JP2009162061A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent movement of a piston from being suppressed by contacting the piston with upper and lower wall surfaces of a cylinder chamber in a compressor. <P>SOLUTION: The piston 62 in which a roller 66 arranged at the inside of the cylinder chamber 71 is integrated with a blade 67 is moved along a side wall surface 71a such that an outer peripheral surface 66a of the roller 66 is abutted on the side wall surface 71a of the cylinder chamber 71. In the state that the outer peripheral surface 66a is abutted on a portion adjacent to a downstream side in a movement direction of the roller 66 of an introduction port 71b on the side wall surface 71a of the cylinder chamber 71 of the outer peripheral surface 66a of the roller 66, three grooves 66c extending in a vertical direction are formed at an area 66d for partitioning a low pressure chamber 71c. The groove 66c does not reach to upper and lower ends of the roller 66, and further, the depth Dm is 1/2 or more of a distance Dr of the outer peripheral surface 66a of the roller 66 and an inner peripheral surface 66, however, it is not penetrated to the inner peripheral surface 66b. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a compressor that compresses a refrigerant.

  In the compressor described in Patent Document 1, a piston in which a roller and a blade are integrally formed is arranged inside a cylinder chamber formed inside the cylinder, and the piston makes the cylinder chamber a suction chamber (low-pressure chamber). Chamber) and discharge chamber (high pressure chamber). Then, the roller moves along the side wall surface while contacting the side wall surface of the cylinder chamber, whereby the volume of the discharge chamber increases and the refrigerant in the discharge chamber is compressed.

JP 2004-124948 A

  Here, in the compressor described in Patent Document 1, since the temperature of the refrigerant rises as the refrigerant in the discharge chamber is compressed, the portion that becomes the wall of the discharge chamber of the cylinder becomes a high temperature and undergoes a significant linear expansion deformation. On the other hand, since the refrigerant is not compressed in the suction chamber, the temperature of the portion that becomes the wall of the suction chamber of the cylinder is lower than that of the portion that becomes the wall of the discharge chamber. Since the piston is disposed between the discharge chamber and the suction chamber, the temperature is between the temperature of the portion that becomes the wall of the discharge chamber and the temperature of the portion that becomes the wall of the suction chamber. The expansion deformation amount is an intermediate deformation amount between the expansion deformation amounts of the two portions. Therefore, due to the difference in the linear expansion amount, the portion on the discharge chamber side of the piston does not contact the upper and lower wall surfaces of the cylinder chamber, but the portion on the suction chamber side contacts the upper and lower wall surfaces of the cylinder chamber. As a result, the movement of the piston may be hindered.

  An object of the present invention is to provide a compressor in which the piston does not come into contact with the upper and lower wall surfaces of the cylinder chamber and the movement of the piston is not hindered.

  A compressor according to a first aspect of the present invention is disposed in a sealed space, and is provided on a cylinder having a cylinder chamber therein, a piston disposed in the cylinder chamber, and a side wall surface of the cylinder chamber. And has an inlet for introducing a refrigerant into the cylinder chamber from the outside, and a discharge port for discharging the refrigerant from the cylinder chamber to the sealed space, and the piston is configured in an annular shape The outer circumferential surface of the cylinder chamber moves along the side wall surface so as to contact the side wall surface of the cylinder chamber, and the cylinder chamber is compressed with the refrigerant and the compressed refrigerant is discharged from the discharge port. A high-pressure chamber that discharges into a sealed space and a low-pressure chamber into which refrigerant is introduced from the introduction port, and a roller that changes the volume of the high-pressure chamber and the low-pressure chamber are formed integrally with the roller. And a blade that extends outward from the outer peripheral surface of the roller and divides the cylinder chamber into the high-pressure chamber and the low-pressure chamber together with the roller, and the outer peripheral surface of the roller is the cylinder chamber Of the portion defining the low-pressure chamber on the outer peripheral surface of the roller, except for the upper end and the lower end thereof, in a state where it is in contact with the portion of the side wall surface adjacent to the downstream side in the moving direction of the roller. At least one of the concave portion and the convex portion is formed at least in part.

  In this compressor, at least one of a concave portion and a convex portion is formed in the portion of the roller, and the surface area of the outer peripheral surface of the roller is increased in this portion, so that the portion near the concave portion and the convex portion of the piston However, it is efficiently cooled by the refrigerant introduced into the low pressure chamber from the inlet. Thereby, the amount of linear expansion deformation in the low pressure chamber side portion of the piston is reduced, and it is possible to reliably prevent the piston from contacting the upper and lower wall surfaces of the cylinder chamber.

