JP2020183727A - Rotary compressor - Google Patents

Abstract

To provide a rotary compressor further improved in efficiency.SOLUTION: A compression portion has a piston rotor 13A revolving about an axis O, a cylinder 12A covering the piston rotor 13A from an outer peripheral side, an upper bearing and a lower bearing configuring a compression chamber with the cylinder 12A, and a blade B disposed in the compression chamber and separating the compression chamber into a low pressure space Vl and a high pressure space Vh. The inside of the blade B is radially divided into a first region A1 positioned at a high pressure space Vh side and a second region A2 positioned at a low pressure space Vl side, and the first region A1 is a hollow portion.SELECTED DRAWING: Figure 2

Description

The present invention relates to a rotary compressor.

For example, a rotary compressor is known as a device used for compressing a refrigerant in an air conditioner. The rotary compressor includes a shaft, a piston rotor mounted on the eccentric portion of the shaft, a cylinder having a cylinder chamber for accommodating the piston rotor, and upper bearings and lower bearings arranged on both axial sides of the cylinder chamber. It includes a blade that projects toward the cylinder chamber and a housing that houses them. The blade is normally in sliding contact with the outer peripheral surface of the piston rotor to divide the cylinder chamber into a low-pressure space and a high-pressure space (see Patent Document 1 below).

Japanese Unexamined Patent Publication No. 2012-137008

By the way, while the high-temperature and high-pressure refrigerant after compression is distributed in the high-pressure space, the low-temperature and low-pressure refrigerant before compression is distributed in the low-pressure space. These high-temperature and high-pressure refrigerants and low-temperature and low-pressure refrigerants are adjacent to each other via blades only. Therefore, there is a possibility that the heat of the refrigerant on the high temperature side propagates toward the refrigerant on the low temperature side through the blade. As a result, the refrigerant before compression is heated, and the efficiency of the rotary compressor is reduced.

The present invention has been made to solve the above problems, and an object of the present invention is to provide a rotary compressor with further improved efficiency.

The rotary compressor according to one aspect of the present invention includes a crankshaft that can rotate around an axis, a compression unit in which a compression chamber that compresses a refrigerant with the rotation of the crankshaft is formed, the crankshaft, and the above. A housing forming a discharge space for accommodating a compression portion is provided, and the compression portion includes a piston rotor provided on the crankshaft and swiveling around the axis at a position eccentric from the axis, and a piston rotor. An annular cylinder covering from the outer peripheral side, an upper bearing and a lower bearing forming the compression chamber together with the cylinder by covering the cylinder from the axial direction, respectively, are arranged in the compression chamber in the radial direction with respect to the axis. The inside of the blade has a blade that is movable in the radial direction while the tip of the piston rotor is in contact with the outer peripheral surface of the piston rotor and separates the compression chamber into a low pressure space and a high pressure space. Is divided into a first region located on the high pressure space side and a second region located on the low pressure space side with reference to the radial direction, and the first region is a hollow portion.

According to the above configuration, the inside of the blade is divided into a first region located on the high pressure space side and a second region located on the low pressure space side, and the first region is a hollow portion. Therefore, for example, the heat insulating property of the blade can be improved as compared with a configuration in which the inside of the blade is solid as a whole. As a result, the transfer of heat from the high pressure space side to the low pressure space side can be suppressed.

In the rotary compressor, the second region may be a solid part.

According to the above configuration, the strength of the blade can be ensured as compared with a configuration in which the inside of the blade is hollow as a whole, for example. That is, according to the above configuration, it is possible to achieve both the heat insulating property and the strength of the blade.

In the rotary compressor, a blade accommodating portion, which is a space for accommodating the blade, is formed in the cylinder, and the first region may be communicated with the discharge space through the blade accommodating portion.

According to the above configuration, the first region is communicated with the discharge space through the blade accommodating portion. Here, a refrigerant that has been compressed by the compression unit for a certain period of time is circulating in the discharge space. The refrigerant immediately after compression is, for example, about 150 ° C. (high temperature), whereas the refrigerant circulating in the discharge space is about 100 ° C. (intermediate temperature). In the above configuration, such an intermediate temperature refrigerant flows into the first region in the blade through the blade accommodating portion. Therefore, the transfer of heat between the high-pressure space side and the low-pressure space side can be suppressed by the intervention of the refrigerant having the intermediate temperature.

