Compressor and air conditioning device

Abstract

The invention provides a compressor and an air conditioner, which can reduce discharge pressure loss. A compressor (30) is provided with: a motor (31); a shaft (33) which is rotated by the motor (31) and which is provided with a pin part (32); and a compression mechanism including a main bearing (35) and a sub-bearing (36) that rotatably support the shaft (33), and a cylinder (38) that forms a compression chamber (37) together with the main bearing (35) and the sub-bearing (36) and compresses a fluid by means of a pin section (32) that rotates within the compression chamber (37), the main bearing (35) having a discharge port (48) through which the compressed fluid is discharged, and the sub-bearing (36) having a discharge port (48) through which the pin section (32) rotates within the compression chamber (37). The cylinder (38) has a cutout (42) that constitutes a flow path for the compressed fluid connected from the compression chamber (37) to the discharge port (48), and at least the outer peripheral portion (50) of the cutout (42) on the compression chamber (37) side is a curved surface or chamfered.

Description

Technical Field

[0001] The present invention relates to a compressor and an air-conditioning device. Background Art

[0002] A rotary compressor compresses the refrigerant within a hollow cylindrical body (cylinder) by rotating a rotating shaft (shaft) and a hollow cylindrical body (roller) inserted into an eccentric portion (pin) on the shaft. The compressed refrigerant is discharged through a discharge port located in the main bearing covering the upper portion of the cylinder or the auxiliary bearing covering the lower portion. The discharge port is located near the blades that separate the cylinder body, spanning the inner and upper or lower end surfaces of the cylinder body.

[0003] However, in this case, the flow path of the refrigerant flowing from the cylinder to the discharge port is rapidly narrowed, increasing the pressure loss. Therefore, a notch is provided in the cylinder to constitute the flow path of the refrigerant connecting the cylinder and the discharge port.

[0004] Conventionally, a technique is known in which a discharge groove is formed as a circular cutout and has the same diameter as the discharge port to reduce overcompression and overcompression loss of the refrigerant and improve compressor efficiency (for example, see Patent Document 1).

[0005] Prior art literature

[0006] Patent Literature

[0007] Patent Document 1: Japanese Patent Application Laid-Open No. 2021-161878 Summary of the Invention

[0008] Problems to be solved by the invention

[0009] The above-mentioned conventional technology has the effect of smoothing the flow of the refrigerant, but has a problem in that the discharge pressure loss due to fluid resistance is large because the outer peripheral portion of the cutout has corners (edges).

[0010] Means for solving problems

[0011] In view of the above problems, the present invention provides a compressor, characterized by comprising: an electric motor;

[0012] a rotating shaft that is rotated by a motor and includes an eccentric portion; and

[0013] The compression mechanism includes: a first bearing and a second bearing that rotatably support the rotating shaft; and a hollow cylindrical body that, together with the first bearing and the second bearing, forms a compression chamber, and compresses the fluid through the eccentric portion rotating in the compression chamber.

[0014] The first bearing has a discharge port for discharging the compressed fluid.

[0015] The cylindrical body has a cutout that constitutes a flow path for the compressed fluid connected from the compression chamber to the discharge port. At least an outer peripheral portion of the cutout on the compression chamber side is a curved surface or is chamfered.

[0016] Effects of the Invention

[0017] According to the present invention, discharge pressure loss can be reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is a diagram showing a configuration example of an air-conditioning apparatus according to this embodiment.

[0019] Figure 2 It is a diagram showing a first structural example of the compressor according to the present embodiment.

[0020] Figure 3 It is a diagram showing a structural example of a compression mechanism.

[0021] Figure 4 This is a diagram of the compression mechanism viewed from the motor side.

[0022] Figure 5 This is a diagram showing an example of a conventional cylinder.

[0023] Figure 6 This is a diagram showing a cross section of a conventional discharge port and a notch cut along the axial direction of the shaft.

[0024] Figure 7 This is a diagram showing a first example of a cylinder included in the compressor according to this embodiment.

[0025] Figure 8 This is a diagram showing a second example of the cylinder included in the compressor according to this embodiment.

[0026] Figure 9 This is a diagram showing a third example of the cylinder included in the compressor according to the present embodiment.

[0027] Figure 10 It is a diagram showing a second configuration example of the compressor according to the present embodiment.

