Variable-capacity compressor

Abstract

[Problem] To provide a variable-capacity compressor in which it is possible to suppress vibration and noise caused by the shaking of an angle-varying part of a swash plate. [Solution] A variable-capacity compressor 1 comprises: a drive shaft 8; a swash plate 9 rotated by the drive shaft 8; and an angle-varying part 11 that is provided to the swash plate 9 and has penetratingly disposed therein a saddle-shaped part through which the drive shaft 8 is inserted. The inclination angle of the swash plate 9 is regulated by the saddle-shaped part. The angle-varying part 11 is configured such that a specific portion on the inner wall of the saddle-shaped part gets pressed against the drive shaft 8 by centrifugal force generated in association with the rotation of the drive shaft 8.

Description

Variable displacement compressor

[0001] The present invention relates to a variable displacement compressor used in an air conditioning system for a vehicle.

[0002] Conventionally, this type of variable displacement compressor is configured to draw and compress refrigerant by converting the rotation of a swash plate, which is rotated by a drive shaft, into the reciprocating motion of pistons in cylinder bores. In this case, the swash plate is provided with a variable angle portion, and the variable angle portion of the swash plate is connected to a rotor that rotates integrally with the drive shaft via a connecting mechanism, and the drive shaft is inserted into a saddle portion (through hole) formed in the variable angle portion.

[0003] The discharge capacity could be changed by changing the inclination angle of the swash plate relative to the drive shaft, but the inclination angle of the swash plate was restricted by the saddle portion of the angle-changing section (see, for example, Patent Document 1 and Patent Document 2).

[0004] Korean Patent Publication No. 10-2015-0008588 Japanese Patent Application Laid-Open No. 2002-349427

[0005] While the above-mentioned patent documents are concerned with suppressing compressor vibration and noise caused by wobble of the drive shaft, this type of variable displacement compressor also poses a problem of vibration and noise caused by wobble of the variable angle portion of the swash plate. This is because the tilt angle (variation angle) is regulated by the drive shaft, which is a rotating body, and the saddle portion of the variable angle portion, so clearance is required between the drive shaft and the saddle portion, and the degree of wobble varies depending on the resulting positional relationship.

[0006] The present invention has been made to solve the above-mentioned conventional technical problems, and has an object to provide a variable displacement compressor that can suppress vibration and noise caused by wobbling of the variable angle portion of the swash plate.

[0007] The variable displacement compressor of the present invention comprises a drive shaft, a swash plate rotated by the drive shaft, and a variable angle portion provided on the swash plate and having a saddle portion through which the drive shaft is inserted, the saddle portion regulating the inclination angle of the swash plate, and the variable angle portion is configured such that a specific point on the inner wall of the saddle portion is pressed against the drive shaft by centrifugal force generated as the drive shaft rotates.

[0008] The variable displacement compressor of the present invention is characterized in that the weight distribution of the angle-changing portion in the above invention is set so that the angle-changing portion is biased in a specific direction by centrifugal force generated with rotation of the drive shaft.

[0009] The variable displacement compressor of the invention of claim 3 is characterized in that, in the invention of claim 1, the variable angle portion has a weight, and this weight is provided at either position with respect to an axis passing through the center of the saddle portion.

[0010] The variable displacement compressor of the invention of claim 4 is characterized in that, in the invention of claim 1, the variable angle portion has at least a pair of weights, and each weight is provided in an asymmetrical position with respect to an axis passing through the center of the saddle portion.

[0011] A variable displacement compressor according to a fifth aspect of the present invention is characterized in that, in the first aspect of the present invention, the variable angle portion has at least a pair of weights, each weight having a different weight.

[0012] The variable displacement compressor of the invention of claim 6 is characterized in that it comprises pistons arranged in cylinder bores formed in a housing in each of the above inventions, a conversion mechanism that converts the rotation of the swash plate into the reciprocating motion of the pistons, a rotor fixed to a drive shaft, and a connecting mechanism that connects the swash plate to the rotor so that it can tilt, and the angle changing section has an arm that forms part of the connecting mechanism.

[0013] The variable displacement compressor of the invention of claim 7 is characterized in that it comprises pistons arranged in cylinder bores formed in the housing of the invention of claim 1, a conversion mechanism that converts the rotation of the swash plate into the reciprocating motion of the pistons, a rotor fixed to the drive shaft, and a connecting mechanism that connects the swash plate to the rotor so that it can tilt, and the variable angle section has an arm that forms part of the connecting mechanism, and the weights on one side and the other side of a line passing through the center of the arm and the center of the saddle section are different.

