Compressor

Abstract

The present invention provides a compressor capable of suppressing a phenomenon that a gas refrigerant flows back between a discharge valve and an end plate in a closed state. This compressor is provided with: a fixed-side end plate (211) in which is formed a main port (213) that communicates with a compression chamber for compressing a refrigerant and a discharge chamber (C2) into which the compressed refrigerant is introduced; and a vane valve (610) that opens and closes a discharge port (213a) of the main port (213) located on the discharge chamber (C2) side, in which a groove (214) is formed around the discharge port (213a) on the surface of the fixed-side end plate (211) where the discharge port (213a) opens, and in which the groove (214) overlaps a portion on the tip (611) side of the vane valve (610) in a closed state when the fixed-side end plate (211) is viewed in plan.

Description

Technical Field

[0001] The present invention relates to a compressor. Background Art

[0002] For example, in a scroll compressor, which is a type of compressor, a compression chamber for compressing refrigerant and a discharge chamber into which the compressed refrigerant is introduced are separated by an end plate, and a port for connecting the compression chamber and the discharge chamber is formed on the end plate. In addition, in order to prevent the refrigerant from flowing back from the discharge chamber to the compression chamber through the port, a discharge valve (leaf valve) for opening and closing the discharge port is provided on the end plate.

[0003] In order to reliably seal the discharge port, the discharge valve in the closed state is preferably in close contact with the end plate. However, in reality, due to the dimensional accuracy error of the components or the warping of the discharge valve caused by long-term use, a small gap sometimes occurs between the discharge valve and the end plate. And it is known that after the compressor stops, when the pressure of the air conditioning system is equalized, the refrigerant flows back through the gap and generates a high-frequency sound.

[0004] Patent document 1 discloses the following technology: although it is not intended to suppress high-frequency sounds, in a rotary compressor, a plurality of recesses with a diameter of 0.1 μm to 10 μm are formed by spraying roughly spherical projectiles onto the sealing surface of the port, and an oil film is formed through the recesses, thereby achieving improvements in the sealing and wear resistance of the port portion.

[0005] Prior art literature

[0006] Patent Literature

[0007] Patent Document 1: Japanese Patent Application Publication No. 2008-95624.

[0008] However, since the diameter of the recessed portion of Patent Document 1 is 0.1 μm to 10 μm, its depth is smaller than 0.1 μm to 10 μm, and there is a possibility that the lubricating oil cannot be fully retained by the recessed portion. Nevertheless, in the method of forming the recessed portion by ejecting a roughly spherical shot, it is difficult to easily form a deep recessed portion. Summary of the invention

[0009] The present invention has been made in view of the above-mentioned circumstances, and an object of the present invention is to provide a compressor capable of suppressing the phenomenon in which the gas refrigerant flows back from between the discharge valve in a closed state and the end plate.

[0010] In order to solve the above-mentioned problems, the compressor of the present invention adopts the following structure.

[0011] That is, a compressor of one embodiment of the present invention comprises: an end plate, which is formed with a port, the port connecting a compression chamber for compressing refrigerant and a discharge chamber into which the compressed refrigerant is introduced; and a discharge valve, which opens and closes a discharge port of the port located on the discharge chamber side, and a groove is formed around the discharge port on the surface of the end plate where the discharge port opens, and when the end plate is viewed from above, the groove overlaps with a portion of the top end side of the discharge valve in a closed state.

[0012] Effects of the Invention

[0013] According to the present invention, it is possible to suppress the phenomenon in which the gas refrigerant flows back from between the discharge valve in a closed state and the end plate. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Figure 1 It is a longitudinal sectional view of a compressor according to one embodiment of the present invention.

[0015] Figure 2 yes Figure 1 A partial enlarged view (longitudinal sectional view) of the leaf valve and the vicinity of the groove shown.

[0016] Figure 3 This is a plan view of the leaf valve and the vicinity of the groove in Example 1.

[0017] Figure 4 This is a top view of the leaf valve and the vicinity of the groove in Example 2.

[0018] Figure 5 It is a partial enlarged view (longitudinal cross-sectional view) of the leaf valve and the vicinity of the groove according to the modified example. DETAILED DESCRIPTION

[0019] Hereinafter, a compressor according to an embodiment of the present invention will be described with reference to the drawings.

[0020] [About compressor]

[0021] The compressor 10 is a device that compresses refrigerant containing lubricating oil.

