WO2007049523A1

WO2007049523A1 - Variable displacement compressor

Info

Publication number: WO2007049523A1
Application number: PCT/JP2006/320963
Authority: WO
Inventors: Toshikatsu Miyaji; Ryuichi Hirose; Naoki Ishikawa; Satoshi Kubo
Original assignee: Calsonic Kansei Corporation
Priority date: 2005-10-27
Filing date: 2006-10-20
Publication date: 2007-05-03
Also published as: JP2007120394A; EP1942275A1; JP4794274B2; KR20080066928A; EP1942275A4; CN101297115A; US20090246050A1

Abstract

A variable displacement compressor comprising a rotating member (21) secured to and rotating integrally with a drive shaft (10), a sleeve (22) fitted to the drive shaft (10) slidably in the axial direction, a tilting member (24) rotatably fitted to a sleeve (22) through pivot pins (61), a link mechanism (40) connecting the rotating member (21) to the tilting member (24) and transmitting the rotating torque of the rotating member (21) to the tilting member (24) while allowing inclination of the tilting member (24), and tilting guide faces (22c, 25d) formed on the sleeve (22) and the tilting member (24) as a surface perpendicular to the pivot pins (61) and brought into slidable contact with each other.

Description

Variable capacity compressor

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 fixed to the drive shaft and rotating integrally with the drive shaft, a sleeve mounted on the drive shaft so as to be slidable in the axial direction, and a sleeve A swash plate that can be freely tilted, a link mechanism that is interposed between the rotor and the swash plate and transmits the rotation of the rotor to the swash plate, and a piston that reciprocates as the swash plate rotates. (See, for example, Japanese Patent Laid-Open Nos. 2003-172417 and 10-176658). The link mechanism connects the rotor and the swash plate so that the rotation angle of the swash plate can be changed while transmitting the rotation of the rotor to the swash plate. Changing the tilt angle of the swash plate changes the piston stroke.

FIG. 9 shows a link mechanism corresponding to Japanese Patent Laid-Open No. 10-176658.

[0004] The link mechanism in FIG. 9 includes a pair of opposed rotor arms 145 and 146 projecting from the rotor 140 toward the swash plate 141, and a single projecting projecting from the swash plate 141 toward the rotor 140. A swash plate arm 147 and a pair of link arms 142A and 142B are provided. These five arms 145, 142A, 147, 143B, 146 are stacked in the direction of torque transmission, whereby the rotation of the rotor 140 is transmitted to the swash plate. One end of each of the pair of link arms 142A and 142B is rotatably connected to the pair of rotor arms 145 and 146 by the first connecting pin 143, and the other end is connected to the swash plate arm 147 by the second connection. Pins 144 are rotatably connected. As a result, the link arms 142A and 142B rotate with respect to the rotor arms 145 and 146 around the connecting pin 143, and the swash plate arm 147 rotates with respect to the link arms 142A and 142B around the connecting pin 144. As a result, the inclination angle of the swash plate 141 can be changed with respect to the drive shaft (not shown).

Disclosure of the invention

[0005] During the operation of the compressor (when the drive shaft rotates), the rotor arm 145 and the link arm 142A The contact surface and the contact surface between the link arm 142A and the swash plate arm 147 serve as a rotational torque transmission surface and a rotational sliding contact surface. That is, the contact surface between the rotor arm 145 and the link arm 142A is in sliding contact with the connecting pin 143 as a center while receiving a surface pressure due to a large rotational torque Ft. Further, the contact surface between the link arm 142A and the swash plate arm 147 rotates and slides relative to the connection pin 144 while receiving a surface pressure due to a large rotational torque Ft. Therefore, when the inclination angle of the swash plate 141 is changed, the contact surface between the link arm 142A and the swash plate arm 147 where the sliding resistance between the contact surfaces of the rotor arm 145 and the link arm 142A is extremely large. The sliding resistance between them is extremely large.

[0006] When the compressor is in operation (when the drive shaft is rotating), the swash plate 141 receives a compression reaction force Fp as much as a piston force connected to the swash plate 141. This compression reaction force Fp may be shifted forward in the rotational direction of the link mechanism as shown in Fig. 9 (see Fig. 2). In this case, a twisting load is applied to the swash plate arm 147 in the Y direction in the figure, and the swash plate 141 and the link 142 are bitten and twisted at two points (C, C), further increasing the sliding resistance. End up.

