on a side of the accommodated end is larger than a
second seating diameter of a second contact portion at another end
of the coil spring on a side of the press-in end.
2. The vane compressor according to claim 1, wherein an outer
diameter of the first contact portion is larger than an outer
diameter of the second contact portion.
3. The vane compressor according to claim 2, wherein the coil
spring has a radially-enlarged portion whose outer diameter is
gradually enlarged along a direction from the second contact
portion to the first contact portion.
4. The vane compressor according to claim 3, wherein the number of
active coils in the radially-enlarged portion is set so that shear
stress of the radially-enlarged portion of the coil spring is made
equivalent-to or smaller-than shear stress of a coiled portion that
is a portion of the coil spring other than the radially-enlarged
portion.
5. The vane compressor according to claim 4, wherein pitch of the
radially-enlarged portion is smaller than pitch of the coiled
portion.
6. The vane compressor according to claim 3, wherein coils in the
radially-enlarged portion are contacted with each other.
7. The vane compressor according to claim 1, wherein the first
contact portion has a washer, and an outer diameter of the washer
is the seating diameter.
Description
TECHNICAL FIELD
[0001] The present invention relates to a vane compressor in which
compression chambers are formed in a cylinder chamber by vanes
provided on a rotor that rotates in the cylinder chamber and that
compresses refrigerant in the compression chambers.
BACKGROUND ART
[0002] In a vane compressor, a cylinder chamber having an oval
inner wall is formed in a cylinder block, and a rotatable rotor is
disposed in the cylinder chamber. Plural vane slots are formed on
an outer circumferential surface of the rotor, and vanes are
inserted reciprocatably in the vane slots, respectively. The vanes
are protruded from the vane slots so as to be slidably contacted
with the oval inner wall of the cylinder chamber, and thereby
segment the cylinder chamber into plural compression chambers.
Refrigerant is compressed by utilizing volume changes of the
compression chambers along with rotations of the rotor. Since it is
required to make the vanes protruded from the vane slots,
backpressure is applied to the vanes. In addition, when protruding
the vanes from the vane slots, it is required to prevent noises due
to impacts of the vanes onto the oval inner wall (hereinafter,
referred as chattering).
[0003] In a gas compressor disclosed in a Patent Document 1 listed
below, chattering of vanes is prevented by connecting a
high-pressure supply passage in addition to a normal backpressure
supply passage in order to apply oil pressure other than, normal
backpressure. However, chattering of vanes may occur in a state
where the oil pressure is not raised sufficiently, such as at a
start-up time of the compressor.
[0004] In a vane pump disclosed in a Patent Document 2 listed
below, a coil spring(s) is disposed between a bottom surface of a
vane(s) and a bottom of a vane slot(s), and thereby chattering is
prevented by pushing the vane by the coil spring in addition to the
above-mentioned backpressure. In the vane pump disclosed in the
Patent Document 2, chattering can be prevented more stably than in
the gas compressor disclosed in the Patent Document 1.
[0005] Note that, in the vane pump disclosed in the Patent Document
2, a guide pin (guide member) that is shorter than an expanding
length of the coil spring is inserted into the coil spring in order
to prevent bending of the coil spring when compressed. One end of
the guide pin is fixed to the bottom of the vane slot, and another
end is inserted into the vane. In this configuration, an
accommodation hole(s) for accommodating the guide pin and the coil
spring is formed on the vane. Alternatively, one end of the guide
pin is fixed to the vane, and another end is inserted into the vane
slot. In this configuration, an accommodation hole(s) for
accommodating the guide pin and the coil spring is formed on the
rotor.
PRIOR ART DOCUMENT
Patent Documents
[0006] Patent Document 1: Japanese Patent Unexamined Application
Publication No. 2007-100602
[0007] Patent Document 2: Japanese Examined Utility Model
Application Publication No. H8-538
SUMMARY OF INVENTION
[0008] Chattering can be prevented more surely by the vane pump
disclosed in the Patent Document 2 than the gas compressor
disclosed in the Patent Document 1, but inclination of the vane in
the vane slot and contacts of an end of the guide pin with an inner
surface of the accommodation hole may occur and thereby the inner
surface of the accommodation hole may be damaged. It is required to
form the accommodation hole with high accuracy in order to prevent
the guide pin from bring contacted with the accommodation hole, but
the bottom surface of the vane or the bottom of the vane slot on
which the accommodation hole is formed is small and thereby
accuracy improvement is difficult. In addition, production costs
may increase in order to obtain accuracy improvement.
[0009] An object of the present invention is to provide a vane
compressor that can prevent a guide member from being contacted
with an inner surface of an accommodation hole without forming the
accommodation hole for the guide member with nigh accuracy, and can
form the accommodation hole at low costs.
