JP2023033954A - rotary compressor - Google Patents

Abstract

To provide a rotary compressor capable of avoiding excessive supply of lubrication oil to be supplied to a rotary compression mechanism part and securing strength even when a diameter of a shaft is reduced.SOLUTION: A rotary compressor includes: a closed vessel; an electric part disposed on one side in the closed vessel; a rotary compression mechanism part disposed on the other side in the closed vessel; a shaft connecting the electric part with the rotary compression mechanism part; and lubrication oil stored in the closed vessel. The rotary compression mechanism part includes: an eccentric part; a roller fitted to the eccentric part; a cylinder accommodating the roller; and a bearing plate closing the cylinder and supporting the shaft. The bearing plate includes an oil supply passage having one end facing the lubrication oil and the other end communicated with inside of the cylinder.SELECTED DRAWING: Figure 1

Description

The present invention relates to rotary compressors.

For example, rotary compressors are provided as compressors for air conditioners. The rotary compressor is connected to an electric part, a shaft (crankshaft) corresponding to the rotation axis of the electric part, and accommodates a rotary compression mechanism driven by the operation of the electric part, the electric part, and the rotary compression mechanism. Equip a closed container. Such rotary compressors are disclosed, for example, in Patent Documents 1 and 2 below.

JP-A-11-182429 Japanese Patent Publication No. 2020-526707

By the way, in a general rotary compressor as shown in Patent Documents 1 and 2, for example, appropriate locations in the rotary compression mechanism (rotating roller, cylinder, shaft, main bearing (main frame), sub-bearing (bearing plate ), etc., is stored in a sealed container. Further, as shown in Patent Document 1, an oil supply passage for supplying lubricating oil is provided in the core of the shaft, and a member called a paddle made by twisting a metal plate is attached inside the oil supply passage. As a result, the lubricating oil is sucked into the oil supply passage by the differential pressure between the inside and outside of the cylinder (compression chamber) and the centrifugal force of the paddles, and is supplied to the appropriate locations in the rotary compression mechanism.

However, if the paddle is included in the lubricating oil supply mechanism, the amount of oil supplied to the rotary compression mechanism may become excessively large, depending on operating conditions such as high-speed operation. In recent years, the diameter of the shaft has been reduced in order to reduce the weight of the rotary compressor and reduce the energy loss in the sliding area. may not be guaranteed. Therefore, a design for compensating for the strength of the shaft is required.

The present invention has been made in view of the above problems, and provides a rotary compressor that can avoid excessive lubricating oil supplied to the rotary compression mechanism, and also ensures strength even if the diameter of the shaft is reduced. for the purpose of providing

The rotary compressor according to the present invention is
a closed container;
a motorized part arranged on one side in the closed container;
a rotary compression mechanism disposed on the other side in the closed container;
a shaft connecting the electric portion and the rotary compression mechanism;
Lubricating oil stored in the closed container;
with
The rotary compression mechanism section is
a roller that rotates eccentrically as the shaft rotates;
a cylinder housing the roller;
a bearing plate that closes the cylinder and supports the shaft;
with
The bearing plate has an oil supply passage whose one end faces the lubricating oil and whose other end communicates with the inside of the cylinder.

According to this aspect of the present invention, the bearing plate is provided with an oil supply passage, one end of which faces the lubricating oil and the other end of which communicates with the cylinder of the rotary compression mechanism. For example, the inside of the cylinder) can be lubricated with lubricating oil. Therefore, excessive supply of lubricating oil to the rotary compression mechanism can be avoided.

Further, according to this aspect of the present invention, lubricating oil is supplied to the rotary compression mechanism through the oil supply passage provided in the bearing plate, so there is no need to provide a separate oil supply passage in the shaft. Therefore, even if the diameter of the shaft is reduced, the strength of the shaft is sufficiently secured.

Further, in the rotary compressor according to the present invention,
It is preferable that opening and closing of the oil supply passage be switched according to the rotation angle of the shaft.

According to this aspect of the present invention, the sliding region between the eccentric rotating element (roller, thrust receiving portion, etc.) mounted on the eccentric portion and the bearing plate (for example, the lower end surface of the roller and the By arranging the oil supply passage in the region where the upper end surface of the bearing plate overlaps, the oil supply passage can be switched between opening and closing according to the rotation angle of the shaft. That is, with such a simple structure, it is possible to control the amount of oil supplied to the rotary compression mechanism.

Furthermore, in the rotary compressor according to the present invention,
A plurality of the oil supply passages are provided in the bearing plate,
At least one oil supply passage among the plurality of oil supply passages and another oil supply passage among the plurality of oil supply passages are preferably opened at different timings according to the rotation angle of the shaft.