[0022] In the following description, a scroll compressor is used as an example of the compressor 10 in which the compression mechanism 200 and the motor 400 as the driving part are housed in the internal space of the casing 100 which is a closed space, but it can also be a so-called open scroll compressor in which the driving part is arranged outside the closed space.

[0023] like Figure 1 As shown, the compressor 10 includes a housing 100 , a compression mechanism 200 , a crankshaft 310 , and a motor 400 .

[0024] The housing 100 includes a motor housing 110 , an upper housing 120 and a lower housing 130 .

[0025] The motor case 110 is a cylindrical member extending in the direction of the axis X1 and having both ends opened.

[0026] The motor housing 110 surrounds the compression mechanism 200 , the crankshaft 310 , and the electric motor 400 around the axis X1 .

[0027] The upper housing 120 is a member that closes an opening of the motor housing 110 .

[0028] The upper housing 120 is fixed to the motor housing 110 by bolts 530 .

[0029] The lower case 130 is a member that closes the other opening of the motor case 110 .

[0030] The lower housing 130 is fixed to the motor housing 110 by bolts 540 .

[0031] An inverter cover 140 is attached to the lower case 130. An inverter (not shown) is accommodated in a space defined by the lower case 130 and the inverter cover 140.

[0032] The compression mechanism 200 , the crankshaft 310 , the electric motor 400 , and various other components are housed in a sealed space defined by the casing 100 (the motor housing 110 , the upper housing 120 , and the lower housing 130 ) configured as described above.

[0033] The compression mechanism 200 is a mechanism for compressing a low-pressure gas refrigerant taken in from the outside of the casing 100 through a suction port (not shown).

[0034] The compression mechanism 200 includes a fixed scroll 210 and an orbiting scroll 220 .

[0035] The fixed scroll 210 is a member including a fixed-side end plate 211 and a spiral fixed-side wall body 212 provided upright from the fixed-side end plate 211 .

[0036] The fixed scroll 210 is fixed to the upper housing 120 by bolts 550. In addition, the outer peripheral surface of the fixed side end plate 211 of the fixed scroll 210 contacts the inner peripheral surface of the motor housing 110 and the inner peripheral surface of the upper housing 120 in a sealed state. Thus, the closed space inside the housing 100 is divided into a receiving chamber C1 defined by the fixed scroll 210, the motor housing 110 and the lower housing 130, and a discharge chamber C2 defined by the fixed scroll 210 and the upper housing 120.

[0037] In addition, the sealing performance between the fixed scroll 210 and the motor housing 110 and the upper housing 120 is ensured by, for example, an O-ring.

[0038] The fixed-side end plate 211 is formed with a main port (port) 213 that allows the discharge chamber C2 and the compression chamber C3 (described later) partitioned by the fixed-side end plate 211 to communicate with each other.

[0039] The main port 213 is a circular hole penetrating in the thickness direction of the fixed-side end plate 211 at a substantially central portion of the fixed-side end plate 211 (a position corresponding to a space with the highest refrigerant pressure in the compression chamber C3 ).

[0040] A leaf valve (discharge valve) 610 and a retainer 620 for limiting the amount of deflection of the leaf valve 610 are provided on the surface of the fixed-side end plate 211 on the discharge chamber C2 side. The detailed structure of the leaf valve 610 and its vicinity will be described later.

[0041] The orbiting scroll 220 includes an orbiting-side end plate 221 and a spiral orbiting-side wall body 222 erected from the orbiting-side end plate 221 .

[0042] The orbiting scroll 220 is configured to perform an orbiting motion relative to the fixed scroll 210 by means of a crankshaft 310 rotating about the axis X1 (more specifically, a crankpin 312 orbiting about the axis X1 ) and a known anti-rotation mechanism.

[0043] The fixed scroll 210 and the orbiting scroll 220 are meshed with each other through their respective walls to form a compression chamber C3.

[0044] The crankshaft 310 is a component for transmitting driving force from the motor 400 to the orbiting scroll 220 .

[0045] The crankshaft 310 includes a shaft body 311 and a crankpin 312 .

[0046] The shaft body 311 is a shaft-shaped member extending along the axis X1 and is driven by the motor 400 to rotate around the axis X1.