[0010] An aspect of the present invention provides a vane
compressor comprising: a cylinder block in which a cylinder chamber
having an oval inner wall on an inner surface thereof is formed;
and a rotor rotatably provided in the cylinder chamber, wherein the
rotor includes a rotor main body that rotates in the cylinder
chamber, a plurality of vanes whose base ends are supported by a
plurality of vane slots formed in the rotor main body and that are
provided so as to be able to protrude from the rotor main body,
coil springs disposed between bottoms of the vane slots and the
vanes to urge the vanes toward the oval inner wall, and guide
members each of which has a press-in end that is pressed into a
bottom of one of the vane and the vane slot and an accommodated end
that is to be accommodated in an escape hole provided on a bottom
of another of the vane and the vane slot, and is inserted into the
coil spring to prevent the coil spring from bending, when an outer
diameter of the guide member is denoted by a, an inner diameter of
the coil spring is denoted by b1, an outer diameter of the coil
spring is denoted by b2, and an inner diameter or an inner width of
an accommodation portion for the coil spring is denoted by c, an
inequality (b1-a)<(c-b2) is satisfied, and a first seating
diameter of a first contact portion at an end of the coil spring on
a side of the accommodated end is larger than a second seating
diameter of a second contact portion at another end of the coil
spring on a side of the press-in end.
[0011] Inclination of the guide member is less predominant on the
side of the press-in end where the guide member is pressed-in than
on the side of the accommodation end opposite thereto. Since the
guide member is disposed in the coil spring and the
radially-enlarged portion is provided by making the seating
diameter of the end of the coil spring on the side of the
accommodation end of the guide member larger than the seating
diameter of the other end of the coil spring on the side of the
press-in end of the guide member in the invention according to
claim 1, the coil spring can be prevented from intruding into the
escape hole when the escape hole is enlarged in order to prevent
the guiding member from being contacted with the escape hole. In
addition, the coil spring is restricted from bending because an
inner side of the coil spring may be contacted with the guide
member when the coil spring bends and bustles. This can prevent the
escape hole (accommodation hole) from being damaged. Therefore,
high-accuracy forming of the escape hole (accommodation hole) and
accuracy improvement are not needed and thereby the escape hole
(accomodation hole) can be formed at low costs.
[0012] Here, it is preferable that an outer diameter of the first
contact portion is larger than an outer diameter of the second
contact portion.
[0013] According to this, it becomes possible no make the seating
diameter of the first contact portion larger than the seating
diameter of the second contact portion with a simple
configuration.
[0014] Further, it is preferable that the coil spring has a
radially-enlarged portion whose outer diameter is gradually
enlarged along a direction from the second contact portion to the
first contact portion.
[0015] According to this, it becomes possible to make the seating
diameter of the first contact portion larger than the seating
diameter of the second contact portion with a simple configuration
while preventing stress concentration.
[0016] Furthermore, it is preferable that the number of active
coils in the radially-enlarged portion is set so that shear stress
of the radially-enlarged portion of the coil spring is made
equivalent-to or smaller-than shear stress of a coiled portion that
is a portion of the coil spring other than the radially-enlarged
portion.
[0017] According to this, a load is applied to one of the
radially-enlarged portion and the coiled portion more than another
of them, so that the one can be prevented from being damaged.
[0018] In addition, it is preferable that pitch of the
radially-enlarged portion is smaller than pitch of the coiled
portion.
[0019] According to this, a load is applied to one of the
radially-enlarged portion and the coiled portion more than another
of them, so that the one can be prevented from being damaged.
[0020] In addition, it is preferable than coils in the
radially-enlarged portion are contacted with each other.
[0021] According to this, a load is applied to one of the
radially-enlarged, portion and the coiled portion more than another
of them, so that the one can be prevented from being damaged.
[0022] In addition, it is preferable that the first contact portion
has a washer, and an outer diameter of the washer is the seating
diameter.
[0023] According to this, it becomes possible to make the seating
diameter of the first contact portion larger than the seating
diameter of the second contact portion with a simple
configuration.
BRIEF DESCRIPTION OF DRAWINGS
[0024] FIG. 1 It is a cross-sectional view of a first embodiment of
an electrical compressor including a vane compressor.
[0025] FIG. 2 It is a partial cross-sectional view of an inside of
a cylinder chamber in the first embodiment.
[0026] FIG. 3 It is an enlarged cross-sectional view snowing a coil
spring and an accommodation hole.
[0027] FIG. 4(a) is a side view of the coil spring when expands,
and (b) is a side view of the coil spring when compressed.
[0028] FIG. 5(a) is a cross-sectional view showing on environment
of coil springs (compressed) in a second embodiment of a vane
compressor, and (a) is a cross-sectional view showing the
environment of the coil springs (expanding).
