JP2023180875A - Rotary compressor and air conditioner - Google Patents

Abstract

To provide a rotary compressor, etc. having high reliability.SOLUTION: A rotary compressor comprises a cylinder 5a, a roller 5b, a crankshaft 4, an upper bearing 5c, a lower bearing 5d, and a vane. The crankshaft 4 is provided with an oil supply flow passage, and provided with oil supply holes 41c and 41d. The oil supply holes 41c and 41d guide lubricating oil from the oil supply flow passage to a gap between at least one of the upper bearing 5c and the lower bearing 5d and an eccentric part 4b. The positions of the oil supply holes 41c and 41d in the axial direction of the crankshaft 4 are within an axial range where the cylinder 5a is provided. The geometrical moment of inertia of a plane perpendicular to the axial direction of the crankshaft 4 and including the oil supply hole 41c or 41d in the crankshaft 4 is larger than the geometrical moment of inertia of a plane perpendicular to the axial direction of the crankshaft 4 and including the oil supply flow passage in a main shaft part 4a.SELECTED DRAWING: Figure 4

Description

The present invention relates to a rotary compressor and the like.

Regarding rotary compressors, for example, the techniques described in Patent Documents 1 and 2 are known. That is, Patent Document 1 describes that a thrust sliding surface near an eccentric axis of a crankshaft of a rotary compressor is partially provided with an inclined shape. Further, Patent Document 2 describes that a crankshaft of a rotary compressor is provided with an oil supply hole and a gas vent hole.

JP2012-077728A Japanese Patent Application Publication No. 2015-040472

In the technology described in Patent Document 1, lubricating oil is easily supplied to the lower bearing etc. by providing a groove in the crankshaft that is recessed radially inward at a location corresponding to the upper end of the lower bearing ( Figure 1 of Patent Document 1). However, when such grooves are provided on the surface of the crankshaft, the rigidity of the crankshaft is reduced, making the crankshaft more likely to deform due to the compressive load of the refrigerant or the like. As a result, there is a possibility that the crankshaft hits the upper bearing or the lower bearing unevenly.

Further, in the technology described in Patent Document 2, a lower oil supply hole for supplying oil to the sliding surface between the crankshaft and the sub-bearing (lower bearing) is provided at a location corresponding to the sub-bearing on the crankshaft. (Figure 1 of Patent Document 2). However, when such a lower oil supply hole is provided in the crankshaft, the rigidity of the crankshaft is reduced, so that uneven contact of the crankshaft with the sub bearing etc. may occur. Therefore, there is room to further improve the reliability of the rotary compressor.

Therefore, an object of the present invention is to provide a highly reliable rotary compressor.

In order to solve the above-mentioned problems, a rotary compressor according to the present invention includes a cylinder, an annular roller that revolves within the cylinder, a main shaft part, and an annular roller that is eccentric with respect to the main shaft part, a shaft having an eccentric portion that makes sliding contact with the inner circumferential surface of the roller; an upper bearing that is provided above the cylinder and pivotally supports the shaft; and an upper bearing that is provided below the cylinder and pivotally supports the shaft. The shaft includes a lower bearing and a plate-shaped vane that partitions a space between the cylinder and the roller. an oil supply hole through which lubricating oil flows, the oil supply hole guiding the lubricating oil from the oil supply flow path to a gap between at least one of the upper bearing and the lower bearing and the eccentric portion, The position of the oil supply hole in the axial direction of the shaft is within the axial range in which the cylinder is provided, and is perpendicular to the axial direction of the shaft, and is a cross section of a surface of the shaft that includes the oil supply hole. The moment of inertia is perpendicular to the axial direction of the shaft and is larger than the moment of inertia of a surface of the main shaft portion including the oil supply flow path.

According to the present invention, a highly reliable rotary compressor etc. can be provided.

FIG. 1 is a longitudinal cross-sectional view of a rotary compressor according to a first embodiment. FIG. 2 is a sectional view taken along the line II-II in FIG. 1 of the rotary compressor according to the first embodiment. FIG. 3 is a diagram including a longitudinal section of a compression mechanism section of the rotary compressor according to the first embodiment. FIG. 3B is a partially enlarged view of region K1 shown in FIG. 3A in the rotary compressor according to the first embodiment. It is a perspective view including a crankshaft and a compression mechanism part of a rotary compressor concerning a 1st embodiment. It is an explanatory view regarding the position of the oil supply hole of the rotary compressor concerning a 1st embodiment. FIG. 3 is an explanatory diagram of a process in which a roller moves within the cylinder of the rotary compressor according to the first embodiment. FIG. 7 is a diagram including a longitudinal section of a compression mechanism section of a rotary compressor according to a second embodiment. It is a perspective view including the crankshaft and the compression mechanism part of the rotary compressor based on 2nd Embodiment. FIG. 7 is a cross-sectional view of a compression mechanism section including an upper oil supply hole of a rotary compressor according to a third embodiment. It is an explanatory view of a process in which a roller moves inside a cylinder of a rotary compressor concerning a 3rd embodiment. It is a block diagram of the air conditioner based on 4th Embodiment.

≪First embodiment≫
<Configuration of rotary compressor>
FIG. 1 is a longitudinal cross-sectional view of a rotary compressor 100 according to the first embodiment.
The rotary compressor 100 is a device that compresses gaseous refrigerant. As shown in FIG. 1, the rotary compressor 100 includes an airtight container 1, an electric motor 2, balance weights 31 and 32, a crankshaft 4 (shaft), a compression mechanism section 5, and a sound deadening cover 6. ing.

The airtight container 1 is a container that houses the electric motor 2, the crankshaft 4, the compression mechanism section 5, and the like, and is substantially airtight. The closed container 1 includes a cylindrical tube chamber 1a, a lid chamber 1b that closes the upper side of the tube chamber 1a, and a bottom chamber 1c that closes the lower side of the tube chamber 1a.

A suction pipe P1 is inserted into and fixed to the cylindrical chamber 1a of the closed container 1. The suction pipe P1 is a pipe that guides the refrigerant to the suction chamber C2 (see FIG. 2) of the compression mechanism section 5. Note that an accumulator 200 for performing gas-liquid separation of the refrigerant is connected to the upstream side of the suction pipe P1. Furthermore, a discharge pipe P2 is inserted into and fixed to the lid chamber 1b of the closed container 1. The discharge pipe P2 is a pipe that guides the refrigerant compressed by the compression mechanism section 5 to the outside of the rotary compressor 100. Lubricating oil for improving the lubricity and sealing properties of the rotary compressor 100 is sealed in the closed container 1, and is stored as an oil reservoir M1 at the bottom of the closed container 1.

