JP7228730B1 - Rotary compressor and air conditioner - Google Patents

Abstract

[Problem] To provide a highly reliable rotary compressor, etc. A rotary compressor includes a cylinder 5a, a roller 5b, a crankshaft 4, an upper bearing 5c, a lower bearing 5d, and a vane, and the crankshaft 4 is provided with an oil supply passage. At the same time, oil supply holes 41c and 41d are provided, and the oil supply holes 41c and 41d guide the lubricating oil from the oil supply flow path to the gap between the eccentric portion 4b and at least one of the upper bearing 5c and the lower bearing 5d, and The positions of the oil supply holes 41c and 41d in the axial direction of the shaft 4 are within the range in the axial direction in which the cylinder 5a is provided, and are perpendicular to the axial direction of the crankshaft 4. The moment of inertia of a surface including 41d is perpendicular to the axial direction of the crankshaft 4 and larger than the moment of inertia of a surface including the oil supply flow path in the main shaft portion 4a. [Selection diagram] Figure 4

Description

The present invention relates to rotary compressors and the like.

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

JP 2012-077728 A JP 2015-040472 A

In the technique described in Patent Document 1, lubricating oil is easily supplied to the lower bearing and the like by providing a groove that is recessed radially inward at a portion of the crankshaft corresponding to the vicinity of the upper end of the lower bearing ( FIG. 1 of Patent Document 1). However, when such grooves are provided on the surface of the crankshaft, the rigidity of the crankshaft is lowered, so that the crankshaft is easily deformed by the compressive load of the refrigerant or the like. As a result, there is a possibility of uneven contact of the crankshaft against the upper and lower bearings.

Further, in the technique 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 portion of the crankshaft corresponding to the sub-bearing. (Fig. 1 of Patent Document 2). However, if such a lower oil supply hole is provided in the crankshaft, the rigidity of the crankshaft is reduced, so that there is a possibility that the crankshaft may come into uneven contact with the sub-bearing or the like. Therefore, there is room for further improving the reliability of the rotary compressor.

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

In order to solve the above-described problems, a rotary compressor according to the present invention includes a cylinder and an annular roller that revolves within the cylinder, a main shaft portion, and an eccentric roller with respect to the main shaft portion. an eccentric portion that slides on the inner peripheral surface of a roller; an upper bearing that is provided above the cylinder and supports the shaft; and an upper bearing that is provided below the cylinder and supports the shaft. a lower bearing; and a plate-shaped vane that partitions a space between the cylinder and the roller. and a lower movement regulating portion provided below the eccentric portion on the radially inner side of the roller and regulating the axial movement of the shaft, wherein the The shaft is provided with an oil supply passage for guiding lubricating oil in the axial direction, and is provided with an oil supply hole through which the lubricating oil flows from the oil supply passage. The oil supply hole provided in at least one of the side movement restricting portions guides the lubricating oil from the oil supply passage to the gap between the eccentric portion and at least one of the upper bearing and the lower bearing, and the shaft The position of the oil feed hole in the axial direction of is within the axial range in which the cylinder is provided, is perpendicular to the axial direction of the shaft, and is the cross-sectional secondary of the surface of the shaft that includes the oil feed hole The moment is perpendicular to the axial direction of the shaft and is larger than the geometrical moment of inertia of the surface of the main shaft including the oil supply passage. In addition, about others, it demonstrates in embodiment.

ADVANTAGE OF THE INVENTION According to this invention, a highly reliable rotary compressor etc. can be provided.

1 is a longitudinal sectional view of a rotary compressor according to a first embodiment; FIG. FIG. 2 is a sectional view taken along the line II-II in FIG. 1 in the rotary compressor according to the first embodiment; It is a figure including the vertical section of the compression mechanism part of the rotary compressor concerning a 1st embodiment. 3B is a partially enlarged view of a region K1 shown in FIG. 3A in the rotary compressor according to the first embodiment; FIG. 1 is a perspective view including a crankshaft and a compression mechanism of a rotary compressor according to a first embodiment; FIG. FIG. 4 is an explanatory diagram regarding positions of oil supply holes of the rotary compressor according to the first embodiment; FIG. 4 is an explanatory diagram of a process in which a roller moves within a cylinder of the rotary compressor according to the first embodiment; It is a figure including the longitudinal section of the compression mechanism part of the rotary compressor which concerns on 2nd Embodiment. It is a perspective view including a crankshaft and a compression mechanism part of a rotary compressor concerning a 2nd embodiment. FIG. 11 is a cross-sectional view of a compression mechanism including an upper oil feed hole of a rotary compressor according to a third embodiment; It is explanatory drawing of the process which a roller moves the inside of the cylinder of the rotary compressor which concerns on 3rd Embodiment. FIG. 11 is a configuration diagram of an air conditioner according to a fourth embodiment;

<<First embodiment>>
<Configuration of rotary compressor>
FIG. 1 is a longitudinal 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 a sealed container 1, an electric motor 2, balance weights 31 and 32, a crankshaft 4 (shaft), a compression mechanism portion 5, and a silencer cover 6. ing.