[0029] FIG. 6(a) is a cross-sectional view taken along a line
VIA-VIA shown in FIG. 5(a), and (b) is a cross-sectional view taken
along a line VIB-VIB shown in FIG. 5(b).
[0030] FIG. 7(a) is a side view of a coil spring when expands in a
third embodiment of a vane compressor, and (b) is a side view of
the coil spring when compressed.
[0031] FIG. 8(a) is a side view of a coil spring when expands in a
fourth embodiment of a vane compressor, and (b) is a side view of
the coil spring when compressed.
[0032] FIG. 9(a) is a side view of a coil spring when expands in a
fifth embodiment of a vane compressor, and (b) is a side view of
the coil spring when compressed.
[0033] FIG. 10(a) is a side view of a coil spring when expands in a
sixth embodiment of a vane compressor, and (b) is a side view of
the coil spring when compressed.
DESCRIPTION OF EMBODIMENTS
First Embodiment
[0034] A first embodiment will be explained with reference to FIG.
1 to FIG. 4(b).
[0035] As shown in FIG. 1, an electrical compressor 1 includes a
vane compressor 3 and an electrical motor 5 for driving the vane
compressor 3. The electrical compressor 1 is used for a cooling
system of an air-conditioner for a vehicle. In this cooling system,
high-temperature and high-pressure refrigerant that is
adiabatically compressed by the electrical compressor 1 is
liquidized by a condenser. The liquidized refrigerant is expanded
by an expansion valve, and generates cool air by heat exchange at
an evaporator. The refrigerant is heated at the evaporator to be
evaporated. The evaporated refrigerant is returned to the
compressor 1 again to be adiabatically compressed. Refrigerant
discharge volume of the compressor 1 (3) is adjusted according to
changes of a thermal load to the cooling system and so on.
Lubrication oil is contained in the refrigerant for lubrication in
any part of the compressor 1 (3).
[0036] The electrical compressor 1 includes a front housing 31, a
middle housing 33 and a rear housing 35. These housings 31, 33 and
35 are coupled with each other by bolts. In addition, the vane
compressor 3, the electrical motor 5 and a drive circuit 29 are
provided inside the housings 31, 33 and 35. The vane compressor 3
is housed in the middle housing 33, the electrical motor 5 is
housed in the rear housing 35, and the drive circuit 29 is housed
in the front housing 31. The drive circuit 29 controls revolving
speed of the electrical motor 5.
[0037] The electrical motor 5 includes a stator 49, a rotor 51
formed of magnetic material, and a motor shaft 53. The stator 49
has nine stator teeth, and a coil is wound around each of the
teeth. The stator teeth and the coils are aligned along a
circumferential direction of the rear housing 35. The motor shaft
53 is pressed-into and fixed -with t he rotor 51. An end (a left
end in FIG. 1) of the motor shaft 53 is spline-coupled with a rotor
shaft 41 of the vane compressor 3, and supported by the middle
housing 33 via a bail bearing 55 together with the rotor shaft 41.
On the other hand, another end (a right end in FIG. 1) of the motor
shaft 53 is supported by the rear housing 35 via a ball bearing
57.
[0038] Rotations of the electrical motor 5 are transmitted from the
motor shaft 53 to the rotor shaft 41 to drive the vane compressor
3. The vane compressor 3 compresses refrigerant, and the compressed
refrigerant is introduced into an inside of the electrical motor 5
via discharge ports 47 to cool the stator 49 and then discharged
from a discharge port 59 of the rear housing 35 after oil is
separated by an oil separator.
[0039] In FIG. 2, an arrow M indicates a vane 15 in a state where
its protrusion amount from a vane slot 13 is maximum, and an arrow
N indicates a state where an entire of a vane 15 is accommodated in
a vane slot 13.
[0040] As shown in FIG. 1 and FIG. 2, the vane compressor 3
includes a rotor 11, plural vanes 15, a cylinder block 7, a front
block 37, a rear block 39, and the rotor shaft 41. The cylinder
block 7, the front block 37 and the rear block 39 are fixed with
the middle housing 33 by bolts. One end (a left end in FIG. 1) of
the rotor shaft 41 is rotatably supported by the front block 37. A
middle of the rotor shaft 41 is rotatably supported by the rear
block 39. The rotor 11 has a rotor main body 23 that is
spline-coupled with the rotor shaft 41. The rotor main body 23
rotates in the cylinder chamber 17 along with rotations of the
rotor shaft 41. An inner surface of the cylinder chamber 17 inside
the cylinder block 7 is formed as an oval inner wall 9, and the
center of the rotor 11 and the center of the oval inner wall 9 are
coincided with each other.
