JP2004028090A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a swash plate compressor for improving lubricity of internal components, and reducing a cost by improving the cooling capacity and reducing the amount of sealed oil. <P>SOLUTION: In the swash plate compressor, a shaft 52 comprises a communication hole 20 formed in the radial direction at a position between a rotor 67 and a rotary swash plate 69, and an axial passage 10 passing through from a center part of the communication hole 20 to an end part in the axial direction. Refrigerant gas from a crank chamber 41 to an intake chamber 42 is discharged via the communication passage 20 and the axial passage 10. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a compressor, and more particularly, to internal lubrication of a swash plate type compressor used in a vehicle air conditioner or the like.
[0002]
[Prior art]
Conventionally, a swash plate type compressor shown in FIG. 12 has been proposed (hereinafter, referred to as prior art 1). FIG. 12 is a sectional view showing a swash plate type compressor according to the related art 1. Referring to FIG. 12, this conventional swash plate type compressor 110 is called a single swash plate type compressor. The piston type compressor 110 is provided with a cylinder block 50 formed integrally with a casing, a crankcase 51 provided at one end of the cylinder block 50, and a valve plate 61 at the other end of the cylinder block 50. And a cylinder head 63.
[0003]
The cylinder block 50 is provided so as to extend along the length direction of the shaft 52 provided through the center of the swash plate type compressor 110 at equal angular intervals concentrically around the center bearing hole 50a. The cylinder bore 60 is provided. The valve plate 61 is provided between the cylinder block 50 and the cylinder head 63, and includes a suction valve and a discharge valve 113b (not shown).
[0004]
The crankcase 51 is provided with a boss portion 51b that protrudes cylindrically around the center axis. Around the boss 51b, a pulley 56 of a hollow ring having one end sealed and the other end opened is provided for transmitting a driving force from the driving mechanism to the shaft 52 via a bearing 57. One end of the pulley 56 is connected to a hub 59 provided on one end 52 a of the shaft 52 via a leaf spring 58. In FIG. 12, although the shaft 52 is directly driven by the pulley 56 of the driving source, an electromagnetic clutch or the like may be provided to turn on / off the driving force from the external driving source.
[0005]
The shaft 52 is provided between a center hole 51a provided in a boss portion 51b of the crankcase 51 and a bearing hole 50a provided in a central portion of the cylinder block 50 in the axial direction. It is rotatably supported by 53 and 54. Note that a member indicated by reference numeral 55 provided in the center hole 51a is a sealing portion (lip seal) for shutting off the crank chamber 41 from the outside of the compressor.
[0006]
Further, a rotor 67 is disposed adjacent to an inner surface 51c of the crankcase 51 of the shaft 52 via a thrust bearing 68, and one end surface of the rotor 67 is rotatably supported by the inner surface 51c of the crankcase 51. .
[0007]
A rotating swash plate (Cam Plate) 69 is provided around the shaft 57 on the other end side of the rotor 67. One end of the rotary swash plate 69 is provided with a protruding crank pin 69b, and penetrates a long hole 67a formed in a protruding portion protruding from the other end of the rotor 67. By the hinge mechanism formed by the pin 69b and the long hole 67b, the rotary swash plate 69 can be inclined in a direction along a plane including the axis.
[0008]
In the cylinder head 63, a suction chamber 42 for sucking a fluid to be compressed from the external refrigerant circuit and a discharge chamber 43 for discharging the compressed fluid to the external refrigerant circuit via a discharge port (not shown) are defined. Have been. In the cylinder head 63, a control valve mechanism 64 is provided. The control valve mechanism 64 is connected to the discharge chamber 43 via a first passage 65 formed in the cylinder head 63, while a second passage provided in the cylinder block 50, the valve plate 61 and the cylinder head 63. It communicates with the crankcase 41 via 66.