[0007] In Patent Document 1 that solves such a problem, a force in which a washer is interposed between the contact surfaces of the rotor arm and the link arm and between the contact surfaces of the link arm and the swash plate arm. Even with such a structure, the same problem occurs.

[0008] The present invention has been made paying attention to the problems of the prior art, and an object thereof is to provide a variable capacity compressor capable of reducing a torsional load applied to a link mechanism.

[0009] One aspect of the present invention is a variable capacity compressor, a rotating member fixed to a drive shaft and rotating integrally therewith, and a three-piece mounted on the drive shaft so as to be slidable in the axial direction. A tilting member rotatably mounted on the sleeve by a pivot pin, and connecting the rotating member and the tilting member to allow tilting of the tilting member while allowing the rotating member to rotate torque of the rotating member. A tilting guide formed on a surface orthogonal to the pivot pin on each of the sleeve and the tilting member and in sliding contact with each other. A surface.

Brief Description of Drawings

[0010] FIG. 1 is a cross-sectional view of a variable capacity compressor according to an embodiment of the present invention. FIG. 2 is a perspective view of an assembly in which a swash plate and a rotor are assembled to a drive shaft.

FIG. 3 is an exploded perspective view of the assembly.

[FIG. 4] FIG. 4 is a sectional view of the assembly.

FIG. 5 (a) is a cross-sectional view taken along the line Va—Va in FIG. 4, and FIG. 5 (b) is a cross-sectional view taken along the line Vb—Vb in FIG.

FIG. 6 is a perspective view including a partially broken portion in a state where a sleeve is assembled to a swash plate hub.

[FIG. 7] FIG. 7 is a view showing a state in which a sleeve is assembled to a swash plate hub. FIG. 7 (a) is a front view, FIG. 7 (b) is a side view, and FIG. Sectional view along line VIIc-VIIc in Fig. 7 (b)

[Fig. 8] Fig. 8 is a cross-sectional view taken along line VIII-VIII in Fig. 7 (c), and Fig. 8 (a) is a view of the swash plate hub parallel to the sleeve. (b) is a view of the swash plate hub tilted with respect to the sleeve.

FIG. 9 is a sectional view showing an example of a link mechanism of a conventional variable capacity compressor.

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, a variable capacity compressor according to an embodiment of the present invention will be described with reference to the drawings.

FIG. 1 is a cross-sectional view of a variable capacity compressor.

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) arranged at equal intervals in the circumferential direction, and a cylinder block 2 joined to the front end surface of the cylinder block 2 and cranked inside. A front housing 4 that forms a chamber 5 and a rear housing 6 that is joined to a rear end surface of the cylinder block 2 via a valve plate 9 and that forms a suction chamber 7 and a discharge chamber 8 therein. The cylinder block 2, the front housing 4 and the rear housing 6 are fastened and fixed by a plurality of through bolts 13 to constitute a compressor housing.

The valve plate 9 is formed with a suction hole 11 that communicates the cylinder bore 3 and the suction chamber 7, and a discharge hole 12 that communicates the cylinder bore 3 and the discharge chamber 8.

A suction valve mechanism (not shown) that opens and closes the suction hole 11 is provided on the surface of the valve plate 9 on the cylinder block 2 side. Discharge on the rear housing 6 side of the valve plate 9 A discharge valve mechanism (not shown) for opening and closing the hole 12 is provided. A gasket (not shown) is interposed between the valve plate 9 and the rear housing 6 so that the airtightness of the suction chamber 7 and the discharge chamber 8 is maintained.

[0016] The central through hole 14 as a bearing hole at the center of the cylinder block 2 and the front housing 4 is supported by a drive shaft 10 via radial bearings 15 and 19, thereby driving shaft 10 force S crank It is freely rotatable in chamber 5. A thrust bearing 20 is interposed between the front end surface of a rotor 21 (described later) fixed to the drive shaft 10 and the inner wall surface of the rear housing 6, and the rear end of the central through hole 14 of the cylinder block 2. A thrust bearing 16 is interposed between the adjusting screw 17 as a fixing member fixed to the side and the rear end surface of the drive shaft 10.

The crank chamber 5 includes a rotor 21 as a rotating member fixed to the drive shaft 10, a sleeve 22 slidably mounted on the drive shaft 10 in the axial direction, and a pivot pin 61 on the sleeve 22. And a swash plate 24 as a tilting member that can be pivoted with respect to the sleeve 22. That is, the swash plate 24 is attached to the drive shaft 10 via the sleeve 22 and the pivot pin 61, so that it can tilt with respect to the drive shaft 10 and slide in the axial direction of the drive shaft 10. . In this example, the swash plate 24 includes a knob 25 attached to the sleeve 22 so as to be tiltable, and a swash plate body 26 fixed to a boss portion 25a of the hub 25.

