Rotary compressor and air conditioner

Abstract

The present invention provides a rotary compressor with high reliability. The rotary compressor includes a cylinder (5a), a roller (5b), a crankshaft (4), an upper bearing (5c), a lower bearing (5d), and blades. An oil supply flow path is provided on the crankshaft (4), and oil supply holes (41c, 41d) are provided. The oil supply holes (41c, 41d) guide lubricating oil from the oil supply flow path to the gap between at least one of the upper bearing (5c) and the lower bearing (5d) and the eccentric portion (4b). The position of the oil supply holes (41c, 41d) on the crankshaft (4) in the axial direction is within the range of the axial direction of the cylinder (5a). The sectional moment of inertia of the surface of the crankshaft (4) containing the oil supply holes (41c, 41d) is perpendicular to the axial direction of the crankshaft (4) and is larger than the sectional moment of inertia of the surface of the main shaft portion (4a) containing the oil supply flow path, which is perpendicular to the axial direction of the crankshaft (4).

Description

Technical Field

[0001] This invention relates to a rotary compressor, etc. Background Technology

[0002] Regarding rotary compressors, technologies described in Patent Documents 1 and 2 are known, for example. Specifically, Patent Document 1 describes a method where an inclined shape is partially provided on the thrust sliding surface near the eccentric shaft of the rotary compressor crankshaft. Furthermore, Patent Document 2 describes a method where an oil supply port and an exhaust port are provided on the crankshaft of the rotary compressor.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: Japanese Patent Application Publication No. 2012-077728

[0006] Patent Document 2: Japanese Patent Application Publication No. 2015-040472 Summary of the Invention

[0007] The technical problem that the invention aims to solve

[0008] In the technology described in Patent Document 1, by providing a groove in the crankshaft that is recessed radially inward to a portion corresponding to the upper end of the lower bearing, lubricating oil can be easily supplied to the lower bearing, etc. (Patent Document 1) Figure 1 However, if such a groove is placed on the surface of the crankshaft, the crankshaft's rigidity will be reduced, making it more susceptible to deformation due to refrigerant compression loads. As a result, it is possible for one end of the crankshaft to contact the upper and lower bearings.

[0009] Furthermore, in the technology described in Patent Document 2, the lower oil supply hole for supplying oil to the sliding surface of the crankshaft and the sub-bearing (lower bearing) is located in the crankshaft at a position corresponding to the sub-bearing (Patent Document 2). Figure 1 However, if such a lower oil supply hole is located on the crankshaft, the crankshaft's rigidity is reduced, which could lead to contact between one end of the crankshaft and the auxiliary bearing, etc. Therefore, there is room for further improvement in the reliability of the rotary compressor.

[0010] Therefore, the objective of this invention is to provide a rotary compressor or the like with high reliability.

[0011] Solutions for solving technical problems

[0012] To address the aforementioned issues, the rotary compressor of the present invention comprises a cylinder and an annular roller revolving within the cylinder, and further comprises: a shaft having a main shaft portion and an eccentric portion eccentrically positioned relative to the main shaft portion and slidingly contacting the inner circumferential surface of the roller; an upper bearing disposed on the upper side of the cylinder for supporting the shaft; a lower bearing disposed on the lower side of the cylinder for supporting the shaft; and plate-shaped blades separating the space between the cylinder and the roller. The shaft has an upper movement limiting portion disposed on the radially inner side of the roller above the eccentric portion and limiting axial movement of the shaft, and an upper movement limiting portion disposed on the radially inner side of the roller below the eccentric portion and limiting axial movement of the shaft. The movable lower movement limiting part has an oil supply flow path on the shaft for guiding lubricating oil axially, and an oil supply hole for the lubricating oil flowing from the oil supply flow path. The oil supply hole is located in at least one of the upper and lower movement limiting parts. The oil supply hole guides the lubricating oil from the oil supply flow path to the gap between at least one of the upper and lower bearings and the eccentric part. The axial position of the oil supply hole on the shaft is within the axial range of the cylinder barrel, perpendicular to the axial direction of the shaft, and the moment of inertia of the surface of the shaft including the oil supply hole is greater than the moment of inertia of the surface of the main shaft including the oil supply flow path, which is perpendicular to the axial direction of the shaft. Other structures are described in the embodiments.

[0013] Invention Effects

[0014] According to the present invention, a rotary compressor with high reliability can be provided. Attached Figure Description

[0015] Figure 1 This is a longitudinal cross-sectional view of the rotary compressor according to the first embodiment.

[0016] Figure 2 It is the rotary compressor of the first embodiment. Figure 1 Sectional view along line II-II.

[0017] Figure 3A This is a longitudinal cross-sectional view of the rotary compressor of the first embodiment, including the compression mechanism.

[0018] Figure 3B It is the rotary compressor in the first embodiment Figure 3A A magnified view of a portion of region K1 shown.

[0019] Figure 4 This is a perspective view of the rotary compressor of the first embodiment, including the crankshaft and the compression mechanism.

[0020] Figure 5 This is an explanatory diagram regarding the location of the oil supply port of the rotary compressor in the first embodiment.

[0021] Figure 6 This is an explanatory diagram illustrating the process of the roller moving within the cylinder of the rotary compressor in the first embodiment.

[0022] Figure 7 This is a longitudinal cross-sectional view of the rotary compressor of the second embodiment, including the compression mechanism.

[0023] Figure 8 This is a perspective view of the rotary compressor of the second embodiment, including the crankshaft and the compression mechanism.

[0024] Figure 9 This is a cross-sectional view of the compression mechanism portion of the rotary compressor according to the third embodiment, including the oil supply port on the upper side.

[0025] Figure 10 This is an explanatory diagram illustrating the process of the roller moving within the cylinder of the rotary compressor in the third embodiment.

[0026] Figure 11 This is a structural diagram of the air conditioner according to the fourth embodiment.

[0027] In the picture:

[0028] Symbol Explanation

[0029] 1 – Sealed container; 2 – Electric motor; 4, 4A, 4B – Crankshaft (shaft); 4a – Main shaft section; 4b, 4Ab – Eccentric section; 4c – Upper movement restriction section; 4d – Lower movement restriction section; 41c, 42c – Oil supply port (upper oil supply port); 41d – Oil supply port (lower oil supply port); 4e – Oil supply path; 5, 5A – Compression mechanism section; 5a – Cylinder; 5b – Roller; 5c – Upper bearing; 5d – Lower bearing; 51c – First chamfer section; 51d – Second chamfer section; 5e – Blade; 71 – Outdoor heat exchanger; 7 2 - Outdoor fan, 73 - Expansion valve, 74 - Four-way valve, 75 - Indoor heat exchanger, 76 - Indoor fan, 100 - Rotary compressor, C1 - Cylinder chamber (space), F1 - Part, G1 - Clearance (clearance between upper bearing and eccentric part), G2 - Clearance (clearance between lower bearing and eccentric part), H1 - Oil supply hole (upper side oil supply hole), H2 - Oil supply hole (lower side oil supply hole), L1 - Straight line, R1 - Area, R2 - Area (area on the opposite side), W1 - Air conditioner, Z1 - Central axis (central axis of the shaft). Detailed Implementation

[0030] First Implementation Method

[0031] <Structure of a rotary compressor>

[0032] Figure 1 This is a longitudinal cross-sectional view of the rotary compressor 100 according to the first embodiment.