  Moreover, in this compressor, since the recessed part and the convex part are not provided at the upper and lower ends of the outer peripheral surface of the roller, it is possible to suppress the lubricating oil from flowing into the low pressure chamber from the upper and lower ends of the roller.

  A compressor according to a second aspect of the present invention is the compressor according to the first aspect of the present invention, wherein the concave portion is formed on the outer peripheral surface of the roller, and the concave portion does not penetrate to the inner peripheral surface of the roller. It is characterized by that.

  In this compressor, it is possible to prevent the lubricating oil from flowing into the low pressure chamber from the inner portion of the roller via the recess.

  A compressor according to a third aspect of the present invention is the compressor according to the second aspect of the present invention, wherein the depth of the concave portion is 1/2 or more of the distance between the outer peripheral surface and the inner peripheral surface of the roller. It is characterized by that.

  In this compressor, since the recess extends deep inside the roller, the piston can be reliably cooled.

  A compressor according to a fourth aspect of the present invention is the compressor according to the second or third aspect of the present invention, characterized in that the recess extends along the outer peripheral surface of the roller to form a groove.

  In this compressor, since the concave portion forms a groove along the outer peripheral surface of the roller, the surface area of the roller becomes sufficiently large in the portion where the concave portion is formed, and the piston can be reliably cooled.

  As described above, according to the present invention, the following effects can be obtained.

  In the first invention, at least one of the concave portion and the convex portion is formed on the roller, and since the surface area of the outer peripheral surface of the roller is increased in this portion, the portion near the concave portion and the convex portion of the piston is It is efficiently cooled by the refrigerant introduced into the low pressure chamber from the inlet. Thereby, the amount of linear expansion deformation in the low pressure chamber side portion of the piston is reduced, and it is possible to reliably prevent the piston from contacting the upper and lower wall surfaces of the cylinder chamber.

  Further, in the first invention, since the concave portion and the convex portion are not provided at the upper and lower ends of the outer peripheral surface of the roller, it is possible to suppress the lubricating oil from flowing into the low pressure chamber from the upper and lower ends of the roller.

  In the second invention, it is possible to prevent the lubricating oil from flowing into the low pressure chamber from the inner portion of the roller via the recess.

  In the third aspect of the invention, since the recess extends deep inside the roller, the piston can be reliably cooled.

  In the fourth invention, since the concave portion forms a groove along the outer peripheral surface of the roller, the surface area of the roller becomes sufficiently large in the portion where the concave portion is formed, and the piston can be reliably cooled.

  Embodiments of a compressor according to the present invention will be described below with reference to the drawings.

  FIG. 1 is a schematic configuration diagram of a compressor according to the present embodiment. The compressor 1 is, for example, a compressor used in an air conditioner such as an air conditioner. The compressor 1 compresses the refrigerant from which moisture has been removed and is introduced from the accumulator 2, and is discharged from a discharge passage 25 disposed at the upper end portion thereof. Discharge the compressed refrigerant. As shown in FIG. 1, the compressor 1 includes a casing 11, a motor 12, and a compression mechanism 13.

  The casing 11 includes a body 21, a top 22 and a bottom 23. The trunk | drum 21 is a substantially cylindrical member extended in the up-down direction, The upper and lower ends are opening. In addition, two connection ports 24 are formed on the side surface of the body 21 along the vertical direction to which the discharge pipe 2a for discharging the refrigerant of the accumulator 2 is connected at the lower right end. The top 22 is a member that closes the opening at the upper end of the body 21. The top 22 is provided with the discharge channel 25 described above. The bottom 23 is a member that closes the opening at the lower end of the body 21. In the casing 11, a sealed space 26 surrounded by the body 21, the top 22, and the bottom 23 is formed.

  The motor 12 is disposed in the sealed space 26 and has a stator 31 and a rotor 32. The stator 31 is fixed to the inner wall surface of the body 21. The rotor 32 is disposed on the radially inner side of the stator 31, and an upper end portion of a shaft 60 extending in the vertical direction is fixed to a substantially central portion thereof. In the motor 12, the rotor rotates together with the shaft 60 by the magnetic force generated between the stator 31 and the rotor 32. Note that the configuration of the stator 31 and the rotor 32 is the same as that of a conventional motor, and thus detailed description thereof is omitted here.