[0009]
A piston 62 is arranged in a cylinder bore 60 of the cylinder block 50. The piston 62 has a shoe holding portion 62a which is recessed toward the shaft side at an end opposite to the compression side, and an outer peripheral portion of the rotary swash plate 69 and both ends of the outer peripheral portion are provided in the shoe holding portion 62a. A pair of substantially hemispherical shoes 70, 70 are accommodated such that the flat surfaces are in sliding contact with the surfaces. A third passage 71 is provided in the cylinder block 50 and the valve plate 61 to communicate the bearing hole 50a with the suction chamber 42.
[0010]
In such a swash plate compressor 110, when the shaft 57 rotates, the rotor 67 rotates the rotating swash plate 69 via the hinge mechanisms 67b and 69b. Since the rotary swash plate 69 is inclined with respect to the shaft 52, when the rotary swash plate 69 rotates, the rotational movement is performed via the shoes 70, 70 housed in the shoe holding portion 62 a of the piston 62. Is converted into a reciprocating motion in the cylinder bore 60. Accordingly, when the piston 62 moves (retreats) in the cylinder bore 60 toward the crankcase 51 along the axial direction in FIG. 12, the refrigerant flows from the suction chamber 42 into the cylinder bore 60 via the suction hole 61a and the suction valve (not shown). When the gas is sucked and the piston 62 moves (forwards) toward the cylinder head 63 along the axial direction in FIG. 12, the sucked refrigerant gas is compressed and discharged to the discharge chamber 43 through the discharge valve 113b. Is discharged from an outlet (not shown) to an external refrigerant circuit (not shown).
[0011]
Here, refrigerant gas 103 containing lubricating oil leaking from the outer periphery of the piston 62 and the inner diameter of the cylinder bore 60 due to compression, and the discharge chamber 43 directly from the discharge chamber 43 via the first passage 65, the control valve mechanism 64, and the second passage 66. The supplied refrigerant gas 104 for controlling the volume flows into the crank chamber 41, then passes through the gap between the outer periphery of the shaft 52 and the bearing 53, passes through the rollers, reaches the bearing hole 50 a, and reaches the third passage 71. It is discharged to the suction chamber 42. At this time, the lubricating oil in the refrigerant gas reaches the suction chamber 42 without being separated. In addition, the circulation of the refrigerant gas in the crank chamber 41 is poor, and there is a problem in lubricity of the rotary swash plate 69 other than the grid-shaped hatched portions.
[0012]
In addition, there is a swash plate type compressor shown in FIG. 13 (hereinafter, referred to as conventional technology 2). As shown in FIG. 13, the swash plate type compressor 120 according to the prior art 2 is the same as the swash plate compressor 120 according to the prior art 1 shown in FIG. 12 except that a communication hole 101 and an axial passage 102 are provided in a shaft 52. It has a configuration. That is, a communication hole 101 is provided in the boss portion 52b of the shaft 52 in the radial direction from the outer peripheral surface of the shaft 52 in the vicinity of the radial bearing 59 provided in the central hole 51a and the rotor 67 fixed to the shaft 52. An axial passage 102 is provided from the center of the communication hole 101 to the end 52 b of the shaft 52 in the cylinder block 50.
[0013]
As shown in FIG. 13, a refrigerant gas 106 containing lubricating oil leaking from the outer periphery of the piston 62 and the inner diameter of the cylinder bore 60 due to compression, and a capacity control supplied directly from the discharge chamber 43 via the second passage 66 and the like. The refrigerant gas 107 flows into the crank chamber 41, then wraps around the outer periphery of the rotary swash plate 69, is guided from the thrust bearing 68 to the communication hole 101 provided in the shaft 52 and the axial passage 102, and flows into the bearing hole 50 a. It enters and is discharged to the suction chamber 42 through the communication hole 71. At this time, part of the lubricating oil in the refrigerant gas is separated by the centrifugal force due to the rotation of the shaft 52 in the communication hole 101 of the shaft 52, and is discharged to the crank chamber 41 without falling into the suction chamber 42.