[0033] The rotary compressor 100 is a device for compressing gaseous refrigerant. For example... Figure 1 As shown, the rotary compressor 100 includes a sealed container 1, an electric motor 2, counterweights 31 and 32, a crankshaft 4 (shaft), a compression mechanism 5, and a silencer 6.

[0034] The sealed container 1 is a container that houses the electric motor 2, crankshaft 4, compression mechanism 5, etc., and is substantially sealed. The sealed container 1 has a cylindrical cavity 1a, a cover cavity 1b that blocks the upper side of the cylindrical cavity 1a, and a bottom cavity 1c that blocks the lower side of the cylindrical cavity 1a.

[0035] A suction pipe P1 is inserted and fixed in the cylindrical chamber 1a of the sealed container 1. The suction pipe P1 guides the refrigerant to the suction chamber C2 of the compressor unit 5 (see reference). Figure 2 The suction pipe P1 is connected to a liquid receiver 200 for refrigerant gas-liquid separation. Additionally, a discharge pipe P2 is inserted into and fixed to the cover cavity 1b of the sealed container 1. The discharge pipe P2 guides the refrigerant compressed by the compression mechanism 5 to the outside of the rotary compressor 100. Lubricating oil for improving the lubricity and sealing of the rotary compressor 100 is sealed in the sealed container 1, and an oil reservoir M1 is stored at the bottom of the sealed container 1.

[0036] Electric motor 2, which drives the crankshaft 4 to rotate, is located inside the sealed container 1. For example... Figure 1 As shown, the electric motor 2 includes a stator 2a and a rotor 2b. The stator 2a is a cylindrical component made of stacked electromagnetic steel plates, fixed to the inner circumferential surface of the cylindrical cavity 1a. A predetermined winding 21a is wound on the stator 2a. The rotor 2b is a cylindrical component having an iron core formed of electromagnetic steel plates and permanent magnets (not shown) embedded in the iron core, rotatably disposed radially inside the stator 2a. A crankshaft 4 is coaxially fixed to the rotor 2b.

[0037] Crankshaft 4 is a shaft that rotates integrally with rotor 2b, driven by motor 2. Crankshaft 4 extends vertically and is rotatably supported by upper bearing 5c ​​and lower bearing 5d. Figure 1 As shown, the crankshaft 4 includes a main shaft portion 4a, an eccentric portion 4b, an upper movement limiting portion 4c, and a lower movement limiting portion 4d.

[0038] The main shaft 4a is coaxially fixed to the rotor 2b of the motor 2. Furthermore, the main shaft 4a is positioned above and below the eccentric portion 4b, which will be described later. The eccentric portion 4b is the part that is eccentric and rotates relative to the main shaft 4a. The eccentric portion 4b is cylindrical in shape and is integrally formed with the main shaft 4a. The eccentric portion 4b is located radially inside the roller 5b at the lower part of the crankshaft 4.

[0039] like Figure 1 As shown, the crankshaft 4 is provided with an axially oriented oil supply path 4e for guiding lubricating oil, and oil supply holes 41c and 41d for the flow of lubricating oil from the oil supply path 4e. The oil supply path 4e is a flow path that guides the lubricating oil stored in the sealed container 1 as an oil reservoir M1 to the compression mechanism 5. The oil supply path 4e is arranged axially along the crankshaft 4 and opens at the lower end of the crankshaft 4.

[0040] Furthermore, the upper end of the oil supply passage 4e is located, for example, near the upper end of the upper movement restriction part 4c. Additionally, a pre-twisted, thin, plate-shaped metal sheet 4f is provided near the lower end of the oil supply passage 4e to act as an oil pump. The metal sheet 4f rotates integrally with the crankshaft 4, thereby drawing lubricating oil through the oil supply passage 4e. Furthermore, although in Figure 1 The illustration is omitted, but it is also possible to appropriately set transverse holes to guide lubricating oil from the oil supply path 4e to the radial inner side of roller 5b.

[0041] The upper movement limiting part 4c and the lower movement limiting part 4d are parts that limit the axial movement of the crankshaft 4. The upper movement limiting part 4c is provided radially inside the roller 5b on the upper side of the eccentric part 4b. Similarly, the lower movement limiting part 4d is provided radially inside the roller 5b on the lower side of the eccentric part 4b. Figure 1 As shown, the upper movement restriction part 4c is provided radially with an oil supply hole 41c that guides the lubricating oil from the oil supply path 4e to the outside of the crankshaft 4. Similarly, the lower movement restriction part 4d is also provided radially with other oil supply holes 41d. Details of the oil supply holes 41c and 41d will be described later.

[0042] The compression mechanism 5 is a mechanism that compresses gaseous refrigerant in tandem with the rotation of the crankshaft 4, and is located below the electric motor 2. The compression mechanism 5 includes a cylinder 5a, a roller 5b, an upper bearing 5c, a lower bearing 5d, a blade 5e, a blade spring 5f, and a discharge valve 5g.

[0043] Figure 2 yes Figure 1 Sectional view along line II-II.

[0044] in addition, Figure 2 It is a horizontal plane including the upper oil supply hole 41c. Figure 1 (II-II line) Cross-sectional view of the rotary compressor 100 cut off and viewed from below.

[0045] Figure 2 The cylinder 5a shown is connected to the roller 5b and the upper bearing 5c ​​(see reference). Figure 3A ), lower bearing 5d (refer to) Figure 3AThe components that together form cylinder chamber C1 are generally annular (cylindrical). Furthermore, cylinder chamber C1 is the space between cylinder barrel 5a and roller 5b. Cylinder chamber C1 includes a suction pipe P1 (see reference). Figure 1 It guides the refrigerant into the suction chamber C2 and compresses the refrigerant into the compression chamber C3.

[0046] Roller 5b is accompanied by motor 2 (see reference) Figure 1 The component that revolves within the cylinder 5a under the drive of the crankshaft 4 is annular (cylindrical). Furthermore, the roller 5b slides in contact with the inner circumferential surface of the cylinder 5a and revolves within the cylinder 5a. Additionally, the eccentric portion 4b of the crankshaft 4 (refer to...) Figure 1 It is cylindrical, and its outer diameter is slightly shorter than the inner diameter of roller 5b. Furthermore, the eccentric portion 4b (refer to...) Figure 1 While sliding in contact with the inner circumferential surface of roller 5b, roller 5b revolves around the inner side of cylinder 5a.

[0047] Blade 5e is a plate-shaped component that separates the space between cylinder 5a and roller 5b (i.e., cylinder chamber C1). Specifically, the front end of blade 5e is pressed against the outer circumferential surface of roller 5b, thereby dividing cylinder chamber C1 into suction chamber C2 and compression chamber C3.

[0048] like Figure 2 As shown, an arc-shaped base end portion 5h protruding radially outward from the cylinder 5a is integrally formed with the cylinder 5a. An intake pipe P1 (see reference) is inserted and fixed in the intake passage (not shown) that radially penetrates the base end portion 5h and the cylinder 5a. Figure 1 Furthermore, it is administered sequentially through the inhalation tube P1 (see reference). Figure 1 The gaseous refrigerant is guided into the intake chamber C2 via the intake passage (not shown).