The electric motor 2 is a drive source that rotates the crankshaft 4 and is installed inside the closed container 1. As shown in FIG. 1, the electric motor 2 includes a stator 2a and a rotor 2b. The stator 2a is a cylindrical member made of laminated electromagnetic steel plates, and is fixed to the inner peripheral surface of the cylindrical chamber 1a. A winding 21a is wound around the stator 2a in a predetermined manner. The rotor 2b is a cylindrical member having an iron core formed of an electromagnetic steel plate and a permanent magnet (not shown) embedded in the iron core, and is rotatably arranged inside the stator 2a in the radial direction. ing. A crankshaft 4 is coaxially fixed to the rotor 2b.

The crankshaft 4 is a shaft that rotates together with the rotor 2b as the electric motor 2 is driven. The crankshaft 4 extends in the vertical direction and is rotatably supported by an upper bearing 5c and a lower bearing 5d. As shown in FIG. 1, the crankshaft 4 includes a main shaft portion 4a, an eccentric portion 4b, an upper movement restriction portion 4c, and a lower movement restriction portion 4d.

The main shaft portion 4a is coaxially fixed to the rotor 2b of the electric motor 2. The main shaft portion 4a is provided above an eccentric portion 4b, which will be described next, and is also provided below the eccentric portion 4b. The eccentric portion 4b is a portion that rotates eccentrically with respect to the main shaft portion 4a. The eccentric portion 4b has a cylindrical outer shape and is formed integrally with the main shaft portion 4a. The eccentric portion 4b is arranged at the lower part of the crankshaft 4 and radially inside the roller 5b.

As shown in FIG. 1, the crankshaft 4 is provided with an oil supply passage 4e that guides lubricating oil in the axial direction, and oil supply holes 41c and 41d through which the lubricant from the oil supply passage 4e flows. There is. The oil supply channel 4e is a channel that guides lubricating oil stored in the closed container 1 as an oil reservoir M1 to the compression mechanism section 5. The oil supply passage 4e is provided in the axial direction of the crankshaft 4 and opens at the lower end of the crankshaft 4.

Note that the upper end of the oil supply channel 4e is located near the upper end of the upper movement restricting portion 4c, for example. Further, near the lower end of the oil supply channel 4e, a thin metal piece 4f twisted in a predetermined manner is provided as an oil pump. As the metal piece 4f rotates together with the crankshaft 4, lubricating oil is pumped up through the oil supply channel 4e. Although not shown in FIG. 1, a horizontal hole or the like may be provided as appropriate to guide lubricating oil from the oil supply channel 4e to the inner side of the roller 5b in the radial direction.

The upper movement restriction part 4c and the lower movement restriction part 4d are parts that restrict movement of the crankshaft 4 in the axial direction. The upper movement regulating portion 4c is provided above the eccentric portion 4b on the radially inner side of the roller 5b. Further, the lower movement regulating portion 4d is provided below the eccentric portion 4b on the radially inner side of the roller 5b. As shown in FIG. 1, an oil supply hole 41c that guides the lubricating oil in the oil supply passage 4e to the outside of the crankshaft 4 is provided in the upper movement restricting portion 4c in the radial direction. Similarly, another oil supply hole 41d is provided in the lower movement restricting portion 4d in the radial direction. Note that details of the oil supply holes 41c and 41d will be described later.

The compression mechanism section 5 is a mechanism that compresses gaseous refrigerant as the crankshaft 4 rotates, and is provided below the electric motor 2. The compression mechanism section 5 includes a cylinder 5a, a roller 5b, an upper bearing 5c, a lower bearing 5d, a vane 5e, a vane spring 5f, and a discharge valve 5g.

FIG. 2 is a sectional view taken along the line II--II in FIG.
Note that FIG. 2 is a cross-sectional view of the rotary compressor 100 taken along a horizontal plane (line II-II in FIG. 1) including the upper oil supply hole 41c and viewed from below.
The cylinder 5a shown in FIG. 2 is a member that forms a cylinder chamber C1 together with the roller 5b, the upper bearing 5c (see FIG. 3A), and the lower bearing 5d (see FIG. 3A), and has a generally annular (cylindrical) shape. Note that the cylinder chamber C1 is a space between the cylinder 5a and the roller 5b. The cylinder chamber C1 includes a suction chamber C2 into which refrigerant is introduced via a suction pipe P1 (see FIG. 1), and a compression chamber C3 which compresses the refrigerant.

The roller 5b is a member that revolves within the cylinder 5a as the electric motor 2 (see FIG. 1) is driven, and has an annular (cylindrical) shape. The roller 5b is configured to revolve inside the cylinder 5a while slidingly contacting the inner peripheral surface of the cylinder 5a. The eccentric portion 4b (see FIG. 1) of the crankshaft 4 described above has a cylindrical shape, and its outer diameter is slightly shorter than the inner diameter of the roller 5b. The eccentric portion 4b (see FIG. 1) moves while slidingly contacting the inner peripheral surface of the roller 5b, so that the roller 5b revolves inside the cylinder 5a.

The vane 5e is a plate-like member that partitions a space between the cylinder 5a and the roller 5b (that is, the cylinder chamber C1). That is, by pressing the tip of the vane 5e against the outer peripheral surface of the roller 5b, the cylinder chamber C1 is partitioned into a suction chamber C2 and a compression chamber C3.

As shown in FIG. 2, an arcuate base end portion 5h projecting radially outward from the cylinder 5a is provided integrally with the cylinder 5a. A suction pipe P1 (see FIG. 1) is inserted and fixed into a suction passage (not shown) that radially penetrates the base end portion 5h and the cylinder 5a. Then, the gaseous refrigerant is introduced into the suction chamber C2 through the suction pipe P1 (see FIG. 1) and the suction passage (not shown) in sequence.

Although not shown in FIG. 2, a vane spring mounting hole (not shown) for mounting the vane spring 5f (see FIG. 1) is provided in the radial direction at a predetermined location of the base end 5h. It is being Further, a radial slit (not shown) is provided in the cylinder 5a so as to communicate the vane spring mounting hole (not shown) with the radially inner space of the cylinder 5a. This slit is a space for moving the vane 5e back and forth in the radial direction, and is provided slightly wider than the plate thickness of the vane 5e.

The vane spring 5f shown in FIG. 1 is a spring that urges the vane 5e radially inward, and is installed in the vane spring mounting hole (not shown) described above. The tip of the vane 5e is pressed against the outer peripheral surface of the roller 5b due to the pressure difference between the inside and outside of the compression mechanism section 5 and the biasing force of the vane spring 5f. Thereby, the cylinder chamber C1 between the cylinder 5a and the roller 5b is partitioned into a suction chamber C2 and a compression chamber C3.