[0028] Explanation of symbols

[0029] 10: Air conditioning unit; 11: Indoor unit; 12: Indoor heat exchanger; 13: Indoor fan; 14: Indoor fan drive motor; 20: Outdoor unit; 21: Compressor; 22: Four-way valve; 23: Outdoor expansion valve; 24: Outdoor heat exchanger; 25: Outdoor fan; 26: Outdoor fan drive motor; 27: Liquid accumulator; 28: Control unit; 30: Compressor; 31: Motor; 31a: Stator; 31b: Rotor; 32 : Pin portion; 33: Shaft; 34: Container; 35: Main bearing; 36: Auxiliary bearing; 37: Compression chamber; 38: Cylinder; 38a: Upper cylinder; 38b: Lower cylinder; 39: Roller; 40: Blade; 41: Elastic component; 42: Cutout; 43: Suction nozzle; 44, 45: Space; 46: Discharge nozzle; 47: Discharge valve; 48: Discharge outlet; 49: Storage groove; 50: Peripheral portion; 51: Suction port; 52: Partition plate. DETAILED DESCRIPTION

[0030] Figure 1 This figure shows an example configuration of an air conditioning apparatus according to the present embodiment. The air conditioning apparatus 10 includes an indoor unit 11 installed in a space to be air-conditioned (indoors) and an outdoor unit 20 installed outdoors. The air conditioning apparatus 10 performs air conditioning by circulating a refrigerant as a fluid between the indoor unit 11 and the outdoor unit 20, thereby exchanging heat with the indoor air.

[0031] The indoor unit 11 and the outdoor unit 20 may each be composed of two or more units, and two or more indoor units 11 may be connected to a single outdoor unit 20. Refrigerants that can be used include hydrofluorocarbons (HFCs) and hydrofluoroolefins (HFOs). Examples of HFCs include R32 (CH2F2) and R410A (CH2F2+C2HF3), and examples of HFOs include R1234yf (CF3CF=CH2).

[0032] The indoor unit 11 includes an indoor heat exchanger 12, an indoor fan 13, and an indoor fan drive motor 14. The indoor fan 13 is driven by the indoor fan drive motor 14 to draw in indoor air and send it into the indoor heat exchanger 12. The indoor heat exchanger 12 is configured with multiple heat transfer tubes through which refrigerant circulates. The air entering the unit contacts the surfaces of the multiple heat transfer tubes, exchanging heat with the refrigerant. The air that has undergone heat exchange in the indoor heat exchanger 12 is discharged into the room.

[0033] In addition, the indoor unit 11 may further include various sensors for measuring indoor temperature, humidity, etc., an indoor expansion valve for decompressing and expanding the refrigerant to control the flow rate of the refrigerant, and the like.

[0034] The outdoor unit 20 includes a compressor 21, a four-way valve 22, an outdoor expansion valve 23, an outdoor heat exchanger 24, an outdoor fan 25, and an outdoor fan drive motor 26. The compressor 21 includes a liquid accumulator 27, which is driven by the compressor drive motor. The compressor draws low-pressure gas refrigerant from the liquid accumulator 27, boosts the pressure, and discharges it as high-pressure gas refrigerant. The liquid accumulator 27 is a container that prevents transient liquid backflow into the compressor 21 and separates the liquid, thereby adjusting the refrigerant to an appropriate dryness. Dryness is the proportion of steam in wet steam, which represents a mixture of steam and fine liquid droplets.

[0035] The four-way valve 22 is a valve that switches the direction of refrigerant flow according to the operating state (operating mode) of the air conditioning unit 10. The operating modes include cooling mode, heating mode, and air supply mode. The outdoor expansion valve 23 is a valve that reduces the pressure of high-pressure refrigerant and expands it, and is a valve that can control the flow rate of the refrigerant. The outdoor fan 25 is driven by the outdoor fan drive motor 26, sucking in outdoor air and sending it to the outdoor heat exchanger 24. The outdoor heat exchanger 24 is also constructed in the same way as the indoor heat exchanger 12, with multiple heat transfer tubes through which the refrigerant circulates. The air sent in contacts the surfaces of the multiple heat transfer tubes and exchanges heat with the refrigerant. The air that has undergone heat exchange through the outdoor heat exchanger 24 is sent to the outside.