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

A suction pipe P1 is inserted into and fixed to the tubular chamber 1a of the sealed container 1. As shown in FIG. 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. As shown in FIG. Note that an accumulator 200 for performing gas-liquid separation of the refrigerant is connected to the upstream side of the suction pipe P1. A discharge pipe P2 is inserted into and fixed to the lid chamber 1b of the sealed container 1. As shown in FIG. The discharge pipe P<b>2 is a pipe that guides the refrigerant compressed by the compression mechanism 5 to the outside of the rotary compressor 100 . Lubricating oil for enhancing the lubricating property and sealing property of the rotary compressor 100 is sealed in the sealed container 1, and is stored in the bottom portion of the sealed container 1 as an oil reservoir M1.

The electric motor 2 is a drive source that rotates the crankshaft 4 and is installed inside the sealed 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 formed by stacking 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. The rotor 2b is a cylindrical member having an iron core made of an electromagnetic steel sheet and permanent magnets (not shown) embedded in the iron core, and is rotatably arranged radially inside the stator 2a. ing. A crankshaft 4 is coaxially fixed to the rotor 2b.

The crankshaft 4 is a shaft that rotates integrally with the rotor 2b as the electric motor 2 is driven. The crankshaft 4 extends vertically 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 restricting portion 4c, and a lower movement restricting portion 4d.

The main shaft portion 4 a is coaxially fixed to the rotor 2 b of the electric motor 2 . The main shaft portion 4a is provided above the eccentric portion 4b, which will be described below, 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 integrally formed with the main shaft portion 4a. The eccentric portion 4b is arranged below 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 for guiding lubricating oil in the axial direction, and is provided with oil supply holes 41c and 41d through which the lubricating oil flows from the oil supply passage 4e. there is The oil supply flow path 4 e is a flow path that guides the lubricating oil stored as the oil reservoir M<b>1 in the closed container 1 to the compression mechanism portion 5 . The oil supply passage 4 e is provided in the axial direction of the crankshaft 4 and opens at the lower end of the crankshaft 4 .

The upper end of the oil supply passage 4e is located, for example, in the vicinity of the upper end of the upper movement restricting portion 4c. A thin plate-like metal piece 4f that is bent in a predetermined manner is provided as an oil pump in the vicinity of the lower end of the oil supply passage 4e. As the metal piece 4f rotates together with the crankshaft 4, lubricating oil is pumped up through the oil supply passage 4e. Although not shown in FIG. 1, a horizontal hole or the like may be appropriately provided for guiding the lubricating oil from the oil supply passage 4e to the inner side in the radial direction of the roller 5b.

The upper movement restricting portion 4c and the lower movement restricting portion 4d are portions that restrict the movement of the crankshaft 4 in the axial direction. The upper movement restricting portion 4c is provided above the eccentric portion 4b radially inside the roller 5b. Further, the lower movement restricting portion 4d is provided below the eccentric portion 4b on the inner side in the radial direction of the roller 5b. As shown in FIG. 1, the upper movement restricting portion 4c is provided with an oil supply hole 41c extending in the radial direction for guiding the lubricating oil in the oil supply passage 4e to the outside of the crankshaft 4. As shown in FIG. Another oil supply hole 41d is similarly provided in the lower movement restricting portion 4d in the radial direction. Details of the oil supply holes 41c and 41d will be described later.