[0049] In addition, although Figure 2 The illustration is omitted, but a leaf spring 5f is provided radially at a predetermined location at the base end 5h (see reference). Figure 1 The blade spring mounting hole (not shown) is provided in the cylinder 5a. Additionally, a radial slit (not shown) is provided in the cylinder 5a to allow the blade 5e to move radially in and out of the cylinder. This slit, which is a space for the blade 5e to move in and out radially, is set to be slightly wider than the thickness of the blade 5e.

[0050] Figure 1 The blade spring 5f shown is a spring that applies a force to the blade 5e radially inward, and is provided in the aforementioned blade spring mounting hole (not shown). Furthermore, the pressure difference between the inside and outside of the compression mechanism 5 and the force of the blade spring 5f press the tip of the blade 5e against the outer circumferential surface of the roller 5b. Thus, the cylinder chamber C1 between the cylinder 5a and the roller 5b is separated into a suction chamber C2 and a compression chamber C3.

[0051] A discharge notch N1 is provided at a predetermined location on the inner circumference of the upper surface of cylinder 5a. This discharge notch N1 guides the compressed refrigerant to the discharge valve 5g (see reference). Figure 1 The gap, such as Figure 2 As shown, its edges are rounded. Furthermore, the opening of the suction passage (not shown) that guides the refrigerant to the suction chamber C2 and the discharge notch N1 are both close to the blade 5e in the circumferential direction. That is, the suction passage (not shown) opens circumferentially towards one side of the blade 5e. Additionally, the discharge notch N1 is located circumferentially on the other side of the blade 5e.

[0052] Figure 3A This is a longitudinal cross-section of the rotary compressor, including the compression mechanism section 5.

[0053] Figure 3A The upper bearing 5c ​​shown is a sliding bearing that supports the crankshaft 4 shaft for free rotation, and is located on the upper side (axial side) of the cylinder 5a. This upper bearing 5c, together with the cylinder 5a and the lower bearing 5d, is fastened to the cylinder cavity 1a by multiple bolts (not shown) and fixed thereto. Figure 1 The inner circumferential surface of the cylinder 5a. The lower bearing 5d is a sliding bearing that supports the crankshaft 4 shaft for free rotation, and is located on the lower side (the other side of the axial direction) of the cylinder 5a.

[0054] Additionally, in the upper bearing 5c, at the discharge notch N1 of the cylinder 5a (refer to...) Figure 2 The corresponding part is equipped with a compression chamber C3 (refer to) Figure 2 The compressed refrigerant is guided to the discharge valve in a 5g (reference) manner. Figure 1 The orifice (not shown). Discharge valve 5g (refer to...) Figure 1 ) is used to transfer compressed refrigerant into a sealed container 1 (refer to Figure 1 The valve (leaf spring) discharging from the space within the refrigerant is positioned on the upper bearing 5c ​​to block the aforementioned orifice. Furthermore, when the pressure of the compressed refrigerant overcomes the spring force of the discharge valve 5g, the discharge valve 5g (refer to...)... Figure 1 )Open.

[0055] Figure 1 The silencing cover 6 shown is a cover used to suppress noise accompanying refrigerant compression, and is fixed to the upper bearing 5c ​​in a state of partially covering the upper surface of the upper bearing 5c. The silencing cover 6 is provided with multiple holes (not shown) for releasing the compressed refrigerant into the space inside the sealed container 1.

[0056] Figure 3B yes Figure 3A A magnified view of a portion of region K1 shown.

[0057] Figure 3B The oil supply port 41c shown is for the oil supply flow path 4e (see reference). Figure 1 The lubricating oil is guided to the hole in G1, the gap between the upper bearing 5c ​​and the eccentric part 4b, and is provided in the crankshaft 4 (refer to Figure 1 The upper movement restriction part 4c. Another oil supply port 41d is for the oil supply flow path 4e (refer to...) Figure 1 The lubricating oil is guided to the hole G2 in the gap between the lower bearing 5d and the eccentric part 4b, which is located in the crankshaft 4 (refer to Figure 1 The lower side movement restriction part 4d of the crankshaft 4. Furthermore, the axial oil supply holes 41c and 41d of the crankshaft 4 are located where the cylinder 5a (see reference) is located. Figure 3A Within the axial range of ).

[0058] As mentioned above, Figure 3A The upper movement limiting part 4c and the lower movement limiting part 4d shown are parts that restrict the axial movement of the crankshaft 4 and are provided on the radially inner side of the roller 5b. The upper movement limiting part 4c, the eccentric part 4b and the lower movement limiting part 4d are integrally formed together with the main shaft part 4a and are adjacent to each other in the vertical direction in this order.

[0059] like Figure 3A As shown, the upper surface of the upper movement limiting part 4c is in contact with or close to the lower surface of the upper bearing 5c. Furthermore, in the rotary compressor 100 (see reference...) Figure 1 When an upward force is applied to the crankshaft 4 during the drive, the upper surface of the upper movement limiting part 4c contacts the lower surface of the upper bearing 5c, thereby limiting the upward movement of the crankshaft 4. Additionally, the lower surface of the lower movement limiting part 4d contacts or approaches the upper surface of the lower bearing 5d. Furthermore, when a downward force is applied to the crankshaft 4, the lower movement limiting part 4d limits the downward movement of the crankshaft 4.

[0060] By configuring the upper movement limiting part 4c and the lower movement limiting part 4d in this way, the axial movement of the crankshaft 4 is restricted. Furthermore, it ensures that the cylinder chamber C1 (refer to...) Figure 2 While increasing the volume of the eccentric part 4b, the axial length of the eccentric part 4b can be shortened. Therefore, the sliding loss when the eccentric part 4b slides in contact with the roller 5b can be reduced, thereby improving the energy conversion efficiency when compressing the refrigerant.

[0061] Figure 3B The upper bearing 5c ​​shown has a first chamfered portion 51c that is chamfered all around its lower circumference near the end of its inner circumference. The first chamfered portion 51c is used to guide lubricating oil through the gap G1 to the chamfer between the upper bearing 5c ​​and the eccentric portion 4b. In addition, a spiral oil supply groove 52c is provided on the inner circumferential surface of the upper bearing 5c ​​(see reference). Figure 3A Furthermore, the lubricating oil flowing from the oil supply hole 41c is guided through the gap G1 between the first chamfered portion 51c and the eccentric portion 4b to the spiral oil supply groove 52c (see reference). Figure 3A).

[0062] The lower bearing 5d has a second chamfered portion 51d, which is chamfered all the way around the upper end of its inner circumference. The second chamfered portion 51d is a chamfer for guiding lubricating oil through the gap G2 between the lower bearing 5d and the eccentric portion 4b. In addition, an oil supply groove 52d is provided on the inner circumferential surface of the lower bearing 5d along the axial direction of the crankshaft 4 (see reference). Figure 3A Furthermore, the lubricating oil flowing from the oil supply hole 41d is guided to the oil supply groove 52d through the gap G2 between the second chamfered portion 51d and the eccentric portion 4b (see reference). Figure 3A ).

