U.S. patent application number 12/091662 was filed with the patent office on 2009-10-01 for variable capacity compressor.
This patent application is currently assigned to Calsonic Kansei Corporation. Invention is credited to Ryuichi Hirose, Naoki Ishikawa, Satoshi Kubo, Toshikatsu Miyaji.
Application Number | 20090246050 12/091662 |
Document ID | / |
Family ID | 37967635 |
Filed Date | 2009-10-01 |
United States Patent
Application |
20090246050 |
Kind Code |
A1 |
Miyaji; Toshikatsu ; et
al. |
October 1, 2009 |
VARIABLE CAPACITY COMPRESSOR
Abstract
A variable capacity compressor includes a rotating member 21
fixed to a drive shaft 10 so as to rotate with the drive shaft 10,
a sleeve 22 axially slidably attached to the drive shaft 10, a
tilting member 24 tiltably attached to the sleeve 22 by a pivot pin
61, a linkage mechanism 40 connecting the rotating member 21 with
the tilting member 24 and configured to transfer a rotary torque of
the rotating member 21 to the tilting member 24 as allowing the
tilting member to be tiltable, and a tilting guide face 22c formed
on the sleeve 22 and a tilting guide face 25d formed on the tilting
member 24 which are formed as planes orthogonal to the pivot pin 61
and are configured to slidingly contact one another.
Inventors: |
Miyaji; Toshikatsu;
(Tochigi, JP) ; Hirose; Ryuichi; (Tochigi, JP)
; Ishikawa; Naoki; (Gunma, JP) ; Kubo;
Satoshi; (Tochigi, JP) |
Correspondence
Address: |
FOLEY AND LARDNER LLP;SUITE 500
3000 K STREET NW
WASHINGTON
DC
20007
US
|
Assignee: |
Calsonic Kansei Corporation
Nakano-ku, Tokyo
JP
|
Family ID: |
37967635 |
Appl. No.: |
12/091662 |
Filed: |
October 20, 2006 |
PCT Filed: |
October 20, 2006 |
PCT NO: |
PCT/JP2006/320963 |
371 Date: |
August 5, 2008 |
Current U.S.
Class: |
417/437 |
Current CPC
Class: |
F04B 27/1072
20130101 |
Class at
Publication: |
417/437 |
International
Class: |
F04B 35/01 20060101
F04B035/01 |
Foreign Application Data
Date |
Code |
Application Number |
Oct 27, 2005 |
JP |
2005-313123 |
Claims
1. A variable capacity compressor comprising: a rotating member
fixed to a drive shaft and configured to rotate integrally with the
drive shaft; a sleeve axially slidably attached to the drive shaft;
a tilting member tiltably attached to the sleeve by a pivot pin; a
linkage mechanism connecting the rotating member with the tilting
member and configured to transfer a rotary torque of the rotating
member to the tilting member as allowing the tilting member to
tilt; a piston configured to reciprocate in response to rotation of
the tilting member; tilting guide faces respectively formed on the
sleeve and the tilting member, the tilting guide faces formed as
planes orthogonal to the pivot pin and configured to slidingly
contact one another.
2. The variable capacity compressor according to claim 1, wherein
the linkage mechanism comprising: an arm extending from a rotating
member toward the tilting member; an arm extending from the tilting
member toward the rotating member; and a linking pin pivotally
connecting the arm of the rotating member and the arm of the
tilting member directly or indirectly.
3. The variable capacity compressor according to claim 1, wherein
the linkage mechanism comprising: a pair of opposite arms extending
from the rotating member toward the tilting member; a pair of
opposite arms extending from the tilting member toward the rotating
member; a linkage member having a first end that is slidably fit
between the arms of the rotating member and a second end that is
slidably fit between the arms of the tilting member, a first
linking pin pivotally connecting the first end of the linkage
member and the arms of the rotating member; and a second linking
pin pivotally connecting the second end of the linkage member and
the arms of the tilting member.
4. The variable capacity compressor according to claim 3, wherein a
pair of tilting guides of the sleeve and a pair of the tilting
guides of the tilting member are provided on both sides of the
driving shaft, and a width between the pair of tilting guides of
the sleeve is larger than a width of the first end of the linkage
member and a width of the second end of the linkage member.