A discharge notch N1 is provided at a predetermined location on the inner peripheral edge of the upper surface of the cylinder 5a. This discharge notch N1 is a notch that guides the compressed refrigerant to the discharge valve 5g (see FIG. 1), and has an arcuate edge as shown in FIG. 2. Note that 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 vane 5e in the circumferential direction. That is, the suction passage (not shown) opens on one side of the vane 5e in the circumferential direction. Further, the discharge notch N1 is provided on the other side of the vane 5e in the circumferential direction.

FIG. 3A is a diagram including a longitudinal section of the compression mechanism section 5 of the rotary compressor.
The upper bearing 5c shown in FIG. 3A is a sliding bearing that rotatably supports the crankshaft 4, and is provided above the cylinder 5a (on one side in the axial direction). The upper bearing 5c is fastened together with the cylinder 5a and the lower bearing 5d with a plurality of bolts (not shown), and is further fixed to the inner peripheral surface of the cylindrical chamber 1a (see FIG. 1). The lower bearing 5d is a sliding bearing that rotatably supports the crankshaft 4, and is provided below the cylinder 5a (on the other side in the axial direction).

In addition, in the upper bearing 5c, the refrigerant compressed in the compression chamber C3 (see FIG. 2) is guided to the discharge valve 5g (see FIG. 1) at a location corresponding to the discharge notch N1 (see FIG. 2) of the cylinder 5a. Holes (not shown) are provided. The discharge valve 5g (see FIG. 1) is a valve (plate spring) for discharging compressed refrigerant into the space inside the closed container 1 (see FIG. 1), and is attached to the upper bearing 5c so as to close the hole described above. is set up. When the pressure of the compressed refrigerant overcomes the elastic force of the discharge valve 5g, the discharge valve 5g (see FIG. 1) opens.

The muffling cover 6 shown in FIG. 1 is a cover for suppressing noise caused by compression of refrigerant, and is fixed to the upper bearing 5c while partially covering the upper surface of the upper bearing 5c. The sound deadening cover 6 is provided with a plurality of holes (not shown) for releasing compressed refrigerant into the space inside the closed container 1.

FIG. 3B is a partially enlarged view of region K1 shown in FIG. 3A.
The oil supply hole 41c shown in FIG. 3B is a hole that guides lubricating oil from the oil supply passage 4e (see FIG. 1) to the gap G1 between the upper bearing 5c and the eccentric part 4b, and is a hole that guides the lubricating oil from the oil supply channel 4e (see FIG. 1) to the gap G1 between the upper bearing 5c and the eccentric portion 4b. It is provided in the upper movement regulating portion 4c. The other oil supply hole 41c is a hole that guides lubricating oil from the oil supply passage 4e (see FIG. 1) to the gap G2 between the lower bearing 5d and the eccentric portion 4b, and It is provided in the lower movement restricting portion 4d. Note that the positions of the oil supply holes 41c and 41d in the axial direction of the crankshaft 4 are within the axial range in which the cylinder 5a (see FIG. 3A) is provided.

As described above, the upper movement restricting portion 4c and the lower movement restricting portion 4d shown in FIG. 3A are portions that restrict the movement of the crankshaft 4 in the axial direction, and are provided on the radially inner side of the roller 5b. The upper movement restriction part 4c, the eccentric part 4b, and the lower movement restriction part 4d are integrally formed with the main shaft part 4a, and are vertically adjacent to each other in this order.

As shown in FIG. 3A, the upper surface of the upper movement restricting portion 4c is in contact with or close to the lower surface of the upper bearing 5c. When a force is applied to push the crankshaft 4 upward while the rotary compressor 100 (see FIG. 1) is being driven, the upper surface of the upper movement regulating portion 4c comes into contact with the lower surface of the upper bearing 5c, causing the crankshaft to move upward. The upward movement of the shaft 4 is restricted. Further, the lower surface of the lower movement restricting portion 4d is in contact with or close to the upper surface of the lower bearing 5d. When a force pushing down the crankshaft 4 is applied, the downward movement of the crankshaft 4 is restricted by the lower movement restricting portion 4d.

By providing the upper movement restricting portion 4c and the lower movement restricting portion 4d in this manner, movement of the crankshaft 4 in the axial direction is restricted. Moreover, the axial length of the eccentric portion 4b can be shortened while ensuring the volume of the cylinder chamber C1 (see FIG. 2). Therefore, sliding loss when the eccentric portion 4b comes into sliding contact with the roller 5b can be reduced, and energy efficiency when compressing the refrigerant can be increased.

The upper bearing 5c shown in FIG. 3B has a first chamfered portion 51c that is chamfered around the entire circumference near the lower end of the inner circumferential surface. The first chamfered portion 51c is a chamfered portion for guiding lubricating oil through the gap G1 between the upper bearing 5c and the eccentric portion 4b. Further, a spiral oil supply groove 52c (see FIG. 3A) is provided on the inner peripheral surface of the upper bearing 5c. The lubricating oil flowing out from the oil supply hole 41c is guided to the spiral oil supply groove 52c (see FIG. 3A) via the gap G1 between the first chamfered part 51c and the eccentric part 4b. .

The lower bearing 5d has a second chamfered portion 51d that is chamfered around the entire circumference near the upper end of its inner peripheral surface. The second chamfered portion 51d is a chamfered portion for guiding lubricating oil through the gap G2 between the lower bearing 5d and the eccentric portion 4b. Furthermore, an oil supply groove 52d (see FIG. 3A) is provided in the axial direction of the crankshaft 4 on the inner peripheral surface of the lower bearing 5d. The lubricating oil flowing out from the oil supply hole 41d is guided to the oil supply groove 52c (see FIG. 3A) via the gap G2 between the second chamfered portion 51d and the eccentric portion 4b.

FIG. 4 is a perspective view including the crankshaft 4 and compression mechanism section 5 of the rotary compressor.
Note that the compression mechanism section 5 in FIG. 4 is a perspective view taken along a predetermined plane including the central axis of the crankshaft 4. As shown in FIG. 4, the upper movement restricting portion 4c and the lower movement restricting portion 4d each have a predetermined columnar shape that is shorter in length in the vertical direction than the eccentric portion 4b. The shape of the cross section of the upper movement restriction part 4c and the lower movement restriction part 4d may be, for example, circular or elliptical, or may be other shapes as shown in FIG. 2.