[0014] In a variable displacement compressor according to an eighth aspect of the present invention, the variable angle portion has weights, and at least one of the weight, number, and attachment position of the weights is different on one side of a line passing through the center of the arm and the center of the saddle portion.

[0015] According to the present invention, in a variable displacement compressor comprising a drive shaft, a swash plate rotated by the drive shaft, and a variable angle portion provided on the swash plate and having a saddle portion through which the drive shaft is inserted, the saddle portion regulating the inclination angle of the swash plate, the variable angle portion is configured such that a specific point on the inner wall of the saddle portion is pressed against the drive shaft by centrifugal force generated as the drive shaft rotates. Therefore, regardless of the clearance between the saddle portion and the drive shaft, i.e., the precision of the parts, it is possible to suppress the adverse effects on the drive shaft caused by wobbling of the variable angle portion and the resulting vibration and noise.

[0016] In addition, the inclination between the drive shaft and the saddle portion (the inclination perpendicular to the direction in which the swash plate tilts) is also reduced, which has the effect of stabilizing the sliding properties of the variable angle portion on the drive shaft and improving controllability.

[0017] In this case, for example, as in the invention of claim 2, by setting the weight distribution of the variable angle portion so that the variable angle portion is biased in a specific direction by the centrifugal force generated by the rotation of the drive shaft, it becomes possible to press the variable angle portion against the drive shaft without changing the weight of the entire variable angle portion, thereby suppressing changes in the control gas due to a reduction in the weight of the variable angle portion.

[0018] More specifically, a weight may be provided at either position relative to an axis passing through the center of the saddle portion of the variable angle section, as in the invention of claim 3. Alternatively, at least a pair of weights may be provided at the variable angle section, with each weight being provided at an asymmetrical position relative to the axis passing through the center of the saddle portion, as in the invention of claim 4. Alternatively, each weight may have a different weight, as in the invention of claim 5.

[0019] As in the sixth aspect of the present invention, the variable displacement compressor includes pistons disposed in cylinder bores formed in the housing, a conversion mechanism that converts the rotation of the swash plate into reciprocating motion of the pistons, a rotor fixed to the drive shaft, and a connecting mechanism that connects the swash plate to the rotor so that it can tilt. The variable angle portion has an arm that forms part of the connecting mechanism, and as in the seventh aspect of the present invention, the variable angle portion is configured so that the weight is different on one side of a line passing through the center of the arm and the center of the saddle portion, and centrifugal force causes the variable angle portion to lean toward either the center of the arm or the line passing through the center of the saddle portion, with the arm as the fulcrum. This allows a specific point on the inner wall of the saddle portion to be stably pressed against the drive shaft.

[0020] In this case, too, weights may be provided in the variable angle section as in the invention of claim 8, and at least one of the weight, number, and mounting position of these weights may be configured to be different on one side of a line passing through the center of the arm and the center of the saddle section.

[0021] 5 is a longitudinal side view of a variable displacement compressor according to one embodiment to which the present invention is applied; FIG. 6 is a plan view of the drive shaft, rotor, and swash plate of the variable displacement compressor of FIG. 1; FIG. 7 is a perspective view of the drive shaft, rotor, and swash plate of the variable displacement compressor of FIG. 1; FIG. 8 is a perspective view of the variable angle portion of the variable displacement compressor of FIG. 1 (Embodiment 1); FIG. 9 is a schematic diagram illustrating the centrifugal force when the drive shaft of the variable displacement compressor of FIG. 1 rotates; FIG. 11 is a diagram illustrating the relationship between the load with which the saddle portion of the variable angle portion is pressed against the drive shaft and the rotation speed of the variable displacement compressor in the case of FIG. 5; FIG. 12 is a perspective view of the variable angle portion of another embodiment of the variable displacement compressor of FIG. 1 (Embodiment 2); and FIG. 13 is a schematic diagram illustrating the variable angle portion of another embodiment of the variable displacement compressor of FIG. 1 (Embodiment 3).

[0022] Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

[0023] A variable displacement compressor 1 according to an embodiment of the present invention is a swash plate type compressor used in an air conditioning system for a vehicle.

[0024] (1) Basic Configuration of Variable Displacement Compressor 1 The variable displacement compressor 1 of the embodiment includes a cylinder block 2 having a plurality of cylinder bores 2A, a front housing 3 provided at one end of the cylinder block 2, and a cylinder head 6 provided at the other end of the cylinder block 2 via a valve plate 4.