According to this aspect of the present invention, by providing a plurality of oil supply passages in the sliding region between the eccentric rotary element and the bearing plate, at least one oil supply passage and other oil supply passages are provided according to the rotation angle of the shaft. Roads open at different times. As a result, it is possible to continuously supply lubricating oil to the rotary compression mechanism.

Furthermore, in the rotary compressor according to the present invention,
The shaft may comprise an internal shaft lubrication structure including an lubrication passage extending longitudinally within the shaft.

According to the present invention, it is possible to provide a rotary compressor in which excessive supply of lubricating oil to the rotary compression mechanism is avoided and in which strength is ensured even if the diameter of the shaft is reduced.

FIG. 2 is a vertical cross-sectional view of the rotary compressor according to the embodiment; FIG. 2 is a partial cross-sectional view of the rotary compression mechanism according to the present embodiment (a partial cross-sectional view taken along line AA in FIG. 1); 4 is a timing chart showing changes in the amount of refueling according to the present embodiment;

Hereinafter, a rotary compressor according to an embodiment of the present invention will be described in detail with reference to the drawings. First, referring to FIG. 1, the overall configuration of a rotary compressor 1 according to one embodiment of the present invention will be described. Here, FIG. 1 is a vertical sectional view of the rotary compressor 1. FIG.

As shown in FIG. 1 , a rotary compressor 1 according to this embodiment includes an electric section 10 and a rotary compression mechanism section 20 driven by the electric section 10 . The motor-driven section 10 and the rotary compression mechanism section 20 are housed in a closed container 30 made of steel and having a container main body portion 31 and a lid portion 32 .

The electric part 10 is arranged on one side (the upper side in the height direction) inside the sealed container 30 , and the rotary compression mechanism part 20 is arranged on the other side (the lower side in the height direction) inside the sealed container 30 . .

The electric section 10 is a brushless DC motor including a stator 11, a rotor 12, and a shaft 13 (a crankshaft corresponding to the rotation axis of the rotor 12). Here, the stator 11 includes a laminate (stator core) 11a in which a plurality of electromagnetic steel plates having a donut shape in a plan view and having a substantially cylindrical air space formed inside are laminated in the height direction, and a tooth portion provided in the laminate 11a. A stator coil 11b wound by a concentrated winding method is provided.

The stator coil 11 b is electrically connected to a terminal 33 attached to the lid portion 32 of the container 30 . When power is supplied from the terminal 33 to the stator coil 11b, current flows through the stator coil 11b. As a result, a rotating magnetic field is generated that acts on the rotor 12, causing the rotor 12 to rotate.

The rotor 12 includes a laminated body (rotor core) 12a in which a plurality of electromagnetic steel plates having a substantially circular shape in plan view are laminated in the height direction, and permanent magnets provided in the laminated body 12a. Laminates 12 a of rotor 12 are arranged in a cylindrical air space formed inside stator 11 . At this time, a slight gap is formed between the inner end of the tooth portion of the stator 11 and the outer surface of the rotor 12 . Furthermore, a through hole 12b is formed in the center of the rotor 12 so as to penetrate in the height direction. The shaft 13 is inserted into the through hole 12b and supports the rotor 12. As shown in FIG.

Next, as shown in FIG. 1, the rotary compression mechanism section 20 includes a cylinder 21, an eccentric section 22, a roller 23, a thrust receiving section 24, and the like. Here, as shown in FIG. 1, the cylinder 21 is internally provided with a compression chamber 211 penetrating vertically. A main frame 25 and a bearing plate 26 for supporting the shaft 13 are attached to the upper and lower surfaces of the cylinder 21, respectively. The opening of the cylinder 21 (compression chamber 211 ) is closed by the main frame 25 and the bearing plate 26 .

Further, as shown in FIG. 1 , the eccentric portion 22 is accommodated in the compression chamber 211 and integrally formed with the shaft 13 . Furthermore, the roller 23 is provided around the outer surface of the eccentric portion 22 . Further, vanes (not shown) are slidably arranged in vertical grooves (vane slots) formed in the cylinder 21 and face the compression chamber 211 . At this time, the inner end of the vane contacts the outer surface of the roller 23 . Thereby, the compression chamber 211 is divided into a low-pressure chamber and a high-pressure chamber. Additionally, a coil spring (not shown) is positioned outwardly of the flutes to bias the outer ends of the vanes.

In the rotary compression mechanism portion 20 having the structure described above, when the shaft 13 rotates, the eccentric portion 22 and the roller 23 rotate eccentrically within the compression chamber 211 . At this time, the roller 23 rotates eccentrically along the inner surface of the compression chamber 211 . Further, as the roller 23 rotates eccentrically, the vane contacting the outer surface of the roller 23 is pushed outward of the cylinder 21 . As the roller 23 continues to rotate eccentrically, the vane slides in the opposite direction and returns to its original position.