Description
TECHNICAL FIELD
[0001] The present invention relates to a variable capacity
compressor.
BACKGROUND ART
[0002] A conventional variable capacity compressor includes a drive
shaft, a rotor which is fixed to the drive shaft and rotates
integrally with the drive shaft, a sleeve which is axially slidably
attached to the drive shaft, a swash plate which is tiltably
attached to the sleeve, a link mechanism provided between the rotor
and the swash plate to rotate the swash plate together with the
rotor, and a piston which reciprocate in response to the rotation
of the swash plate (see, for example, Japanese Patent Application
Laid-Open Publications No. 2003-172417 and No. 10-176658). The
linkage mechanism connects the rotor with the swash plate so as to
permit change of an inclination angle of the swash plate while
transferring rotary torque from the rotor to the swash plate. The
changes of the inclination angle of the swash plate cause piston
stroke to change.
[0003] FIG. 9 is a view of a linkage mechanism disclosed in the
Publication No. 10-176658.
[0004] The linkage mechanism in FIG. 9 includes a pair of rotor
arms 145, 146 which extend from a rotor 140 toward a swash plate
141 and are opposed to each other, a single swash plate arm 147
which extends from the swash plate 141 toward the rotor 140, and a
pair of link arms 142A, 142B. These five arms 145, 142A, 147, 143B,
and 146 are stacked in the torque transfer direction so that
rotation of the rotor 140 is transferred to the swash plate. The
link arms 142A, 142B have a first end which is rotatably linked to
the rotor arms 145, 146 by a first linking pin 143 and a second end
which is rotatably linked to the swash plate arm 147 by a second
linking pin 144. With this, the link arms 142A, 142B rotate about
the linking pin 143 with respect to the rotor arms 145, 146, and
the swash arm 147 rotates about the linking pin 144 with respect to
the link arms 142A, 142B. Therefore, the inclination angle of the
swash plate 141 with respect to a drive shaft (not shown) is
changeable.
DISCLOSURE OF THE INVENTION
[0005] When the compressor is operative, that is, when the drive
shaft rotates, a contact between the rotor arm 145 and the link arm
142A and a contact between the link arm 142A and the swash plate
arm 147 function as a torque transferring interface and also as a
rotational slide-contact interfaces. In other words, the rotor arm
145 and the link arm 142A rotationally slides with respect to one
another under a large pressure of the torque Ft. The link arm 142A
and the swash plate arm 147 also rotationally slide with respect to
one another under a large pressure of the torque Ft. Accordingly,
when changing the inclination angle of the swash plate 141, the
slide friction at the contact between the rotor arm 145 and the
link arm 142A becomes extremely high and the slide friction at the
contact between the link arm 142A and the swash plate arm 147 also
becomes extremely high.
[0006] And also, when the compressor is operative, that is, when
the drive shaft rotates, the swash plate 141 receives a large
compression reaction force Fp from the pistons that are connected
to the swash plate 141. As shown in FIG. 9, the compression
reaction force Fp can be applied to a position anterior to the
linkage mechanism in the rotating direction, depending on the
rotation speed (see FIG. 2). With this, torsion load is given to
the swash plate arm 147 in a direction Y in the figure.
Accordingly, the link 142 gets stuck in the swash plate 141 at two
points (C, C) and this causes a further increased slide
friction.
[0007] To solve the above problem, the Publication No. 2003-172417
has a washer between the rotor arm and the link arm and a washer
between the link arm and the swash plate arm, but similar problems
are remained.
[0008] The present invention is provided to solve the problem. An
object of the present invention is to provide a variable capacity
compressor capable of decreasing torsion load applied to a linkage
mechanism.
[0009] An aspect of the present invention provides a variable
capacity compressor. The variable capacity compressor includes: a
rotating member fixed to a drive shaft and configured to rotate
integrally with the drive shaft; a sleeve axially slidably attached
to the drive shaft; a tilting member tiltably attached to the
sleeve by a pivot pin; a linkage mechanism connecting the rotating
member with the tilting member and configured to transfer a rotary
torque of the rotating member to the tilting member as allowing the
tilting member to tilt; a piston configured to reciprocate in
response to rotation of the tilting member; and tilting guide faces
respectively formed on the sleeve and the tilting member. The
tilting guide faces are formed as planes orthogonal to the pivot
pin and configured to slide one another.