[0063] Figure 4 This is a perspective view of a rotary compressor, including the crankshaft 4 and the compression mechanism 5.

[0064] In addition, regarding Figure 4 The compression mechanism 5 is shown in a perspective view cut along a predetermined plane that includes the central axis of the crankshaft 4. Figure 4 As shown, the upper movement limiting part 4c and the lower movement limiting part 4d are both predetermined cylindrical shapes, with their lengths in the vertical direction shorter than those of the eccentric part 4b. The cross-sectional shapes of the upper movement limiting part 4c and the lower movement limiting part 4d can be, for example, circular or elliptical; alternatively, they can also be... Figure 2 Other shapes as shown.

[0065] The length of the upper movement limiting part 4c protruding radially from the main shaft part 4a can be, for example, longest in the direction of eccentricity of the eccentric part 4b, and shortest on the side opposite to the direction of eccentricity of the eccentric part 4b. Furthermore, the direction of eccentricity of the eccentric part 4b refers to the direction in which the central axis of the eccentric part 4b (not shown) is radially oriented relative to the central axis of the main shaft part 4a (not shown).

[0066] In the circumferential direction of the upper movement restriction part 4c, and in the direction of eccentricity of the eccentric part 4b (in... Figure 4 The upper surface of the portion roughly corresponding to the inner side of the paper (in the middle) contacts or approaches the lower surface of the upper bearing 5c. On the other hand, in the circumferential direction of the upper movement restriction portion 4c, on the side opposite to the orientation of the eccentric portion 4b (in... Figure 4 The upper surface of the portion roughly corresponding to the paper surface and the front side, and the upper bearing 5c, form a predetermined gap G1 between the first chamfered portion 51c and the bearing 5c ​​(see reference). Figure 3B In addition, in the upper movement restriction part 4c, an oil supply hole 41c is provided on the side opposite to the eccentric part 4b in the direction of eccentricity.

[0067] Therefore, the lubricating oil flowing out through the upper oil supply hole 41c travels a shorter distance towards the first chamfered portion 51c, thus making it easier to move upwards towards the bearing 5c ​​(refer to...). Figure 3BLubricating oil is supplied to the inner circumferential surface of the ). Additionally, lubricating oil is supplied to the lower movement restriction part 4d (see reference). Figure 3B Similarly, an oil supply hole 41d is provided on the side opposite to the eccentric direction of the eccentric part 4b (see reference). Figure 3B ).

[0068] Furthermore, the positions of the oil supply holes 41c and 41d are not limited to the side opposite to the orientation of the eccentric part 4b. For example, they can also be located in the following... Figure 5 The area S1 shown (the part displayed by the dot) is equipped with an oil supply hole 41c, etc.

[0069] Figure 5 This is an explanatory diagram regarding the location of the oil supply port 41c.

[0070] in addition, Figure 5 The structure shown is similar to Figure 2 The structure shown is the same, but the cross-sectional lines have been omitted for illustrative purposes. Additionally, for the first chamfered portion 51c (see reference...), Figure 3B The gap G1 facing upwards (refer to) Figure 3B Add a shading to the F1 key in a prominent manner.

[0071] For example, the eccentric part 4b can also be eccentric relative to the main shaft part 4a. Figure 5 The opposite side of arrow A1) Figure 5 Using arrow A2 as a reference, within a range of ±90° circumferentially on crankshaft 4 ( Figure 5 An oil supply port 41c is provided inside the area S1 (as shown in the dot display). Additionally, another oil supply port 41d (refer to...) Figure 3B The same applies. Thus, for example, the lubricating oil flowing through the oil supply hole 41c is directed towards the first chamfered portion 51c (see reference). Figure 3B The shorter travel distance during operation allows for improved oil supply to the upper bearing 5c.

[0072] Incidentally, even when an oil supply hole 41c is provided at a location corresponding to the eccentricity of the eccentric portion 4b, lubricating oil is supplied to the inner circumferential side of the upper bearing 5c. However, in this case, the lubricating oil is supplied via an annular gap G1 (see reference). Figure 3B The lubricating oil flows in a roundabout manner, thus increasing the travel distance of the lubricating oil supplied from the oil supply hole 41c to the upper bearing 5c. The same applies to the lower oil supply hole 41d.

[0073] Furthermore, the section moment of inertia of the surface containing the oil supply hole 41c of the upper movement restriction portion 4c (i.e., crankshaft 4) that is perpendicular to the axial direction of crankshaft 4 is preferably perpendicular to the axial direction of crankshaft 4 and includes the oil supply flow path 4e of the main shaft portion 4a (see reference). Figure 1The moment of inertia of the surface of the crankshaft 4 is larger. Similarly, the moment of inertia of the surface of the crankshaft 4 that includes the oil supply hole 41d and is perpendicular to the axial direction of the crankshaft 4 and the lower movement restriction portion 4d (i.e., the crankshaft 4) is preferably larger than that of the surface of the crankshaft 4 that includes the oil supply flow path 4e and is perpendicular to the axial direction of the crankshaft 4 and the main shaft portion 4a (refer to...). Figure 1 The cross-sectional moment of inertia of the surface is large.

[0074] With this structure, compared to the case where the oil supply hole is provided in the main shaft portion 4a, the oil supply holes 41c and 41d are provided in the upper movement restriction portion 4c and the lower movement restriction portion 4d, which have a large cross-sectional moment of inertia, thus suppressing the reduction of the rigidity of the crankshaft 4. In addition, in addition to being able to supply sufficient oil to the upward bearing 5c ​​through the upper oil supply hole 41c, the downward bearing 5d can also be supplied sufficient oil through the lower oil supply hole 41d.

[0075] Additionally, the first chamfered portion 51c is preferred (refer to...). Figure 3B The gap G1 facing upwards (refer to) Figure 3B ) part F1 ( Figure 5 The area of ​​the shaded portion is larger than the flow path area of ​​the oil supply hole 41c. Here, the "flow path area" of the oil supply hole 41c refers to the area of ​​the oil supply hole 41c when cut by a predetermined plane perpendicular to the flow path direction of the oil supply hole 41c. Furthermore, the area of ​​the aforementioned portion F1 is a generalization... Figure 5 The area of ​​gap G1 shown is projected onto the annular first chamfered portion 51c (see reference). Figure 3B The area of ​​the common part in the case of ) . According to this structure, the lubricating oil flowing out through the oil supply hole 41c can easily pass through the gap G1 on the lower side of the first chamfered portion 51c (refer to Figure 3B It is guided to the inner circumferential side of the upper bearing 5c. Therefore, it promotes the lubrication of the upper bearing 5c.

[0076] Additionally, the second chamfered portion 51d is preferred (refer to...). Figure 3B G2 (refer to the bottom side gap) Figure 3B The area of ​​the portion (not shown) is larger than the flow path area of ​​the oil supply hole 41d. According to this structure, the lubricating oil flowing out through the oil supply hole 41d easily passes through the gap G2 on the upper side of the second chamfered portion 51d (see reference). Figure 3B This is guided to the inner circumferential side of the lower bearing 5d. Therefore, it promotes the lubrication of the lower bearing 5d.