[0036] The outdoor unit 20 also includes a control device 28. The control device 28 is connected to the compressor 21, the four-way valve 22, the outdoor expansion valve 23, the indoor fan drive motor 14, and the outdoor fan drive motor 26, and controls these components. The control device 28 controls, among other things, the speed of the compressor 21, the opening of the outdoor expansion valve 23, the speed of the indoor fan drive motor 14, and the speed of the outdoor fan drive motor 26. The control device 28 can perform these controls based on information detected by various sensors. Furthermore, the control device 28 is not limited to being located in the outdoor unit 20; it may also be located in the indoor unit 11 or elsewhere.

[0037] In cooling mode, the indoor heat exchanger 12 functions as an evaporator and the outdoor heat exchanger 24 functions as a condenser. As indicated by the arrows, the refrigerant enclosed in the system circulates in the order of the compressor 21, the four-way valve 22, the outdoor heat exchanger 24, the outdoor expansion valve 23, the indoor heat exchanger 12, the four-way valve 22, the accumulator 27, and the compressor 21. In heating mode, conversely, the indoor heat exchanger 12 functions as a condenser and the outdoor heat exchanger 24 functions as an evaporator. The directions of the arrows are reversed, and the refrigerant enclosed in the system circulates in the order of the compressor 21, the four-way valve 22, the indoor heat exchanger 12, the outdoor expansion valve 23, the outdoor heat exchanger 24, the four-way valve 22, the accumulator 27, and the compressor 21.

[0038] Here, the air-conditioning device 10 is taken as an example as a device including the compressor 21 , but the present invention is not limited thereto and a refrigerator, a cooling unit, or the like may also be used.

[0039] Figure 2 This is a diagram showing a first configuration example of a compressor according to this embodiment. The compressor 30 is, for example, Figure 1 The compressor of the air conditioner shown is a rotary compressor. Compressor 30 includes a motor 31 as an electric motor, a shaft 33 having a pin 32 that is rotated by motor 31, and a compression mechanism. Compressor 30 houses motor 31, shaft 33, and compression mechanism within a sealed container 34.

[0040] The compression mechanism includes: a main bearing 35 as a first bearing and a secondary bearing 36 as a second bearing that rotatably support the shaft 33; and a cylinder body 38, which together with the main bearing 35 and the secondary bearing 36 constitute a compression chamber 37, and compresses the fluid through the pin portion 32 rotating in the compression chamber 37.

[0041] Motor 31 consists of a hollow cylindrical stator (stator) 31a and a rotating rotor (rotor) 31b rotatably disposed within stator 31a and equipped with permanent magnets. Shaft 33 is located at the center of rotor 31b when viewed from one side in its longitudinal (axial) direction and rotates as rotor 31b rotates.

[0042] The container 34 is a hollow container with a circular cross section and a long side. The shaft 33 is arranged at the center of the cross section. The motor 31 is arranged on one side of the shaft 33 along the longitudinal direction of the container 34, and the compression mechanism is arranged on the other side.

[0043] like Figure 3 As shown, the compression mechanism divides the compression chamber 37 into two compartments using a hollow cylindrical body (roller) 39 into which a pin 32 is inserted, and a partition (vane) 40. Refrigerant, acting as a fluid, is drawn into one compartment within the compression chamber 37. Roller 39 rotates eccentrically about shaft 33 while in contact with the inner wall of cylinder 38, thereby reducing the volume of the compartment and compressing the refrigerant drawn into it. When viewed from the motor 31, shaft 33 rotates counterclockwise. Vanes 40 are provided with elastic members 41, such as springs, at their ends to maintain their tips in constant contact with roller 39 and to maintain a constant pressure against roller 39.

[0044] The cylinder 38 is provided with a notch 42 forming a refrigerant flow path connecting the compression chamber 37 to a discharge port provided in the main bearing 35. Therefore, the refrigerant compressed in the compression chamber 37 is sent to the discharge port through the notch 42 and discharged from the discharge port.

[0045] Refer again Figure 2The compression mechanism draws in refrigerant through the suction nozzle 43 and discharges the refrigerant compressed in the compression chamber 37 from the discharge port. However, a discharge valve is provided at the discharge port. The discharge valve is pushed up by the pressure of the refrigerant, and the refrigerant is discharged into the space 44 above the main bearing 35 through the gap formed by the push. The refrigerant is then transported to the space 45 above the motor 31 in the container 34 through the gap between the stator 31a and the rotor 31b, and is discharged from the discharge nozzle 46 provided at the top of the container 34.