BRIEF DESCRIPTION OF THE DRAWINGS
[0010] FIG. 1 is a cross-sectional view of a variable capacity
compressor of a first embodiment according to the present
invention;
[0011] FIG. 2 is a perspective view of an assembly in that a swash
plate and a rotor are mounded to a driving shaft;
[0012] FIG. 3 is an exploded perspective view of the assembly;
[0013] FIG. 4 is a cross-sectional view of the assembly;
[0014] FIG. 5(a) is a cross-sectional view of the assembly along
line Va-Va in FIG. 4, and FIG. 5(b) is a cross-sectional view of
the assembly along line Vb-Vb in FIG. 4;
[0015] FIG. 6 is a perspective view of an assembly in that a hub of
the swash plate is mounded to a sleeve;
[0016] FIGS. 7(a) to 7(c) are views of the assembly in that the hub
of the swash plate is mounded to the sleeve, wherein FIG. 7(a) is a
front view of the assembly, FIG. 7(b) is a side view of the
assembly, and FIG. 7(c) is a cross-sectional view of the assembly
along line VIIc-VIIc in FIG. 7(b);
[0017] FIGS. 8(a) and 8(b) are cross-sectional views of the
assembly along line VIII-VIII in FIG. 7(c), wherein FIG. 8(a)
showing the state in that the hub is parallel to the sleeve, and
FIG. 8(b) showing a condition in that the hub inclines with respect
to the sleeve; and
[0018] FIG. 9 is a cross-sectional view of an example of a
conventional linkage mechanism of a variable capacity
compressor.
DETAILED DESCRIPTION OF THE INVENTION
[0019] A variable capacity compressor of an embodiment of the
present invention will be described with reference to the
accompanying drawings.
[0020] FIG. 1 is a cross-sectional view of the variable capacity
compressor.
[0021] As shown in FIG. 1, the variable capacity compressor 1 of
the present embodiment is a swash plate type variable capacity
compressor. The variable capacity compressor 1 includes a cylinder
block 2 having a plurality of cylinder bores 3 (see FIG. 2) placed
evenly spaced apart in a circumferential direction, a front housing
4 attached to a front end of the cylinder block 2 and defining a
crank chamber 5 with the cylinder block 2, and a rear housing 6
attached to a rear end of the cylinder block 2 via a valve plate 9
and defining a suction chamber 7 and a discharge chamber 8 therein.
The cylinder block 2, the front housing 4, and the rear housing 6
are fixedly connected to one another by a plurality of bolts 13 so
as to make up a housing of the compressor.
[0022] The valve plate 9 is formed with suction ports 11 that
communicate the cylinder bores 3 with the suction chamber 7, and a
discharge ports 12 that communicate the cylinder bores 3 with the
discharge chamber 8.
[0023] A suction valve system (not shown) adapted to open or close
the suction ports 11 is attached to the valve plate 9 on the
cylinder block side. A discharge valve system (not shown) adapted
to open or close the discharge ports 12 is attached to the valve
plate 9 on the rear housing side. A gasket is interposed between
the valve plate 9 and the rear housing 6 to maintain airtightness
of the suction chamber 7 and the discharge chamber 8.
[0024] A drive shaft 10 is rotatably supported by radial bearings
15, 19 in center through holes 14, 18 which are bearing holes
formed at center portions of the cylinder block 2 and the front
housing 4. With this structure, the drive shaft 10 is rotatable in
the crank chamber 5. A thrust bearing 20 is interposed between a
front face of a later-described rotor 21 that is fixed to the shaft
10 and an interior face of the front housing 6. A thrust bearing 16
is interposed between a rear end face of the shaft 10 and an
adjustable screw 17 which is a stationary member fixed in the
center through hole 14 of the cylinder block 2.