The compression mechanism 5 is a mechanism that compresses gaseous refrigerant as the crankshaft 4 rotates, and is provided below the electric motor 2 . The compression mechanism portion 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 cross-sectional view taken along the line II--II in 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.
A cylinder 5a shown in FIG. 2 is a member that forms a cylinder chamber C1 together with a roller 5b, an upper bearing 5c (see FIG. 3A), and a lower bearing 5d (see FIG. 3A), and has a generally annular (cylindrical) shape. 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 that 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 revolves inside the cylinder 5a while being in sliding contact with the inner peripheral surface of the cylinder 5a. The eccentric portion 4b (see FIG. 1) of the crankshaft 4 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 being in sliding contact with 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 the space (that is, the cylinder chamber C1) between the cylinder 5a and the roller 5b. That is, the cylinder chamber C1 is partitioned into the suction chamber C2 and the compression chamber C3 by pressing the tip of the vane 5e against the outer peripheral surface of the roller 5b.

As shown in FIG. 2, an arc-shaped base end portion 5h protruding radially outward from the cylinder 5a is provided integrally with the cylinder 5a. A suction pipe P1 (see FIG. 1) is inserted and fixed in a suction passage (not shown) radially penetrating the base end portion 5h and the cylinder 5a. Then, the gaseous refrigerant is led to 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 radially at a predetermined location of the base end 5h. It is A radial slit (not shown) is provided in the cylinder 5a so as to allow communication between the vane spring mounting hole (not shown) and the radially inner space of the cylinder 5a. This slit is a space for advancing and retreating the vane 5e 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 biases the vane 5e radially inward, and is installed in the vane spring mounting hole (not shown). The tip of the vane 5e is pressed against the outer peripheral surface of the roller 5b by the pressure difference between the inside and outside of the compression mechanism 5 and the biasing force of the vane spring 5f. Thereby, the cylinder chamber C1 between the cylinder 5a and the roller 5b is divided into the suction chamber C2 and the 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. The discharge notch N1 is a notch that guides the compressed refrigerant to the discharge valve 5g (see FIG. 1), and as shown in FIG. 2, has an arcuate edge. Both the opening of the suction passage (not shown) that guides the refrigerant to the suction chamber C2 and the discharge notch N1 are close to the vane 5e in the circumferential direction. That is, the suction passage (not shown) opens to one side of the vane 5e in the circumferential direction. Also, 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 on the upper side (one side in the axial direction) of the cylinder 5a. The upper bearing 5c is fastened with a plurality of bolts (not shown) together with the cylinder 5a and the lower bearing 5d, and is further fixed to the inner peripheral surface of the cylindrical chamber 1a (see FIG. 1). The lower bearing 5d is a slide bearing that rotatably supports the crankshaft 4, and is provided below the cylinder 5a (on the other side in the axial direction).

In the upper bearing 5c, a portion corresponding to the discharge notch N1 (see FIG. 2) of the cylinder 5a guides the refrigerant compressed in the compression chamber C3 (see FIG. 2) to the discharge valve 5g (see FIG. 1). A hole (not shown) is provided. The discharge valve 5g (see FIG. 1) is a valve (plate spring) for discharging the compressed refrigerant into the space inside the sealed container 1 (see FIG. 1). 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 muffler cover 6 shown in FIG. 1 is a cover for suppressing noise accompanying compression of the refrigerant, and is fixed to the upper bearing 5c in a state of partially covering the upper surface of the upper bearing 5c. The muffling cover 6 is provided with a plurality of holes (not shown) for releasing the compressed refrigerant into the space inside the sealed 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 the lubricating oil from the oil supply passage 4e (see FIG. 1) to the gap G1 between the upper bearing 5c and the eccentric portion 4b. is provided in the upper movement restricting portion 4c. The other oil supply hole 41c is a hole that guides the 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. It is provided in the lower movement restricting portion 4d. 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 axial movement of the crankshaft 4, and are provided radially inward of the roller 5b. The upper movement restricting portion 4c, the eccentric portion 4b, and the lower movement restricting portion 4d are integrally formed with the main shaft portion 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 restricting portion 4c contacts the lower surface of the upper bearing 5c. 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 downward force acts on the crankshaft 4, 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 way, the movement of the crankshaft 4 in the axial direction is restricted. Further, the axial length of the eccentric portion 4b can be shortened while ensuring the volume of the cylinder chamber C1 (see FIG. 2). Therefore, it is possible to reduce the sliding loss when the eccentric portion 4b is in sliding contact with the roller 5b, and to increase the energy efficiency when compressing the refrigerant.