[0047] The shaft body 311 is supported rotatably around the axis X1 by a main bearing 510 fixed to the motor housing 110 and a sub-bearing 520 fixed to the lower housing 130 .

[0048] The crankpin 312 is a shaft-shaped member provided at an end portion of the shaft body 311 on the upper housing 120 side.

[0049] The crank pin 312 extends along another axis X2 that is eccentric with respect to the axis X1. Therefore, when the shaft body 311 rotates about the axis X1, the crank pin 312 revolves around the axis X1.

[0050] The crankpin 312 is connected to a boss portion formed on the orbiting scroll 220 via a bearing 223 .

[0051] The compressor 10 constructed as described above is driven as follows.

[0052] That is, the shaft body 311 of the crankshaft 310 is driven by the motor 400 to rotate about the axis X1 , thereby driving the orbiting scroll 220 connected to the crankpin 312 .

[0053] The gas refrigerant taken into the accommodation chamber C1 on the lower housing 130 side through the suction port (not shown) is introduced into the accommodation chamber C1 on the compression mechanism 200 side through the refrigerant passage formed between the inner peripheral surface of the motor housing 110 and the outer peripheral surface of the electric motor 400 (stator).

[0054] The refrigerant introduced into the accommodation chamber C1 on the compression mechanism 200 side is sucked into the compression chamber C3. At this time, since the compression chamber C3 is configured to gradually reduce in volume due to the orbiting motion of the orbiting scroll 220, the gas refrigerant is compressed accordingly.

[0055] The compressed high-temperature and high-pressure gas refrigerant is introduced into the discharge chamber C2 through a main port 213 provided at a substantially central portion of the fixed-side end plate 211 of the fixed scroll 210 .

[0056] The gas refrigerant introduced into the discharge chamber C2 is discharged to the outside of the compressor 10 through a discharge port (not shown) provided in the upper casing 120 .

[0057] [About the leaf valve and its surrounding structures]

[0058] like Figure 1 and Figure 2 As shown, the leaf valve 610 and the retainer 620 are provided on the fixed-side end plate 211 on the discharge chamber C2 side.

[0059] The leaf valve 610 is a thin plate-shaped member (valve) that opens and closes the opening (discharge port 213 a ) on the outlet side of the main port 213 .

[0060] The retainer 620 is a plate-shaped member that is overlapped with the leaf valve 610 .

[0061] The base end 622 of the retainer 620 is fixed to the fixed-side end plate 211 by the bolt 560 in a state of sandwiching the base end 612 of the leaf valve 610 .

[0062] Thus, the leaf valve 610 is fixed to the fixed-side end plate 211 together with the retainer 620 .

[0063] The top end 621 of the retainer 620 is located higher than the base end 622 , and the outer shape of the retainer 620 is gradually tilted from the base end 622 toward the top end 621 in a side view.

[0064] When the compressor 10 stops, the leaf valve 610 closes the discharge port 213a. When the compressor 10 starts to operate and the pressure of the refrigerant in the compression chamber C3 reaches a predetermined pressure or more, the top end 611 bends upward to open the discharge port 213a. Then, the refrigerant flows from the compression chamber C3 to the discharge chamber C2 via the main port 213. At this time, the bending amount of the leaf valve 610 is limited by the retainer 620.

[0065] Furthermore, when the pressure in the compression chamber C3 decreases, the leaf valve 610 returns to its original position and closes the discharge port 213a again.

[0066] That is, during the operation of the compressor 10 , the tip 611 of the leaf valve 610 repeatedly reciprocates between the fixed-side end plate 211 and the retainer 620 .

[0067] In the leaf valve 610 configured in this way, due to errors in the dimensional accuracy of the components or warping of the leaf valve 610 caused by long-term use, a small gap may be generated between the leaf valve 610 and the fixed-side end plate 211. In addition, when the pressure of the air conditioning system is equalized after the compressor 10 stops, the refrigerant may flow back through the gap to generate a high-frequency sound.

[0068] Therefore, in the present embodiment, in order to suppress the backflow of the gas refrigerant, the groove 214 is formed in the fixed-side end plate 211 .

[0069] Hereinafter, the structure of the groove 214 will be described using multiple embodiments.

[0070] [Example 1]

[0071] like Figure 2 and Figure 3 As shown, the groove 214 is formed on the surface of the fixed-side end plate 211 that contacts the leaf valve 610 in the closed state.