In the rotary compressor, the first region may be provided with a plurality of heat radiation fins extending in a direction orthogonal to the radial direction and arranged at intervals in the radial direction.

According to the above configuration, by providing the heat radiation fins in the first region, the heat between the refrigerant in the first region and the refrigerant outside the first region (that is, in the high pressure space) is generated. Movement can be promoted. As a result, it is possible to suppress the transfer of heat from the high pressure space side to the low pressure space side via the blade.

According to the present invention, it is possible to provide a rotary compressor with further improved efficiency.

It is a vertical sectional view of the rotary compressor which concerns on 1st Embodiment of this invention. It is sectional drawing which shows the structure of the piston rotor and the blade which concerns on 1st Embodiment of this invention. It is sectional drawing which shows the structure of the blade which concerns on 1st Embodiment of this invention. It is sectional drawing which shows the structure of the blade which concerns on 2nd Embodiment of this invention. It is an enlarged view of the main part which shows a part of FIG.

[First Embodiment]
The first embodiment of the present invention will be described with reference to FIGS. 1 to 3. As shown in FIG. 1, the rotary compressor 100 according to the present embodiment includes an accumulator 24, suction pipes 26A and 26B, and a compressor main body 10. The compressor body 10 includes a crankshaft 16 extending along the axis O, a motor 18 for rotating the crankshaft 16, a compression unit 10A for compressing a refrigerant as the crankshaft 16 rotates, a crankshaft 16, and a motor 18. And a housing 11 that covers the compression portion 10A.

The compression unit 10A is the piston rotors 13A and 13B (first piston rotor 13A, second) that rotate (rotate) around the axis O at positions eccentric from the axis O (rotor axis O1 and O2) as the crankshaft 16 rotates. The piston rotor 13B), the first piston rotor 13A, and the second piston rotor 13B are covered from the outer peripheral side to rotatably support the annular cylinders 12A and 12B for accommodating them and the crankshaft 16. It has 17A and a lower bearing 17B, and a blade B that separates the compression chamber C formed in the cylinders 12A and 12B into two spaces.

The compression unit 10A is a so-called two-cylinder type rotary compressor in which cylinders 12A and 12B are provided in two upper and lower stages in a cylindrical housing 11. The housing 11 surrounds the cylinders 12A and 12B to form a discharge space V from which the compressed refrigerant is discharged. Inside the cylinders 12A and 12B, a cylindrical first piston rotor 13A and a second piston rotor 13B having an outer shape smaller than the inside of the inner wall surface of the cylinder are arranged, respectively. The first piston rotor 13A and the second piston rotor 13B are inserted and fixed to the crankshafts 14A and 14B (first crankshaft 14A, second crankshaft 14B) of the crankshaft 16, respectively.

The first piston rotor 13A of the cylinder 12A on the upper stage side and the second piston rotor 13B on the lower stage side are provided so that their phases differ from each other by 180 °. That is, the first piston rotor 13A is eccentric in the direction opposite to the eccentric direction of the second piston rotor 13B. Further, a disc-shaped partition plate 15 is provided between the upper and lower cylinders 12A and 12B. The space in the cylinder 12A on the upper stage side and the space on the lower stage side are partitioned from each other by the partition plate 15 to form compression chambers C1 and C2, respectively.