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

The lower bearing 5d has a second chamfered portion 51d formed by chamfering the entire periphery near the upper end of the inner peripheral surface. The second chamfered portion 51d is chamfered for guiding lubricating oil through the gap G2 between the lower bearing 5d and the eccentric portion 4b. An oil supply groove 52d (see FIG. 3A) is provided in the axial direction of the crankshaft 4 in the inner peripheral surface of the lower bearing 5d. Lubricating oil flowing out from the oil supply hole 41d is guided to the oil supply groove 52c (see FIG. 3A) through 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 5 of the rotary compressor.
4 shows a perspective view of the compression mechanism 5 cut along a predetermined plane including the central axis of the crankshaft 4. As shown in FIG. As shown in FIG. 4, the upper movement restricting portion 4c and the lower movement restricting portion 4d each have a predetermined columnar shape whose length in the vertical direction is shorter than that of the eccentric portion 4b. The cross-sectional shape of the upper movement restricting portion 4c and the lower movement restricting portion 4d may be, for example, circular or elliptical, or may be other shapes as shown in FIG.

The length by which the upper movement restricting portion 4c protrudes radially from the main shaft portion 4a is, for example, the longest in the eccentric direction of the eccentric portion 4b, and the longest on the side opposite to the eccentric direction of the eccentric portion 4b. It may be shortened. The direction in which the eccentric portion 4b is eccentric means the direction in which the central axis (not shown) of the main shaft portion 4a is used as a reference, and the direction is directed radially toward the central axis (not shown) of the eccentric portion 4b. ing.

In the circumferential direction of the upper movement restricting portion 4c, the upper surface of a portion that coincides with the eccentric direction of the eccentric portion 4b (generally the back side of the paper surface in FIG. 4) is in contact with or close to the lower surface of the upper bearing 5c. On the other hand, in the circumferential direction of the upper movement restricting portion 4c, a first chamfered portion 51c faces the predetermined gap G1 (see FIG. 3B). Further, in the upper movement restricting portion 4c, an oil supply hole 41c is provided on the side opposite to the eccentric direction of the eccentric portion 4b.

As a result, the movement distance of 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 peripheral surface of the upper bearing 5c (see FIG. 3B). easier. Similarly, the lower movement restricting portion 4d (see FIG. 3B) is also provided with an oil supply hole 41d (see FIG. 3B) on the side opposite to the eccentric direction of the eccentric portion 4b.
The positions where the oil supply holes 41c and 41d are provided are not limited to positions on the side opposite to the eccentric direction of the eccentric portion 4b. ) 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.
Although the configuration shown in FIG. 5 is the same as that shown in FIG. 2, hatching of the cross section is omitted for explanation. A portion F1 where the first chamfered portion 51c (see FIG. 3B) faces the upper gap G1 (see FIG. 3B) is hatched so as to stand out.
For example, on the basis of the direction (arrow A2 in FIG. 5) opposite to the direction (arrow A1 in FIG. 5) in which the eccentric portion 4b is eccentric with respect to the main shaft portion 4a, ±90° in the circumferential direction of the crankshaft 4. An oil supply hole 41c may be provided within the range (inside the dot-displayed area S1 in FIG. 5). The same applies to the other oil supply hole 41d (see FIG. 3B). As a result, for example, the movement distance of the lubricating oil flowing out through the oil supply hole 41c toward the first chamfered portion 51c (see FIG. 3B) is shortened, thereby promoting the supply of oil to the upper bearing 5c.

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 so as to detour through the annular gap G1 (see FIG. 3B), the lubricating oil flowing out from the oil supply hole 41c does not move until it is supplied to the upper bearing 5c. longer distance. The same applies to the lower oil supply hole 41d.

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

According to such a configuration, the oil supply holes 41c and 41d are provided in the upper movement restricting portion 4c and the lower movement restricting portion 4d, which have a larger geometrical moment of inertia than in the case where the oil supply holes are provided in the main shaft portion 4a. , the decrease in rigidity of the crankshaft 4 can be suppressed. Further, it is possible to sufficiently supply oil to the upper bearing 5c through the upper oil supply hole 41c, and to sufficiently supply oil to the lower bearing 5d through the lower oil supply hole 41d.

In addition, the area of the portion F1 (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. Large is preferred. Here, the "flow 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 direction of the oil supply hole 41c. In short, the area of the portion F1 is the area of the 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 that has flowed out through the oil supply hole 41c is guided to the inner peripheral side of the upper bearing 5c through the gap G1 (see FIG. 3B) below the first chamfered portion 51c. easier. Therefore, lubrication of the upper bearing 5c is promoted.