[0072] The groove 214 is formed around the discharge port 213a which is circular when viewed from above. Specifically, the groove 214 is formed to extend over the entire periphery of the discharge port 213a and along the circumferential direction of the discharge port 213a. That is, the groove 214 is annular. In this case, it is preferred that the center of the discharge port 213a coincides with the center of the groove 214 (see Figure 3 ).

[0073] like Figure 2 As shown, the groove 214 is formed from the surface of the fixed side end plate 211 (at Figure 2 The groove 214 is recessed into a substantially U-shape. The maximum value of the depth dimension of the groove 214 is 0.5 mm or more and 1.0 mm or less, and the maximum value of the width dimension is 0.5 mm or more and 1.0 mm or less.

[0074] At this time, if Figure 3 As shown, the semicircular top end 611 of the leaf valve 610 overlaps with the annular groove 214 (specifically, a portion of the groove 214 corresponding to the position of the semicircular portion on the top end 611 side of the leaf valve 610) when looking down at the fixed side end plate 211.

[0075] That is, the groove 214 is designed so that its position overlaps with the top end 611 of the leaf valve 610. Alternatively, the leaf valve 610 is designed so that its top end 611 overlaps with the groove 214.

[0076] [Example 2]

[0077] like Figure 4 As shown in FIG. 1 , the groove 214 is formed around the discharge port 213a which is circular when viewed from above. Specifically, the groove 214 is formed to extend over half of the periphery of the discharge port 213a and along the circumferential direction of the discharge port 213a. That is, the groove 214 is in a semicircular ring shape. In this case, it is preferred that the center of the discharge port 213a coincides with the center of the groove 214 (see FIG. 1 ). Figure 4 ).

[0078] At this time, if Figure 4 As shown, the semicircular tip 611 of the leaf valve 610 overlaps with the semicircular groove 214 in a plan view of the fixed-side end plate 211. This is the same as in the first embodiment.

[0079] In the second embodiment, the groove 214 is semicircular (180 degrees), but if it overlaps with the semicircular top 611 of the leaf valve 610, the groove 214 may be formed to exceed 180 degrees (if it is 360 degrees, it is the first embodiment).

[0080] Here, if Figure 2 As shown, in Embodiments 1 and 2, the tip 611 of the leaf valve 610 overlapping the annular groove 214 may not completely cover the groove 214 corresponding to the position on the tip 611 side, but only needs to cover at least a portion of the groove 214 .

[0081] However, it is preferable that the tip 611 of the leaf valve 610 reaches a position halfway along the groove 214 corresponding to the position on the tip 611 side.

[0082] In addition, if Figure 5 As shown, the top end 611 of the leaf valve 610 may also completely cover the groove 214 .

[0083] According to this embodiment, the following effects are achieved.

[0084] A groove 214 is formed around the discharge port 213a on the surface of the fixed side end plate 211 where the discharge port 213a opens. When the fixed side end plate 211 is viewed from above, the groove 214 overlaps with the portion on the top 611 side of the leaf valve 610 in the closed state. Therefore, the lubricating oil contained in the refrigerant accumulates in the groove 214, and the leaf valve 610 is brought into close contact with the fixed side end plate 211 by the lubricating oil having surface tension. As a result, the leaf valve 610 and the fixed side end plate 211 are sealed by the lubricating oil, so that the phenomenon of the refrigerant gas flowing back from the leaf valve 610 in the closed state and the fixed side end plate 211 can be avoided.

[0085] Furthermore, when the groove 214 is formed over at least half of the periphery of the discharge port 213 a , the leaf valve 610 and the fixed-side end plate 211 can be effectively sealed, particularly on the tip 611 side where the warping of the leaf valve 610 is greatly affected.

[0086] Furthermore, when the groove 214 is formed over the entire circumference of the discharge port 213 a , it is possible to more reliably seal between the leaf valve 610 and the fixed-side end plate 211 .

[0087] In addition, when the depth dimension of the groove 214 is 0.5 mm or more and 1.0 mm or less, the lubricating oil can be sufficiently stored in the groove 214 .

[0088] In addition, when the maximum value of the width dimension of the groove 214 is 0.5 mm or more and 1.0 mm or less, the lubricating oil can be sufficiently stored in the groove 214 .

[0089] Here, the structure of the groove 214 is applicable not only to the main port 213 but also to the multi-port (other port) 215 formed in the fixed-side end plate 211 to prevent over-compression.