[0014]
As a compressor having substantially the same function as that shown in FIG. 13, there is a compressor disclosed in Patent Document 1. The compressor shown in Patent Document 1 is different from that shown in FIG. 13 in that the positions of the discharge chamber and the suction chamber are interchanged, and a hole provided directly in the valve plate instead of the communication passage 71 is interposed. Although a configuration is provided in communication with the discharge chamber, the function is the same as that shown in FIG.
[0015]
[Patent Document 1]
JP 2000-283028 A
[Problems to be solved by the invention]
As described above, in the prior art 1, the lubricating oil in the refrigerant gas reaches the suction chamber 42 without being separated, and the circulation of the refrigerant gas in the crank chamber 41 is poor. Only a part of the end face on the cylinder bore side of the plate 69, that is, the grid-like hatched portion, was lubricated, and there was a problem in lubricity between the rotary swash plate 69 and the shoe 70.
[0017]
Further, the swash plate type compressor 120 according to the related art 2 has the improved thrust bearing 68 and the radial bearing 54 in circulation performance as compared with the related art 1, but the end surface of the rotary swash plate 69 on the side opposite to the cylinder bore, that is, Only the hatched portions indicated by the lattice hatches are lubricated, and there is a problem in lubricity between the rotary swash plate 69 and the shoes 70.
[0018]
As described above, any of the swash plate compressors of the prior arts 1 and 2 has a problem in lubrication of internal components in the crankcase. For this reason, the durability is reduced due to insufficient lubrication of the internal parts, the cost must be increased due to the need to set a large amount of oil in the initial compressor, and the cooling capacity is increased due to the increased oil circulation rate in the refrigeration circuit. There were drawbacks such as lowering.
[0019]
Therefore, a technical problem of the present invention is to provide a compressor, in particular, a swash plate type compressor, capable of improving lubrication injection of internal components and reducing the amount of filled oil.
[0020]
[Means for Solving the Problems]
According to the present invention, the suction chamber communicates between the crank chamber and the suction chamber to extract gas from the crank chamber to the suction chamber, and an extraction passage extends through the crank chamber and extends in the axial direction. A shaft provided with a passage and a communication hole, a rotary swash plate slidably mounted on the shaft, and a rotor fixedly mounted on the shaft and connected to the rotary swash plate via a hinge mechanism Wherein the axial passage extends in the shaft in the axial direction of the shaft, the communication hole communicates with the axial passage and forms a part of the bleed passage, and the rotor includes first and second air passages. Wherein the first side wall faces the rotary swash plate, and the communication hole is provided closer to the first side wall than to the second side wall. A compressor is obtained.
[0021]
Further, according to the present invention, in the compressor, the rotary swash plate includes a side wall facing the first side wall of the rotor, and the rotary swash plate has a maximum with respect to a plane perpendicular to the axial direction. The communication hole is inclined within an angle range between the inclination angle and the minimum inclination angle, and the communication hole is formed between the first side wall of the rotor and the rotation swash plate when the rotation swash plate is at the maximum inclination angle. A compressor is obtained, which is arranged between the compressor and the opposing side wall.
[0022]
Further, according to the present invention, in the compressor, the compressor may further include an extension pipe provided in the communication hole so as to extend in a length direction of the communication hole. .
[0023]
According to the present invention, in the compressor, the compressor is characterized in that the extension pipe has a linear shape, a curved shape, or a funnel shape.
[0024]
Further, according to the present invention, in any one of the compressors, the communication hole is provided to extend in a radial direction of the shaft.
[0025]
Further, according to the present invention, in any one of the compressors, the communication hole is provided so as to be inclined with respect to the axial direction of the shaft.
[0026]
Further, according to the present invention, in any one of the compressors, the communication hole has a conical shape in which a small-diameter portion is connected to the axial passage.
[0027]
According to the present invention, in any one of the compressors, the communication hole is a through hole.
[0028]
Furthermore, according to the present invention, in the compressor, in the compressor, the axial passage is connected to an intermediate portion of the communication hole.