Also, the area of the portion (not shown) where the second chamfered portion 51d (see FIG. 3B) faces the lower gap G2 (see FIG. 3B) is larger than the flow path area of the oil supply hole 41d. preferable. According to such a configuration, the lubricating oil that has flowed out through the oil supply hole 41d is easily guided to the inner peripheral side of the lower bearing 5d through the gap G2 (see FIG. 3B) on the upper side of 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.
6, the compression mechanism 5 is cut at the position of the II-II line in FIG. 1 and the cross section when viewed from above is shown. is left-right reversed.
A 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 positioned at the "top dead center" inside the cylinder 5a. The aforementioned "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 to the position of the inner peripheral surface of the cylinder 5a by the roller 5b, and the entire cylinder chamber C1 becomes the 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. Then, when the pressure of the refrigerant overcomes the elastic force of the discharge valve 5g (see FIG. 1), which is a plate spring, the discharge valve 5g opens, and the inside of the sealed container 1 (see FIG. 1) is discharged through the discharge notch N1. high-pressure refrigerant is discharged to.

Further, the upper movement restricting portion 4c (see FIG. 4) also rotates with the rotation of the crankshaft 4 (see FIG. 4), and lubricating oil is supplied to the upper bearing 5c through 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 through the oil supply hole 41d. As a result, 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 geometrical 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 geometrical moment of inertia of the main shaft portion 4a. It is Therefore, compared with the case where grooves are provided on the surface of the main shaft portion 4a or the main shaft portion 4a is provided with an oil supply hole, deterioration in rigidity of the crankshaft 4 can be suppressed. In particular, it is possible to suppress a decrease in 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 likely to receive the compressive load. Further, even when the rotary compressor 100 is driven at high speed, since the rigidity of the crankshaft 4 is ensured, deformation of the crankshaft 4 due to compressive load, centrifugal force, and magnetic attraction force can be suppressed. As a result, it is possible to suppress uneven contact of the crankshaft 4 with the upper bearing 5c and the lower bearing 5d, thereby suppressing damage to the upper bearing 5c and the lower bearing 5d.

Further, an oil supply hole 41c is provided in the upper movement restricting portion 4c, and another oil supply hole 41d is provided in the lower movement restricting portion 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 enhanced.

<<Second embodiment>>
In the second embodiment, the upper movement regulating portion 4c (see FIG. 3A) and the lower movement regulating portion 4d (see FIG. 3A) described in the first embodiment are not particularly provided, and the eccentric portion 4Ab (see FIG. 7) is not provided. ) is longer 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). Others are the same as those of the first embodiment. Therefore, the portions different from the first embodiment will be described, and the description of the overlapping portions 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 has a main shaft portion 4a and an eccentric portion 4Ab. The eccentric portion 4Ab is provided radially inside the roller 5b and is in sliding contact with the inner peripheral 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.

An oil supply hole H1 is provided in the upper portion of the eccentric portion 4Ab to guide the lubricating oil in the oil supply passage 4e (see FIG. 1) of the crankshaft 4A to the gap between the eccentric portion 4Ab and the upper bearing 5c. . Similarly, in the lower portion of the eccentric portion 4Ab, an oil supply hole H2 is provided for guiding the lubricating oil in the oil supply passage 4e (see FIG. 1) of the crankshaft 4A to the gap between the eccentric portion 4Ab and the lower bearing 5d. there is 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, in the vicinity of the lower end of the inner peripheral surface of the upper bearing 5c, similarly to the first embodiment, a first chamfered portion 51c is provided over the entire circumference. 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 through the gap between the lower bearing 5d and the eccentric portion 4Ab.

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. Moreover, 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 geometrical moment of inertia of a surface that is perpendicular to the axial direction of the crankshaft 4A and that includes the oil feed 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 geometrical moment of inertia of the surface of the main shaft portion 4a including the oil supply passage 4e (see FIG. 1). Similarly, the moment of inertia of a surface perpendicular to the axial direction of the crankshaft 4A and including the oil feed hole H2 in the eccentric portion 4Ab (that is, the crankshaft 4A) is perpendicular to the axial direction of the crankshaft 4A. , larger than the geometrical moment of inertia of the surface of the main shaft portion 4a including the oil supply passage 4e (see FIG. 1). According to such a configuration, compared with the case where the main shaft portion 4a is provided with the oil supply hole, it is possible to suppress the deterioration of the rigidity of the crankshaft 4A. In addition, sufficient oil can be supplied to the upper bearing 5c and the lower bearing 5d through the oil supply holes H1 and H2.