[0041] Plural vane slots 13 are formed on an outer circumferential
surface of the rotor main body 23 at even intervals along a
circumferential direction. A vane 15 is reciprocatably inserted in
each of the vane slots 13. The vane(s) 15 protrudes from the vane
slot(s) 13, and an end of the vane 15 is contacted with the oval
inner wall 9 to segment the cylinder chamber 17 into plural
compression chambers. Refrigerant is compressed by volume changes
of the compression chambers along with rotations of the rotor
11.
[0042] In addition to the vane 15, a pair of guide pins (guide
members) 19 and a pair of coil springs 21 are accommodated in each
of the vane slots 13. The vane slot(s) 13 in the present embodiment
is a storage hole 61 for accommodating the guide pins 19 and the
coil springs 21.
[0043] The coil springs 21 urges the vane 15 toward, the oval inner
wall 9. One end of the coil spring(s) 21 is contacted with a base
end surface of the vane 15. The base end surface of the vane 15
that is contacted with the one end of the coil spring(s) 21 is a
first seat surface 71. The one end of the coil spring(s) 21 that is
contacted with the first seat surface 71 is a first contact portion
73.
[0044] The guide pin(s) 19 is inserted into the coil spring 21, and
prevents the coil spring 21 from bending. Therefore, serpentine
flection of the coil spring 21 caused by its bending can be
prevented. The guide pin 19 is longer than the expanding guide pin
19 (maximum length when installed), so that it can guide expansions
and compressions of the coil spring 21 consistently.
[0045] The accommodation hole 61 (vane slot 13) is formed of a
storage portion 63 that is located on an outer circumferential side
of the rotor main body 23 and accommodates the vane 15 so as to
enable it to protrude, a press-in portion 65 that is located at a
bottom side thereof and communicates with the accomodation portion
63, and an escape hole 67 formed in the vane 15 so as to
communicate with the accommodation portion 63. While the vane 15
reciprocates, the guide pin 19 is inserted-into and drawn-from the
escape hole 67. The guide pin 19 never avoids reciprocation of the
vane 15 by the insertion/drawing of the guide pin 19 into/from the
escape hole 67 during the reciprocations of the vane 15.
[0046] A base end of the guide pen 19 is pressed into the press-in
portion 65. The base end of she guide pin 19 that is pressed into
the press-in portion 65 is a press-in end 69. The guide pin 19 is
fixed to she bottom of the vane slot 13 by pressing the press-in
end 69 into the press-in portion 65. An inner diameter of she
press-in portion 65 is smaller than an inner width of the
accommodation portion 63, and a step between an inner surface of
the accommodation portion 63 and an inner surface of the press-in
portion 65 is a second seat surface 77 that receives another end of
the coil spring 21. The other end of the coil spring 21 that is
contacted with the second seat surface 77 is a second contact
portion 79. On the other hand, an opposite end of the guide pin 19
to the press-in end 69 is a stored end 70 that is inserted-into and
drawn-from the escape hole 67.
[0047] A high-pressure refrigerant supply passage 81 is formed in
the accommodation hole 61 (vane slot 13). High-pressure refrigerant
supplied through the high-pressure refrigerant supply passage 81 is
applied to the vane 15 as backpressure.
[0048] As shown in FIG. 3, when an outer diameter of the guide pin
19 is denoted by a, an inner diameter of the coil spring 21 is
denoted by b1, an outer diameter of the coil spring 21 is denoted
by b2, and an inner diameter of the accommodation portion 63 in the
accommodation hole 61 (vane slot 13) is denoted by c, an inequality
(b1-a) <(c-b2) is satisfied. From the satisfaction of this
relation, serpentine flection of the coil spring 21 can be
prevented even when the coil spring 21 bends and thereby an inner
side of the coil spring 21 is contacted with an outer side of the
guide pin 19. However, the coil spring 21 is not contacted with the
inner surface of the accommodation portion 63 (accommodation hole
61), so that the coil spring 21 can expand smoothly and can be
compressed smoothly.
[0049] As shown in FIG. 4(a) and FIG. 4(b), the first contact
portion 73 contacted with the first seat surface 71 of the vane 15
is formed at the one end of the coil spring 21, and the second
contact portion 79 contacted with the second seat surface 77 of the
accommodation hole 61 is formed at the other end. In the present
embodiment, formed is a radially-enlarged portion 80 whose outer
diameter is gradually enlarged along a direction from the second
contact portion 79 to the first contact portion 73. The
above-explained first contact portion 73 is formed at a free end of
the radially-enlarged portion 80. Therefore, an outer diameter of
the first contact portion 73 is larger than an outer diameter of
the second contact portion 79. Namely, in the coil spring 21,
formed is the radially-enlarged portion 80 whose outer diameter is
gradually enlarged along a direction from the press-in end 69 to
the accommodated end 70 of the guide pin 19.