[0029]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view of a compressor according to a first embodiment of the present invention, in which a rotary swash plate forms a maximum tilt angle with respect to a plane perpendicular to a shaft (maximum tilt angle), that is, a compression capacity is reduced. The state at the maximum is shown.
[0030]
Referring to FIG. 1, a compressor 100 according to a first embodiment of the present invention includes a cylinder block 50 and a crankcase 51 provided at a front end of the cylinder block 50 and defining a crank chamber 41. The cylinder block 50 and the crankcase 51 have a bearing hole 50a and a center hole 51a, respectively. Radial bearings 53 and 54 are provided in the bearing hole 50a and the center hole 51a, respectively, and rotatably support the shaft 52. ing. The gap between the center hole 51 a and the shaft 52 is sealed by a lip seal 55 located closer to the front end of the shaft 52 than the radial bearing 54. The shaft 52 extends in the axial direction of the compressor 100 through the crank chamber. A boss 51b is formed in the crankcase 51. A pulley 56 is rotatably supported by a radial bearing 57 around the boss 51b. The pulley 56 is connected to a drive source (not shown) by a belt (not shown). One end of the shaft 52 passes through the crankcase, and is connected to the pulley 56 by a leaf spring 58 and a coupling member 59. Although FIG. 1 shows a configuration in which the shaft 52 is directly driven by the pulley 56, an electromagnetic clutch or the like may be provided to turn on / off (ON, OFF) the external drive source.
[0031]
The cylinder block 50 is provided with a plurality of cylinder bores 60 extending from the rear end of the cylinder block 50 to the crank chamber 41 in the axial direction. The number of the cylinder bores 60 is an odd number, for example, seven in the illustrated example.
[0032]
A piston 62 is inserted into the cylinder bore 60 so that the piston 62 can slide back and forth in the axial direction.
[0033]
The valve plate 61 further has a plurality of pairs of through holes 61a and 61b between the front end face and the rear end face. Each pair of through holes functions as a pair of suction holes 61 a and discharge holes 61 b, and is provided corresponding to the cylinder bore 60. A cylinder head 63 is provided on a rear end surface of the valve plate 61. The cylinder head 63 defines a suction chamber 42 and a discharge chamber 43 in cooperation with the valve plate 61. In the cylinder head 63, a control valve mechanism 64 is provided. The control valve mechanism 64 opens and communicates with the suction chamber 42, and is connected to the discharge chamber 43 via a first passage 65 formed in the cylinder head 63. On the other hand, the control valve mechanism 64 communicates with the crank chamber 41 via a second passage 66 provided in the cylinder block 50, the valve plate 61, and the cylinder head 63. In other words, the crank chamber 41 is connected to the discharge chamber 43 via the control valve mechanism 64.
[0034]
In the crank chamber 41, a rotor 67 is mounted and fixed so as to rotate with the rotation of the shaft 52. The rotor 67 is axially supported by the crankcase 51 via a thrust bearing 68. Further, the rotor 67 has a tab or arm portion 67a having a long hole 67b. A rotating swash plate 69 is provided on the shaft 52 so as to be slidable in the axial direction. The rotary swash plate 69 has a tab or arm portion 69a provided with a pin 69b. The pin 69b of the rotary swash plate 69 is inserted into the long hole 67b of the rotor 67. That is, the rotary swash plate 69 is connected to the rotor 67 via a hinge mechanism including a pin 69b and a long hole 67b. With this hinge mechanism, the swash plate 69 can change its inclination with respect to a plane perpendicular to the axial direction of the shaft 52 within a predetermined angle range between the maximum inclination angle and the minimum inclination angle. Here, the maximum tilt angle is the tilt angle of the rotary swash plate when the compression capacity is maximum, while the minimum tilt angle is the tilt angle of the rotary swash plate when the compression capacity is minimum.