The cylinders 12A and 12B are fixed to the housing 11 by the upper bearing 17A and the lower bearing 17B. More specifically, the upper bearing 17A has a disk shape fixed to the upper part of the compression portion 10A, and its outer peripheral surface is fixed to the inner peripheral surface of the housing 11. The lower bearing 17B has a disk shape fixed to the lower part of the compression portion 10A, and its outer peripheral surface is fixed to the inner peripheral surface of the housing 11. The upper bearing 17A covers the cylinder 12A on the upper stage side from above (one side in the axis O direction). Further, the lower bearing 17B covers the lower cylinder 12B from below (the other side in the axis O direction). That is, the upper bearing 17A forms the above-mentioned compression chamber C1 together with the cylinder 12A and the partition plate 15, and the lower bearing 17B forms the above-mentioned compression chamber C2 together with the cylinder 12B and the partition plate 15. The rotary compressor 100 may have one cylinder instead of such two cylinders. In the case of one cylinder, the upper bearing 17A and the lower bearing 17B respectively cover both sides of the cylinder in the O-direction without providing the partition plate 15.

In the compressor main body 10, an accumulator 24 for gas-liquid separation of the refrigerant prior to supply to the compressor main body 10 is fixed to the housing 11 via a stay 25. Suction pipes 26A and 26B for sucking the refrigerant in the accumulator 24 into the compressor main body 10 are provided between the accumulator 24 and the compressor main body 10. One end of the suction pipes 26A and 26B is connected to the lower part of the accumulator 24, and the other end communicates with the suction ports 23A and 23B formed in the cylinders 12A and 12B through the openings 22A and 22B, respectively. A rotor 19A of a motor 18 for rotationally driving the crankshaft 16 is integrally provided on one end side of the crankshaft 16. A stator 19B is fixedly provided on the inner peripheral surface of the housing 11 so as to face the outer peripheral portion of the rotor 19A.

Subsequently, the internal configuration of the compression unit 10A will be described with reference to FIG. Since the cylinder 12A on the upper stage and the cylinder 12B on the lower stage have the same configuration as each other, the cylinder 12A on the upper stage will be typically described below. As shown in FIG. 2, the cylinder 12A has an annular cylinder body 12H centered on the axis O, and two overhanging portions P1 and P2 provided on the outer peripheral surface 12S of the cylinder body 12H. There is. The overhanging portions P1 and P2 extend in a fan shape from the outer peripheral surface 12S toward the outer side in the radial direction with respect to the axis O. The outer peripheral surfaces of the overhanging portions P1 and P2 are brought into contact with and fixed to the inner peripheral surface of the housing 11 by, for example, shrink fitting. The two overhanging portions P1 and P2 are provided at intervals in the circumferential direction with respect to the axis O. Further, the overhanging portion P1 has a larger size in the circumferential direction than the overhanging portion P2. The number and shape of these overhanging portions P1 and P2 may be appropriately determined according to the design and specifications.

The inner peripheral side of the cylinder body 12H is formed as the above-mentioned compression chamber C1 by opening in a circular shape about the axis O. The first piston rotor 13A is housed in the compression chamber C1. The blade B is supported in the blade accommodating portion Sb in a state of being urged by the elastic member G with respect to the cylinder body 12H. The blade B is urged inward in the radial direction with respect to the axis O by the elastic member G. As a result, the tip Bt of the blade B is in a state of being in normal contact with the outer peripheral surface of the first piston rotor 13A. That is, when the first piston rotor 13A rotates eccentrically, the tip Bt of the blade B is in sliding contact with the outer peripheral surface of the first piston rotor 13A in a state of being urged by the elastic member G.

The blade B itself is movable (movable) in the radial direction with respect to the axis O. The compression chamber C1 is separated into two spaces (high pressure space Vh and low pressure space Vl) by the blade B. More specifically, when the rotation direction (swivel direction) of the first piston rotor 13A is positive, the space on the front side of the rotation direction R with respect to the blade B is the high pressure space Vh, and the space on the rear side in the rotation direction is low pressure. It is said to be space Vl. In the high-pressure space Vh, the refrigerant sent from the low-pressure space Vl side is compressed and distributed at a high temperature and high pressure. This high-temperature and high-pressure refrigerant is taken out from a discharge port (not shown) formed in the cylinder body 12H via a discharge space V in the housing 11.