[0050] In this configuration, a seating diameter r1 of the first
contact portion 73 on a side of the accommodated end 70 of the
guide pin 19 is larger than a seating diameter r2 of the second
contact portion 79 on a side of the press-in end 69 of the guide
pin 19 (r1>r2). In addition, since the seating diameter r1 of
the first contact portion 73 is larger than the seating diameter r2
of the second contact portion 79, intrusion of the coil spring 21
into the escape hole 67 can be prevented even if the escape hole 67
is enlarged in order to prevent the guide pin 19 from being
contacted with the escape hole 67.
[0051] The rotor shaft 41 of the vane compressor 3 rotates when the
motor shaft 53 of the electrical motor 5 is rotated, so that the
rotor main body 23 rotates in the cylinder chamber 17. The vane(s)
15 is urged toward the oval inner wall 9 of the cylinder chamber 17
by the coil springs 21, and thereby reciprocated while contacting
its end with the oval inner wall 9. Refrigerant is compressed by
volume change of the compression chamber between the neighboring
vanes 15. When the refrigerant is compressed, the high-pressure
refrigerant is supplied into the accommodation hole 61 (vane slot
13) via the high-pressure refrigerant supply passage 81. After the
supply of the high-pressure refrigerant, the vane(s) 15 is urged
toward the oval inner wail 9 also by backpressure caused by the
high-pressure refrigerant in addition to spring forces of the coil
springs 21. Therefore, chattering can be prevented even at a
compression start time when the backpressure caused by the
high-pressure refrigerant is not applied, because the spring forces
of the coil springs 21 are applied to the vane 15.
[0052] In the present embodiment, the seating diameter r1 of the
first contact portion 73 of the coil spring 21 is made larger than
the seating diameter r2 of the second contact portion 79, so that a
large gap is formed between the first contact portion 73 and the
guide pin 19.
[0053] In addition, since the seating diameter r1 is larger than
the seating diameter r2 of the second contact portion 79, intrusion
of the coil spring 21 into the escape hole 67 can be prevented even
if the escape hole 67 is enlarged in order to prevent the guide pin
19 from being contacted with the escape hole 67. Therefore, it is
not required, for the prevention of the guide pin 19 from being
contacted with the escape hole 67, to form the accommodation hole
61 with high accuracy, so that the escape hole 67 (accommodation
hole 61) can be formed at low costs.
[0054] In addition, since formed is the radially-enlarged portion
80 whose outer diameter is gradually enlarged along a direction
from the second contact portion 79 to the first contact portion 73
in the present embodiment, the seating diameter r1 of the first
contact portion 73 can be made larger than the seating diameter r2
of the second contact portion 79 with a simple configuration.
Second Embodiment
[0055] A second embodiment will be explained with reference to FIG.
5(a) to FIG. 6(b).
[0056] Also in the present embodiment, the vane(s) 15 reciprocates
in the vane slot(s) 13 formed on the rotor main body 23, and its
end is slidably contacted with the oval inner wall 9 of the
cylinder chamber 17. In addition, coil springs 21 for urging the
vane 15 toward the oval inner wall 9 of the cylinder chamber 17 are
disposed between the bottom surface of the vane 15 and the bottom
of the vane slot 13. Further, the guide pins (guide members) 19 for
preventing the coil springs 21 from bending are inserted into the
coil springs 21. The guide pin(s) 19 is longer than the expanding
guide pin 19 (maximum length when installed), so that it can guide
expansions and compressions of she coil spring 21 consistently.
[0057] In the present embodiment, the guide pin(s) 19 is fixed to
the vane 15 by pressing the press-in end 69 of the guide pin 19
into the vane 15. The press-in portion(s) 65 into which the
press-in end 69 is pressed is formed in the vane 15. The
accommodation portion 63 for accommodating the guide pins 19 and
the coil springs 21 is formed continuously with the press-in
portion 65. The accommodation portion 63 includes a vane-side
accommodation portion 83 formed on the vane 15, and a rotor-side
accommodation portion 85 formed on the rotor main body 23. The
accommodation hole 61 is formed of the press-in portion 65, she
vane-side accommodation portion 83, the rotor-side accommodation
portion 85 and an after-explained escape hole 67. An opposite end
of the guide pin 19 to the press-in end 69 is the accommodated end
70 that is accommodated in the rotor-side accommodation portion
85.
[0058] An inner diameter of the press-in portion 65 is smaller than
an inner width of the vane-side accommodation portion 83, and a
step between an inner surface of the press-in portion 65 and an
inner surface of the vane-side accommodation portion 83 is a second
seat surface 77 that receives the other end of the coil spring 21.
The other end of the coil spring 21 that is contacted with the
second seat surface 77 is the second contact portion 79.