[0035]
A plurality of pairs of shoes 70 are provided on the outer peripheral portion of the rotating swash plate 69 at equal angular positions. The outer peripheral portion of the rotary swash plate 69 is mounted between the shoes 70 so as to be slidable between the pair of shoes 70. The pair of shoes 70 is supported by a shoe support 62 a provided on the piston 62. The plurality of pairs of shoes 70 slide on the inner surface of each shoe support 62a. Therefore, the rotating swash plate 69 is connected to the piston 62 via the pair of shoes 70.
[0036]
In the embodiment of the present invention, the shaft 52 is provided with the axial passage 10 and the communication hole 20. The axial passage 10 extends from the rear end 52 b along the axial direction of the shaft 52 and is provided in the shaft 52. The axial passage 10 has a predetermined length shorter than the length of the shaft 52 so as not to reach the front end 52a of the shaft 52 on the boss 51b side. The predetermined length is determined by the position of the communication hole 20 as described later. The axial passage 10 communicates with a bearing hole 50 a of the cylinder block 50 at a rear end 52 b of the shaft 52. The bearing hole 50 a communicates with the cylinder block 50 and the suction chamber 42 via a third passage 71 provided continuously with the valve plate 61. The communication hole 20, the axial passage 10, the bearing hole 50 a of the cylinder block 50, and the third passage 71 form a bleed passage that communicates between the crank chamber 41 and the suction chamber 42.
[0037]
In the embodiment of the present invention, the communication hole 20 is located between the rotor 67 and the rotary swash plate 69 when the rotary swash plate 69 is in the maximum inclined state. More specifically, the rotor 67 has a rear side wall 67c and a front side wall 67d, while the rotating swash plate 69 also has a front side wall 69c and a rear side wall 69d. The rear wall 67c of the rotor 67 is located at the position P1 of the shaft 52. The front side wall 69c of the rotary swash plate 69 is at the position P2 on the shaft 52 when the rotary swash plate 69 is at the maximum tilt angle. In the embodiment of the present invention, the position of the communication hole 20 is between the position P1 and the position P2, and the position of the communication hole 20 provides effective lubricating oil distribution as described later. However, the position of the communication hole 20 does not limit the present invention. For example, the communication hole 20 may be located between the position P2 which is the position of the rotary swash plate 69 and the position P3 which is the position of the rear side wall 69d when the rotary swash plate 69 is in the maximum inclined state. The communication hole 20 may be located between the position P3 and the position P4. The position P4 is the position of the front side wall 69c in the case where the rotary swash plate is in the minimum inclined state. Actually, the rear wall 67c of the rotor 67 is closer to the communication hole 20 than the front wall 67d of the rotor 67, and the communication hole 20 is not located on the front side of the rotor 67.
[0038]
In the structure described above, there are two general movements of the refrigerant gas. The movement of one refrigerant gas is the movement of the refrigerant gas supplied from the discharge chamber 43. The supplied refrigerant gas enters the crank chamber 41 and moves along the flow of the refrigerant gas indicated by F1. Then, the supplied refrigerant gas passes through the rotary swash plate 69 and enters the communication hole 20 as shown by the flow F2 of the refrigerant gas in FIG. The supplied refrigerant gas moves along the flow of the refrigerant gas as indicated by arrows F5 and F6, reaches the bearing hole 50a, enters the third passage 71, and reaches the suction chamber 42. On the other hand, as indicated by the flow F3 of the refrigerant gas in the crank chamber 41, the blow-by gas leaks from between the piston 62 and the cylinder bore 60 when the refrigerant gas is compressed. Then, the blow-by gas passes through the rotary swash plate 69 and enters the communication hole 20 as shown by the flow F4 of the refrigerant gas. Then, like the refrigerant gas supplied from the discharge chamber 43, the blow-by gas moves along the refrigerant gas flows F5 and F6, reaches the bearing hole 50a, enters the third passage 71, and reaches the suction chamber 42. . Since the lubricating oil contained in the refrigerant gas moves along with the movement of the refrigerant gas, the lubricating oil moves along the movement of the refrigerant gas. Effective lubrication is achieved.