[0090] like Figure 1 As shown, the multi-port 215 is a circular hole that penetrates the fixed-side end plate 211 in the thickness direction at a portion of the fixed-side end plate 211 on the outer peripheral side of the main port 213 .

[0091] Although not shown in the drawings, the multi-port 215 is also provided with components corresponding to the leaf valve 610 and the retainer 620 .

[0092] In addition, for illustration, Figure 1 The illustrated multiport 215 is depicted in a different location than the actual location.

[0093] The compressor according to the above-described embodiment can be understood, for example, as follows.

[0094] That is, the compressor 10 of the first embodiment of the present invention comprises: an end plate 211, which is formed with a port 213, which connects a compression chamber C3 for compressing refrigerant and a discharge chamber C2 into which the compressed refrigerant is introduced; and a discharge valve 610, which opens and closes a discharge port 213a of the port located on the discharge chamber side, and a groove 214 is formed around the discharge port on the surface of the end plate where the discharge port opens, and when looking down at the end plate, the groove overlaps with a portion on the side of the top end 611 of the discharge valve in a closed state.

[0095] According to the compressor of this aspect, a groove is formed around the discharge port on the surface of the end plate where the discharge port is opened, and when the end plate is viewed from above, the groove overlaps with the top end side of the discharge valve in a closed state, so that the lubricating oil contained in the refrigerant accumulates in the groove, and the discharge valve and the end plate are closely contacted by the lubricating oil having surface tension. As a result, the discharge valve and the end plate are sealed by the lubricating oil, so that the phenomenon of the refrigerant gas flowing back from the discharge valve in a closed state and the end plate can be avoided.

[0096] In addition, in the compressor of the second embodiment of the present invention, in the first embodiment, another port 215 connecting the compression chamber and the discharge chamber is formed on the end plate, and the compressor is provided with another discharge valve, which opens and closes another discharge port of the other port located on the discharge chamber side, and another groove is formed around the other discharge port on the surface of the end plate where the other discharge port opens, and when the end plate is viewed from above, the other groove overlaps with a portion of the top end side of the other discharge valve in a closed state.

[0097] According to the compressor of this aspect, it is possible to avoid the phenomenon of refrigerant gas backflow not only at one port but also at other ports.

[0098] In addition, in a compressor according to a third aspect of the present invention, in the first aspect, a groove is formed on the tip end side of the discharge valve over at least half of the circumference of the discharge port.

[0099] According to the compressor of this aspect, the groove is formed at least halfway around the discharge port on the tip side of the discharge valve, so that the discharge valve and the end plate can be effectively sealed, especially on the tip side where the warping of the discharge valve is greatly affected.

[0100] Furthermore, in a compressor according to a fourth aspect of the present invention, in the first aspect, the groove is formed over the entire circumference of the discharge port.

[0101] According to the compressor of this aspect, since the groove is formed over the entire circumference of the discharge port, it is possible to more reliably seal between the discharge valve and the end plate.

[0102] Furthermore, in a compressor according to a fifth aspect of the present invention, in any one of the first to fourth aspects, a maximum value of a depth dimension of the groove is not less than 0.5 mm and not more than 1.0 mm.

[0103] According to the compressor of this aspect, since the depth dimension of the groove is 0.5 mm or more and 1.0 mm or less, the lubricating oil can be sufficiently stored in the groove.

[0104] Furthermore, in a compressor according to a sixth aspect of the present invention, in any one of the first to fifth aspects, a maximum value of a width dimension of the groove is not less than 0.5 mm and not more than 1.0 mm.

[0105] According to the compressor of this aspect, since the maximum value of the width dimension of the groove is 0.5 mm or more and 1.0 mm or less, the lubricating oil can be sufficiently stored in the groove.

[0106] Furthermore, in a compressor according to a seventh aspect of the present invention, in any one of the second to sixth aspects, the other groove is formed on the tip end side of the other discharge valve over at least half of the circumference of the other discharge port.

[0107] According to the compressor of this aspect, other grooves are formed at least halfway around other discharge ports on the top end side of other discharge valves, so that the discharge valve and the end plate can be effectively sealed, particularly on the top end side where the discharge valve is greatly affected by warping.

[0108] Furthermore, in the compressor according to an eighth aspect of the present invention, in any one of the second to sixth aspects, the other groove is formed over the entire circumference of the other discharge port.