The length of the upper movement restricting portion 4c protruding in the radial direction from the main shaft portion 4a is, for example, longest in the direction in which the eccentric portion 4b is eccentric, and longest in the direction opposite to the direction in which the eccentric portion 4b is eccentric. It may be made shorter. Note that the eccentric direction of the eccentric portion 4b refers to the direction in the radial direction toward the central axis (not shown) of the eccentric portion 4b with respect to the central axis (not shown) of the main shaft portion 4a. ing.

In the circumferential direction of the upper movement regulating portion 4c, the upper surface of the portion that corresponds to the direction in which the eccentric portion 4b is eccentric (approximately to the back of the paper in FIG. 4) contacts or is close to the lower surface of the upper bearing 5c. On the other hand, in the circumferential direction of the upper movement regulating portion 4c, a first chamfer is formed between the upper surface of the portion on the opposite side to the direction in which the eccentric portion 4b is eccentric (approximately on the front side in the paper in FIG. 4) and the upper bearing 5c. 51c faces a predetermined gap G1 (see FIG. 3B). Further, in the upper movement restricting portion 4c, an oil supply hole 41c is provided on the opposite side to the direction in which the eccentric portion 4b is eccentric.

As a result, the distance traveled by the lubricating oil flowing out through the upper oil supply hole 41c toward the first chamfered portion 51c is shortened, so that the lubricating oil is supplied to the inner circumferential surface of the upper bearing 5c (see FIG. 3B). It becomes easier. Similarly, for the lower movement restricting portion 4d (see FIG. 3B), an oil supply hole 41d (see FIG. 3B) is provided on the opposite side to the eccentric direction of the eccentric portion 4b.
Note that the positions where the oil supply holes 41c and 41d are provided are not limited to the positions opposite to the direction in which the eccentric portion 4b is eccentric. ) may be provided with an oil supply hole 41c or the like.

FIG. 5 is an explanatory diagram regarding the position of the oil supply hole 41c.
Note that the configuration shown in FIG. 5 is the same as that shown in FIG. 2, but the cross-sectional hatching is omitted for the sake of explanation. Furthermore, a portion F1 where the first chamfered portion 51c (see FIG. 3B) faces the upper gap G1 (see FIG. 3B) is hatched to make it more conspicuous.
For example, with respect to the direction in which the eccentric portion 4b is eccentric with respect to the main shaft portion 4a (arrow A1 in FIG. 5) and the opposite direction (arrow A2 in FIG. 5) as a reference, the angle is ±90° in the circumferential direction of the crankshaft 4. The oil supply hole 41c may be provided within the range (inside the dotted region S1 in FIG. 5). Note that the same applies to the other oil supply hole 41d (see FIG. 3B). As a result, for example, the distance traveled by the lubricating oil flowing out through the oil supply hole 41c toward the first chamfered portion 51c (see FIG. 3B) is shortened, so that oil supply to the upper bearing 5c is facilitated.

Incidentally, even when the oil supply hole 41c is provided at a location corresponding to the eccentric direction of the eccentric portion 4b, lubricating oil is supplied to the inner peripheral side of the upper bearing 5c. However, in this case, since the lubricating oil flows in a detour manner through the annular gap G1 (see FIG. 3B), the lubricating oil flowing out from the oil supply hole 41c moves until it is supplied to the upper bearing 5c. The distance becomes longer. Note that the same can be said about the lower oil supply hole 41d.

Further, the moment of inertia of the surface of the upper movement regulating portion 4c (that is, the crankshaft 4) that is perpendicular to the axial direction of the crankshaft 4 and includes the oil supply hole 41c is perpendicular to the axial direction of the crankshaft 4. It is preferable that the moment of inertia of the surface of the main shaft portion 4a including the oil supply flow path 4e (see FIG. 1) be larger than the moment of inertia of the surface of the main shaft portion 4a. Similarly, the moment of inertia of a surface perpendicular to the axial direction of the crankshaft 4 and including the oil supply hole 41d in the lower movement restricting portion 4d (that is, the crankshaft 4) is perpendicular to the axial direction of the crankshaft 4. It is preferable that the moment of inertia of the surface of the main shaft portion 4a including the oil supply flow path 4e (see FIG. 1) is larger than the moment of inertia of the surface of the main shaft portion 4a.

According to such a configuration, the oil supply holes 41c and 41d are provided in the upper movement regulating part 4c and the lower movement regulating part 4d, which have a larger moment of inertia than in the case where the oil supply hole is provided in the main shaft part 4a. , a decrease in rigidity of the crankshaft 4 can be suppressed. Further, not only can the upper bearing 5c be sufficiently supplied with oil through the upper oil supply hole 41c, but also the lower bearing 5d can be sufficiently supplied with oil through the lower oil supply hole 41d.

Further, the area of the portion F1 (the hatched portion in FIG. 5) where the first chamfered portion 51c (see FIG. 3B) faces the upper gap G1 (see FIG. 3B) is larger than the flow path area of the oil supply hole 41c. Larger is preferable. Here, the "flow passage area" of the oil supply hole 41c is the area of the oil supply hole 41c when cut along a predetermined plane perpendicular to the flow path direction of the oil supply hole 41c. In short, the area of the portion F1 described above is the area of a common portion when the area of the gap G1 shown in FIG. 5 is projected onto the annular first chamfered portion 51c (see FIG. 3B). According to such a configuration, the lubricating oil flowing out through the oil supply hole 41c is guided to the inner peripheral side of the upper bearing 5c via the gap G1 (see FIG. 3B) below the first chamfered portion 51c. It becomes easier. Therefore, lubrication of the upper bearing 5c is promoted.

Further, the area of the portion (not shown) where the second chamfered portion 51d (see FIG. 3B) faces the lower gap G2 (see FIG. 3B) may be larger than the flow path area of the oil supply hole 41d. preferable. According to such a configuration, the lubricating oil flowing out through the oil supply hole 41d is easily guided to the inner peripheral side of the lower bearing 5d via the gap G2 (see FIG. 3B) above the second chamfered portion 51d. . Therefore, lubrication of the lower bearing 5d is promoted.

FIG. 6 is an explanatory diagram of the process in which the roller 5b moves within the cylinder 5a.
Note that since FIG. 6 shows a cross section of the compression mechanism section 5 taken from the line II-II in FIG. 1 and viewed from above, it is different from FIG. The left and right are reversed.
Further, the rotation angle θ shown in FIG. 6 is the rotation angle of the crankshaft 4 (see FIG. 1). In the example of FIG. 6, the rotation angle θ is 0° when the roller 5b is located at the "top dead center" inside the cylinder 5a. The above-described "top dead center" is the position of the roller 5b when the center of the roller 5b is closest to the tip of the vane 5e.