The positions of the oil supply holes H1 and H2 in the circumferential direction 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 with reference to 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, the 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 portion 5 of the rotary compressor.
As shown in FIG. 8, the oil supply hole H1 on the upper side of the eccentric portion 4Ab includes a hole portion H11 provided near the upper end of the peripheral surface of the eccentric portion 4Ab and a chamfered portion around the hole portion H11. and a notch portion H12. Regarding the notch H12, the edge of the hole H11 is cut downward in a U-shape from a predetermined position on the peripheral edge of the upper surface of the eccentric portion 4Ab, and the upper end of the hole H11 is cut radially inward. missing. Lubricating oil is introduced to the upper side of the eccentric portion 4Ab through the oil supply hole H1.

The oil supply hole H2 on the lower side of the eccentric portion 4Ab includes a hole portion H21 provided near the lower end of the peripheral surface of the eccentric portion 4Ab, and a notch portion H22 formed by cutting the periphery of the hole portion H21 like a chamfer. have. Regarding the notch H22, the edge of the hole H21 is notched upward in an inverted U shape from a predetermined position on the periphery of the lower surface of the eccentric portion 4Ab, and the lower end of the eccentric portion 4Ab is cut radially inward. missing. Lubricating oil is introduced to the upper side of the eccentric portion 4Ab through the oil supply hole H2.

<effect>
According to the second embodiment, even when 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 are relatively short, the oil supply holes H1 and H2 are provided in the eccentric portion 4Ab. can be provided. As a result, lubricating oil can be sufficiently supplied to the upper bearing 5c and the lower bearing 5d while suppressing a decrease in rigidity of the crankshaft 4A.

<<Third Embodiment>>
The third embodiment differs from the first embodiment in the circumferential positions of the oil supply holes 42c and the like (see FIG. 9). In addition, about others, it is the same as that of 1st Embodiment. Therefore, the portions different from the first embodiment will be described, and the description of the overlapping portions will be omitted.

FIG. 9 is a cross-sectional view of the compression mechanism portion 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. An arrow A3 shown in FIG. 9 indicates the direction in which the roller 5b revolves within the cylinder 5a.
As shown in FIG. 9, the upper movement restricting portion 4c is provided with an oil supply hole 42c. 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).

A straight line L1 passing through the central 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, R1 and R1. Suppose 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 side opposite to the direction (arrow A3) in which the roller 5b moves with the rotation of the crankshaft 4B. there is 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 positions of the upper oil supply hole 42c and the lower oil supply hole (not shown) substantially match in the circumferential direction. Note that the positions of the oil supply hole 42c and the like are not limited to this, and may be 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.
10, the state in which the rotation angle of the crankshaft 4B (see FIG. 9) is 270° when the top dead center is 0° is the same as in FIG. For example, when the compression load from the compression chamber C3 is relatively large and the rotation angle is 270°, the crankshaft 4B (see FIG. 9) is pressed to the side opposite to the vane 5e (the lower side of the paper surface 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-described region R2 (see FIG. 9), the oil supply hole 42c is close to the portion on which the compressive load acts on the upper bearing 5c (see FIG. 1). The same applies to the lower oil supply hole (not shown). As a result, lubricating oil is easily supplied to the portions of the upper bearing 5c (see FIG. 1) and the lower bearing 5d (see FIG. 1) where a compressive load acts.

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

<<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 description thereof will be omitted.

FIG. 11 is a configuration diagram of an air conditioner W1 according to the fourth embodiment.
The solid line arrows in FIG. 11 indicate the flow of the refrigerant during the heating operation.
On the other hand, dashed arrows in FIG. 11 indicate the flow of the refrigerant during the 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, an indoor fan 76 and .

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 a configuration similar to that of the first embodiment (see FIG. 1). Although not shown in FIG. 11 , an accumulator for performing gas-liquid separation of the refrigerant is connected to the refrigerant suction side of the rotary compressor 100 .
The outdoor heat exchanger 71 is a heat exchanger that exchanges heat between a refrigerant flowing through its heat transfer tubes (not shown) and outside air sent from the outdoor fan 72 . The outdoor fan 72 is a fan that sends outside air to the outdoor heat exchanger 71 . The outdoor fan 72 is provided with an outdoor fan motor 72 a as a drive source and is installed near the outdoor heat exchanger 71 .