[0046] Figure 4 This diagram shows the compression mechanism as viewed from the motor 31. The main bearing 35 is provided with a discharge port for discharging the refrigerant compressed within the compression chamber 37. A discharge valve 47 is provided to seal the discharge port. Discharge valve 47 is a plate-shaped device with one side longer than the other. It seals the discharge port on one side and is fixed to the main bearing 35 on the other side. When the refrigerant pressure within the compression chamber 37 exceeds a specified pressure, discharge valve 47 is pushed upward, allowing the refrigerant within the compression chamber 37 to be discharged toward the main bearing 35 through the gap created by the upward movement of discharge valve 47.

[0047] Figure 5 This is a diagram showing an example of a conventional cylinder. Figure 5 (a) is a diagram showing a state where the main bearing 35 is superimposed on the cylinder block 38. Figure 5 (b) is an enlarged view of the discharge port. The discharge port 48 is provided in the main bearing 35. The notch 42 is formed in a groove-like shape from the compression chamber 37 side of the cylinder 38, i.e., the inner side, to the upper end of the cylinder 38. When viewed from the motor 31, the notch 42 is formed in a roughly semicircular shape and is adjacent to the storage groove 49 that houses the vanes 40. This prevents compressed refrigerant from remaining in the compression chamber 37 and causing overcompression.

[0048] like Figure 5 As shown in (b), the diameter of the roughly semicircular cutout 42 is approximately the same as the diameter of the discharge port 48 of the main bearing 35, which is located above the cutout 42. This prevents the flow path from expanding or contracting, thereby reducing discharge pressure loss. Furthermore, the corners of the accommodating groove 49 formed in the cylinder 38 on the compression chamber 37 side are chamfered to minimize pressure loss during the reciprocating motion of the vane 40.

[0049] However, if Figure 6 As shown, the edge of the cutout 42 provided on the cylinder 38 Figure 5 The cross section taken along the cutting line AA shown in (a) is formed such that the upper corner of the inner side of the cylinder 38 is cut obliquely. Figure 6 The discharge port 48 of the main bearing 35 is also shown in FIG. 3 , but the outer peripheral portion 50 on the compression chamber 37 side has an edge, and the fluid resistance is increased by the edge. This increases the pressure loss and reduces the performance of the compressor.

[0050] Therefore, in order to reduce fluid resistance, reduce pressure loss, and improve compressor performance, the shape of the cutout 42 is set to the shape described below.

[0051] Figure 7 This is a diagram showing a first example of the cylinder 38 included in the compressor 30 according to the present embodiment. Figure 7 (a) is a diagram showing the cylinder 38 as viewed obliquely from the motor 31 side. Figure 7 (b) is a diagram showing a cross section cut along cutting line BB. Figure 5 As described above, the cylinder 38 has the cutout 42 formed on the compression chamber 37 side, that is, the inner side of the cylinder 38. The cutout 42 is formed in a substantially semicircular shape when viewed from the motor 31 side and is adjacent to the housing groove 49 that houses the vane 40.

[0052] A notch 42 is provided on one side across the storage groove 49, and a suction port 51 is provided on the other side for sucking refrigerant into the compression chamber 37. The roller 39 rotates while contacting the inside of the cylinder 38 in the compression direction indicated by the arrow, thereby compressing the refrigerant.

[0053] like Figure 7 As shown in (b), the outer peripheral portion 50 of the inner side of the cylinder 38 of the cutout 42 is R-chamfered to form a curved surface (roughly R-shaped). Figure 7 In the cross section cut along the cutting line BB in (a), the curvature radius of the curved portion of the curved surface is 0.5 mm or more. If the curvature radius is less than 0.5 mm, the effect of reducing fluid resistance is small, and processing to form such a curvature radius is difficult.

[0054] In addition, the outer peripheral portion 50 of the cutout 42 is not limited to a curved surface, and the edge can also be cut obliquely to perform C-chamfering (hereinafter referred to as chamfering). Chamfering is performed by cutting at an angle of approximately 45° relative to the upper end face or lower end face of the cylinder body 38 at a position that is at least 0.5 mm away from the edge in the radial direction of the cylinder body 38 and the axial direction of the shaft 33 in the direction of the auxiliary bearing 36. That is, the position that is, for example, 0.7 mm away from the edge in the radial direction of the cylinder body 38 is connected to the position of the inner surface of the cylinder body 38 that is the same 0.7 mm away in the direction of the auxiliary bearing 36, and the chamfering is performed by cutting off the corner. In this case as well, if it is less than 0.5 mm, the effect of reducing fluid resistance is small and processing is difficult, so it is set to be greater than 0.5 mm.