[0025] The crank chamber 5 accommodates the rotor 21, that is a
"rotating member", fixed to the drive shaft 10, a sleeve 22 axially
slidably attached to the drive shaft 10, and a swash plate 24, that
is a "tilting member", pivotably attached to the sleeve 22 by pivot
pins 61. In other words, the swash plate 24 is attached to the
drive shaft 10 via the sleeve 22 and pivot pins 61, so that the
swash plate 24 is tiltable with respect to the drive shaft 10 and
is slidable in the axial direction of the drive shaft 10. In this
embodiment, the swash plate 24 includes a hub 25 tiltably attached
to the sleeve 22 and a swash plate body 26 fixed to a boss 25a of
the hub 25.
[0026] Pistons 29 is slidably contained in the cylinder bore 3, and
engaged with the swash plate 24 via a pair of hemispherical-shaped
shoes 30, 30.
[0027] Between the rotor 21 as the rotating member and the hub 25
of the swash plate 24 as the tilting member, a linkage mechanism 40
is interposed. The linkage mechanism 40 transfers rotary torque
from the rotor 21 to the swash plate 24 as allowing the inclination
angle of the swash plate 24 to change.
[0028] When the sleeve 22 moves toward the cylinder block 2, the
inclination angle of the swash plate 24 reduces. On the other hand,
when the sleeve 22 moves away from the cylinder block 2, the
inclination angle of the swash plate 24 increases. Reference number
53 in FIG. 1 represents a stopper such as a c-ring for a return
spring 52. The stopper 53 is fixed in a circular groove formed on
the drive shaft 10 to support the return spring 52 as compressing
between the sleeve 22 and the stopper 53.
[0029] When the drive shaft 10 rotates, the rotor 21 rotates
integrally with the drive shaft 10. The rotation of the rotor 21 is
transferred to the swash plate 24 via the linkage mechanism 40. The
rotation of the swash plate 24 is converted into a reciprocating
movement of the pistons 29 so that the pistons 29 reciprocate in
the cylinder bores 3. By the reciprocating movements of the pistons
29, refrigerant is sucked from the suction chamber 7 into the
cylinder bores 3 through the suction ports 11 of the valve plate 9,
compressed in the cylinder bores 3, and discharged to the discharge
chamber 8 through the discharge ports 12 of the valve plate 9.
[0030] The variable capacity compressor includes a pressure control
mechanism. The pressure control mechanism controls a pressure
difference (pressure balance) between the crank chamber pressure Pc
in back of the piston 29 and the suction chamber pressure Ps in
front of the piston 29 so as to change the inclination angle of the
swash plate 24 to change the piston stroke. When changing the
piston stroke, the discharge capacity of the compressor
changes.
[0031] The pressure control mechanism includes an extraction
passage (not shown) that connects and communicates the crank
chamber 5 with the suction chamber 7, a supply passage (not shown)
that connects and communicates the crank chamber 5 with the
discharge chamber 8, and a control valve 33 that is provided in the
midstream of the supply passage to open and close the supply
passage.
[0032] The extraction passage opens regardless of the opening and
closing of the control valve 33, so that the refrigerant gas
constantly flows through the extraction passage from the crank
chamber 5 to the suction chamber 7.
[0033] When the control valve 33 opens the gas supply passage, the
refrigerant flows from the discharge chamber 8 into the crank
chamber 5 through the gas supply passage, and this increases the
crank chamber pressure Pc. When the crank chamber pressure Pc
increases, the inclination angle of the swash plate 24 decreases as
the sleeve 22 moves toward the cylinder block 2. As a result, the
piston stroke becomes smaller and the discharging amount
decreases.
[0034] On the other hand, when the control valve 33 closes the gas
supply passage, the refrigerant is gradually extracted from the
crank chamber 5 to the suction chamber 7 through the gas extraction
passage, and this causes a reduction in the pressure difference
between the crank chamber pressure Pc and the suction chamber
pressure Ps. As a result, the inclination angle of the swash plate
24 increases as the sleeve 22 moves away from the cylinder block 2,
so that the piston strokes become longer and the discharging mount
increase.
[0035] Next, a supporting structure of the swash plate will be
described with reference to FIGS. 2 to 8(b).