[0039]
Further, the communication hole 20 has an effect of separating the refrigerant gas and the lubricating oil. The refrigerant gas is drawn into the communication hole 20 because there is a pressure difference between the suction chamber 42 and the crank chamber 41.
[0040]
However, due to the centrifugal force generated by the rotation of the shaft 52, part of the lubricating oil separated from the refrigerant gas and adhered to the wall around the communication hole 20 is dispersed around the shaft 52. The lubricating oil dispersion due to the centrifugal force forms another lubricating oil movement, so that effective lubrication of the moving parts in the crankcase 41 can be achieved. In addition, since the communication hole 20 always communicates with the crank chamber 41, the position of the communication hole 20 is preferably located between the position P1 and the position P2.
[0041]
FIG. 2 is a side view of a shaft of the swash plate type compressor of FIG. FIG. 3 is a sectional view showing an example of the shaft of FIG. Referring to FIGS. 2 and 3, in the embodiment of the present invention, the communication hole 20 is a straight through hole formed in the shaft 52. The communication hole 20 extends in the radial direction of the shaft 52. The axial passage 10 is connected to the center of the communication hole 20. Since the communication hole 20 is a straight through hole, it can be easily formed.
[0042]
FIG. 4 is a view showing a modified example of the shaft of FIG. FIG. 5 is a partially cutaway side view of the shaft of FIG. FIG. 6 is a side view showing another modified example of the shaft of FIG. FIG. 7 is a partially cutaway side view of the shaft of FIG.
[0043]
The direction of lubricating oil dispersion depends on the inner wall that defines the communication hole 20. Considering the lubricating oil dispersion direction, for example, the communication hole 21 may extend obliquely with respect to the axial direction of the shaft 52 as shown in FIGS. It may be formed as a special communication hole 22 having a conical shape with a small diameter portion connected thereto. In addition, the special communication hole 22 may be a combination of conical holes such that the small diameter portions of the conical holes face each other as shown in FIGS. 6 and 7.
[0044]
FIG. 8 is a partial side sectional view of a pipe inserted into a shaft according to the second embodiment of the present invention. FIG. 9 is a partial side sectional view showing a modification of the pipe of FIG. FIG. 10 is a partial side sectional view showing another modified example of the pipe of FIG.
[0045]
The lubricating oil and the refrigerant gas separation and lubricating oil dispersion range depend on the distance between the center of the shaft 52 and the open end of the communication hole 20. In order to more effectively separate the lubricating oil and the refrigerant gas, as shown in FIG. 8, the compressor according to the second embodiment further has a pipe 30 attached to the communication hole 20. The pipe 30 extends the length of the communication hole 20. Since the pipe 30 protrudes from the shaft 52, in this case, the communication hole 20 needs to be located between the position P1 and the position P2. Otherwise, the pipe 30 may hinder the sliding operation of the rotary swash plate 69.
[0046]
In FIG. 8, the pipe 30 is provided in a half of the communication hole 20, but another pipe may be provided in the other half of the communication hole. The shape of the pipe can be varied if the pipe provides a suitable extension of the communication hole 20. For example, a bent tube 31 shown in FIG. 9 or a funnel-shaped tube 32 shown in FIG. 10 can be used to extend the communication hole 20.
[0047]
FIG. 11 is a partially cutaway side view of a shaft according to a third embodiment of the present invention. Referring to FIG. 11, the communication hole 23 according to the third embodiment does not penetrate the shaft 52 and communicates in one radial direction between the axial passage 10 and the crank chamber 41. The effective length of the communication hole 23 for gas oil separation is the same as that according to the first embodiment.
[0048]
In the above-described embodiment, in order to make the flows F1 to F6 of the refrigerant gas effective, the gap between the shaft 52 and the radial bearing 53 is preferably as narrow as possible in consideration of the smooth rotation of the shaft 52.