[0055] By thus forming a curved surface or chamfering the outer peripheral portion 50 of the notch 42 on the compression chamber 37 side, the refrigerant can flow smoothly from the compression chamber 37 to the notch 42 , reducing fluid resistance and pressure loss.

[0056] Figure 8: is a diagram showing a second example of the cylinder 38 included in the compressor of this embodiment. Figure 8 In the figure, only the portion showing the cutout 42 is enlarged. The cylinder 38 and Figure 7 Similarly, in the cylinder block 38 shown, the outer peripheral portion 50 inside the notch 42 of the cylinder block 38 is formed into a curved surface (approximately R-shaped) or chamfered, but the width of the curved or chamfered portion varies on the high crank angle side and the low crank angle side.

[0057] In the case of compressing refrigerant, the most protruding portion of the pin 32 in the direction perpendicular to the axial direction of the shaft 33 is aligned with the extending direction of the blade 40, and the crank angle is 0°. Figure 7 The compression direction shown in (a) indicates counterclockwise rotation as viewed from the motor 31. Therefore, when the shaft 33 rotates counterclockwise once, the most protruding portion of the pin portion 32 temporarily leaves the blade 40, passes in front of the notch 42 adjacent to the blade 40, and returns to the position of the blade 40. The crank angle is the angle between the direction in which the most protruding portion of the pin portion 32 points and the direction in which the blade 40 extends. When the most protruding portion of the pin portion 32 points closer to the blade 40 than the center of the notch 42, the crank angle is greater than when it is aligned with the center of the notch 42, resulting in a higher crank angle. The opposite side, due to a smaller crank angle, is a lower crank angle.

[0058] The wider the width of the curved or chamfered outer peripheral portion 50 of the cutout 42, the larger the radius of curvature, and the wider the chamfered area, the further reduced discharge pressure loss can be achieved. On the other hand, since the area of ​​the cutout 42 opening inside the cylinder 38 is increased, the high-pressure and low-pressure sides are connected via the cutout 42 through the roller 39. This causes refrigerant on the high-pressure side to flow back toward the low-pressure side, reducing the crankshaft angle at which compression can be achieved. This reduction in the crankshaft angle at which compression can be achieved leads to compression loss.

[0059] This backflow occurs on the low crank angle side, so it can be suppressed by making the width of the outer peripheral portion 50 smaller on the low crank angle side than on the high crank angle side. When the low crank angle side is curved, the radius of curvature can be set to a minimum of 0.5 mm, while the radius of curvature on the high crank angle side can be set to a radius greater than 0.5 mm. This can suppress the decrease in the compressible crank angle and reduce compression loss. Furthermore, by reducing the width on the low crank angle side while increasing the width on the high crank angle side, compression loss can be suppressed and discharge pressure loss can be reduced.

[0060] Figure 9 This is a diagram showing a third example of the cylinder 38 included in the compressor 30 according to the present embodiment. Figure 9 (a) is a diagram showing the cylinder 38 as viewed obliquely from the motor 31 side. Figure 9(b) is a diagram showing a cross section cut along cutting line CC. Figure 7 In the example shown, only the outer peripheral portion 50 on the inner side of the cylinder body 38 of the cutout 42 is curved or chamfered. This leaves an edge on the outer peripheral portion 50 on the discharge-side end surface (upper end surface) of the cylinder body 38 of the cutout 42, causing discharge pressure loss due to fluid resistance. Therefore, the outer peripheral portion 50 on the upper end surface of the cylinder body 38 of the cutout 42 can also be curved or chamfered.

[0061] In the case of a curved surface, the outer peripheral portion 50 of the notch 42 on the upper end surface side of the cylinder 38 can also have a curvature radius of 0.5 mm or more, similar to the outer peripheral portion 50 inside the cylinder 38. This can further reduce discharge pressure loss.