As shown in FIG. 3, the inside of the blade B is divided into two spaces with the extending direction of the blade B itself (that is, the radial direction with respect to the axis O) as a reference (reference line CL). Specifically, this reference line CL equally divides the blade B in the width direction (that is, the axis O and the direction orthogonal to the radial direction). The high-voltage space Vh side of the blade B inside the reference line CL is the first region A1, and the low-voltage space Vl side is the second region A2. Further, the first region A1 is a hollow portion. That is, a space is formed in the first region A1. The first region A1 extends in the extending direction (diameter direction) of the blade B. On the other hand, the second region A2 is regarded as a solid part. That is, the second region A2 is formed integrally with other portions by the same material as the material constituting the blade B itself.

The radial outer end of the first region A1 communicates with the blade accommodating portion Sb described above. That is, the radial outer end of the first region A1 is an opening H that opens toward the blade accommodating portion Sb. The blade accommodating portion Sb communicates with the discharge space V at the radial outer end. Therefore, the refrigerant in the discharge space V can flow into the first region A1 through the blade accommodating portion Sb. The temperature of the refrigerant in the discharge space V is lower than that of the refrigerant immediately after being compressed by the compression unit 10A. As an example, the temperature of the refrigerant immediately after compression is about 150 ° C., whereas the temperature of the refrigerant flowing in the discharge space V is about 100 ° C.

Next, the operation of the rotary compressor 100 according to the present embodiment will be described. When operating the rotary compressor 100, the motor 18 is first driven by an external power supply. As the motor 18 is driven, the crankshaft 16 rotates around the axis O. As the crankshaft 16 rotates, the first crankshaft 14A and the second crankshaft 14B rotate around the central axis (axis O) of the crankshaft 16. The first piston rotor 13A and the second piston rotor 13B rotate eccentrically in the compression chambers C1 and C2 so as to follow this turning. The eccentric rotation of the first piston rotor 13A and the second piston rotor 13B changes the volumes of the compression chambers C1 and C2, and the refrigerant taken into the compression chambers C1 and C2 is compressed. The compressed refrigerant is taken out to the outside through the discharge space V in the housing 11.

By the way, in the high pressure space Vh in the compression chamber C, the high temperature and high pressure refrigerant after compression is circulated, whereas in the low pressure space, the low temperature and low pressure refrigerant before compression is circulated. These high-temperature and high-pressure refrigerants and low-temperature and low-pressure refrigerants are adjacent to each other via only the blade B. Therefore, there is a possibility that the heat of the refrigerant on the high temperature side propagates toward the refrigerant on the low temperature side through the blade B. As a result, the refrigerant before compression is heated, and the efficiency of the rotary compressor 100 may decrease. Therefore, in the present embodiment, as described above, only the first region A1 inside the blade B is hollow. Further, the first region A1 is communicated with the discharge space V through the blade accommodating portion Sb.

Therefore, for example, the heat insulating property of the blade B can be improved as compared with a configuration in which the inside of the blade B is solid as a whole. As a result, the transfer of heat from the high-pressure space Vh side to the low-pressure space Vl side can be suppressed. Therefore, the efficiency of the rotary compressor 100 can be further improved.

Further, according to the above configuration, the strength of the blade B can be ensured as compared with the configuration in which the inside of the blade B is hollow as a whole, for example. That is, according to the above configuration, it is possible to achieve both the heat insulating property and the strength of the blade B.

In addition, according to the above configuration, the first region A1 is communicated with the discharge space V through the blade accommodating portion Sb. Here, a refrigerant that has been compressed by the compression unit 10A for a certain period of time is circulating in the discharge space V. The refrigerant immediately after compression is, for example, about 150 ° C. (high temperature), whereas the refrigerant circulating in the discharge space V is about 100 ° C. (intermediate temperature). In the above configuration, such an intermediate temperature refrigerant flows into the first region A1 in the blade B through the blade accommodating portion Sb. Therefore, the transfer of heat between the high-pressure space Vh side and the low-pressure space Vl side can be suppressed by the intervention of the refrigerant having the intermediate temperature.

The first embodiment of the present invention has been described above. It should be noted that various changes and modifications can be made to the above configuration as long as the gist of the present invention is not deviated.