A piston 29 is slidably accommodated in each cylinder bore 3, and this piston 29 is connected to a swash plate 24 via a pair of hemispherical piston shoes 30, 30.

[0019] A link mechanism 40 is interposed between the rotor 21 as the rotating member and the swash plate 24 as the tilting member. The link mechanism 40 allows the rotational torque of the rotor 21 to be transmitted to the swash plate 24 while allowing the tilt angle of the swash plate 24 to be changed.

[0020] The inclination angle of the swash plate 24 decreases as the sleeve 22 moves closer to the cylinder block 2 side against the return spring 52, while the inclination angle of the swash plate 24 decreases, while the sleeve 22 resists the return spring 51. Then, when it moves away from the cylinder block 2, the inclination angle of the swash plate 24 increases. Reference numeral 53 in FIG. 1 is a return spring stopper (for example, a C ring) that is locked in an annular groove formed in the drive shaft 10 and that compresses and holds the return spring 52 between the sleeve 22 and the like. is there.

[0021] When the drive shaft 10 rotates, the rotor 21 rotates together with the drive shaft 10, and the rotation of the rotor 21 rotates. The rotation is transmitted to the swash plate 24 via the link mechanism 40. The rotation of the swash plate 24 is converted into the back-and-forth movement of the piston 29, and the piston 29 reciprocates in the cylinder bore 3. When the piston 29 reciprocates, the refrigerant in the suction chamber 7 is sucked into the cylinder bore 3 through the suction hole 11 of the valve plate 9 and then compressed in the cylinder bore 3, and the compressed refrigerant is discharged into the discharge hole 12 of the valve plate 9. It is discharged to the discharge chamber 8 through.

[0022] This variable capacity compressor is provided with a pressure control mechanism. The pressure control mechanism changes the tilt angle of the swash plate 24 by adjusting the differential pressure (pressure balance) between the crank chamber pressure Pc on the rear side of the piston 29 and the suction chamber pressure Ps on the front side of the piston 29. Change the piston stroke. When the piston stroke changes, the refrigerant discharge capacity of the compressor changes.

[0023] Specifically, the pressure control mechanism includes an extraction passage (not shown) that connects the crank chamber 5 and the suction chamber 7, and an air supply passage (not shown) that connects the crank chamber 5 and the discharge chamber 8. And a control valve 33 provided in the middle of the air supply passage for controlling the opening and closing of the air supply passage.

[0024] Since the extraction passage is open regardless of whether the control valve 33 is opened or closed, the refrigerant gas in the crank chamber 5 always flows into the suction chamber 7 through the extraction passage.

When the supply passage is opened by the control valve 33, high-pressure refrigerant gas flows from the discharge chamber 8 through the supply passage into the crank chamber 5, thereby increasing the pressure in the crank chamber 5. When the pressure in the crank chamber 5 rises, the sleeve 22 moves closer to the cylinder block 2 and the inclination angle of the swash plate 24 decreases, thereby reducing the piston stroke and reducing the discharge amount.

[0026] On the other hand, when the supply passage is closed by the control valve 33, the refrigerant gas in the crank chamber 5 always escapes to the suction chamber 7 through the extraction passage, so that the pressure difference between the suction chamber 7 and the crank chamber 5 gradually increases. Will get smaller. Then, while the sleeve 22 moves away from the cylinder block 2, the inclination angle of the swash plate 24 increases, the piston stroke increases, and the discharge amount increases.

Next, the support structure for the swash plate will be described in more detail with reference to FIGS.

2 is a perspective view of an assembly in which a swash plate and a rotor are assembled to a drive shaft, FIG. 3 is an exploded perspective view of the assembly, FIG. 4 is a sectional view of the assembly, and FIG. 5 (a) is in FIG. Fig. 5 (b) is a cross-sectional view taken along the line Vb-Vb in Fig. 4, and Fig. 6 is a swash plate hub. 7 is a perspective view including a partially broken portion in a state where a sleeve is assembled, FIG. 7 is a diagram showing a state where a sleeve is assembled to a hub of a swash plate, (a) is a front view, and (b) is a side view. Yes (c) is a cross-sectional view taken along line VIIc-VIIc in (b), FIG. 8 is a cross-sectional view taken along line VIII-VIII in FIG. 7 (c), and FIG. FIG. 8 (b) is a diagram showing a state in which the swash plate hub is parallel, and FIG. 8 (b) is a diagram showing a state in which the swash plate hub is inclined with respect to the sleeve.