[0025] A drive shaft 8 is installed across a crank chamber 7 defined by the cylinder block 2 and the front housing 3, and a swash plate 9 is disposed around the center of the drive shaft 8. A variable angle portion 11, as shown in Figure 4, is attached to the center of the swash plate 9. A saddle portion 12 (Figure 4) consisting of a through hole is provided in the center of the variable angle portion 11, and the drive shaft 8 is inserted into the saddle portion 12.

[0026] The saddle portion 12 formed on the variable angle portion 11 is shaped so that the inclination angle of the swash plate 9 (the angle at which the swash plate 9 is inclined relative to the drive shaft 8) is perpendicular to the annular plane of the swash plate 9 and can be tilted within a range of maximum and minimum inclination angles around a pivot axis perpendicular to the plane containing the top dead center position and bottom dead center position of the swash plate 9, thereby regulating the inclination angle of the swash plate 9.

[0027] The top dead center position of the swash plate 9 refers to the position where the discharge stroke (compression side) of the piston 13 ends, and the bottom dead center position refers to the position where the suction stroke (expansion side) of the piston 13 ends. The swash plate 9 is connected to a rotor 14 fixed to the drive shaft 8 via a connecting mechanism 16, so that the inner wall (side surface) of the saddle portion 12 is slidably supported on the outer circumferential surface of the drive shaft 8, and the inclination angle of the swash plate 9 can be changed.

[0028] The saddle portion 12 is formed with a minimum inclination angle restricting portion that abuts against the drive shaft 8. In this embodiment, when the inclination angle θ of the swash plate 9 when the annular plane of the swash plate 9 is perpendicular to the drive shaft 8 is set to 0°, the minimum inclination angle restricting portion of the saddle portion 12 is formed so that the inclination angle of the swash plate 9 is preferably greater than 0° and less than 0.5°.

[0029] A tilt angle reducing spring 17, which is a compression coil spring, is mounted between the rotor 14 and the swash plate 9 to urge the swash plate 9 to the minimum tilt angle. Also, a tilt angle increasing spring 19, which is also a compression coil spring, is mounted between the swash plate 9 and the spring support member 18 to urge the swash plate 9 in the direction of increasing the tilt angle to a predetermined tilt angle smaller than the maximum tilt angle.

[0030] At the minimum tilt angle, the biasing force of the tilt angle increasing spring 19 is set to be greater than the biasing force of the tilt angle decreasing spring 17. Therefore, when the drive shaft 8 is not rotating, the swash plate 9 is positioned to form a predetermined tilt angle at which the resultant force of the biasing force of the tilt angle decreasing spring 17 and the biasing force of the tilt angle increasing spring 19 becomes zero.

[0031] One end of the drive shaft 8 passes through a boss 21 that protrudes outward from the front housing 3, extending to the outside, and is connected to a power transmission device 22. A shaft seal 23 is inserted between the drive shaft 8 and the boss 21 to isolate the inside from the outside. The drive shaft 8 and rotor 14 are supported in the radial direction by bearings 24 and 26, and in the thrust direction by a bearing 27 and a thrust plate 28. Power from an external drive source is transmitted to the power transmission device 22, and the drive shaft 8 is rotatable in synchronization with the rotation of the power transmission device 22. The gap between the thrust plate 28 and the abutting portion of the drive shaft 8 is adjusted to a predetermined distance by an adjustment screw 29.

[0032] A piston 13 is disposed within the cylinder bore 2A, and the outer periphery of a swash plate 9 is accommodated in the inner space of the end of the piston 13 that protrudes toward the crank chamber 7. The swash plate 9 is configured to move in conjunction with the piston 13 via a pair of shoes 31 (which constitute the conversion mechanism of the present invention). Therefore, rotation of the swash plate 9 allows the piston 13 to reciprocate within the cylinder bore 2A.

[0033] The cylinder head 6 is defined by a suction chamber 32 at the center and a discharge chamber 33 that annularly surrounds the radially outer portion of the suction chamber 32. The suction chamber 32 communicates with the cylinder bore 2A via a communication hole 34 provided in the valve plate 4 and an intake valve (not shown). The discharge chamber 33 communicates with the cylinder bore 2A via a discharge valve (not shown) and a communication hole 36 provided in the valve plate 4.