When the rotation angle θ is 0°, the tip of the vane 5e is retracted by the roller 5b to the inner peripheral surface of the cylinder 5a, and the entire cylinder chamber C1 becomes a compression chamber C3. As the rotation angle of the roller 5b increases, the volume of the compression chamber C3 decreases, and the refrigerant is compressed. When the pressure of the refrigerant overcomes the elastic force of the discharge valve 5g (see Fig. 1), which is a leaf spring, the discharge valve 5g opens, and the inside of the closed container 1 (see Fig. 1) is opened via the discharge notch N1. High pressure refrigerant is discharged.

Further, as the crankshaft 4 (see FIG. 4) rotates, the upper movement restricting portion 4c (see FIG. 4) also rotates, and lubricating oil is supplied to the upper bearing 5c via the oil supply hole 41c. Similarly, as the crankshaft 4 rotates, the lower movement restricting portion 4d (see FIG. 4) also rotates, and lubricating oil is supplied to the lower bearing 5d via the oil supply hole 41d. Thereby, the upper bearing 5c and the lower bearing 5d are sufficiently lubricated.

<Effect>
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 hole 41c and the oil supply hole 41d is larger than the moment of inertia of the main shaft portion 4a. has been done. Therefore, a decrease in the rigidity of the crankshaft 4 can be suppressed 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 in the main shaft portion 4a. In particular, a decrease in the rigidity of the crankshaft 4 can be suppressed near the lower end of the upper bearing 5c and near the upper end of the lower bearing 5d, which are most susceptible to compressive loads. Further, even when the rotary compressor 100 is driven at high speed, the rigidity of the crankshaft 4 is ensured, so deformation of the crankshaft 4 due to compression load, centrifugal force, and magnetic attraction force can be suppressed. As a result, it is possible to suppress uneven contact of the crankshaft 4 to the upper bearing 5c and the lower bearing 5d, which in turn suppresses damage to the upper bearing 5c and the lower bearing 5d.

Further, in addition to the oil supply hole 41c provided in the upper movement restriction part 4c, another oil supply hole 41d is provided in the lower movement restriction part 4d. As a result, lubricating oil is sufficiently supplied to the upper bearing 5c and the lower bearing 5d, so that the performance and reliability of the rotary compressor 100 can be improved.

≪Second embodiment≫
In the second embodiment, the upper movement restriction part 4c (see FIG. 3A) and the lower movement restriction part 4d (see FIG. 3A) described in the first embodiment are not particularly provided, and the eccentric part 4Ab (see FIG. 7 (see) is longer in the axial direction than in the first embodiment. Further, the second embodiment differs from the first embodiment in that two oil supply holes H1 and H2 (see FIG. 7) are provided in the eccentric portion 4Ab (see FIG. 7). Note that other aspects are the same as those in the first embodiment. Therefore, the parts that are different from the first embodiment will be explained, and the explanation of the overlapping parts will be omitted.

FIG. 7 is a diagram including a longitudinal section of the compression mechanism section 5 of the rotary compressor according to the second embodiment.
As shown in FIG. 7, the crankshaft 4A includes a main shaft portion 4a and an eccentric portion 4Ab. The eccentric portion 4Ab is provided on the radially inner side of the roller 5b, and is in sliding contact with the inner circumferential surface of the roller 5b. The vertical length of the eccentric portion 4Ab is slightly shorter than the vertical lengths of the cylinder 5a and the roller 5b.

Furthermore, an oil supply hole H1 is provided in the upper part of the eccentric part 4Ab to guide the lubricating oil from the oil supply passage 4e (see FIG. 1) of the crankshaft 4A to the gap between the eccentric part 4Ab and the upper bearing 5c. . Similarly, an oil supply hole H2 is provided in the lower part of the eccentric part 4Ab to guide lubricating oil from the oil supply passage 4e (see FIG. 1) of the crankshaft 4A to the gap between the eccentric part 4Ab and the lower bearing 5d. There is. Note that the positions of the oil supply holes H1 and H2 in the axial direction of the crankshaft 4A are within the axial range in which the cylinder 5a is provided.

Further, near the lower end of the inner circumferential surface of the upper bearing 5c, a first chamfered portion 51c is provided over the entire circumference, similar to the first embodiment. The lubricating oil flowing upward 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 downward through the oil supply hole H2 is guided to the oil supply groove 52d via the gap between the lower bearing 5d and the eccentric portion 4Ab.

Note that 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. Further, 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 makes it easier to supply lubricating oil to the upper bearing 5c and the lower bearing 5d.

Further, the moment of inertia of a surface that is perpendicular to the axial direction of the crankshaft 4A and includes the oil supply hole H1 in the eccentric portion 4Ab (that is, the crankshaft 4A) is perpendicular to the axial direction of the crankshaft 4A, It is larger than the moment of inertia of the surface of the main shaft portion 4a that includes the oil supply flow path 4e (see FIG. 1). Similarly, the moment of inertia of a plane perpendicular to the axial direction of the crankshaft 4A and including the oil supply hole H2 in the eccentric portion 4Ab (that is, the crankshaft 4A) is perpendicular to the axial direction of the crankshaft 4A. , is larger than the moment of inertia of the surface of the main shaft portion 4a that includes the oil supply passage 4e (see FIG. 1). According to such a configuration, a decrease in the rigidity of the crankshaft 4A can be suppressed compared to a case where the oil supply hole is provided in the main shaft portion 4a. Further, the upper bearing 5c and the lower bearing 5d can be sufficiently supplied with oil through the oil supply holes H1 and H2.

Note that the circumferential positions of the oil supply holes H1 and H2 are the same as in the first embodiment (see FIG. 5). That is, it is preferable that the oil supply holes H1 and H2 be provided within a range of ±90° in the circumferential direction of the crankshaft 4A based on the direction opposite to the direction in which the eccentric portion 4Ab is eccentric with respect to the main shaft portion 4a. . As a result, portions where the upper and lower gaps of the eccentric portion 4Ab face the first chamfered portion 51c and the second chamfered portion 51d always exist near the oil supply holes H1 and H2. Therefore, lubricating oil is easily supplied to the upper bearing 5c and the lower bearing 5d.