[0059] The escape hole(s) 67 is formed on the bottom of the vane
slot 13 so as to communicate with the rotor-side accommodation
portion 85. While the vane 15 reciprocates, the guide pin 19 is
inserted-into and drawn-from the escape hole 67. An inner diameter
of the escape hole 67 is smaller than an inner diameter of the
rotor-side accommodation portion 85, and a step between an inner
surface of the escape hole 67 and an inner surface of the
rotor-side accommodation portion 85 is a first seat surface 71. The
one end of the coil spring 21 that is contacted with the first seat
surface 71 is the first contact portion 73.
[0060] As shown in FIG. 6(a) and FIG. 6(b), the high-pressure
refrigerant supply passage 81 is formed in the accommodation hole
61. High-pressure refrigerant supplied through the high-pressure
refrigerant supply passage 81 is applied to the vane 15 as
backpressure.
[0061] Also in the present embodiment, the inequality
(b1-a)<(c-b2) is satisfied similarly to the above-explained
first embodiment. From the satisfaction of this relation,
serpentine flection of the coil spring 21 can be prevented even
when the coil spring 21 bends and thereby an inner side of the coil
spring 21 is contacted with an outer side of the guide pin 19.
However, the coil spring 21 is not contacted with the inner surface
of the accommodation portion 63 (accommodation hole 61), so that
the coil spring 21 can expand smoothly and can be compressed
smoothly.
[0062] Also in the present embodiment, similarly to the
above-explained first embodiment (FIG. 4(a) and FIG. 4(b)), the
first contact portion 73 is formed at the one end of the coil
spring 21, and the second contact portion 79 is formed at the other
end. In addition, also formed is the radially-enlarged portion 80
whose outer diameter is gradually enlarged along a direction from
the second contact portion 79 to the first contact portion 73.
Therefore, since the seating diameter r1 of the first contact
portion 73 is larger than the seating diameter r2 of the second
contact portion 79 (r1>r2), intrusion of the coil spring 21 into
the escape hole 67 can be prevented even if the escape hole 67 is
enlarged in order to prevent the guide pin 19 from being contacted
with the escape hole 67.
[0063] Also in the present embodiment, the rotor shaft 41 of the
vane compressor 3 rotates -when the motor shaft 53 of the
electrical motor 5 is rotated, so that the rotor main body 23
rotates in the cylinder chamber 17. The vane(s) 15 is urged toward
the oval inner wail 9 of the cylinder chamber 17 by the coil
springs 21, and thereby reciprocated while contacting its end with
the oval inner wall 9. Refrigerant is compressed by volume change
of the compression chamber between the neighboring vanes 15. When
the refrigerant is compressed, the high-pressure refrigerant is
supplied into the accommodation hole 61 (vane slot 13) via the
high-pressure refrigerant supply passage 81. After the supply of
the high-pressure refrigerant, the vane(s) 15 is urged toward, the
oval inner wall 9 also by backpressure caused by the high-pressure
refrigerant in addition to the spring forces of the coil springs
21. Therefore, chattering can be prevented even at a compression
start time when the backpressure caused by the high-pressure
refrigerant is not applied, because the spring forces of the coil
springs 21 are applied to the vane 15.
[0064] Also in the present embodiment, the seating diameter r1 of
the first contact portion 73 of the coil spring 21 is made larger
than the seating diameter r2 of the second contact portion 79, so
that a large gap is formed between the first contact portion 73 and
the guide pin 19.
[0065] In addition, since the seating diameter r1 is larger than
the seating diameter r2 of the second contact portion 79, intrusion
of the coil spring 21 into the escape hole 67 can be prevented even
if the escape hole 67 is enlarged in order to prevent the guide pin
19 from being contacted with the escape hole 67. In addition, it is
not required, for the prevention of the guide pin 19 from being
contacted with the escape hole 67, to form the accommodation hole
61 with high accuracy. In addition, since it is not needed to
improve accuracy of the escape hole 67 (accommodation hole 61), the
escape hole 67 (accommodation hole 61) can be formed at low
costs.
[0066] In addition, since formed is the radially-enlarged portion
80 whose outer diameter is gradually enlarged along a direction
from the second contact portion 79 to the first contact portion 73
in the present embodiment, the seating diameter r1 of the first
contact portion 73 can be made larger than the seating diameter r2
of the second contact portion 79 with a simple configuration.
Third Embodiment
[0067] A third embodiment will be explained with reference to FIG.
7(a) and FIG. 7(b). The present embodiment is different from the
above-explained first or second embodiment only in respect to the
coil spring(s) 21. Therefore, explanations for other configurations
(configurations identical to those in the first embodiment or the
second embodiment) will be omitted, and only the coil spring 21
will be explained.