[0034] The front housing 3, cylinder block 2, valve plate 4, and cylinder head 6 are fastened together with a plurality of through bolts 37 via gaskets (not shown) to form a housing 38. The discharge chamber 33 is connected to a discharge-side refrigerant circuit of the air conditioning system via a discharge passage including a muffler space, a check valve, etc. (not shown). The suction chamber 32 is connected to a suction-side refrigerant circuit of the air conditioning system via a suction passage (not shown).

[0035] The cylinder head 6 is further provided with a control valve 41. The control valve 41 adjusts the opening of a communication passage 42 that connects the discharge chamber 33 with the crank chamber 7, thereby controlling the amount of discharge gas introduced into the crank chamber 7. The refrigerant in the crank chamber 7 flows into the suction chamber 32 via a communication passage (not shown) and an orifice formed in the suction valve.

[0036] Therefore, by changing the pressure in the crank chamber 7 using the control valve 41 and changing the inclination angle of the swash plate 9 (i.e., changing the stroke of the piston 13), the discharge capacity of the variable capacity compressor 1 can be variably controlled.

[0037] When the air conditioner is operating (i.e., when the variable displacement compressor 1 is in operation), the amount of current supplied to the solenoid built into the control valve 41 is adjusted based on an external signal, and the discharge capacity is variably controlled so that the pressure in the suction chamber 32 reaches a predetermined value. The control valve 41 can optimally control the suction pressure according to the external environment.

[0038] Furthermore, when the air conditioner is not operating (i.e., when the variable displacement compressor 1 is not operating), the solenoid built into the control valve 41 is de-energized to forcibly open the communication passage 42, thereby controlling the discharge capacity of the variable displacement compressor 1 to a minimum.

[0039] (2) Coupling Mechanism 16 A rotor 14 is fixed to the drive shaft 8, and a pair of first arms 43 protrude from the rotor 14. One end 44A of a link arm 44 formed in a substantially cylindrical shape is guided inside the pair of first arms 43. Furthermore, a first linking pin 46 serving as a coupling means is inserted into a through hole formed in the first arm 43 and a through hole formed in the one end 44A of the link arm 44, so that the link arm 44 can rotate about the axis of the first linking pin 46 while being guided by the pair of first arms 43.

[0040] Furthermore, the first connecting pin 46 is pressed into and held in a through hole formed in the link arm 44, and a small gap is formed between the outer periphery of the first connecting pin 46 and the through hole formed in the first arm 43.

[0041] The other end 44B of the link arm 44 forms a pair of arms projecting from the cylindrical one end 44A, and a second arm 47 (arm of the present invention) projecting from the variable angle portion 11 of the swash plate 9 is guided inside the other end 44B. A second connecting pin 48 serving as a connecting means is inserted through a through hole formed in the other end 44B of the link arm 44 and a through hole formed in the second arm 47, thereby connecting the link arm 44 and the swash plate 9 (variable angle portion 11). The link arm 44 and the swash plate 9 (variable angle portion 11) can rotate relatively around the axis of the second connecting pin 48.

[0042] Furthermore, the second connecting pin 48 is press-fitted and held in the through hole of the second arm 47, and a small gap is formed between the outer periphery of the second connecting pin 48 and the through hole formed in the link arm 44.

[0043] The first arm 43, the second arm 47, the link arm 44, the first connecting pin 46, and the second connecting pin 48 constitute the connecting mechanism 16. Therefore, the swash plate 9 is connected to the rotor 14 fixed to the drive shaft 8 via the connecting mechanism 16, and rotates when subjected to the rotational torque of the rotor 14, and its inclination angle can be changed along the drive shaft 8.

[0044] (3) Adjustable Angle Portion 11 (Part 1) Next, the adjustable angle portion 11 of the embodiment will be described with reference to Figure 4. The adjustable angle portion 11 of the embodiment has three mounting holes 49, through which rivets 50 or the like are inserted to attach the adjustable angle portion 11 to the center of the swash plate 9. Alternatively, the adjustable angle portion 11 may be integrally formed with the center of the swash plate 9.

[0045] As described above, the saddle portion 12, which is a through-hole, is provided in the center of the variable angle portion 11. This saddle portion 12 is shaped so that the swash plate 9 can tilt within a range of maximum and minimum inclination angles relative to the drive shaft 8 inserted therein, thereby restricting the inclination angle of the swash plate 9. In this embodiment, a weight 51 is integrally formed only on one side of the line passing through the center of the second arm 47 (the arm in the present invention) and the center of the saddle portion 12 (the left side in FIG. 4 in this embodiment).