[0077] Figure 6 This is an explanatory diagram illustrating the process of roller 5b moving within cylinder 5a.

[0078] In addition, Figure 6 In, it is shown that in Figure 1 The position of line II-II cuts off the compression mechanism section 5, and the cross-section is viewed from above. Therefore, the cross-section is the same as the cross-section viewed from below. Figure 2 Left and right are opposite.

[0079] in addition, Figure 6 The rotation angle θ shown is crankshaft 4 (reference). Figure 1 The rotation angle. Figure 6 In the example, the rotation angle θ of the roller 5b inside the cylinder 5a when it is at the "top dead center" is set to 0°. The "top dead center" mentioned above is the position of the roller 5b when the center of the roller 5b is closest to the front end of the blade 5e.

[0080] When the rotation angle θ is 0°, the leading edge of blade 5e is retracted to the inner circumferential surface of cylinder 5a by roller 5b, and the entire cylinder chamber C1 becomes compression chamber C3. As the rotation angle of roller 5b increases, the volume of compression chamber C3 decreases, and the refrigerant is compressed. Furthermore, the pressure of the refrigerant overcomes the pressure of the discharge valve 5g (refer to...) which acts as a leaf spring. Figure 1 When the elastic force of ) is applied, the discharge valve 5g opens, and discharge flows through the discharge port N1 into the sealed container 1 (refer to Figure 1 High-pressure refrigerant is discharged from inside the device.

[0081] Additionally, with crankshaft 4 (refer to) Figure 4 The rotation of the upper movement restriction part 4c (refer to) Figure 4 The bearing 5c ​​also rotates, supplying lubricating oil to the upper bearing 5c ​​via the oil supply hole 41c. Similarly, the lower movement restriction part 4d (see reference) Figure 4 The upper bearing 5c ​​rotates along with the crankshaft 4, supplying lubricating oil to the lower bearing 5d via the oil supply hole 41d. This ensures adequate lubrication of both the upper bearing 5c ​​and the lower bearing 5d.

[0082] <Effect>

[0083] According to the first embodiment, the rotary compressor 100 is configured such that the moment of inertia of the surface of the crankshaft 4 including the oil supply holes 41c and 41d is larger than that of the main shaft portion 4a. Therefore, compared to the case where a groove is provided on the surface of the main shaft portion 4a or an oil supply hole is provided on the main shaft portion 4a, the reduction in the rigidity of the crankshaft 4 can be suppressed. In particular, the reduction in the rigidity of the crankshaft 4 near the lower end of the upper bearing 5c ​​and near the upper end of the lower bearing 5d, which are most susceptible to compression loads, can be suppressed. Furthermore, even when the rotary compressor 100 is driven at high speed, the rigidity of the crankshaft 4 can be ensured, thus suppressing deformation of the crankshaft 4 caused by compression loads, centrifugal force, and magnetic attraction. As a result, contact between the crankshaft 4 and one end of the upper bearing 5c ​​and lower bearing 5d can be suppressed, thereby suppressing damage to the upper bearing 5c ​​and lower bearing 5d.

[0084] In addition to the oil supply hole 41c provided in the upper movement restriction part 4c, other oil supply holes 41d are also provided in the lower movement restriction part 4d. As a result, lubricating oil is adequately supplied to the upper bearing 5c ​​and the lower bearing 5d, thereby improving the performance and reliability of the rotary compressor 100.

[0085] Second Implementation Method

[0086] In the second embodiment, the upper movement restriction part 4c described in the first embodiment is not specifically provided (see reference). Figure 3A ), lower side movement restriction part 4d (refer to) Figure 3A Instead, the eccentric part 4Ab (refer to) Figure 7 The axial length of the second embodiment is correspondingly longer than that of the first embodiment. Furthermore, the second embodiment differs from the first embodiment in that, in the eccentric portion 4Ab (refer to...) Figure 7 It is equipped with two oil supply ports H1 and H2 (refer to...) Figure 7 Furthermore, everything else is the same as in the first embodiment. Therefore, the parts that differ from the first embodiment will be described, and the repeated parts will be omitted.

[0087] Figure 7 This is a longitudinal cross-section of the rotary compressor including the compression mechanism 5 according to the second embodiment.

[0088] like Figure 7 As shown, the crankshaft 4A includes a main shaft portion 4a and an eccentric portion 4Ab. The eccentric portion 4Ab is located radially inside the roller 5b and slides in contact with the inner circumferential surface of the roller 5b. The vertical length of the eccentric portion 4Ab is slightly shorter than the vertical length of the cylinder 5a and the roller 5b.

[0089] Additionally, an oil supply path 4e for the crankshaft 4A is provided at the upper part of the eccentric portion 4Ab (see reference). Figure 1 The lubricating oil is guided to the oil supply hole H1 in the gap between the eccentric part 4Ab and the upper bearing 5c. Similarly, an oil supply path 4e for the crankshaft 4A is provided at the lower part of the eccentric part 4Ab (refer to...). Figure 1 The lubricating oil is guided to the oil supply hole H2 in the gap between the eccentric part 4Ab and the lower bearing 5d. In addition, the positions of the axial oil supply holes H1 and H2 of the crankshaft 4A are within the axial range of the cylinder 5a.

[0090] Furthermore, similar to the first embodiment, a first chamfered portion 51c is provided around the entire circumference of the inner circumference of the upper bearing 5c ​​near the lower end of its inner circumference. Also, lubricating oil flowing upwards through the oil supply hole H1 is guided to the spiral oil supply groove 52c through the gap between the upper bearing 5c ​​and the eccentric portion 4Ab. Similarly, lubricating oil flowing downwards through the oil supply hole H2 is guided to the oil supply groove 52d through the gap between the lower bearing 5d and the eccentric portion 4Ab.

[0091] Furthermore, the area of ​​the portion of the first chamfered portion 51c facing the gap between the upper bearing 5c ​​and the eccentric portion 4Ab is preferably larger than the flow path area of ​​the oil supply hole H1. Similarly, the area of ​​the portion of the second chamfered portion 51d facing the gap between the lower bearing 5d and the eccentric portion 4Ab is preferably larger than the flow path area of ​​the oil supply hole H2. This facilitates the supply of lubricating oil to the upper bearing 5c ​​and the lower bearing 5d.

[0092] Furthermore, the section moment of inertia of the surface containing the oil supply hole H1 of the eccentric portion 4Ab (i.e., crankshaft 4A) perpendicular to the axial direction of crankshaft 4A and the main shaft portion 4a, which contains the oil supply flow path 4e (see reference) is also greater than that of the surface containing the oil supply hole H1. Figure 1 The moment of inertia of the surface of the crankshaft 4A is larger. Similarly, the moment of inertia of the surface of the crankshaft 4A that includes the oil supply hole H2 and is perpendicular to the axial direction of the crankshaft 4A and is eccentric to the eccentric portion 4Ab (i.e., crankshaft 4A) is larger than that of the surface of the crankshaft 4A that includes the oil supply flow path 4e (refer to the main shaft portion 4a) and is perpendicular to the axial direction of the crankshaft 4A. Figure 1 The cross-sectional moment of inertia of the surface is large. Based on this structure, compared to the case where an oil supply hole is provided in the main shaft section 4a, the reduction in the rigidity of the crankshaft 4A can be suppressed. Furthermore, sufficient oil supply can be provided to the upper bearing 5c ​​and the lower bearing 5d via the oil supply holes H1 and H2.