FIG. 8 is a perspective view including the crankshaft 4A and the compression mechanism section 5 of the rotary compressor.
As shown in FIG. 8, the oil supply hole H1 on the upper side of the eccentric part 4Ab has a hole H11 provided near the upper end of the circumferential surface of the eccentric part 4Ab, and a chamfer-like cutout around the hole H11. It has a notch H12. To explain the notch H12, the edge of the hole H11 is cut downward in a U-shape from a predetermined location on the periphery of the upper surface of the eccentric part 4Ab, and the upper end of the hole H11 is cut radially inward. It's missing. Then, lubricating oil is led to the upper side of the eccentric portion 4Ab via the oil supply hole H1.

The oil supply hole H2 on the lower side of the eccentric part 4Ab includes a hole H21 provided near the lower end of the circumferential surface of the eccentric part 4Ab, and a notch H22 formed by cutting out the circumference of the hole H21 like a chamfer. have. Regarding the notch H22, the edge of the hole H21 is cut upward from a predetermined location on the periphery of the lower surface of the eccentric part 4Ab in an inverted U shape, and the lower end of the eccentric part 4Ab is cut radially inward. It's missing. The lubricating oil is led to the upper side of the eccentric portion 4Ab via the oil supply hole H2.

<Effect>
According to the second embodiment, even if the distance between the eccentric part 4Ab and the upper bearing 5c and the distance between the eccentric part 4Ab and the lower bearing 5d are relatively short, the oil supply holes H1 and H2 are provided in the eccentric part 4Ab. can be provided. Thereby, lubricating oil can be sufficiently supplied to the upper bearing 5c and the lower bearing 5d while suppressing a decrease in the rigidity of the crankshaft 4A.

≪Third embodiment≫
The third embodiment differs from the first embodiment in the circumferential position where the oil supply hole 42c and the like (see FIG. 9) are provided. Note that other aspects are the same as those in the first embodiment. Therefore, the parts that are different from the first embodiment will be explained, and the explanation of the overlapping parts will be omitted.

FIG. 9 is a cross-sectional view of the compression mechanism section 5 including the upper oil supply hole 42c of the rotary compressor according to the third embodiment.
In addition, in FIG. 9, hatching of the cross section is omitted for explanation. Further, arrow A3 shown in FIG. 9 indicates the direction in which the roller 5b revolves within the cylinder 5a.
As shown in FIG. 9, an oil supply hole 42c is provided in the upper movement restriction portion 4c. Further, although not shown in FIG. 9, another oil supply hole (not shown) is provided in the lower movement restricting portion 4d (see FIG. 1).

Then, a straight line L1 passing through the center axis Z1 of the crankshaft 4B and extending in the direction in which the eccentric portion 4b is eccentric (arrow A4 in FIG. 9) divides the cross section of the crankshaft 4B including the oil supply hole 42c into two regions R1, Suppose that it is divided into R2. In such a case, of the two regions R1 and R2, the oil supply hole 42c is provided inside the region R2 on the opposite side to the direction (arrow A3) in which the roller 5b moves with the rotation of the crankshaft 4B. There is. To explain from another point of view, the oil supply hole 42c is provided so as to open at a position opposite to the direction of the velocity vector (not shown) when the roller 5b revolves. The same applies to the other lower oil supply hole (not shown). In other words, the upper oil supply hole 42c and the lower oil supply hole (not shown) are substantially aligned in circumferential position. Note that the positions of the oil supply hole 42c and the like are not limited to this, and may be located at other positions in the region R2.

FIG. 10 is an explanatory diagram of the process in which the roller 5b moves within the cylinder 5a.
In FIG. 10, the state in which the rotation angle of the crankshaft 4B (see FIG. 9) is 270 degrees when the top dead center is 0 degrees is the same as in FIG. For example, in a state where the compression load from the compression chamber C3 is relatively large at a rotation angle of 270°, the crankshaft 4B (see FIG. 9) is pressed to the side opposite to the vane 5e (lower side in FIG. 10), and further, The upper bearing 5c (see FIG. 1) and the lower bearing 5d (see FIG. 1) are pressed by the crankshaft 4B.

Here, since the oil supply hole 42c is provided in the above-mentioned region R2 (see FIG. 9), the oil supply hole 42c is close to a portion of the upper bearing 5c (see FIG. 1) on which a compressive load acts. Note that the same can be said of the lower oil supply hole (not shown). This facilitates supply of lubricating oil to the portions of the upper bearing 5c (see FIG. 1) and the lower bearing 5d (see FIG. 1) on which compressive loads act.

<Effect>
According to the third embodiment, the oil supply hole 42c is provided inside the region R2 on the opposite side to the direction in which the roller 5b moves (the same applies to the other oil supply hole). As a result, lubricating oil is supplied to the portions of the upper bearing 5c and the lower bearing 5d that are pressed in the radial direction from the crankshaft 4B (portions on which a compressive load acts). As a result, the upper bearing 5c and the lower bearing 5d can be appropriately lubricated.

≪Fourth embodiment≫
In the fourth embodiment, an air conditioner W1 (see FIG. 11) including the rotary compressor 100 (see FIG. 1) described in the first embodiment will be described. Note that the configuration of the rotary compressor 100 is the same as that described in the first embodiment (see FIG. 1), so a description thereof will be omitted.

FIG. 11 is a configuration diagram of an air conditioner W1 according to the fourth embodiment.
Note that the solid arrows in FIG. 11 indicate the flow of refrigerant during heating operation.
On the other hand, dashed arrows in FIG. 11 indicate the flow of refrigerant during cooling operation.
The air conditioner W1 is a device that performs air conditioning such as cooling and heating. As shown in FIG. 11, 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. It is equipped with 76.

In the example of FIG. 11, a rotary compressor 100, an outdoor heat exchanger 71, an outdoor fan 72, an expansion valve 73, and a four-way valve 74 are provided in the outdoor unit U1. On the other hand, the indoor heat exchanger 75 and the indoor fan 76 are provided in the indoor unit U2.

The rotary compressor 100 has the same configuration as the first embodiment (see FIG. 1). Although not shown in FIG. 11, an accumulator for separating the refrigerant into gas and liquid is connected to the refrigerant suction side of the rotary compressor 100.
The outdoor heat exchanger 71 is a heat exchanger that performs heat exchange between the refrigerant flowing through its heat transfer tubes (not shown) and the outside air sent from the outdoor fan 72. The outdoor fan 72 is a fan that sends outside air into the outdoor heat exchanger 71. The outdoor fan 72 includes an outdoor fan motor 72a as a driving source, and is installed near the outdoor heat exchanger 71.