[0046] Therefore, in the variable angle portion 11 of this embodiment, one side (the left side as you face FIG. 4) of the line passing through the center of the second arm 47 and the center of the saddle portion 12 is heavier than the other side (the right side as you face FIG. 4). In other words, the weight distribution of the variable angle portion 11 is such that one side of the line passing through the center of the second arm 47 and the center of the saddle portion 12 is heavier than the other side. However, the weight of the entire variable angle portion 11 remains the same before and after the weight 51 is formed.

[0047] (4) Operation of the variable angle unit 11 when the drive shaft 8 rotates Next, with reference to Figures 5 and 6, we will explain the operation of the variable angle unit 11 when the drive shaft 8 rotates, with the above configuration. In Figure 5, the solid arrow indicates the direction of rotation of the drive shaft 8, the lower side of the variable angle unit 11 on the left side of Figure 5 indicates the side where the weight 51 is located, the upper side of the variable angle unit 11 on the right side of Figure 5 is the expansion side (suction stroke) and the lower side is the compression side (discharge stroke), and the hatched arrow indicates the force acting due to centrifugal force.

[0048] 5, when the drive shaft 8 rotates, the variable angle portion 11 also rotates together with the swash plate 9, generating centrifugal force in the variable angle portion 11. This centrifugal force is greater on the heavier side of the variable angle portion 11, i.e., the side where the weight 51 is provided, so the variable angle portion 11 receives a force that tends to lean in the direction indicated by the arrow in FIGS. 4 and 5 (one of the lines passing through the center of the second arm 47 and the center of the saddle portion 12), with the second arm 47, which is part of the connecting mechanism 16, as the fulcrum.

[0049] As a result, a specific point P on the inner wall of the variable angle portion 11 (on the right side, opposite the weight 51 in FIG. 4) is subjected to a load that presses it against the drive shaft 8. The pressing load (force) acting on the variable angle portion 11 due to this centrifugal force is shown in FIG. 6. The higher the rotation speed of the drive shaft 8, the greater the pressing load, and at 3000 rpm or higher, the pressing force reaches 10 N or more.

[0050] In this way, in the present invention, the variable angle portion 11 is configured so that a specific point P on the inner wall of the saddle portion 12 is pressed against the drive shaft 8 by the centrifugal force generated as the drive shaft 8 rotates, so that it is possible to suppress the adverse effects on the drive shaft 8 caused by wobble of the variable angle portion 11 and the resulting vibration and noise, regardless of the clearance between the saddle portion 12 and the drive shaft 8, i.e., regardless of the part precision. In addition, the inclination between the drive shaft 8 and the saddle portion 12 (the inclination perpendicular to the direction in which the swash plate 9 tilts) is also reduced, which stabilizes the sliding of the variable angle portion 11 on the drive shaft 8 and improves controllability.

[0051] Furthermore, if the weight of the entire variable angle portion 11 is kept constant before and after forming the weight 51, as in the embodiment, it is possible to suppress changes in the control gas due to a decrease in the weight of the variable angle portion 11. Note that, without forming the weight 51, it is also possible to change the shape (e.g., thickness) or material to achieve a weight distribution in which the variable angle portion 11 leans in a specific direction due to the centrifugal force generated by the rotation of the drive shaft 8. In this case, too, the weight of the entire variable angle portion 11 is kept constant before and after changing the weight distribution.

[0052] (5) Variable Angle Section 11 (Part 2) Next, Figure 7 shows another embodiment of the variable angle section 11. In this embodiment, weights 51 and 52 (a pair of weights) are integrally formed on one side and the other side of a line passing through the center of the second arm 47 and the center of the saddle section 12. One weight 51 (on the left side of Figure 7) has a different weight from the other weight 52 (on the right side); weight 51 is larger in size and weight than weight 52.

[0053] Even with this configuration, the centrifugal force generated as the drive shaft 8 rotates causes a specific point P on the inner wall of the saddle portion 12 of the variable angle portion 11 to be pressed against the drive shaft 8, thereby suppressing the adverse effects on the drive shaft 8 caused by the wobbling of the variable angle portion 11 and the resulting vibrations and noise.

[0054] In this example, the weight of the entire variable angle section 11 does not change before and after providing the weights 51 and 52. Furthermore, instead of providing the pair of weights 51 and 52 as described above, more weights may be provided so that the weights of the weights differ.