[0093] Furthermore, regarding the circumferential positions of the oil supply holes H1 and H2, it can be said that they are similar to those in the first embodiment (see reference). Figure 5 The same applies. Specifically, it is preferable to provide oil supply holes H1 and H2 within a circumferential range of ±90° of the crankshaft 4A, with the orientation of the eccentric portion 4Ab opposite to the orientation of the main shaft portion 4a as a reference. Therefore, the portions of the upper and lower sides of the eccentric portion 4Ab facing the first chamfered portion 51c and the second chamfered portion 51d are always present near the oil supply holes H1 and H2. This facilitates the supply of lubricating oil to the upper bearing 5c ​​and the lower bearing 5d.

[0094] Figure 8 This is a perspective view of a rotary compressor, including the crankshaft 4A and the compression mechanism 5.

[0095] like Figure 8 As shown, the oil supply hole H1 on the upper side of the eccentric portion 4Ab has: a hole H11, which is provided near the upper end of the peripheral surface of the eccentric portion 4Ab; and a notch H12, which is formed by chamfering around the hole H11. To explain the notch H12, the edge of the hole H11 is cut downwards in a U-shape from a predetermined position on the periphery of the upper surface of the eccentric portion 4Ab; in addition, the upper end of the hole H11 is cut radially inwards. Furthermore, lubricating oil is guided to the upper side of the eccentric portion 4Ab through the oil supply hole H1.

[0096] The oil supply hole H2 on the lower side of the eccentric portion 4Ab has: a hole H21, which is provided near the lower end of the peripheral surface of the eccentric portion 4Ab; and a notch H22, which is formed by chamfering around the hole H21. Regarding the notch H22, the edge of the hole H21 is cut upwards in an inverted U-shape from a predetermined portion on the periphery of the lower surface of the eccentric portion 4Ab, and the lower end of the eccentric portion 4Ab is cut radially inwards. Lubricating oil is guided to the lower side of the eccentric portion 4Ab via the oil supply hole H2.

[0097] <Effect>

[0098] According to the second embodiment, even in structures where the distance between the eccentric portion 4Ab and the upper bearing 5c, and the distance between the eccentric portion 4Ab and the lower bearing 5d, is relatively short, oil supply holes H1 and H2 can be provided in the eccentric portion 4Ab. This suppresses the reduction in the rigidity of the crankshaft 4A and ensures sufficient lubrication to the upper bearing 5c ​​and the lower bearing 5d.

[0099] Third Implementation Method

[0100] The third embodiment includes the provision of an oil supply port 42c, etc. (see reference) Figure 9 The circumferential position of the component differs from that in the first embodiment. Otherwise, it is the same as in the first embodiment. Therefore, the parts that differ from the first embodiment will be described, and repeated parts will be omitted.

[0101] Figure 9 This is a cross-sectional view of the compression mechanism 5 of the rotary compressor according to the third embodiment, including the oil supply port 42c on the upper side.

[0102] In addition, Figure 9 For illustrative purposes, the section lines of the cross-section have been omitted. Additionally, Figure 9 Arrow A3 indicates the direction of the revolution of roller 5b within cylinder 5a.

[0103] like Figure 9 As shown, an oil supply hole 42c is provided in the upper movement restriction part 4c. Additionally, although in Figure 9 Not shown in the middle, but on the lower side, the movement restriction part 4d (see reference). Figure 1 Other oil supply holes are provided (not shown).

[0104] Furthermore, the direction of the central axis Z1 passing through the crankshaft 4B and eccentrically along the eccentric part 4b ( Figure 9The straight line L1 extending from arrow A4 divides the cross-section of crankshaft 4B, which includes oil supply hole 42c, into two regions R1 and R2. In this case, oil supply hole 42c is provided inside region R2, which is opposite to the direction in which roller 5b moves with the rotation of crankshaft 4B (arrow A3). Alternatively, oil supply hole 42c can be provided with an opening opposite to the direction of the velocity vector (not shown) of roller 5b during its revolution. The same applies to the other lower oil supply hole (not shown). That is, the circumferential positions of the upper oil supply hole 42c and the lower oil supply hole (not shown) are approximately aligned. However, the positions of oil supply holes 42c, etc., are not limited to this and can be other positions within region R2.

[0105] Figure 10 This is an explanatory diagram illustrating the process of roller 5b moving within cylinder 5a.

[0106] In addition, Figure 10 In the middle, crankshaft 4B with top dead center set to 0° (refer to...) Figure 9 The state with a rotation angle of 270° and Figure 9 The same. For example, under a rotation angle of 270° with a relatively large compressive load from the compression chamber C3, crankshaft 4B (refer to...) Figure 9 To the side opposite to blade 5e (in) Figure 10 The lower side of the paper (in the middle) is pressed down, and then the crankshaft 4B presses down on the upper bearing 5c ​​(refer to...). Figure 1 ), lower bearing 5d (refer to) Figure 1 ).

[0107] Here, due to the aforementioned region R2 (refer to...) Figure 9 The bearing has an oil supply hole 42c, therefore the oil supply hole 42c is close to the upper bearing 5c ​​(refer to...). Figure 1 The part subjected to compressive load in the bearing ). The same applies to the lower oil supply hole (not shown). Therefore, it is easy to move the bearing 5c ​​upwards (refer to...). Figure 1 ), lower bearing 5d (refer to) Figure 1 Lubricating oil is supplied to the parts subjected to compressive loads in the process.

[0108] <Effect>

[0109] According to the third embodiment, an oil supply hole 42c (and another oil supply hole) is provided inside the region R2 on the side opposite to the direction of movement of the roller 5b. Thus, lubricating oil is supplied to the parts of the upper bearing 5c ​​and the lower bearing 5d that are radially pressed by the crankshaft 4B (the parts subjected to compressive load). As a result, proper lubrication of the upper bearing 5c ​​and the lower bearing 5d can be achieved.

[0110] Fourth Implementation Method

[0111] In the fourth embodiment, the rotary compressor 100 described in the first embodiment (see reference) is used. Figure 1 Air conditioner W1 (refer to) Figure 11 This will be explained further. Additionally, since the structure of the rotary compressor 100 is similar to that of the first embodiment (see reference...), Figure 1 The structure described in the previous section is the same, so the description is omitted.

[0112] Figure 11 This is a structural diagram of the air conditioner W1 according to the fourth embodiment.

[0113] also, Figure 11 The solid arrow indicates the flow of refrigerant during heating operation. On the other hand, Figure 11 The dashed arrows indicate the flow of refrigerant during refrigeration operation.

[0114] Air conditioner W1 is a device used for air conditioning, such as cooling and heating. For example... Figure 11 As shown, the air conditioner W1 includes a rotary compressor 100, an outdoor heat exchanger 71, an outdoor fan 72, an expansion valve 73, a four-way valve 74, an indoor heat exchanger 75, and an indoor fan 76.