[Second Embodiment]
Next, the second embodiment of the present invention will be described with reference to FIGS. 4 and 5. The same components as those in the first embodiment are designated by the same reference numerals, and detailed description thereof will be omitted. As shown in FIG. 4, in the present embodiment, a plurality of heat radiation fins F are provided in the first region A1 in the blade B. These heat radiation fins F are arranged at intervals in the extending direction (diameter direction) of the blade B. Each heat radiation fin F has a plate shape extending in a direction orthogonal to the radial direction. Further, as shown in FIG. 5, the dimension (height dimension) of each heat radiation fin F in the axis O direction is smaller than the height dimension of the first region A1. As a result, the upper part of the small space Vs (one side in the axis O direction) formed between the pair of heat radiation fins F adjacent to each other is communicated with the other small space Vs.

According to the above configuration, since the heat radiation fins F are provided in the first region A1, the refrigerant in the first region A1 and the refrigerant outside the first region A1 (that is, in the high pressure space Vh) can be used. The transfer of heat between can be promoted. As a result, it is possible to suppress the transfer of heat from the high pressure space Vh side to the low pressure space Vl side via the blade B. As a result, the efficiency of the rotary compressor 100 can be further improved.

The second embodiment of the present invention has been described above. It should be noted that various changes and modifications can be made to the above configuration as long as the gist of the present invention is not deviated. For example, in the second embodiment, an example in which each heat radiation fin F extends in a direction orthogonal to the radial direction has been described. However, the configuration of the heat radiation fin F is not limited to the above, and as another example, a configuration in which the heat radiation fin F extends in the radial direction can be adopted. Further, the number of heat radiation fins F provided may be appropriately determined in consideration of design, specifications, and space restrictions.

100 ... Rotary compressor 10 ... Compressor body 10A ... Compressor 11 ... Housing 12A, 12B ... Cylinder 12H ... Cylinder body 12S ... Outer peripheral surface 13A ... First Piston rotor 13S ... Rotor upper surface 13B ... Second piston rotor 14A ... First crankshaft 14B ... Second crankshaft 16 ... Crankshaft 17A ... Upper bearing 17B ... Lower bearing 18 ... Motor 19A ... Rotor 19B ... Stator 22A, 22B ... Opening 23A, 23B ... Suction port 24 ... Accumulator 25 ... Stay 26A, 26B ... Suction pipe A1. .. 1st region A2 ... 2nd region B ... Blade Bt ... Tip C, C1, C2 ... Compressor chamber CL ... Reference line F ... Radiation fin G ... Elastic member H ... Opening O ... Axis lines O1, O2 ... Rotor axis lines P1, P2 ... Overhanging part Sb ... Blade accommodating part V ... Discharge space Vh ... High pressure space Vl ...・ Low pressure space

Claims (4)

A crankshaft that can rotate around the axis and
A compression unit in which a compression chamber for compressing the refrigerant with the rotation of the crankshaft is formed, and
A housing forming a discharge space for accommodating the crankshaft and the compression portion,
With
The compression unit is
A piston rotor provided on the crankshaft and swiveling around the axis at a position eccentric from the axis.
An annular cylinder that covers the piston rotor from the outer peripheral side,
An upper bearing and a lower bearing that form the compression chamber together with the cylinder by covering the cylinder from the axial direction, respectively.
It is arranged in the compression chamber, extends in the radial direction with respect to the axis, and is movable in the radial direction with the tip in contact with the outer peripheral surface of the piston rotor, and the compression chamber is separated into a low pressure space and a high pressure space. Blade and
Have,
The inside of the blade is divided into a first region located on the high pressure space side and a second region located on the low pressure space side with reference to the radial direction, and the first region is a hollow portion. The rotary compressor that has been used. The rotary compressor according to claim 1, wherein the second region is a solid part. A blade accommodating portion, which is a space for accommodating the blade, is formed in the cylinder.
The rotary compressor according to claim 1 or 2, wherein the first region is communicated with the discharge space through the blade accommodating portion. The first region according to any one of claims 1 to 3, wherein a plurality of heat radiation fins extending in a direction orthogonal to the radial direction and arranged at intervals in the radial direction are provided. Rotary compressor.

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