The indoor heat exchanger 75 is a heat exchanger in which heat exchange is performed between the refrigerant flowing through its heat transfer tubes (not shown) and the indoor air (air in the air conditioning room) sent from the indoor fan 76. be. The indoor fan 76 is a fan that sends indoor air to the indoor heat exchanger 75. The indoor fan 76 includes an indoor fan motor 76a as a driving source, and is installed near the indoor heat exchanger 75.

The expansion valve 73 is a valve that reduces the pressure of the refrigerant condensed in the "condenser" (one of the outdoor heat exchanger 71 and the indoor heat exchanger 75). Note that the refrigerant whose pressure has been reduced by the expansion valve 73 is guided to the "evaporator" (the other of the outdoor heat exchanger 71 and the indoor heat exchanger 75).

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 the dashed arrow in FIG. 11), in the refrigerant circuit Q1, the rotary compressor 100, the outdoor heat exchanger 71 (condenser), the expansion valve 73, and the indoor heat exchanger 75 (evaporator) ), the refrigerant is circulated in sequence. On the other hand, during heating operation (see the solid arrow in FIG. 11), in the refrigerant circuit Q1, the rotary compressor 100, indoor heat exchanger 75 (condenser), expansion valve 73, and outdoor heat exchanger 71 (evaporator) ), the refrigerant is circulated in sequence.

<Effect>
According to the fourth embodiment, the air conditioner W1 includes the rotary compressor 100 with high performance and reliability. Thereby, the performance and reliability of the air conditioner W1 can be improved.

≪Modification example≫
Although the rotary compressor 100 and the like according to the present invention have been described above in each embodiment, the present invention is not limited to these descriptions, and various changes can be made.
For example, in the first embodiment and the second embodiment, the lubricating oil in the oil supply channel 4e (see FIG. 1) is guided to the gap G1 (see FIG. 3B) between the upper bearing 5c and the eccentric portion 4b, and Although a configuration has been described in which the guide is also guided to the gap G2 (see FIG. 3B) between the bearing 5d and the eccentric portion 4b, the present invention is not limited to this. That is, the oil supply hole provided in the crankshaft 4 (shaft) supplies lubricating oil from the oil supply passage 4e (see FIG. 1) to the gap between the eccentric portion 4b and at least one of the upper bearing 5c and the lower bearing 5d. You can also guide them. Specifically, an oil supply hole may be provided in at least one of the upper movement restriction part 4c (see FIG. 3A) and the lower movement restriction part 4d (see FIG. 3A) described in the first embodiment.
Further, an oil supply hole may be provided in at least one of the upper and lower parts of the eccentric portion 4Ab (see FIG. 7) described in the second embodiment. In addition, in the second embodiment, when the oil supply hole H1 (see FIG. 7) is provided in the upper part of the eccentric part 4Ab, this oil supply hole H1 communicates with the gap between the upper bearing 5c and the eccentric part 4Ab. It is assumed that there is In addition, in the second embodiment, when the oil supply hole H2 (see FIG. 7) is provided at the lower part of the eccentric part 4Ab, this oil supply hole H2 communicates with the gap between the lower bearing 5d and the eccentric part 4Ab. It is assumed that there is

Further, in the case where one of the oil supply holes 41c and 41d is omitted, it is preferable that the rotary compressor 100 has the following configuration. That is, in a configuration in which the lubricating oil in the oil supply channel 4e (see FIG. 1) is guided at least to the gap G1 (see FIG. 3B) between the upper bearing 5c and the eccentric portion 4b, the first chamfered portion 51c of the upper bearing 5c The area of the portion F1 (see FIG. 5) facing the gap G1 is preferably larger than the flow path area of the oil supply hole 41c. This makes it easier for the lubricating oil flowing out through the oil supply hole 41c to be guided to the inner peripheral side of the upper bearing 5c.
Further, in a configuration in which the lubricating oil in the oil supply channel 4e (see FIG. 1) is guided at least to the gap G2 (see FIG. 3B) between the lower bearing 5d and the eccentric portion 4b, the second chamfered portion 51d of the lower bearing 5d The area of the portion facing the gap G2 is preferably larger than the flow path area of the oil supply hole 41d. Thereby, the lubricating oil flowing out through the oil supply hole 41d is easily guided to the inner peripheral side of the lower bearing 5d. Note that, in the second embodiment, the same can be said about the case where one of the oil supply holes H1 and H2 is omitted.

Further, in each embodiment, a case has been described in which the rotary compressor 100 includes one compression mechanism section 5 (see FIG. 1), but the present invention is not limited to this. For example, although not shown, the crankshaft of a rotary compressor includes two eccentric parts that are eccentric to opposite sides, one eccentric part slidingly contacts the inner peripheral surface of the roller of the first compression mechanism part, The other eccentric part may be in sliding contact with the inner circumferential surface of the roller of the second compression mechanism part. Note that a partition plate is interposed between the cylinders of the two compression mechanisms in the vertical direction. According to such a configuration, the rotational imbalance caused by the movement of one eccentric portion is canceled out by the other eccentric portion, so that vibrations of the rotary compressor are suppressed. In such a configuration, the oil supply hole may be provided in one of the two eccentric parts, or the oil supply hole may be provided in both of the two eccentric parts. Note that the configuration of the oil supply hole is similar to that in the first embodiment (see FIG. 4) or the second embodiment (see FIG. 8). Further, the number of compression mechanism sections may be three or more.

Furthermore, in each embodiment, a case has been described in which the upper bearing 5c is provided with a spiral oil supply groove 52c (see FIG. 3A), and the lower bearing 5d is provided with an axial oil groove 52d (see FIG. 3A). Not limited to. That is, the shape and range of the oil supply grooves 52c and 52d can be changed as appropriate.

Further, in the fourth embodiment, a case has been described in which the air conditioner W1 (see FIG. 11) includes the four-way valve 74 (see FIG. 11), but the present invention is not limited to this. For example, in the case of an air conditioner dedicated to cooling or heating, the four-way valve may be omitted as appropriate.
Moreover, each embodiment can be combined as appropriate. For example, the second embodiment (see FIG. 8) and the fourth embodiment (see FIG. 11) may be combined, or the third embodiment (see FIG. 9) and the fourth embodiment (see FIG. 11) may be combined. You may also combine them.

Further, in each embodiment, a case has been described in which the rotary compressor 100 (see FIG. 1) is arranged vertically, but the present invention is not limited thereto. That is, each embodiment can be applied even when the rotary compressor 100 is placed horizontally or diagonally.
Moreover, the air conditioner W1 (see FIG. 11) described in the fourth embodiment can be applied to various types of air conditioners such as a room air conditioner, a package air conditioner, and a multi-air conditioner for buildings.