[0115] exist Figure 11 In this example, the rotary compressor 100, outdoor heat exchanger 71, outdoor fan 72, expansion valve 73, and four-way valve 74 are located in the outdoor unit U1. On the other hand, the indoor heat exchanger 75 and indoor fan 76 are located in the indoor unit U2.

[0116] The rotary compressor 100 has the same characteristics as in the first embodiment (see reference 1). Figure 1 The same structure. Furthermore, although in Figure 11 The illustration is omitted, but a receiver for refrigerant gas-liquid separation is connected to the refrigerant suction side of the rotary compressor 100.

[0117] The outdoor heat exchanger 71 is a heat exchanger that exchanges heat between the refrigerant flowing in its heat transfer pipes (not shown) and the external air supplied from the outdoor fan 72. The outdoor fan 72 is a fan that supplies external air to the outdoor heat exchanger 71. The outdoor fan 72 is equipped with an outdoor fan motor 72a as a drive source and is located near the outdoor heat exchanger 71.

[0118] The indoor heat exchanger 75 is a heat exchanger that exchanges heat between refrigerant flowing in its heat transfer tubes (not shown) and indoor air (air in the air-conditioned room) supplied from the indoor fan 76. The indoor fan 76 is a fan that supplies indoor air to the indoor heat exchanger 75. The indoor fan 76 has an indoor fan motor 76a as a drive source and is located near the indoor heat exchanger 75.

[0119] Expansion valve 73 is a valve that reduces the pressure of the refrigerant after it has condensed in the "condenser" (one of the outdoor heat exchanger 71 and the indoor heat exchanger 75). In addition, the refrigerant after being reduced in pressure by expansion valve 73 is guided to the "evaporator" (the other of the outdoor heat exchanger 71 and the indoor heat exchanger 75).

[0120] The four-way valve 74 is a valve that switches the refrigerant flow path according to the operating mode of the air conditioner W1. For example, during cooling operation (see...). Figure 11 (The dashed arrow indicates that) in the refrigerant circuit Q1, the refrigerant circulates sequentially through the rotary compressor 100, the outdoor heat exchanger 71 (condenser), the expansion valve 73, and the indoor heat exchanger 75 (evaporator). On the other hand, during heating operation (see...), Figure 11 (Solid arrow) In the refrigerant circuit Q1, the refrigerant circulates sequentially through the rotary compressor 100, the indoor heat exchanger 75 (condenser), the expansion valve 73, and the outdoor heat exchanger 71 (evaporator).

[0121] <Effect>

[0122] According to the fourth embodiment, the air conditioner W1 includes a high-performance and reliable rotary compressor 100. This improves the performance and reliability of the air conditioner W1.

[0123] Variations

[0124] The rotary compressor 100 of the present invention has been described above in various embodiments, but the present invention is not limited to these descriptions and various modifications can be made.

[0125] For example, in the first and second embodiments, the oil supply path 4e (refer to...) Figure 1 The lubricating oil is guided to the gap G1 between the upper bearing 5c ​​and the eccentric part 4b (refer to...). Figure 3B And it is also guided to the gap G2 between the lower bearing 5d and the eccentric part 4b (refer to...). Figure 3B The structure of the crankshaft 4 (shaft) has been described, but is not limited to this. That is, the oil supply port located on the crankshaft 4 (shaft) can also supply oil from the oil supply path 4e (see reference). Figure 1 The lubricating oil is guided to the gap between at least one of the upper bearing 5c ​​and the lower bearing 5d and the eccentric portion 4b. Specifically, the upper movement limiting portion 4c (see the first embodiment) can also be used. Figure 3A ) and the lower movement restriction part 4d (refer to Figure 3A At least one of them shall be provided with an oil supply port.

[0126] Alternatively, the eccentric portion 4Ab (see the second embodiment) can also be described. Figure 7An oil supply hole is provided on at least one of the upper and lower parts of the ). Furthermore, in the second embodiment, an oil supply hole H1 (refer to...) is provided on at least one of the upper and lower parts of the ). Figure 7 When the oil supply hole H1 is located above the eccentric portion 4Ab, it communicates with the gap between the upper bearing 5c ​​and the eccentric portion 4Ab. Furthermore, in the second embodiment, the oil supply hole H2 (refer to...) Figure 7 When the oil supply hole H2 is located at the lower part of the eccentric part 4Ab, it communicates with the gap between the lower bearing 5d and the eccentric part 4Ab.

[0127] Furthermore, if one of the oil supply ports 41c and 41d is omitted, the rotary compressor 100 is preferably configured as follows: That is, in the oil supply path 4e (refer to...) Figure 1 The lubricating oil is guided at least to the gap G1 between the upper bearing 5c ​​and the eccentric part 4b (refer to...). Figure 3B In the structure of the upper bearing 5c, the portion F1 of the first chamfered portion 51c facing the clearance G1 is preferred (refer to...). Figure 5 The area of ​​the bearing 5c ​​is larger than the flow path area of ​​the oil supply hole 41c. As a result, the lubricating oil flowing out through the oil supply hole 41c is easily guided to the inner circumference of the upper bearing 5c.

[0128] Additionally, in the oil supply path 4e (refer to...) Figure 1 The lubricating oil is guided at least to the gap G2 between the lower bearing 5d and the eccentric part 4b (refer to...). Figure 3B In the structure, the area of ​​the second chamfered portion 51d of the lower bearing 5d facing the clearance G2 is preferably larger than the flow path area of ​​the oil supply hole 41d. Therefore, the lubricating oil flowing out through the oil supply hole 41d is easily guided to the inner circumferential side of the lower bearing 5d. Furthermore, in the second embodiment, the same applies even if one of the oil supply holes H1 or H2 is omitted.

[0129] Furthermore, in each embodiment, the rotary compressor 100 includes a compression mechanism 5 (see reference). Figure 1 The following description is provided, but it is not limited to this. For example, although not shown, the crankshaft of the rotary compressor may have two eccentric portions that are eccentrically offset to opposite sides. One eccentric portion slides in contact with the inner circumferential surface of the roller of the first compression mechanism, and the other eccentric portion slides in contact with the inner circumferential surface of the roller of the second compression mechanism. Furthermore, a partition plate is provided between the vertically arranged cylinders of the two compression mechanism sections. With this structure, the rotational imbalance caused by the movement of one eccentric portion is offset by the other eccentric portion, thus suppressing the vibration of the rotary compressor. In this structure, an oil supply hole can be provided on one of the two eccentric portions, or an oil supply hole can be provided on both of the two eccentric portions. Furthermore, the structure of the oil supply hole is the same as in the first embodiment (see...). Figure 4 ) or the second embodiment (refer to) Figure 8The same applies. Additionally, the number of compression mechanism sections can be three or more.

[0130] In addition, in each embodiment, a spiral oil supply groove 52c is provided on the upper bearing 5c ​​(see reference). Figure 3A An axial oil supply groove 52d is provided in the lower bearing 5d (refer to...). Figure 3A The situation described is not limited to this. That is, the shape and range of the oil supply tanks 52c and 52d can be appropriately changed.