[0036] FIG. 2 is a perspective view of an assembly in that the
swash plate and the rotor are mounded to the driving shaft. FIG. 3
is an exploded perspective view of the assembly. FIG. 4 is a
cross-sectional view of the assembly. FIG. 5(a) is a
cross-sectional view of the assembly along the line Va-Va in FIG.
4. FIG. 5(b) is a cross-sectional view of the assembly along the
line Vb-Vb in FIG. 4. FIG. 6 is a perspective view of an assembly
in that the hub of the swash plate is mounded to the sleeve. FIG.
7(a) is a front view of the assembly in that the hub of the swash
plate is mounded to the sleeve. FIG. 7(b) is a side view of the
assembly. FIG. 7(c) is a cross-sectional view of the assembly along
the line VIIc-VIIc in FIG. 7(b). FIGS. 8(a) and 8(b) are
cross-sectional views of the assembly along the line VIII-VIII in
FIG. 7(c), wherein FIG. 8(a) shows a condition in that the hub is
parallel to the sleeve, and FIG. 8(b) shows a condition in that the
hub inclines with respect to the sleeve.
[0037] First, the linkage mechanism 40 will be described in
detail.
[0038] As shown in FIGS. 3, 4 and 5(a), the linkage mechanism 40
includes a pair of arms 41, 41 that extend from the rotor 21 toward
the hub 25 and face each other across a slit 41s, a pair of arms
43, 43 that extend from the hub 25 toward the rotor 21 and face
each other across a slit 43s, and a linkage member 45 that is
inserted in the slit 41s (between the pair of arms 41, 41) of the
rotor 21 and in the slit 43s (between the pair of arms 43, 43) of
the swash plate 24. The pair of arms 41, 41 and 43, 43 are opposite
in an orthogonal direction to the drive shaft 10, that is, a
tangential direction of the rotation.
[0039] The width d1 of the slit 41s of the rotor 21, that is, a
distance d1 between inner surfaces 41d, 41d of the arms 41, 41 and
the width d2 of the slit 43s of the hub 25, that is, a distance d2
between inner surfaces 43d, 43d of the arms 43, 43 are formed the
same. The width d0 of the linkage member 45, that is, a distance d0
between outer surfaces 45e, 45e of the linkage member is
substantially the same as the distances d1 and d2. With this
structure, the linkage member 45 is slidably fit in the slits 41s,
43s so as to slidingly contact each other.
[0040] A first end 45a of the linkage member 45 is pivotably
attached to the pair of arms 41, 41 of the rotor 21 by a first
linking pin 46. A second end 45b of the linkage member 45 is
pivotably attached to the pair of arms 43, 43 of the swash plate 24
by a second linking pin 47. The linking pins 46, 47 are designed to
extend in the orthogonal direction to the drive shaft 10, that is a
tangential direction of the rotation.
[0041] In this embodiment, each the arms 41, 41 of the rotor 21 is
formed with a bearing hole 41a in which the first linking pin 46 is
rotatably fit. The first end 45a of the linkage member 45 is formed
with a fixing hole 45c to which the first linking pin 46 is
inserted with force and fixed. Each arms 43, 43 of the swash plate
24 is formed with a bearing hole 43a to which the second linking
pin 47 is rotatably fit. The second end 45b of the linkage member
45 has a fixing hole 45d to which the second linking pin 47 is
inserted with force and fixed. The first linking pin 46 and the
second linking pin 47 are made in the same diameter and length.
[0042] Next, a pivot mechanism connecting the sleeve 22 with the
hub 25 will be described with reference to FIGS. 3 to 7.
[0043] The hub 25 is pivotally attached to the sleeve 22 by the
pivot pins 61 extending in the orthogonal direction to the drive
shaft 10 and pivots as being guided by the tilting guide face 25c,
25e extending in the orthogonal direction to the pivot pin 61.
[0044] The sleeve 22 is formed in a substantially cylindrical shape
and is slidably attached to the drives shaft 10 in the axial
direction. The sleeve 22 is formed with stationary holes 22b and
22b that are coaxially provided on both sides across the driving
shaft 10. The stationary holes 22b and 22b extend orthogonal to the
drive shaft 10 and fix the pivot pins 61 therein.