Although the illustrated rotary compression mechanism 20 includes one cylinder 21, the number of cylinders is not limited to this. That is, the rotary compression mechanism section 20 may include two or more cylinders 21 .

Furthermore, in the oil reservoir formed at the bottom (end on the other side) of the sealed container 30, for example, the rotary compression mechanism 20 (sliding region between the cylinder 21 and the roller 23, the roller 23 and the main frame 25, Lubricating oil 40 is stored for lubricating the sliding area with the bearing plate 26, etc.).

Next, as shown in FIG. 1, the bearing plate 26 that closes the opening on the other side (the lower side in the height direction in this embodiment) of the cylinder 21 (compression chamber 211) comes into contact with the cylinder 21. It also includes a flange portion 261 that extends in the width direction and a bearing portion 262 that extends downward from the flange portion 261 and supports the shaft 13 . In addition, a through passage 263 (263a, 263b) is formed in the bearing portion 262 along the height direction.

Further, one end of the through passage 263 faces the lubricating oil 40, and the other end of the through passage 263 communicates with the inside of the cylinder 21 (inner diameter side of the roller 23). Here, the pressure of the low pressure portion in the cylinder 21 (compression chamber 211) is lower than the lubricating oil pressure (cylinder external pressure). For example, the pressure on the inner diameter side of the roller 23 also drops through a clearance formed at the uppermost portion in the height direction. As a result, the lubricating oil 40 pulled up to the inner diameter side of the roller 23 through the through passage 263 is sucked up into the cylinder 21 (the inner diameter side of the roller 23) and the sliding portion. That is, the through passage 263 functions as a passage for supplying lubricating oil into the cylinder 21 . Therefore, the through passage is hereinafter referred to as an "oil supply passage".

According to this embodiment, since the oil supply passage 263 is provided inside the bearing plate 26, there is no need to provide an oil supply passage inside the shaft 13, unlike the conventional oil supply mechanism. Therefore, even if the diameter of the shaft 13 is reduced, sufficient strength is ensured. Moreover, since the lubricating oil 40 is sucked up using the differential pressure between the inside and outside of the cylinder 21, it is possible to avoid excessive supply of the lubricating oil 40 to the rotary compression mechanism 20 (cylinder 21).

In addition, in the case of the present embodiment, the oil supply passage 263 is provided in the bearing portion 262 of the bearing plate 26, but it may be provided in another portion of the bearing plate 26, such as the flange portion 261. . Moreover, although two oil supply passages 263a and 263b are shown in FIG. 1, the number of oil supply passages 263 is not limited to this. As described above, the number of oil supply passages 263 is basically plural, but may be optimized to be single (one).

Next, operation of the rotary compressor 1 of the present embodiment will be described with reference to FIGS. 2 and 3. FIG. Here, FIG. 2 is a partial cross-sectional view of the rotary compression mechanism 20 (a partial cross-sectional view cut along line AA in FIG. 1), and shows that the rotation angle (crank angle) of the shaft 13 is 4 is a diagram for explaining the positional relationship between eccentric rotating elements (roller 23, thrust receiving portion 24, etc.) and an oil supply passage 263 in the compression mechanism 20. FIG. FIG. 3 is a timing chart showing changes in the amount of fuel supplied in this embodiment.

As shown in FIG. 2 , when the rotation angle of the shaft 13 is 0°, one of the oil supply paths 263 (oil supply path 263 a ) overlaps the lower end of the roller 23 . As a result, the oil supply passage 263a is closed. On the other hand, the other oil supply path 263 (oil supply path 263b) does not overlap with the roller 23 and is in an open state.

Subsequently, when the roller 23 rotates until the rotation angle of the shaft 13 reaches 90°, both the oil supply passages 263a and 263b are overlapped with the lower end of the roller 23 and closed. Further, when the roller 23 rotates until the rotation angle of the shaft 13 reaches 135°, the oil supply passage 263a that has been blocked up to now opens. Further, when the roller 23 rotates until the rotation angle of the shaft 13 reaches 270°, both the oil supply passages 263a and 263b of the shaft 13 are overlapped with the lower end of the roller 23 and closed again. Further, when the roller 23 rotates until the rotation angle of the shaft 13 reaches 360° (0°), the oil supply passage 263a is closed and the oil supply passage 263b is opened.