Furthermore, in the fourth embodiment, the air conditioner W1 (see FIG. 11) including the rotary compressor 100 has been described, but the present invention is not limited thereto. That is, the rotary compressor 100 can be applied to various devices such as refrigerators, water heaters, air conditioning and hot water systems, and refrigerators.

Further, each embodiment is described in detail to explain the present invention in an easy-to-understand manner, and the present invention is not necessarily limited to having all the configurations described. Furthermore, it is possible to add, delete, or replace some of the configurations of each embodiment with other configurations.
Further, the mechanisms and configurations described above are those considered necessary for explanation, and not all mechanisms and configurations are necessarily shown in the product.

1 Airtight container 2 Electric motor 4, 4A, 4B Crankshaft (shaft)
4a Main shaft part 4b, 4Ab Eccentric part 4c Upper movement restriction part 4d Lower movement restriction part 41c, 42c Oil supply hole (upper oil supply hole)
41d Oil supply hole (lower oil supply hole)
4e Oil supply channel 5, 5A Compression mechanism section 5a Cylinder 5b Roller 5c Upper bearing 5d Lower bearing 51c First chamfer 51d Second chamfer 5e Vane 71 Outdoor heat exchanger 72 Outdoor fan 73 Expansion valve 74 Four-way valve 75 Indoor heat exchange 76 Indoor fan 100 Rotary compressor C1 Cylinder chamber (space)
F1 part G1 gap (gap between upper bearing and eccentric part)
G2 Gap (gap between lower bearing and eccentric part)
H1 Oil supply hole (upper oil supply hole)
H2 Oil supply hole (lower oil supply hole)
L1 straight line R1 area R2 area (opposite area)
W1 Air conditioner Z1 Center axis (center axis of shaft)

In order to solve the above-mentioned problems, a rotary compressor according to the present invention includes a cylinder, an annular roller that revolves within the cylinder, a main shaft part, and an annular roller that is eccentric with respect to the main shaft part, a shaft having an eccentric portion that makes sliding contact with the inner circumferential surface of the roller; an upper bearing that is provided above the cylinder and pivotally supports the shaft; and an upper bearing that is provided below the cylinder and pivotally supports the shaft. a lower bearing; and a plate-shaped vane that partitions a space between the cylinder and the roller ; the shaft is provided above the eccentric portion on the inside of the roller in the radial direction; an upper movement restriction part that restricts movement of the shaft; and a lower movement restriction part that is provided below the eccentric part on the inside of the roller in the radial direction and restricts movement of the shaft in the axial direction; The shaft is provided with an oil supply passage that guides lubricating oil in the axial direction, and is also provided with an oil supply hole through which the lubricant from the oil supply passage flows, and the oil supply hole is connected to the upper movement regulating portion and the lower movement restriction portion. The oil supply hole is provided in at least one of the side movement regulating parts, and the oil supply hole guides lubricating oil from the oil supply flow path into a gap between at least one of the upper bearing and the lower bearing and the eccentric part, and The position of the oil supply hole in the axial direction is within the axial range in which the cylinder is provided, is perpendicular to the axial direction of the shaft, and is a cross-sectional quadratic of a surface of the shaft that includes the oil supply hole. The moment is perpendicular to the axial direction of the shaft and is larger than the moment of inertia of a surface of the main shaft portion including the oil supply flow path. Note that other details will be explained in the embodiment.

Claims (8)

cylinder and
an annular roller that revolves within the cylinder;
A shaft having a main shaft portion, and an eccentric portion that is eccentric with respect to the main shaft portion and comes into sliding contact with the inner circumferential surface of the roller;
an upper bearing provided above the cylinder and pivotally supporting the shaft;
a lower bearing provided on the lower side of the cylinder and pivotally supporting the shaft;
a plate-shaped vane that partitions a space between the cylinder and the roller;
The shaft is provided with an oil supply passage that guides lubricating oil in the axial direction, and is provided with an oil supply hole through which the lubricant from the oil supply passage flows,
The oil supply hole guides lubricating oil from the oil supply flow path to a gap between at least one of the upper bearing and the lower bearing and the eccentric portion,
The position of the oil supply hole in the axial direction of the shaft is within an axial range in which the cylinder is provided,
A moment of inertia of a surface perpendicular to the axial direction of the shaft and including the oil supply hole in the shaft is equal to a moment of inertia of a surface perpendicular to the axial direction of the shaft and including the oil supply flow path in the main shaft portion. Rotary compressor with larger moment of inertia. The shaft is
an upper movement restriction part that is provided above the eccentric part on the radially inner side of the roller and restricts movement of the shaft in the axial direction;
a lower movement restricting portion provided below the eccentric portion on the radially inner side of the roller and restricting movement of the shaft in the axial direction;
The rotary compressor according to claim 1, wherein the oil supply hole is provided in at least one of the upper movement restriction part and the lower movement restriction part. The oil supply hole is provided in at least one of an upper part and a lower part of the eccentric part,
When the oil supply hole is provided in the upper part of the eccentric part, the oil supply hole communicates with a gap between the upper bearing and the eccentric part,
The rotary compression according to claim 1, wherein when the oil supply hole is provided at a lower part of the eccentric part, the oil supply hole communicates with a gap between the lower bearing and the eccentric part. Machine. In a configuration in which lubricating oil from the oil supply flow path is guided to at least a gap between the upper bearing and the eccentric part,
The upper bearing has a first chamfered portion that is chamfered near the lower end of the inner circumferential surface of the upper bearing,
The rotary compressor according to claim 1, wherein an area of a portion of the first chamfer facing the gap is larger than a flow path area of the oil supply hole. In a configuration in which the lubricating oil in the oil supply flow path is guided to at least a gap between the lower bearing and the eccentric part,
The lower bearing has a second chamfered portion that is chamfered near the upper end of the inner circumferential surface of the lower bearing,
The rotary compressor according to claim 1, wherein an area of a portion of the second chamfer facing the gap is larger than a flow path area of the oil supply hole. The oil supply hole is provided within a range of ±90° in the circumferential direction of the shaft based on a direction opposite to a direction in which the eccentric portion is eccentric with respect to the main shaft portion. 1. The rotary compressor according to 1. In a case where the cross section of the shaft including the oil supply hole is divided into two regions by a straight line passing through the central axis of the shaft and extending in the direction in which the eccentric portion is eccentric, out of the two regions, the shaft The rotary compressor according to claim 1, wherein the oil supply hole is provided inside a region opposite to a direction in which the roller moves as the roller rotates. An air conditioner comprising the rotary compressor according to claim 1, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger.

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