[0068] As shown in FIG. 7(a) and FIG. 7(b), with respect to the
coil spring(s) 21 in the present embodiment, the radially-enlarged
portion 80 on a side of the first contact portion 73 has a constant
outer diameter r1, and a coiled portion 25 on a side of the second
contact portion r2 has a constant outer diameter r2 smaller than
the above outer diameter r1. Therefore, the seating diameter r1 of
the first contact portion 73 on a side of the accommodated end 70
of the guide pin 19 is larger than the seating diameter r2 of the
second contact portion 79 on a side of the press-in end 69 of the
guide pin 19 (r1>r2). Note that the radially-enlarged portion 80
in the present embodiment is nor gradually radially-enlarged as in
the first embodiment, but has the constant outer diameter as
explained above.
[0069] Since the seating diameter r1 of the first contact portion
73 is larger than the seating diameter r2 of the second contact
portion 79, intrusion of the coil spring 21 into the escape hole 67
can be prevented even if the escape hole 67 is enlarged in order to
prevent the guide pin 19 from being contacted with the escape hole
67. According also to the coil spring 21 in the present embodiment,
the seating diameter r1 of the first contact portion 73 can be made
larger than the seating diameter r2 of the second contact portion
79 with a simple configuration.
Fourth Embodiment
[0070] A fourth embodiment will be explained with reference to FIG.
8(a) and FIG. 8(b). The present embodiment is different from the
above-explained first or second embodiment only in respect to the
coil spring(s) 21. Therefore, explanations for other configurations
(configurations identical to those in the first embodiment or the
second embodiment) will be omitted, and only the coil spring 21
will be explained.
[0071] As shown in FIG. 8(a) and FIG. 8(b), the coil spring(s) 21
in the present embodiment has, as itself, a constant outer diameter
r2 along its entire length. However, the contact portion 73 has a
washer 87 that can function as the radially-enlarged portion 80. An
outer diameter r1 of the washer 97 is larger than the outer
diameter r2 of the coil spring 21 itself, and the washer 87 is
contacted with the first seat surface 71 of the vane 15 (FIG. 2:
the configuration in the first embodiment) or the first seat
surface 71 of the rotor main body 23 (FIG. 5(a) to FIG. 6(b): the
configuration in the second embodiment). Note that the washer 87
may be fixed to the first contact portion 73, or may be held
between the first contact portion 73 and the first seat surface 71
by a spring force of the coil spring 21 after installation without
being fixed to the first contact portion 73.
[0072] According also to the above-explained configuration in which
the first contact portion 73 has the washer 87 and thereby the
first contact portion 73 has the seating diameter r1, intrusion of
the coil spring 21 into the escape hole 67 can be prevented even if
the escape hole 67 is enlarged in order to prevent the guide pin 19
from being contacted with the escape hole 67. Therefore, according
also to the coil spring 21 in the present embodiment, the seating
diameter r1 of the first contact portion 73 can be made larger than
the seating diameter r2 of the second contact portion 79 with a
simple configuration. According to the present embodiment, other
equivalent advantages by the above-explained first to third
embodiments can be obtained.
Fifth Embodiment
[0073] A fifth embodiment will be explained with reference to FIG.
9(a) and FIG. 9(b). The present embodiment is different from the
above-explained first or second embodiment only in respect to the
coil spring(s) 21. Therefore, explanations for other configurations
(configurations identical to those in the first embodiment or the
second embodiment) will be omitted, and only the coil spring 21
will be explained.
[0074] As shown in FIG. 9(a) and FIG. 9(b), similarly to the first
embodiment, with respect to the coil spring(s) 21 in the present
embodiment, formed is the radially-enlarged port ion 80 whose outer
diameter is gradually enlarged along a direction from the second
contact portion 79 to the first contact portion 73. The first
contact portion 73 is formed at a free end of the radially-enlarged
portion 80. Namely, in the coil spring 21, formed is the
radially-enlarged portion 80 whose outer diameter is gradually
enlarged along a direction from the press-in end 69 to the
accommodated end 70 of the guide pin 19. Therefore, the seating
diameter r1 of the first contact portion 73 on a side of the
accommodated end 70 of the guide pin 19 is larger than the seating
diameter r2 of the second contact portion 79 on a side of the
press-in end 69 of the guide pin 19 (r1>r2).
[0075] Further, with respect to the coil spring(s) 21 in the
present embodiment, the number of active coils in the
radially-enlarged portion 80 is set so that shear stress of the
radially-enlarged portion 80 is made equivalent to shear stress of
the coiled portion 25 other than the radially-enlarged portion 80.
In addition, pitch of the radially-enlarged portion 80 is smaller
than pitch of the coiled portion 25, so that the coil spring(s) 21
in the present embodiment is a variable pitch spring.
[0076] Therefore, when the coil spring 21 is compressed, the coiled
portion 25 is compressed without using its pitch all up as shown in
FIG. 9(b), but the radially-enlarged portion 80 gets into a coil
bind state by using its pitch all up. Although higher shear stress
may be generated in the radially-enlarged portion 80 than in the
coiled portion 25 in a case where pitch of the radially-enlarged
portion 80 is made identical to pitch of the coiled portion 25,
shear stress of the radially-enlarged portion 80 can be decreased
due to the above configuration. As a result, the radially-enlarged
portion 80 can be prevented from being damaged and lifetime of the
coiled portion 25 can be prolonged.