First, the link mechanism 40 will be described.

[0030] As shown in Figs. 3, 4, and 5 (a), the link mechanism 40 includes a pair of opposed arms 41 that protrude from the rotor 21 toward the swash plate 24 and are divided by slits 41s. 41, a pair of arms 43, 43 projecting from the swash plate 24 toward the rotor 21 and divided by a slit 43s, a slit 41s of the port 21 (between the pair of arms 41, 41) and the swash plate A rectangular link member 45 inserted into 24 slits 43s (between the pair of arms 43 and 43). Note that each of the pair of arms 41, 41 and 43, 43 is disposed so as to face in a direction orthogonal to the drive shaft 10 (= a tangential direction of the rotational direction).

[0031] The width dl of the slit 41s of the rotor 21 (that is, the width between the inner surfaces 41d and 41d of the pair of arms 41 and 41 of the rotor 21) and the width d2 of the slit 43s of the swash plate 24 (that is, the width of the swash plate 24) A pair of arms 43 and 43 are formed to have the same width between the inner flanges J surface 43d and 43d), and the width dO of the link member 45 (that is, both of the link members 45) with respect to the widths dl and d2. The width between the outer side surfaces 45e and 45e) is also formed to be substantially the same width, whereby the link member 45 is slidably fitted in both the slits 41s and 43s, and is always in sliding contact.

[0032] One end 45a of the link member 45 is rotatably connected to the pair of arms 41, 41 of the rotor 21 by a first connecting pin 46. The other end 45 b of the link member 45 is rotatably connected to the pair of arms 43, 43 of the swash plate 24 by the second connecting pin 47. Both of the connecting pins 46 and 47 are set in a direction orthogonal to the drive shaft 10 (= tangential direction of the rotational direction).

[0033] In this example, a pair of arms 41, 41 of the rotor 21 is provided with a bearing hole 41a that rotatably supports the first connecting pin 46, and the first end 45a of the link member 45 has a first hole 45a. A fixing hole 45c for fixing the connecting pin 46 by press-fitting is provided. The pair of arms 43, 43 of the swash plate 24 is provided with a bearing hole 43a for rotatably supporting the second connecting pin 47, and the link portion The other end 45b of the material 45 is provided with a fixing hole 45d for fixing the second connecting pin 47 by press fitting. The first connecting pin 46 and the second connecting pin 47 have the same diameter and the same length.

[0034] Next, a pivot mechanism for connecting the sleeve 22 and the hub 25 will be described with reference to FIGS.

The hub 25 is pivotally attached to the sleeve 22 by a pivot pin 61 that extends in a direction orthogonal to the drive shaft 10, and pivots while being guided by tilting guide surfaces 22 c and 25 e orthogonal to the pivot pin 61. It ’s like that.

The sleeve 22 is formed in a substantially cylindrical shape, and is attached to the drive shaft 10 so as to be slidable in the axial direction. In the sleeve 22, fixing holes 22b and 22b are formed concentrically on both sides of the drive shaft 10. The fixing holes 22b and 22b extend in a direction perpendicular to the drive shaft 10, and the pivot pin 61 is fixed to the fixing holes 22b and 22b.

On the other hand, the swash plate hub 25 has bearing holes 25d and 25d formed concentrically on both sides of the drive shaft 10. The bearing holes 25d and 25d extend in a direction orthogonal to the drive shaft 10. The pivot pin 61 is inserted into the bearing holes 25d and 25d of the hub 25 with the sleeve 22 attached to the central port 25c of the hub 25, so that the pivot pin as shown in FIGS. 8 (a) and (b). The hub 25 tilts with respect to the sleeve 22 around 61. The sleeve 22 and the hub 25 are provided with tilting guide surfaces 22c and 25e that are in sliding contact with each other as shown in FIGS. The tilt guide surfaces 22c and 25e are provided on both sides of the drive shaft 10 as surfaces orthogonal to the pivot pin 61. Therefore, the hub 25 is tilted about the pivot pin 61 with respect to the sleeve 22 while being guided by the tilt guide surfaces 22c and 25e.