  The compression mechanism 13 is disposed in the sealed space 26 and is located below the motor 12. The compression mechanism 13 is a so-called swing type compression mechanism, and includes a cylinder 61, a piston 62, a front head 63, a middle plate 64, and a rear head 65 as shown in FIG. FIG. 2 is a plan view showing the configuration of the cylinder 61 and the piston 62 of FIG. 1 and their operations. FIG. 3 is a perspective view of the piston 62 of FIG.

  As shown in FIGS. 1 to 3, the two cylinders 61 are arranged along the vertical direction of FIG. 1, and a substantially circular cylinder chamber in a plan view that penetrates the cylinder 61 in the vertical direction at a substantially central portion thereof. 71 is formed. The upper and lower openings of the cylinder chamber 71 of the cylinder 61 disposed above are closed by the front head 63 and the middle plate 64, respectively. On the other hand, the openings at the upper and lower ends of the cylinder chamber 71 of the cylinder 61 disposed below are closed by the middle plate 64 and the rear head 65, respectively.

  Further, in the cylinder 61, a blade storage space 75 which is connected to the cylinder chamber 71 and extends in the vertical direction in FIG. Is formed.

  Further, the cylinder 61 is formed with an introduction flow path 72 extending rightward in FIG. 1 from the introduction port 71b formed in the right side portion of the side wall surface 71a of the cylinder chamber 71 in FIG. The discharge pipe 2 a of the accumulator 2 connected to is connected to the introduction flow path 72. Thereby, the refrigerant introduced into the compressor 1 from the accumulator 2 flows into the cylinder chamber 71 (more specifically, a low-pressure chamber 71c described later) from the introduction port 71b via the introduction flow path 72.

  The piston 62 has a roller 66 and a blade 67. The roller 66 is formed in an annular shape in plan view, and is disposed inside the cylinder chamber 71. Further, three grooves 66c (concave portions) are formed in a region 66d, which will be described later, of the outer peripheral surface 66a of the roller 66. The groove 66c will be described in detail later.

  The shaft 60 described above penetrates the roller 66 in the vertical direction, and an eccentric portion 60 a provided in the middle of the shaft 60 whose center axis is deviated from the center axis of the shaft 60 is a space inside the roller 66. It is inset. Thereby, in the piston 62, when the shaft 60 rotates, the roller 66 causes its outer peripheral surface 66a to abut against the side wall surface 71a of the cylinder chamber 71 as shown in FIGS. 2 (a) to 2 (d). Then, it moves in the clockwise direction in FIG. 2 along the side wall surface 71a.

  As the piston 62 moves in this manner, the cylinder chamber 71 is divided into the low pressure chamber 71c and the high pressure chamber 71d by the piston 62 (roller 66 and blade 67), and the volumes of the low pressure chamber 71c and the high pressure chamber 71d change. 2B, the outer peripheral surface 66a of the roller 66 is in contact with the portion adjacent to the downstream side of the introduction port 71b in the side wall surface 71a of the cylinder chamber 71 with respect to the moving direction of the roller 66. After that, until the state shown in FIG. 2D is reached, the volume of the high-pressure chamber 71d is reduced and the refrigerant in the high-pressure chamber 71d is compressed. When the state shown in FIG. 2D is reached, the refrigerant compressed to a predetermined pressure or higher in the high pressure chamber 71 d is discharged from the discharge port 74 to the sealed space 26. During this time, the refrigerant to be compressed next is introduced into the low pressure chamber 71c from the introduction port 71b. By repeating the operation as described above, the compressed refrigerant accumulates in the sealed space 26, and the refrigerant accumulated in the sealed space 26 is discharged to the outside from the discharge passage 25.

  Here, of the three grooves 66c described above, the outer peripheral surface 66a of the roller 66 is connected to the moving direction of the roller 66 (FIG. 2 of the side wall surface 71a) as shown in FIG. (A clockwise direction in FIG. 4), the region 66d is defined in the low pressure chamber 71c when it comes into contact with a portion of the side wall surface 71a of the cylinder chamber 71 adjacent to the downstream side of the introduction port 71b. These three grooves 66c extend in the vertical direction so as not to reach the upper end and the lower end of the roller 66, respectively, and are arranged along the outer peripheral surface 66a of the roller 66 (the outer peripheral surface 66a of the roller). Of the portion defining the low-pressure chamber 71c of the other than the upper and lower ends thereof. 2B and 3, a portion where the outer peripheral surface 66 a of the roller 66 is in contact with the side wall surface 71 a of the cylinder chamber 71 in the state of FIG. .