The indoor heat exchanger 75 is a heat exchanger in which heat is exchanged between the refrigerant flowing through the heat transfer tube (not shown) and the indoor air (air-conditioned room air) 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 is provided with an indoor fan motor 76 a as a drive 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). The refrigerant decompressed by the expansion valve 73 is guided to an "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 flow path of the refrigerant according to the operation 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 ) in sequence, the refrigerant circulates. On the other hand, during heating operation (see the solid line arrow in FIG. 11), in the refrigerant circuit Q1, the rotary compressor 100, the indoor heat exchanger 75 (condenser), the expansion valve 73, and the outdoor heat exchanger 71 (evaporator ) in sequence, the refrigerant circulates.

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

Further, when one of the oil supply holes 41c and 41d is omitted, the rotary compressor 100 preferably has the following configuration. That is, in the configuration in which the lubricating oil in the oil supply passage 4e (see FIG. 1) is guided to at least 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 that has flowed out through the oil supply hole 41c to be guided to the inner peripheral side of the upper bearing 5c.
In addition, in the configuration in which the lubricating oil in the oil supply passage 4e (see FIG. 1) is guided to at least 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 passage area of the oil supply hole 41d. This makes it easier for the lubricating oil flowing out through the oil supply hole 41d to be guided to the inner peripheral side of the lower bearing 5d. The same applies to the case where one of the oil supply holes H1 and H2 is omitted in the second embodiment.

Moreover, although each embodiment demonstrated the case where the rotary compressor 100 was provided with the one compression mechanism part 5 (refer FIG. 1), it does not restrict to this. For example, although not shown, the crankshaft of the rotary compressor has two eccentric portions that are eccentric on opposite sides, one of the eccentric portions is in sliding contact with the inner peripheral surface of the roller of the first compression mechanism, The other eccentric portion may be in sliding contact with the inner peripheral surface of the roller of the second compression mechanism. It is assumed 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 by the other eccentric portion, so vibration of the rotary compressor is suppressed. In such a configuration, one of the two eccentric portions may be provided with an oil supply hole, or both of the two eccentric portions may be provided with an oil supply hole. The structure of the oil supply hole is the same as that of the first embodiment (see FIG. 4) or the second embodiment (see FIG. 8). Also, the number of compression mechanism units may be three or more.

Further, in each embodiment, the upper bearing 5c is provided with the spiral oil supply groove 52c (see FIG. 3A), and the lower bearing 5d is provided with the axial groove 52d (see FIG. 3A). is not limited to That is, the shape and range of the oil supply grooves 52c and 52d can be changed as appropriate.

Moreover, in the fourth embodiment, the case where the air conditioner W1 (see FIG. 11) includes the four-way valve 74 (see FIG. 11) has been described, 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 appropriately combined. 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 with

Moreover, although each embodiment demonstrated the case where the rotary compressor 100 (refer FIG. 1) was arrange|positioned vertically, it does not restrict to this. That is, each embodiment can be applied to the case where the rotary compressor 100 is placed horizontally or diagonally.
Also, the air conditioner W1 (see FIG. 11) described in the fourth embodiment can be applied to various types of air conditioners such as room air conditioners, package air conditioners, and multi air conditioners for buildings.

Moreover, although the air conditioner W1 (see FIG. 11) including the rotary compressor 100 has been described in the fourth embodiment, the present invention is not limited to this. That is, the rotary compressor 100 can be applied to various devices such as a refrigerator, a water heater, an air conditioning and hot water system, and a refrigerator.

Moreover, each embodiment is described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to those having all the described configurations. Moreover, it is possible to add, delete, or replace part of the configuration of each embodiment with another configuration.
Further, the mechanisms and configurations described above show those considered necessary for explanation, and do not necessarily show all the mechanisms and configurations on the product.

1 closed container 2 electric motor 4, 4A, 4B crankshaft (shaft)
4a main shaft portion 4b, 4Ab eccentric portion 4c upper movement restricting portion 4d lower movement restricting portion 41c, 42c oil supply hole (upper oil supply hole)
41d oil supply hole (lower oil supply hole)
4e oil supply passage 5, 5A compression mechanism 5a cylinder 5b roller 5c upper bearing 5d lower bearing 51c first chamfered portion 51d second chamfered portion 5e vane 71 outdoor heat exchanger 72 outdoor fan 73 expansion valve 74 four-way valve 75 indoor heat exchange Device 76 Indoor fan 100 Rotary compressor C1 Cylinder chamber (space)
F1 part G1 clearance (clearance 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 (shaft center axis)