[0055] (6) Variable Angle Section 11 (Part 3) Here, even if the weight 51 has the same weight, the force that pulls the variable angle section 11 in a specific direction will differ depending on the position where it is formed. This will be explained using Figure 8. In Figure 8, the line that passes through the center of the second arm 47 and the center O of the saddle section 12 described above is designated as L1. When the weight 51 described above is provided at different positions A and B on the left side of line L1 (the left side of Figure 8), the centrifugal force Cf is the same.

[0056] However, when the component force Af at position A and the component force Bf at position B when the second arm 47 is used as the fulcrum are compared, Bf<Af, as shown in Figure 8. In other words, even when the same weight 51 is provided, the component force of the centrifugal force Cf when the second arm 47 is used as the fulcrum is smaller when the weight 51 is located closer to line L1.

[0057] Therefore, for example, a pair of identical weights 51 are provided on one side (left side) and the other side (right side) of line L1, but as shown by the dashed line in Figure 8, the position of the other weight 51 is provided at position B1, which is closer to line L1 than position A of the one weight 51. This position B1 is symmetrical to B with respect to line L1. In other words, the pair of weights 51 are provided at positions asymmetrical with respect to line L1.

[0058] As a result, the load Af-Bf causes the variable angle portion 11 to move to the left (one side) in Figure 8, achieving the same effect as in the previous embodiment. However, even in this case, the weight of the variable angle portion 11 as a whole remains the same before and after the weights 51 are installed.

[0059] It goes without saying that the specific shapes and values ​​shown in the above embodiments are not limited to those shown therein, and various modifications are possible without departing from the spirit of the present invention. In particular, in each embodiment, the weights, numbers, and mounting positions of the weights 51, 52 of the variable angle portion 11 are different on one side and the other side of the line (L1) passing through the center of the second arm 47 and the center of the saddle portion 12, but a combination of two of these, or all of them, may also be used.

[0060] REFERENCE SIGNS LIST 1 variable displacement compressor 2 cylinder block 2A cylinder bore 3 front housing 6 cylinder head 7 crank chamber 8 drive shaft 9 swash plate 11 variable angle portion 12 saddle portion 13 piston 14 rotor 16 connecting mechanism 31 shoe (conversion mechanism) 38 housing 47 second arm (arm) 51, 52 weight

Claims

1. A variable displacement compressor comprising a drive shaft, a swash plate rotated by the drive shaft, and a variable angle section provided on the swash plate and having a saddle section through which the drive shaft is inserted, the saddle section regulating the inclination angle of the swash plate, characterized in that the variable angle section is configured such that a specific point on the inner wall of the saddle section is pressed against the drive shaft by centrifugal force generated as the drive shaft rotates.

2. A variable displacement compressor as described in claim 1, characterized in that the weight distribution of the variable angle portion is set so that the variable angle portion leans in a specific direction due to centrifugal force generated as the drive shaft rotates.

3. A variable displacement compressor according to claim 1, wherein the variable angle portion has a weight, and the weight is provided at either position relative to an axis passing through the center of the saddle portion.

4. A variable displacement compressor according to claim 1, wherein the variable angle portion has at least a pair of weights, each weight being provided at an asymmetrical position with respect to an axis passing through the center of the saddle portion.

5. A variable displacement compressor according to claim 1, wherein said variable angle portion has at least a pair of weights, each weight having a different weight.

6. A variable displacement compressor according to any one of claims 1 to 5, characterized in that it comprises a piston disposed within a cylinder bore formed in a housing, a conversion mechanism for converting the rotation of the swash plate into reciprocating motion of the piston, a rotor fixed to the drive shaft, and a connecting mechanism for connecting the swash plate to the rotor in a tiltable manner, and the angle changing section has an arm that forms part of the connecting mechanism.

7. A variable displacement compressor as described in claim 1, comprising: pistons disposed within cylinder bores formed in a housing; a conversion mechanism for converting the rotation of the swash plate into the reciprocating motion of the pistons; a rotor fixed to the drive shaft; and a connecting mechanism for connecting the swash plate to the rotor so that the swash plate can tilt relative to the rotor, wherein the variable angle portion has an arm that constitutes part of the connecting mechanism, and the weights of one side and the other side of a line passing through the center of the arm and the center of the saddle portion are different.

8. A variable displacement compressor according to claim 7, characterized in that the variable angle section has weights, and at least one of the weight, number and mounting position of the weights differs on one side of a line passing through the center of the arm and the center of the saddle section.

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