  Further, as shown in FIG. 2A, the depth Dm of the groove 66c is ½ or more of the distance Dr between the outer peripheral surface 66a and the inner peripheral surface 66b of the roller 66. It does not penetrate to the peripheral surface 66b.

  FIGS. 4A and 4B are diagrams showing the state of linear expansion and deformation of the cylinder 61 and the piston 62 when the refrigerant is compressed in the compression mechanism 13, where FIG. 4A shows the present embodiment, and FIG. As shown, the groove 66c is not formed.

  As described above, when the compression of the refrigerant is performed in the compression mechanism 13, the temperature of the refrigerant in the high pressure chamber 71d is increased due to the compression, so the temperature of the portion of the cylinder 61 that becomes the wall of the high pressure chamber 71d is Higher than other parts. On the other hand, since the refrigerant is not compressed in the low pressure chamber 71c, the temperature of the portion of the cylinder 61 that becomes the wall of the low pressure chamber 71c is lower than the temperature of the portion that becomes the wall of the high pressure chamber 71d. Since the piston 62 is disposed between the high pressure chamber 71d and the low pressure chamber 71c, the temperature of the portion of the cylinder 61 that becomes the wall of the high pressure chamber 71d and the temperature of the portion of the cylinder 61 that becomes the wall of the low pressure chamber 71c. The temperature is intermediate to the temperature.

  As a result, as shown in FIG. 4, the portion of the cylinder 61 that becomes the wall of the high pressure chamber 71d (the portion on the left side in FIG. 4) undergoes linear expansion deformation more than the portion that becomes the wall of the low pressure chamber 71c. The linear expansion deformation amount is an intermediate deformation amount between the linear expansion deformation amount of the portion that becomes the high pressure chamber 71d of the cylinder 61 and the linear expansion deformation amount of the portion that becomes the wall of the low pressure chamber 71c. Therefore, due to the difference in the amount of linear expansion deformation, the portion of the roller 66 on the high pressure chamber 71d side does not come into contact with the upper and lower wall surfaces of the cylinder chamber 71 (that is, the front head 63, the middle plate 64, and the rear head 65). However, as shown in FIG. 4B, when the groove 66 c is not formed in the roller 66, the portion of the piston 62 on the low pressure chamber 71 c side comes into contact with the upper and lower wall surfaces of the cylinder chamber 71, and the piston 62 May be hindered.

  However, in this embodiment, as shown in FIG. 4A, since the groove 66c is formed in the roller 66, the outer peripheral surface 66a of the roller 66 has an increased surface area in the region 66d. The portion in the vicinity of the region 66d is efficiently cooled by the refrigerant flowing into the low pressure chamber 71c from the introduction port 71b. As a result, the amount of linear expansion and deformation of the portion of the piston 62 on the low pressure chamber 71 c side is reduced, and the piston 62 does not come into contact with the upper and lower wall surfaces of the cylinder chamber 71.

  Furthermore, since the groove 66c extends along the outer peripheral surface 66a of the roller 66, the surface area in the region 66d of the outer peripheral surface 66a of the roller 66 is sufficiently large, and the portion of the piston 62 on the low pressure chamber 71c side is the low pressure chamber. It is reliably cooled by the refrigerant flowing into 71c.

  In addition, the depth of the groove 66c is ½ or more of the distance Dr between the outer peripheral surface 66a and the inner peripheral surface 66b of the roller 66, and the groove 66c extends deep inside the roller 66. A portion of 62 on the low pressure chamber 71c side is further efficiently cooled by the refrigerant flowing into the low pressure chamber 71c.

  Furthermore, although lubricating oil flows between the shaft 60 and the roller 66, the groove 66c does not reach the upper and lower ends of the roller 66, so that the sealing performance at the upper and lower ends of the roller 66 is maintained, and It is possible to suppress the lubricating oil from flowing into the low pressure chamber 71c from the end. In addition, since the groove 66c does not penetrate the roller 66, the lubricating oil does not flow into the low pressure chamber 71c through the groove 66c.