[0049]
【The invention's effect】
As described above, according to the present invention, the lubricating properties of the internal components in the crank chamber are improved, the durability is improved, the amount of oil to be sealed in the initial compressor can be reduced, and the swash plate type compression leading to cost reduction can be achieved. Machine can be provided.
[0050]
Further, according to the present invention, the oil circulation rate in the refrigeration circuit can be suppressed low, and a swash plate compressor capable of improving the cooling capacity can be provided.
[Brief description of the drawings]
FIG. 1 is a sectional view showing a swash plate type compressor according to a first embodiment of the present invention.
FIG. 2 is a side view of a shaft of the swash plate compressor of FIG.
FIG. 3 is a sectional view showing an example of the shaft of FIG. 2;
FIG. 4 is a view showing a modification of the shaft of FIG. 2;
FIG. 5 is a partially cutaway side view of the shaft of FIG. 4;
FIG. 6 is a side view showing another modified example of the shaft of FIG. 2;
FIG. 7 is a partially cutaway side view of the shaft of FIG. 6;
FIG. 8 is a partial side sectional view of a pipe inserted into a shaft according to a second embodiment of the present invention.
FIG. 9 is a partial side sectional view showing a modified example of the pipe of FIG. 8;
FIG. 10 is a partial side sectional view showing another modified example of the pipe of FIG. 8;
FIG. 11 is a partially cutaway side view of a shaft according to a third embodiment of the present invention.
FIG. 12 is a cross-sectional view showing a swash plate type compressor according to Prior Art 1.
FIG. 13 is a cross-sectional view showing a swash plate type compressor according to Prior Art 2.
[Explanation of symbols]
10 Axial passages 20, 21, 22, 23 Communication holes 30, 31, 32 Pipe 41 Crank chamber 42 Suction chamber 43 Discharge chamber 50 Cylinder block 51 Crank case 51b Boss 52 Shaft 53, 54 Radial bearing 58 Leaf spring 59 Hub 60 Cylinder bore 61 Valve plate 62 Piston 62a Shoe holding part 63 Cylinder head 67 Rotor 67a Long hole 68 Thrust bearing 69 Rotating swash plate 69a Crank pin 70 Shoe 100, 110, 120 Compressor

Claims (9)

A crank chamber, a suction chamber, a bleed passage that communicates between the crank chamber and the suction chamber, and conveys gas from the crank chamber to the suction chamber; A shaft provided with a communication hole, a rotating swash plate slidably mounted on the shaft, and a rotor fixedly mounted on the shaft and connected to the rotating swash plate via a hinge mechanism. Wherein the axial passage extends into the shaft in the axial direction of the shaft, the communication hole communicates with the axial passage and forms a part of the bleed passage, and the rotor includes first and second side walls. Wherein the first side wall faces the rotary swash plate, and the communication hole is provided closer to the first side wall than the second side wall. . 2. The compressor according to claim 1, wherein the rotary swash plate has a side wall facing the first side wall of the rotor, and the rotary swash plate has a maximum tilt angle and a minimum tilt angle with respect to a plane perpendicular to the axial direction. The communication hole is inclined within an angle range between the inclination angle and the position of the communication hole between the first side wall of the rotor and the opposed side wall of the rotary swash plate when the rotary swash plate is at the maximum inclination angle. A compressor, which is arranged between the compressors. 3. The compressor according to claim 2, further comprising an extension pipe provided in said communication hole so as to extend in a length direction of said communication hole. 4. The compressor according to claim 3, wherein the extension pipe has a straight shape, a curved shape, or a funnel shape. 5. The compressor according to claim 1, wherein the communication hole extends in a radial direction of the shaft. 6. 5. The compressor according to claim 1, wherein the communication hole extends obliquely with respect to an axial direction of the shaft. 6. The compressor according to any one of claims 1 to 4, wherein the communication hole has a conical shape with a small diameter portion connected to the axial passage. The compressor according to any one of claims 1 to 7, wherein the communication hole is a through hole. 9. The compressor according to claim 8, wherein the axial passage communicates with an intermediate portion of the communication hole.

Images