[0045] On the other hand, the hub 25 of the swash plate is formed
with bearing holes 25b and 25b that are coaxially provided on both
sides across the driving shaft 10. The bearing holes 25b and 25b
extend orthogonal to the drive shaft 10. The sleeve 22 is attached
in a center hole 25c of the hub 25, and the pivot pins 61 and 61
are inserted in the bearing holes 25b and 25b of the hub 25, so
that, as shown in FIGS. 8(a) and 8(b), the hub 25 is tiltable with
respect to the sleeve 25 about the pivot pins 61. As shown in FIGS.
5 to 7, the sleeve 22 and the hub 25 are formed with the tilting
guide faces 22c, 25e that slidingly contact each other. The tilting
guide faces 22c, 25e are provided on the both sides across the
drive shaft 10 and are orthogonal planes to the pivot pin 61. With
this structure, the hub 25 pivots with respect to the sleeve 22
about the pivot pin 61, as being guided by the tilting guide faces
25c, 25e.
[0046] Operation
[0047] An operation of the compressor of the embodiment will be
explained.
[0048] When the drive shaft 10 rotates, the drive shaft 10 rotates
integrally with the rotor 21. The rotation of the rotor 21 is
transferred to the swash plate 24 via the linkage mechanism 40. The
rotation of the swash plate 24 is converted into a reciprocating
movement of the pistons 29 via the pairs of piston shoes 30, 30 so
that the pistons 29 reciprocate in the cylinder bores 3. By the
reciprocating movements of the pistons 29, refrigerant is sucked
from the suction chamber 7 into the cylinder bores 3 through the
suction ports 11 of the valve plate 9, compressed in the cylinder
bores 3, and discharged to the discharge chamber 8 through the
discharge ports 12 of the valve plate 9.
[0049] In order to change the amount of the discharge capacity, the
control valve 33 is opened or closed. Opening or closing the
control valve 33 change the pressure in the crank chamber 5 and the
pressure balancing between back of the piston 29 and front of the
piston 29 so that the piston stroke is changed.
[0050] More particularly, when the control valve 33 opens the gas
supply passage, the high pressure refrigerant gas flows from the
discharge chamber 8 into the crank chamber 5 through the gas supply
passage, so that the crank chamber pressure Pc increases. When the
crank chamber pressure Pc increases, the inclination angle of the
swash plate 24 decreases as the sleeve 22 moves toward the cylinder
block 2. As a result, the piston stroke becomes smaller and the
discharging amount decreases. On the other hand, when the control
valve 33 closes the gas supply passage, the refrigerant gas is
gradually extracted from the crank chamber 5 to the suction chamber
7 through the gas extraction passage and this causes a reduction in
the pressure difference between the crank chamber pressure Pc and
the suction chamber pressure Ps. As a result, the inclination angle
of the swash plate 24 increases as the sleeve 22 moves away from
the cylinder block 2, so that the piston stroke becomes longer and
the discharging mount increases.
[0051] When the compressor is operative, the swash plate 24
receives compression reaction force Fp from the piston 29. As shown
in FIG. 2, the compression reaction force Fp can be applied to a
position anterior to an upper dead center TDC of the swash plate 24
(i.e., a position where the linkage mechanism is located) in the
rotation direction, depending on the rotation speed of the drive
shaft 10. This is because the compression reaction force from the
piston 29 reaches a maximum value just before the end of the
compression stroke of the piston, that is, just before the upper
dead center of the piston. In such a case, the swash plate 24
receives the compression reaction force Fp at a position anterior
to the dead center TDC in the rotating direction, so that the swash
plate 24 receives torsion load.
[0052] In this embodiment, the torsion load is received on the
tilting guide faces 22c, 25c as well as the link mechanism 40. Few
torsion loads is thus given to the linkage mechanism 40 that is a
rotary-slide interface configured to transfer a rotary-torque and
this results in a reduction of slide friction in the linkage
mechanism 40. That is to say, slide friction between the linkage
member 45 and the arms 41, 43 is reduced. Concretely, slide
friction between the outer surfaces 45e of the linkage member 45
and the inner faces 41d of the arms 41 is reduced and slide
friction between the outer surfaces 45e of the linkage member 45
and the inner faces 43d of the arms 43 is reduced. Therefore, the
controllability of the compressor is improved.