  As described above, in the compressor 1 of the present embodiment, the groove 66c is formed in the region 66d of the outer peripheral surface 66a of the roller 66, and the surface area of the outer peripheral surface 66a of the roller 66 is increased in this portion. Therefore, the portion in the vicinity of the groove 66c of the piston 62 is efficiently cooled by the refrigerant introduced into the low-pressure chamber 71c from the introduction port 71b. Thereby, the amount of linear expansion deformation in the portion of the piston 62 on the low pressure chamber 71c side is reduced, and the piston 62 can be reliably prevented from coming into contact with the upper and lower wall surfaces of the cylinder chamber 71.

  Further, since the groove 66c does not extend to the upper and lower ends of the outer peripheral surface 66a of the roller 66, it is possible to suppress the lubricating oil from flowing into the low pressure chamber 71c from the upper and lower ends of the roller 66.

  Further, the depth Dm of the groove 66c is ½ or more of the distance Dr between the outer peripheral surface 66a and the inner peripheral surface 66b of the roller 66, and the groove 66c extends deep inside the roller 66. Can be reliably cooled.

  Furthermore, since the groove 66c does not penetrate to the inner peripheral surface 66b of the roller 66, the lubricating oil can be prevented from flowing into the low pressure chamber 71c through the groove 66c.

  Further, since the groove 66c extends in the vertical direction along the outer peripheral surface 66a of the roller 66, the surface area in the region 66d of the outer peripheral surface 66a of the roller 66 becomes sufficiently large, and the piston 62 can be reliably cooled.

  As mentioned above, although embodiment of this invention was described based on drawing, specific structure is not restricted to these embodiment, It can change in the range which does not deviate from the summary of invention.

  In the above-described embodiment, the groove 66c extending in the vertical direction is formed in the region 66d of the outer peripheral surface 66a of the roller 66 as the recess, but the shape of the recess is not limited thereto. In one modified example, as shown in FIG. 5, each of the regions 66 d of the outer peripheral surface 66 a of the roller 66 extends along the circumferential direction of the outer peripheral surface 66 a of the roller 66 and is arranged in the vertical direction. Two grooves 81c (concave portions) are formed (Modification 1). In another modification, as shown in FIG. 6, both the groove 66 c similar to the embodiment and the groove 81 c similar to Modification 1 overlap each other in the region 66 d of the outer peripheral surface 66 a of the roller 66. (Modification 2).

  Further, in another modification, as shown in FIG. 7, the region 66d of the outer peripheral surface 66a of the roller 66 extends in the circumferential direction and the vertical direction of the outer peripheral surface 66a of the roller 66, and extends in the vertical direction. Two recessed portions 91c arranged are formed (Modification 3). In another modification, as shown in FIG. 8, the region 66 d of the outer peripheral surface 66 a of the roller 66 is arranged in a substantially circular, vertical direction when viewed from the direction orthogonal to the outer peripheral surface 66 a of the roller 66. Three holes 101c (concave portions) are formed (Modification 4).

  Even in the case of these modified examples 1 to 4, the grooves 66c, 81c, the recess 91c, and the hole 101c are formed in the region 66d of the outer peripheral surface 66a of the roller 66, so that the outer peripheral surface 66a of the roller 66 has a surface area in the region 66d. Since it is large, the portion of the piston 62 on the low pressure chamber 71c side is efficiently cooled by the refrigerant flowing into the low pressure chamber 71c.

  In the above-described embodiment, the three grooves 66c are formed. However, the number of the grooves 66c is not limited to this, and two or less grooves 66c or four or more grooves 66c may be formed. Note that the numbers of the grooves 81c, the recesses 91c, and the holes 101c of the above-described modified examples 1 to 4 are not limited to those described in the modified examples 1 to 4 as described above.

  In the above embodiment, the depth Dm of the groove 66c is ½ or more of the distance Dr between the outer peripheral surface 66a and the inner peripheral surface 66b of the roller 66. However, the present invention is not limited to this. The depth Dm of the roller 66 may be smaller than ½ of the distance Dr between the outer peripheral surface 66a and the inner peripheral surface 66b of the roller 66.

  In the above-described embodiment, the groove 66c, which is a recess, is formed in the region 66d of the outer peripheral surface 66a of the roller 66. However, instead of the recess, the region 66d extends from the region 66d to the outer side in the circumferential direction of the roller 66. A protruding convex portion may be formed. Moreover, it is not restricted to any one of a recessed part and a convex part being formed, Both the recessed part and the convex part may be formed. Even in these cases, the outer peripheral surface 66a of the roller 66 has an increased surface area in the region 66d, and the portion of the piston 62 on the low pressure chamber 71c side is efficiently cooled by the refrigerant flowing into the low pressure chamber 71c.