[0038] Action

Next, the operation of the compressor of this embodiment will be described.

When the drive shaft 10 rotates, the rotor 21 rotates integrally with the drive shaft 10. The rotation of the rotor 21 is transmitted to the swash plate 24 via the link mechanism 40. The rotation of the swash plate 24 is converted into a reciprocating motion of the piston 29 through a pair of pistons 30, 30, and the piston 29 reciprocates in the cylinder bore 3. The reciprocating motion of the piston 29 causes the refrigerant valve plate in the suction chamber 7 to move. After being sucked into the cylinder bore 3 through the suction hole 11 of the cylinder 9, it is compressed in the cylinder bore 3, and is discharged into the discharge chamber 8 through the discharge hole 12 of the compressed refrigerant cover valve plate 9.

[0040] In order to change the refrigerant discharge capacity, the pressure in the crank chamber 5 is adjusted by opening and closing the control valve 33, the pressure balance before and after the piston is adjusted, and the piston stroke is changed.

[0041] More specifically, when the supply passage is opened by the control valve 33, a high-pressure refrigerant gas flows from the discharge chamber 8 through the supply passage into the crank chamber 5, thereby increasing the pressure in the crank chamber 5. Ascend. When the pressure in the crank chamber 5 rises, the sleeve 22 moves closer to the cylinder block 2 and the inclination angle of the swash plate 24 decreases, so that the piston stroke becomes smaller and the discharge amount decreases. On the other hand, when the supply passage is closed by the control valve 33, the refrigerant gas in the crank chamber 5 is always discharged to the suction chamber 7 through the extraction passage, so that the pressure difference between the suction chamber 7 and the crank chamber 5 gradually increases. Eliminates and equalizes pressure. Then, while the sleeve 22 moves away from the cylinder block 2, the inclination angle of the swash plate 24 increases, the piston stroke increases, and the discharge amount increases.

Here, when the compressor is operating, a compression reaction force Fp from the piston 29 is applied to the swash plate 24. As shown in FIG. 2, the compression reaction force Fp may be shifted forward in the rotational direction from the top dead center TDC of the swash plate 24 (position where the link mechanism 40 is located) depending on the rotational speed of the drive shaft 10. This is because the compression reaction force becomes maximum before the top dead center of the end of the compression stroke in the compression stroke of the piston 29. In such a case, the compression reaction force Fp is biased to the swash plate 24 forward in the rotational direction from the top dead center TDC, and a torsional load is applied to the swash plate 24.

[0043] In the present embodiment, the torsional load is received by the link mechanism 40 and the tilt guide surfaces 22c and 25e. For this reason, the torsional load applied to the link mechanism 40 that transmits the rotational torque and rotates and slides is reduced. As a result, the sliding resistance in the link mechanism 40 is reduced. That is, the sliding resistance between the link member 45 and the arms 41 and 43 decreases. More specifically, the sliding resistance between the outer side surface 45e of the link member and the inner side surface 41d of the arm 41 and the sliding resistance between the outer side surface 45e of the link member and the inner side surface 43d of the arm 43 are reduced). Thereby, the controllability of the compressor is improved. In the compressor 1 of the present embodiment, as shown in FIG. 5, the pair of tilting guide surfaces 22c, 22c of the sleeve 22 has a width d4 force. The width dO of the one end 45a of the link member 45 and the link portion. The width 45 of the other end 45b of the material 45 is set wider. Therefore, more torsional loads can be received by the tilt guide surfaces 22c and 22c than the link mechanism 40, and the controllability of the compressor is further improved.

[0045] The features of this embodiment are listed below.

(1) This embodiment is a variable capacity compressor, which is fixed to the drive shaft 10 and rotates integrally with the drive shaft 10, and is slidably mounted on the drive shaft 10 in the axial direction. The rotation of the rotating member 21 while allowing the tilting member 24 to tilt by connecting the sleeve 22, the tilting member 24 rotatably mounted on the sleeve 22 by the pivot pin 61, and the rotating member 21 and the tilting member 24. A link mechanism 40 for transmitting torque to the tilting member 24, and the tilting guide surfaces 22c and 25d formed on the sleeve 22 and the tilting member 24 as surfaces orthogonal to the pivot pin 61 are slidably contacted with each other. This is a variable capacity compressor provided. Therefore, when a compression reaction force is applied to the tilting member 24, it is received by both the torsional load force S sleeve 22 and the link mechanism 40. As a result, the torsional load applied to the link mechanism 40 (the portion that rotates and slides while transmitting torque) is reduced. Thereby, the change of the tilt angle of the tilt member 24 becomes smooth, and the controllability of the compressor is improved. Further, the durability of the link mechanism 40 is improved and the size can be reduced.