[0053] As shown FIG. 5, according to the compressor 1 of this
embodiment, the width d4 between a pair of the opposite tilting
guide faces 22c, 22c is larger than the width d0 of the first end
45a of the linkage member 45 and the width d0 of the second end 45b
of the linkage member 45. With this structure, more torsion load is
received at the tilting guide faces 22c, 22c than at the linkage
mechanism 40 so that the controllability of the compressor is
further improved.
[0054] Here lists characterizations of the present embodiment.
[0055] (1) The present embodiment provides a variable capacity
compressor. The compressor includes a rotating member 21 fixed to a
drive shaft 10 and configured to rotate with the drive shaft 10, a
sleeve 22 axially slidably attached to the drive shaft 10, a
tilting member 24 tiltably attached to the sleeve 22 by a pivot pin
61, and a linkage mechanism 40 connecting the rotating member 21
with the tilting member 24 and configured to transfer a rotary
torque of the rotating member 21 to the tilting member 24 as
allowing the tilting member 24 to tilt. The sleeve 22 and the
tilting member 24 are provided with tilting guide faces 22c, 25d
that are formed as orthogonal planes orthogonal to the pivot pin 61
and are configured to slide one another. With this configuration,
when the swash plate 24 receives compression reaction force Fp,
both of the sleeve 22 and the linkage mechanism 40 receive torsion
load. This decreases torsion load that is received by the linkage
mechanism 40 that is configured to slide as transferring the rotary
torque. Therefore, tilt angle of the tilting member 24 is smoothly
changed so that controllability of the compressor is improved. In
addition, the durability of the linkage mechanism 40 is improved
and the linkage mechanism 40 is downsized.
[0056] (2) According to the present embodiment, the linkage
mechanism 40 includes an arm 41 extending from a rotating member 21
toward a tilting member 24, and an arm 43 extending from the
tilting member 24 toward the rotating member 21 and directly or
indirectly pivoted to the arm 41 of the rotating member by a
linking pin (in the present embodiment, a first linking pin 46 and
a second linking pin 47). With this structure, when changing the
tilt angle of the tilting member 24, the components rotate about a
pivot pin 61 of a sleeve 22 or the linking pin (in the present
embodiment, the linking pins 46 and 47) of the linkage mechanism
40. Therefore, the friction is a rolling friction so that friction
coefficient is extremely small. The controllability of the
compressor is further improved.
[0057] (3) According to the present embodiment, the linkage
mechanism 40 includes a pair of opposite arms 41 that extend from a
rotating member 21 toward a tilting member 24, a pair of opposite
arms 43 that extend from the tilting member 24 toward the rotating
member 21, a linkage member 45 having a first end 45a that is
slidably fit between the arms 41 and a second end 45b that is
slidably fit between the arms 43, a first linking pin 46 that
pivotally connects the first end 45a of the linkage member 45 with
the arms 41 of the rotating member, and a second linking pin 47
that pivotally connects the second end 45b of the linkage member 45
with the arms 43 of the tilting member. With this structure, when
changing the tilt angle of the tilting member 24, the components
rotates about a pivot pin 61 of a sleeve 22 or the linking pins 46,
47 of the linkage mechanism 40. Therefore, the friction is a
rolling friction so that friction coefficient is extremely small.
The controllability of the compressor is further improved.
[0058] (4) According to the present embodiment, a pair of tilting
guides 22c and a pair of the tilting guides 25e are provided on
both sides of the driving shaft 10, and a width d4 between the pair
of tilting guides 22c of the sleeve 22 is larger than the width d0
between the first end 45a of the linkage member 45 and the width d0
between the second end 45b of the linkage member 45. With this
structure, the tilting guide faces 22c of the sleeve 22 receive
heavier torsion load and the burden applied to the linkage
mechanism 40 is reduced. Therefore, the controllability of the
compressor is further improved.
INDUSTRIAL APPLICABILITY
[0059] The present invention is not limited to the embodiments
described above. The present invention can be implemented with
various modifications without departing from technical scope of the
present invention.
* * * * *