[0131] Furthermore, in the fourth embodiment, the air conditioner W1 (refer to...) Figure 11 Equipped with a four-way valve 74 (refer to) Figure 11 The following situations have been described, but are not limited to them. For example, in the case of air conditioners that are dedicated to cooling or heating, the four-way valve may be appropriately omitted.

[0132] Furthermore, the various embodiments can be appropriately combined. For example, the second embodiment (refer to...) can be combined... Figure 8 ) and the fourth embodiment (refer to Figure 11 Alternatively, the third embodiment (see reference) can also be combined. Figure 9 ) and the fourth embodiment (refer to Figure 11 )combination.

[0133] Furthermore, in each embodiment, the rotary compressor 100 (refer to...) Figure 1 The longitudinal configuration has been described, but it is not limited to this. That is, various embodiments can also be applied when the rotary compressor 100 is configured in a horizontal or inclined manner.

[0134] Additionally, the air conditioner W1 described in the fourth embodiment (refer to...) Figure 11 In addition to indoor air conditioning and modular air conditioning, it can also be used in various air conditioning units such as multi-split air conditioning units for buildings.

[0135] Furthermore, in the fourth embodiment, the air conditioner W1 equipped with the rotary compressor 100 (see reference) Figure 11 The description is provided, but it is not limited to this. That is, in addition to being applicable to refrigeration units, hot water supply units, and air conditioning hot water supply systems, the rotary compressor 100 can also be applied to various equipment such as refrigerators.

[0136] Furthermore, the various embodiments are described in detail for the purpose of easily understanding and illustrating the present invention, and are not necessarily limited to having all the structures described. In addition, for a part of the structure of each embodiment, other structures can be added, deleted, or replaced.

[0137] In addition, the above-mentioned mechanisms and structures show those that are deemed necessary for the description, and do not necessarily show all the mechanisms and structures on the product.

Claims

1. A rotary compressor, characterized in that, The device comprises a cylinder and an annular roller revolving within the cylinder, and further comprises: a shaft having a main shaft portion and an eccentric portion eccentrically positioned relative to the main shaft portion and slidingly contacting the inner circumferential surface of the roller; an upper bearing disposed on the upper side of the cylinder and providing shaft support; a lower bearing disposed on the lower side of the cylinder and providing shaft support; and plate-shaped blades separating the space between the cylinder and the roller. The shaft has an upper movement limiting portion disposed on the upper side of the eccentric portion on the radially inner side of the roller and restricting the axial movement of the shaft, and a lower movement limiting portion disposed on the lower side of the eccentric portion on the radially inner side of the roller and restricting the axial movement of the shaft. The shaft is provided with an oil supply path that guides lubricating oil in the axial direction, and an oil supply hole for the lubricating oil to flow from the oil supply path. The oil supply port is located on at least one of the upper movement limiting part and the lower movement limiting part. The oil supply hole guides the lubricating oil from the oil supply path to the gap between at least one of the upper bearing and the lower bearing and the eccentric portion. The position of the oil supply hole on the axial direction of the shaft is within the axial range of the cylinder barrel. The moment of inertia of the section of the shaft containing the oil supply hole is greater than that of the section of the main shaft containing the oil supply flow path, which is perpendicular to the axis of the shaft.

2. A rotary compressor, characterized in that, The device comprises a cylinder and an annular roller revolving within the cylinder, and further comprises: a shaft having a main shaft portion and an eccentric portion eccentrically positioned relative to the main shaft portion and slidingly contacting the inner circumferential surface of the roller; an upper bearing disposed on the upper side of the cylinder and providing shaft support; a lower bearing disposed on the lower side of the cylinder and providing shaft support; and plate-shaped blades separating the space between the cylinder and the roller. The shaft is provided with an oil supply path that guides lubricating oil in the axial direction, and an oil supply hole for the lubricating oil to flow from the oil supply path. The oil supply hole is located on at least one of the upper and lower parts of the eccentric portion. The oil supply hole guides the lubricating oil from the oil supply path to the gap between at least one of the upper bearing and the lower bearing and the eccentric portion. When the oil supply hole is located on the upper part of the eccentric portion, the oil supply hole communicates with the gap between the upper bearing and the eccentric portion, and has: a hole portion located near the upper end of the circumferential surface of the eccentric portion; and a notch portion formed by chamfering the periphery of the hole portion. When the oil supply hole is located at the lower part of the eccentric portion, the oil supply hole communicates with the gap between the lower bearing and the eccentric portion, and has: a hole portion located near the lower end of the circumferential surface of the eccentric portion; and a notch portion formed by chamfering the periphery of the hole portion. The position of the oil supply hole on the axial direction of the shaft is within the axial range of the cylinder barrel. The moment of inertia of the section of the shaft containing the oil supply hole is greater than that of the section of the main shaft containing the oil supply flow path, which is perpendicular to the axis of the shaft.

3. A rotary compressor, characterized in that, The device comprises a cylinder and an annular roller revolving within the cylinder, and further comprises: a shaft having a main shaft portion and an eccentric portion eccentrically positioned relative to the main shaft portion and slidingly contacting the inner circumferential surface of the roller; an upper bearing disposed on the upper side of the cylinder and providing shaft support; a lower bearing disposed on the lower side of the cylinder and providing shaft support; and plate-shaped blades separating the space between the cylinder and the roller. The shaft is provided with an oil supply path that guides lubricating oil in the axial direction, and an oil supply hole for the lubricating oil to flow from the oil supply path. The oil supply hole guides the lubricating oil from the oil supply path to the gap between at least one of the upper bearing and the lower bearing and the eccentric portion. The position of the oil supply hole on the axial direction of the shaft is within the axial range of the cylinder barrel. The moment of inertia of the section of the shaft containing the oil supply hole that is perpendicular to the axis of the shaft is greater than the moment of inertia of the section of the main shaft containing the oil supply flow path that is perpendicular to the axis of the shaft. When the cross-section of the shaft containing the oil supply hole is divided into two regions by a straight line extending through the central axis of the shaft and in the direction of eccentricity of the eccentric portion, the oil supply hole is provided inside the region on the side opposite to the direction in which the roller moves with the rotation of the shaft.

4. The rotary compressor according to any one of claims 1 to 3, characterized in that, In a structure where lubricating oil from the oil supply path is at least guided to the gap between the upper bearing and the eccentric portion, The upper bearing has a first chamfered portion near the lower end of its inner circumferential surface. The area of ​​the portion of the first chamfer facing the gap is larger than the flow path area of ​​the oil supply hole.

5. The rotary compressor according to any one of claims 1 to 3, characterized in that, In a structure where the lubricating oil in the oil supply path is guided at least to the gap between the lower bearing and the eccentric portion,... The lower bearing has a second chamfered portion near the upper end of its inner circumferential surface, which is formed by chamfering. The area of ​​the portion of the second chamfer facing the gap is larger than the flow path area of ​​the oil supply hole.

6. The rotary compressor according to claim 1 or 2, characterized in that, The oil supply hole is located within ±90° of the circumference of the shaft, with reference to the direction opposite to the direction of the eccentric part relative to the spindle part.

7. An air conditioner, characterized in that, It comprises a rotary compressor as described in any one of claims 1 to 3, and further comprises an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger.

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