[0062] When the outer peripheral portion 50 of the cutout 42 of the cylinder body 38 is made into a curved surface or chamfered, the molten metal is flowed into the mold and cooled and solidified to manufacture the cylinder body 38 having the cutout 42, and the outer peripheral portion 50 of the cutout 42 of the manufactured cylinder body 38 is cut, and other casting processing is performed, so that the outer peripheral portion 50 can be made into a curved surface or chamfered.

[0063] However, this requires casting, which is time-consuming. Furthermore, the raw material, such as iron, must be heated to a temperature higher than its melting point to make it liquid and then poured into the mold, which requires a lot of energy.

[0064] Therefore, a sintered material is used as the raw material, and a mold that can make the outer peripheral portion 50 curved or chamfered is used. Pressure is applied while heating is performed at a temperature lower than the melting point, thereby reducing the energy used. Without casting processing, a cylinder body 38 with a cut 42 that makes the outer peripheral portion 50 curved or chamfered can be manufactured.

[0065] Figure 10 It is a diagram showing a second configuration example of the compressor according to the present embodiment. Figure 10 The compressor 30 shown is Figure 2 The compressor 30 shown in FIG. has the same structure, and the compression mechanism is composed of two stages. Figure 2 In the case where the compression mechanism shown is a one-stage compressor ( 30 ), there is one cylinder ( 38 ), the upper portion of the cylinder ( 38 ) is covered by a main bearing ( 35 ), and the lower portion of the cylinder ( 38 ) is covered by a sub-bearing ( 36 ).

[0066] When the compression mechanism is configured as a two-stage mechanism, there are two cylinder bodies 38, and a partition plate 52 is provided between the cylinder bodies 38. Therefore, the lower portion of the upper cylinder body 38a and the lower cylinder body 38b of the two cylinder bodies 38 are covered by the partition plate 52, the upper portion of the upper cylinder body 38a is covered by the main bearing 35, and the lower portion of the lower cylinder body 38b is covered by the auxiliary bearing 36.

[0067] The shaft 33 is provided with two pins 32, which are respectively arranged inside the upper cylinder 38a and the lower cylinder 38b and are respectively inserted into the two rollers 39. The upper cylinder 38a and the lower cylinder 38b are respectively provided with a receiving groove 49 to receive the blades 40.

[0068] In this case, a notch 42 is provided in each of the upper cylinder 38a and the lower cylinder 38b, and a discharge port 48 and a discharge valve 47 are provided in addition to the main bearing 35 and the auxiliary bearing 36. Furthermore, the outer periphery 50 of the notch 42 in each of the upper cylinder 38a and the lower cylinder 38b is curved or chamfered.

[0069] As described above, by providing the compressor and air conditioning apparatus of the present invention, it is possible to reduce the fluid resistance at the refrigerant discharge portion including the notch 42 and reduce the discharge pressure loss.

[0070] So far, the compressor and air-conditioning device of the present invention have been described in detail using the above-mentioned embodiments, but the present invention is not limited to the above-mentioned embodiments. It can be modified in other embodiments, additions, changes, deletions, etc. within the scope that can be thought of by those skilled in the art. In any form, as long as the function and effect of the present invention are achieved, it is included in the scope of the present invention.

[0071] Therefore, according to the present invention, there can be provided (1) a compressor, characterized in that it includes: an electric motor; a rotating shaft, which is rotated by the electric motor and has an eccentric portion; and a compression mechanism, which includes: a first bearing and a second bearing, which can rotatably support the rotating shaft; and a hollow cylindrical body, which together with the first bearing and the second bearing constitute a compression chamber, and the fluid is compressed by the eccentric portion rotating in the compression chamber, the first bearing has a discharge port for discharging the compressed fluid, the cylindrical body has a cutout, the cutout constitutes a flow path for the compressed fluid connected from the compression chamber to the discharge port, and the outer peripheral portion of at least the compression chamber side of the cutout is a curved surface or is chamfered.

[0072] According to the present invention, there can be provided (2) a compressor according to the above-mentioned (1), characterized in that the compression mechanism includes: a hollow cylindrical body in which the eccentric part is inserted; and a partition plate, which abuts against the outer surface of the cylindrical body and divides the compression chamber into two spaces, and the part of the eccentric part that protrudes most from the outer peripheral surface of the rotating shaft abuts against the partition plate via the cylindrical body. When the rotating shaft is rotated and the most protruding part of the eccentric part abuts against the partition plate via the cylindrical body again, the rotation angle is set to the crankshaft angle, and the low crankshaft angle side of the outer peripheral part of the compression chamber side of the cutout is smaller than the high crankshaft angle side.