(2) According to the present embodiment, the link mechanism 40 includes the arm 41 projecting from the rotating member 21 toward the tilting member 24 and the arm 41 projecting from the tilting member 24 toward the rotating member 21. And the arm 43 of the rotating member and the arm 43 rotatably connected by a connecting pin (in this example, the first connecting pin 46 and the second connecting pin 47) directly or indirectly. Therefore, when changing the inclination angle of the tilting member 24, each member rotates around the pivot pin 61 of the sleeve 22 and the connecting pin of the link mechanism 40 (in this example, the connecting pins 46 and 47). Therefore, the friction form is “rolling-sliding friction”, so that the friction coefficient becomes extremely small, and the controllability of the compressor is further improved.

[0048] (3) According to the present invention, the link mechanism 40 includes the pair of opposed arms 41, 41 projecting from the rotating member 21 toward the tilting member 24, and the tilting member 24 to the rotating member 21. Towards A pair of opposed arms 43, 43 projecting from one end 45a is slidably fitted between a pair of arms 41, 41 of the rotating member, and the other end 45b is a pair of tilting members. Link member 45 slidably fitted between the arms 43 and 43, and a first connecting pin 46 for rotatably connecting one end portion 45a of the link member and the arms 41 and 41 of the rotating member. And a second connecting pin 47 that rotatably connects the other end portion 45b of the link member and the arms 43, 43 of the tilting member. Therefore, when changing the inclination angle of the tilting member 24, each member rotates around the pivot pin 61 of the sleeve 22 and the connecting pins 46 and 47 of the link mechanism 40, so that the friction form is “Rolling sliding friction” makes the coefficient of friction extremely small and further improves the controllability of the compressor.

[0049] (4) According to the present embodiment, a pair of tilt guide surfaces 22c and 25e are provided across the drive shaft 10, and the width d4 of the pair of tilt guide surfaces 22c and 22c of the sleeve 22 is linked. It is wider than the width dO of the one end 45a of the member and the width dO of the other end 45b of the link member (see FIG. 5). Therefore, a larger torsional load can be received by the tilt guide surfaces 22c and 22c of the sleeve 22, and the burden on the link mechanism 40 can be reduced. This further improves the controllability of the compressor.

Industrial applicability

It should be noted that the present invention is not limited to the above-described embodiments, and various modifications are possible within the scope of the technical idea of the present invention.

Claims

The scope of the claims

[1] A variable capacity compressor,

A rotating member fixed to the drive shaft and rotating integrally;

A sleeve that is slidably attached to the drive shaft in the axial direction;

A tilting member rotatably mounted on the sleeve by a pivot pin, and connecting the rotating member and the tilting member to allow the tilting member to tilt and transmit the rotational torque of the rotating member to the tilting member A link mechanism to

A piston that reciprocates with the rotational movement of the tilting member;

A tilt guide surface formed as a surface orthogonal to the pivot pin on each of the sleeve and the tilt member and in sliding contact with each other;

A variable capacity compressor.

[2] The variable capacity compressor according to claim 1,

The link mechanism is

The rotating member force, an arm protruding toward the tilting member;

The tilting member force, an arm projecting toward the rotating member;

A connecting pin for directly or indirectly connecting the arm of the rotating member and the arm of the tilting member directly to the rotation;

A variable capacity compressor.

[3] The variable capacity compressor according to claim 1,

The link mechanism is

The rotating member force, a pair of opposing arms protruding toward the tilting member, the tilting member force, a pair of opposing arms protruding toward the rotating member, and one end portion of the rotating member A link member slidably fitted between a pair of arms and having the other end slidably fitted between a pair of arms of the tilting member, one end of the link member and the rotation A first connecting pin that rotatably connects the arm of the member; a second connecting pin that rotatably connects the other end of the link member and the arm of the tilting member;

A variable capacity compressor comprising: [4] The variable capacity compressor according to claim 3,

A pair of the tilt guide surface of the sleeve and the tilt guide surface of the tilt member are provided across the drive shaft, respectively.

Width force of a pair of tilt guide surfaces of the sleeve A variable capacity compressor wider than a width of one end of the link member and a width of the other end of the link member.