  However, in the case where the convex portion is formed, the convex portion is arranged on the outer periphery of the roller 66 so that the convex portion does not prevent the outer peripheral surface 66a of the roller 66 from contacting the side wall surface 71a of the cylinder chamber 71. Of the region 66d of the surface 66a, a recess is formed in at least a part of the region 66d formed in a portion facing the introduction port 71b when contacting the side wall surface 71a of the cylinder chamber 71. It is necessary to form a concave portion in a portion where the convex portion of the side wall surface 71a of the cylinder chamber 71 abuts.

  By utilizing the present invention, the expansion of the portion of the piston on the low pressure chamber side is suppressed, and it is possible to reliably prevent the piston from contacting the upper and lower wall surfaces of the cylinder chamber.

It is a schematic block diagram of the compressor which concerns on embodiment in this invention. It is a top view which shows the structure and operation | movement of these cylinders and pistons of FIG. 2 is a perspective view of the piston. It is a figure which shows the mode of linear expansion deformation of a cylinder and a piston when compression of a refrigerant | coolant is performed in a compression mechanism, (a) is based on this Embodiment, (b) has shown the conventional one. FIG. 10 is a diagram corresponding to FIG. FIG. 10 is a diagram corresponding to FIG. FIG. 10 is a diagram corresponding to FIG. FIG. 10 is a diagram corresponding to FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compressor 12 Motor 13 Compression mechanism 24 Introduction port 26 Sealed space 61 Cylinder 62 Piston 66 Roller 66a Outer peripheral surface 66b Inner peripheral surface 66c Groove 67 Blade 71 Cylinder chamber 71a Side wall surface 71b Inlet port 71c Low pressure chamber 71d High pressure chamber 74 Exhaust port 81c Groove 91c recess 101c hole

Claims (4)

A cylinder (61) disposed in the sealed space (26) and having a cylinder chamber (71) therein;
A piston (62) disposed inside the cylinder chamber (71);
An inlet (71b) provided on the side wall surface (71a) of the cylinder chamber (71), for introducing a refrigerant into the cylinder chamber (71) from the outside;
A discharge port (74) for discharging the refrigerant from the cylinder chamber (71) to the sealed space (26);
The piston (62)
It is configured in an annular shape, and moves along the side wall surface (71a) so that the outer peripheral surface (66a) abuts on the side wall surface (71a) of the cylinder chamber. And a high pressure chamber (71d) for discharging the compressed refrigerant from the discharge port (74) to the sealed space (26), and a low pressure chamber (71c) for introducing the refrigerant from the introduction port (71b). And a roller (66) for changing the volume of the high pressure chamber (71d) and the low pressure chamber (71c),
The roller (66) is integrally formed and extends outward from the outer peripheral surface (66a) of the roller (66), and together with the roller (66), the cylinder chamber (71) is connected to the high pressure chamber (66). 71d) and a blade (67) that divides into the low pressure chamber (71c),
The outer peripheral surface (66a) of the roller (66) is in contact with a portion of the side wall surface (71a) of the cylinder chamber (71) adjacent to the downstream side in the moving direction of the roller (66) of the introduction port (71b). Among the portions defining the low pressure chamber (71c) of the outer peripheral surface (66a) of the roller (66) in the state, at least part of the portion excluding the upper end and the lower end thereof is provided with the recesses (66c, 81c, 91c, 101c) and a compressor (1), wherein at least one of convex portions is formed. The recess (66c, 81c, 91c, 101c) is formed on the outer peripheral surface (66a) of the roller (66),
The compressor (1) according to claim 1, wherein the recess (66c, 81c, 91c, 101c) does not penetrate to the inner peripheral surface (66b) of the roller (66).   The depth (Dm) of the recesses (66c, 81c, 91c, 101c) is ½ or more of the distance (Dr) between the outer peripheral surface (66a) and the inner peripheral surface (66b) of the roller (66). The compressor (1) according to claim 2, characterized in that   The said recessed part (66c, 81c, 91c, 101c) is extended along the outer peripheral surface (66a) of the said roller (66), and forms the groove | channel (66c, 81c), The Claim 2 or 3 characterized by the above-mentioned. The compressor (1) described.

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