[0109] According to the compressor of this aspect, since the other groove is formed over the entire circumference of the other discharge port, it is possible to more reliably seal between the discharge valve and the end plate.

[0110] Furthermore, in the compressor of a ninth aspect of the present invention, in any one of the second to eighth aspects, a maximum value of a depth dimension of the other groove is not less than 0.5 mm and not more than 1.0 mm.

[0111] According to the compressor of this aspect, since the depth dimension of the other grooves is 0.5 mm or more and 1.0 mm or less, the lubricating oil can be sufficiently stored in the grooves.

[0112] Furthermore, in the compressor according to a tenth aspect of the present invention, in any one of the second to ninth aspects, a maximum value of a width dimension of the other groove is not less than 0.5 mm and not more than 1.0 mm.

[0113] According to the compressor of this aspect, since the maximum value of the width dimension of the other grooves is 0.5 mm or more and 1.0 mm or less, the lubricating oil can be sufficiently stored in the grooves.

[0114] [Explanation of symbols]

[0115] 10. Compressor

[0116] 100 Shell

[0117] 110 Motor housing

[0118] 120 Upper shell

[0119] 130 Lower housing

[0120] 140 Inverter cover

[0121] 200 Compression mechanism

[0122] 210 Fixed scroll

[0123] 211 Fixed side end plate

[0124] 212 Fixed side wall

[0125] 213 Primary Port (Port)

[0126] 213a Exhaust port

[0127] 214 slots

[0128] 215 multi-port (port, other port)

[0129] 220 Swirl Scroll

[0130] 221 Swivel side end plate

[0131] 222 Convoluted side wall

[0132] 223 Bearing

[0133] 310 Crankshaft

[0134] 311 Shaft body

[0135] 312 Crankpin

[0136] 400 Electric Motor

[0137] 510 Main bearing

[0138] 520 secondary bearing

[0139] 530 Bolt

[0140] 540 Bolt

[0141] 550 Bolt

[0142] 560 Bolt

[0143] 610 Leaf Valve (Discharge Valve)

[0144] 611 Top

[0145] 612 base end

[0146] 620 Retainer

[0147] 621 Top

[0148] 622 base end

[0149] C1 Containment Chamber

[0150] C2 Exhaust Chamber

[0151] C3 Compression Chamber

[0152] X1 axis

[0153] X2 axis.

Claims

1. A compressor, It is characterized in that have: an end plate formed with a port communicating between a compression chamber for compressing refrigerant and a discharge chamber into which the compressed refrigerant is introduced; and a discharge valve that opens and closes a discharge port of the port located on the discharge chamber side, A groove is formed around the discharge port on the surface of the end plate where the discharge port opens. In a plan view of the end plate, the groove overlaps a portion on the tip end side of the discharge valve in a closed state.

2. The compressor according to claim 1, It is characterized in that The end plate is formed with another port communicating with the compression chamber and the discharge chamber. The compressor includes another discharge valve that opens and closes another discharge port of the other port located on the discharge chamber side. On the surface of the end plate where the other discharge port opens, another groove is formed around the other discharge port. In a plan view of the end plate, the other groove overlaps with a portion on the tip end side of the other discharge valve in a closed state.

3. The compressor according to claim 1, It is characterized in that The groove is formed on the tip end side of the discharge valve over at least half of the circumference of the discharge port.

4. The compressor according to claim 1, It is characterized in that The groove is formed over the entire circumference of the discharge port.

5. The compressor according to claim 1, It is characterized in that The maximum value of the depth dimension of the groove is 0.5 mm or more and 1.0 mm or less.

6. The compressor according to claim 1, It is characterized in that The maximum value of the width dimension of the groove is 0.5 mm or more and 1.0 mm or less.

7. The compressor according to claim 2, It is characterized in that The other groove is formed on the tip end side of the other discharge valve over at least half of the circumference of the other discharge port.

8. The compressor according to claim 2, It is characterized in that The other groove is formed over the entire circumference of the other discharge port.

9. The compressor according to claim 2, It is characterized in that The maximum value of the depth dimension of the other grooves is 0.5 mm or more and 1.0 mm or less.

10. The compressor according to claim 2, It is characterized in that The maximum value of the width dimension of the other grooves is 0.5 mm or more and 1.0 mm or less.

Images