[0073] According to the present invention, there can be provided (3) a compressor according to (1) or (2) above, characterized in that the outer peripheral portion of the notch on the discharge port side is also a curved surface or is chamfered.

[0074] According to the present invention, there can be provided (4) a compressor according to any one of (1) to (3) above, characterized in that the outer peripheral portion of at least the compression chamber side of the cutout is a curved surface, and the curvature radius of the curved surface is greater than 0.5 mm.

[0075] According to the present invention, there can be provided (5) a compressor according to any one of the above (1) to (4), characterized in that the cylindrical body has the cutout, and the outer peripheral portion of at least the compression chamber side of the cutout is a curved surface or chamfered, and is formed using a mold using a sintered material as the raw material.

[0076] According to the present invention, there can be provided (6) a compressor according to any one of (1) to (5) above, characterized in that the compressor has two eccentric portions on the rotating shaft and two compression mechanisms respectively including the cylindrical bodies, each of the cylindrical bodies has the cutout, and the outer peripheral portion of at least the compression chamber side of the cutout is a curved surface or chamfered.

[0077] According to the present invention, there can be provided an air-conditioning apparatus including the compressor according to any one of (1) to (6) above.

Claims

1. A compressor, characterized in that: include: Electric motor; a rotating shaft which is rotated by the motor and has an eccentric portion; as well as The compression mechanism includes: a first bearing and a second bearing, which rotatably support the rotating shaft; and a hollow cylindrical body, which together with the first bearing and the second bearing constitutes a compression chamber, and the eccentric portion rotating in the compression chamber compresses the fluid, The first bearing has a discharge port for discharging the compressed fluid. The cylindrical body has a notch that constitutes a flow path of the compressed fluid connected from the compression chamber to the discharge port, and at least an outer peripheral portion of the notch on the compression chamber side is a curved surface or is chamfered.

2. The compressor according to claim 1, characterized in that The compression mechanism includes: a hollow cylindrical body into which the eccentric part is inserted; and a partition plate which abuts against the outer surface of the cylindrical body and divides the compression chamber into two spaces. The part of the eccentric portion that protrudes most from the outer peripheral surface of the rotating shaft abuts against the partition plate via the cylindrical body. When the rotating shaft is rotated and the rotation angle when the most protruding part of the eccentric portion abuts against the partition plate via the cylindrical body again is set as the crankshaft angle, the low crankshaft angle side of the outer peripheral portion that is curved or chamfered on the compression chamber side of the cutout is smaller than the high crankshaft angle side.

3. The compressor according to claim 1, characterized in that The outer peripheral portion of the discharge port side of the cutout is also a curved surface or is chamfered.

4. The compressor according to any one of claims 1 to 3, characterized in that: At least an outer peripheral portion of the cutout on the compression chamber side is a curved surface, and a radius of curvature of the curved surface is greater than or equal to 0.5 mm.

5. The compressor according to any one of claims 1 to 3, characterized in that: The cylindrical body having the cutout, wherein at least the outer peripheral portion of the cutout on the compression chamber side is a curved surface or chamfered, is formed using a sintered material as a raw material using a die.

6. The compressor according to any one of claims 1 to 3, characterized in that: The compressor includes two eccentric portions on the rotating shaft and two compression mechanisms each including the cylindrical body. Each of the cylindrical bodies has the cutout, and at least an outer peripheral portion of the cutout on the compression chamber side is a curved surface or is chamfered.

7. An air conditioning device, comprising a compressor, characterized in that: The compressor comprises: Electric motor; a rotating shaft which is rotated by the motor and has an eccentric portion; and A compression mechanism, comprising: a first bearing and a second bearing, which rotatably support the rotating shaft; and a hollow cylindrical body, which together with the first bearing and the second bearing constitutes a compression chamber, and the eccentric part rotating in the compression chamber compresses the fluid, The first bearing has a discharge port for discharging the compressed fluid. The cylindrical body has a notch that constitutes a flow path of the compressed fluid connected from the compression chamber to the discharge port, and at least an outer peripheral portion of the notch on the compression chamber side is a curved surface or is chamfered.

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