Claims (7)

a 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 is in sliding contact with the inner peripheral surface of the roller;
an upper bearing that is provided on the upper side of the cylinder and supports the shaft;
a lower bearing that is provided on the lower side of the cylinder and supports the shaft;
A plate-shaped vane that partitions the space between the cylinder and the roller,
The shaft is
an upper movement restricting portion provided above the eccentric portion on the radially inner side of the roller and restricting axial movement of the shaft;
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 shaft is provided with an oil supply passage for guiding lubricating oil in the axial direction, and is provided with an oil supply hole through which the lubricating oil from the oil supply passage flows,
The oil supply hole is provided in at least one of the upper movement restricting portion and the lower movement restricting portion,
the oil supply hole guides the lubricating oil from the oil supply passage 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;
The geometrical moment of inertia of the surface of the shaft that is perpendicular to the axial direction of the shaft and includes the oil supply hole is the moment of inertia of the surface of the shaft that is perpendicular to the axial direction of the shaft and includes the oil supply passage. A rotary compressor that is larger than the moment of inertia of area. a 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 is in sliding contact with the inner peripheral surface of the roller;
an upper bearing that is provided on the upper side of the cylinder and supports the shaft;
a lower bearing that is provided on the lower side of the cylinder and supports the shaft;
A plate-shaped vane that partitions the space between the cylinder and the roller,
The shaft is provided with an oil supply passage for guiding lubricating oil in the axial direction, and is provided with an oil supply hole through which the lubricating oil from the oil supply passage flows,
The oil supply hole is provided in at least one of an upper portion and a lower portion of the eccentric portion,
the oil supply hole guides the lubricating oil from the oil supply passage to a gap between at least one of the upper bearing and the lower bearing and the eccentric portion;
When the oil supply hole is provided in the upper part of the eccentric part, the oil supply hole communicates with the gap between the upper bearing and the eccentric part,
When the oil supply hole is provided in the lower part of the eccentric part, the oil supply hole communicates with the gap between the lower bearing and the eccentric part,
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;
The moment of inertia of a surface of the shaft that is perpendicular to the axial direction of the shaft and that includes the oil supply hole is equal to the moment of inertia of a surface of the shaft that is perpendicular to the axial direction of the shaft and includes the oil supply passage. A rotary compressor that is larger than the moment of inertia of area. a 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 is in sliding contact with the inner peripheral surface of the roller;
an upper bearing that is provided on the upper side of the cylinder and supports the shaft;
a lower bearing that is provided on the lower side of the cylinder and supports the shaft;
A plate-shaped vane that partitions the space between the cylinder and the roller,
The shaft is provided with an oil supply passage for guiding lubricating oil in the axial direction, and is provided with an oil supply hole through which the lubricating oil from the oil supply passage flows,
the oil supply hole guides the lubricating oil from the oil supply passage 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;
The moment of inertia of a surface of the shaft that is perpendicular to the axial direction of the shaft and that includes the oil supply hole is equal to the moment of inertia of a surface of the shaft that is perpendicular to the axial direction of the shaft and includes the oil supply passage. greater than the geometric moment of inertia,
When the cross section of the shaft including the oil feed 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, the shaft A rotary compressor, wherein the oil supply hole is provided inside a region on the side opposite to the direction in which the roller moves along with the rotation of the rotary compressor . In a configuration in which lubricating oil from the oil supply passage is guided to at least a gap between the upper bearing and the eccentric portion,
The upper bearing has a first chamfered portion formed by chamfering the vicinity of the lower end of the inner peripheral surface thereof,
The rotary compressor according to any one of claims 1 to 3 , wherein an area of a portion of the first chamfered portion facing the gap is larger than a flow path area of the oil supply hole. machine. In a configuration in which lubricating oil in the oil supply passage is guided to at least a gap between the lower bearing and the eccentric portion,
The lower bearing has a second chamfered portion formed by chamfering the vicinity of the upper end of the inner peripheral surface thereof,
4. The rotary compressor according to any one of claims 1 to 3 , wherein the area of the portion where the second chamfered portion faces the gap is larger than the flow path area of the oil supply hole. machine. The oil supply hole is provided within a range of ±90° in the circumferential direction of the shaft with reference to a direction opposite to a direction in which the eccentric portion is eccentric with respect to the main shaft portion. 3. The rotary compressor according to claim 1 or 2 . An air conditioner comprising the rotary compressor according to any one of claims 1 to 3 , and an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger.

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