FIG. 3 shows changes in the amount of oil supplied based on the opening and closing operations of the oil supply passages 263a and 263b. That is, when the rotation angle of the shaft 13 is from 0° to 90° (period A in FIG. 3), the lubricating oil 40 is supplied from the oil supply passage 263b to the cylinder 21 (inner diameter side of the roller 23) (oil supply from the oil supply passage 263b amount is indicated by the dash-dotted line). At this time, lubricating oil 40 is not supplied from oil supply path 263a (the amount of oil supplied from oil supply path 263b is indicated by a broken line).

On the other hand, when the rotation angle of the shaft 13 is from 90° to 270° (period B in FIG. 3), the lubricating oil 40 is supplied from the oil supply passage 263a to the cylinder 21 (inner diameter side of the roller 23). Lubricating oil 40 is not supplied from 263b. Finally, when the rotation angle of the shaft 13 is from 90° to 270° (period C in FIG. 3), the lubricating oil 40 is again supplied from the oil supply path 263b to the cylinder 21 (inner diameter side of the roller 23). Lubricating oil 40 is not supplied from 263a.

In this way, the oil supply passage 263 faces the sliding area between the eccentric rotary element (roller 23 in this embodiment) and the bearing plate 26 of the rotary compression mechanism 20, so that the rotation angle of the eccentric rotary element , the oil supply passage 263a and the oil supply passage 263b open and close at different timings. As a result, as shown in FIG. 3, the period in which the oil supply passage 263a is opened and the period in which the oil supply passage 263b is opened are alternately switched. As a result, the lubricating oil 40 can be continuously supplied into the rotary compression mechanism 20 (cylinder 21).

Although the oil supply passages 263a and 263b are provided in the sliding area between the roller 23 and the bearing plate 26 in the present embodiment, the positions of the oil supply passages 263a and 263b are not limited to this. For example, even if the oil supply passages 263a and 263b are positioned in the sliding area between the thrust receiving portion 24 and the bearing plate 26, the same effect can be obtained.

In addition, within the range where the rigidity of the shaft 13 can be ensured, an oil supply structure provided in the shaft 13 (a central hole (oil supply passage) extending in the longitudinal direction of the shaft 13, or depending on the case, a structure with a paddle added thereto. is referred to as "shaft internal lubrication structure"). Further optimization of the amount of oil supplied may be achieved by combining this in-shaft oil supply structure and the oil supply passage 263 .

Also, the case where two oil supply passages 263 are provided has been described, but when there is one oil supply passage 263, the open period and closed period (oil supply period and non-oil supply period) of the oil supply path 263 are determined according to the rotation angle of the shaft 13. can be switched. As a result, the amount of oil supplied to the rotary compression mechanism 20 can be controlled by a simple structure in which the oil supply passage 263 is provided in the sliding area between the eccentric rotating elements (roller 23, thrust receiving portion 24, etc.) and the bearing plate 26. can be done.

Embodiments of the invention have been described in detail. However, the above description is intended to facilitate understanding of the present invention, and is not intended to limit the present invention. The present invention may include modifications and improvements from the above-described embodiments without departing from the spirit thereof. The present invention also includes equivalents thereof.

INDUSTRIAL APPLICABILITY The rotary compressor according to the present invention is used, for example, in domestic/commercial air conditioners and the like. However, its use is not limited to this.

Reference Signs List 1 Rotary compressor 10 Electric part 11 Stator 12 Rotor 13 Rotor shaft 20 Rotary compression mechanism portion 21 Cylinder 211 Compression chamber 22 Eccentric portion 23 Rollers 24 Thrust receiving portions 25 Main frames 26 Bearing plates 263 Oil supply passages 30・・・・Sealed container 40・・・・・・・・Lubricating oil

Claims (4)

a closed container;
a motorized part arranged on one side in the closed container;
a rotary compression mechanism disposed on the other side in the closed container;
a shaft that connects the electric portion and the rotary compression mechanism;
Lubricating oil stored in the closed container;
with
The rotary compression mechanism section is
a roller that rotates eccentrically as the shaft rotates;
a cylinder housing the roller;
a bearing plate that closes the cylinder and supports the shaft;
with
A rotary compressor, wherein the bearing plate includes an oil supply passage whose one end faces the lubricating oil and whose other end communicates with the cylinder. The rotary compressor according to claim 1, wherein opening and closing of the oil supply passage are switched according to the rotation angle of the shaft. A plurality of the oil supply passages are provided in the bearing plate,
3. At least one oil supply passage among the plurality of oil supply passages and another oil supply passage among the plurality of oil supply passages open at different timings depending on the rotation angle of the shaft. rotary compressor according to . The rotary compressor according to any one of claims 1 to 3, wherein the shaft has an internal shaft oil supply structure including an oil supply passage extending longitudinally inside the shaft.

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