[0077] According also to this configuration, intrusion of the coil
spring 21 into the escape hole 67 can be prevented even if the
escape hole 67 is enlarged in order to prevent the guide pin 19
from being contacted with the escape hole 67. Therefore, it is not
needed, for the prevention of the guide pin 19 from being contacted
with the escape hole 67, to form the accommodation hole 61 with
high accuracy, so that the escape hole 67 (accommodation hole 61)
can be formed at low costs.
[0078] In addition, since formed is the radially-enlarged portion
80 whose outer diameter is gradually enlarged along a direction
from the second contact portion 79 to the first contact portion 73
in the present embodiment, the seating diameter r1 of the first
contact portion 73 can be made larger than the seating diameter r2
of the second contact portion 79 with a simple configuration.
According to the present embodiment, other equivalent advantages by
the above-explained first to third embodiments can be also
obtained.
Sixth Embodiment
[0079] A sixth embodiment will be explained with reference to FIG.
10(a) and FIG. 10(b). The present embodiment is different from the
above-explained first or second embodiment only in respect to the
coil spring(s) 21. Therefore, explanations for other configurations
(configurations identical to those in the first embodiment or the
second embodiment) will be omitted, and only the coil spring 21
will be explained.
[0080] As shown in FIG. 10(a) and FIG. 10(b), similarly to the
first embodiment, the coil spring(s) 21 in the present embodiment
has an almost identical shape to a shape of the coil spring 21 in
the above-explained fifth embodiment, it is a variable pitch spring
having the radially-enlarged portion 80 whose outer diameter is
gradually enlarged. However, with respect to the coil spring 21 in
the present embodiment, coils in the radially-enlarged portion 80
are contacted with each other when the coil spring 21 is installed
(or, in its free-length state). Namely, pitch of the
radially-enlarged portion 80 is smaller than pitch of the coiled
portion 25, i.e. set to minimum pitch (=0).
[0081] Although higher shear stress may be generated in the
radially-enlarged portion 80 than in the coiled portion 25 in a
case where pitch of the radially-enlarged portion 80 is made
identical to pitch of the coiled portion 25, shear stress of the
radially-enlarged portion 80 can be decreased by contacting the
coils in the radially-enlarged portion 80 with each other.
Therefore, the radially-enlarged portion 80 can be prevented from
being damaged and lifetime of the coiled portion 25 can be
prolonged. For example, in a case where the coils in the
radially-enlarged portion 80 are contacted with each other in its
free-length state, shear stress of the radially-enlarged portion 80
becomes zero.
[0082] According also to this configuration, intrusion of the coil
spring 21 into the escape hole 67 can be prevented even if the
escape hole 67 is enlarged in order to prevent the guide pin 19
from being contacted with the escape hole 67. Therefore, it is not
needed, for the prevention of the guide pin 19 from being contacted
with the escape hole 67, to form the accommodation hole 61 with
high accuracy, so that the escape hole 67 (accommodation hole 61)
can be formed at low costs.
[0083] In addition, since formed is the radially-enlarged portion
80 whose outer diameter is gradually enlarged along a direction
from the second contact portion 79 to the first contact portion 73
in the present embodiment, the seating diameter r1 of the first
contact portion 73 can be made larger than the seating diameter r2
of the second contact portion 79 with a simple configuration.
According to the present embodiment, other equivalent advantages by
the above-explained first to third embodiments can be also
obtained.
[0084] Note that the present invention can arbitrarily combine the
above-explained embodiments. For example, with respect to the coil
spring, it is possible that the radially-enlarged portion whose
outer diameter is gradually enlarged along a direction from the
second contact portion to the first contact portion and the first
contact portion that is a free end of the radially-enlarged portion
has the washer having a larger diameter than that of the
radially-enlarged portion. Further, coils in the above
radially-enlarged portion may be contacted with each other.
According also to this configuration, equivalent advantages by the
above-explained embodiments can be obtained.
[0085] In addition, the first contact portion 73 of the coil
spring(s) 21 in the above embodiments other than the fourth
embodiments may have the washer 87 shown in FIG. 8(a) and FIG.
8(b).
[0086] In addition, the present invention is not limited to the
above embodiments and can be variably modified. For example, the
vane compressor according to the present invention may be used in a
Limited-Slip Differential in a power train for a vehicle that uses
high-viscous oil as working fluid, other than the above cooling
system. In addition, a drive source for the vane compressor
according to the present invention may be an internal combustion
whose output power is transmitted by a pulley(s) and a belt(s).
* * * * *