KR102089805B1 - Rotary compressor and manufacturing method of rotary compressor - Google Patents

Abstract

The rotary compressor includes an inner surface extending between a piston rotating eccentrically by rotation of the crankshaft, a pair of hollow disc faces, and an inner edge portion of the pair of hollow disc faces, and an outer edge portion of the pair of hollow disc faces. It has an outer surface extending therebetween, and has a cylinder in which the piston is accommodated in a space surrounded by the inner surface, and the cylinder extends radially from the inner surface toward the outer surface and reciprocates by eccentric rotation of the piston. A vane groove accommodating the vane and a vane groove opening penetrating the pair of hollow disc surfaces and communicating with the vane groove, the vane groove opening comprising: a pair of first convex-shaped bends having a first radius of curvature And a second convex-shaped bend disposed on the outer surface side of the cylinder than the pair of first convex-shaped bends, extending between the pair of first convex-shaped bends, and having a second radius of curvature It is formed as a space surrounded by a wall surface portion having a portion, and the second radius of curvature is smaller than the first radius of curvature.

Description

Rotary compressor and manufacturing method of rotary compressor

The present invention relates to a rotary compressor having a vane groove.

As a rotary compressor having a conventional vane groove, for example, Patent Document 1 discloses that an annular cylinder is provided with a vane groove accommodating the vane and a pressure introduction path communicating with an end portion on the outer peripheral surface side of the vane groove. . In Patent Document 1, the pressure introduction passage has a circular opening and penetrates the cylinder in the vertical direction.

Patent Document 1: Japanese Patent Application Publication No. 2014-070596

In the rotary compressor of Patent Document 1, in order to increase the compression amount of the gas refrigerant per one revolution of the piston while maintaining the outer dimensions of the cylinder, the cylinder is increased so that the inner diameter of the cylinder, the eccentric distance of the piston, and the sliding distance of the vane are increased. There is a need to configure.

In the rotary compressor of Patent Document 1, in order to increase the eccentric distance of the piston while maintaining the outer dimension of the cylinder, it is necessary to increase the inner diameter of the cylinder. In the rotary compressor of Patent Document 1, if the inner diameter of the cylinder is increased while maintaining the outer dimensions of the cylinder, the distance between the arrangement position of the vane groove and the pressure introduction path and the outer peripheral surface of the cylinder becomes small.

In addition, in the rotary compressor of Patent Document 1, in order to increase the sliding distance of the vane while maintaining the outer dimension of the cylinder, it is necessary to increase the length of the vane groove. In the rotary compressor of Patent Document 1, when the length of the vane groove is increased while maintaining the outer dimension of the cylinder, the distance between the arrangement position of the pressure introduction path and the outer peripheral surface of the cylinder becomes small.

In the rotary compressor described in Patent Document 1, when manufacturing the rotary compressor of Patent Document 1, external pressure is applied from the outer surface of the sealed container toward the center of the cylinder to fix the outer surface of the cylinder to the inner surface of the sealed container. There are cases. In the rotary compressor described in Patent Document 1, as the distance between the pressure introduction path and the outer circumferential surface of the cylinder decreases, the rigidity of the cylinder against the external force applied from the outer circumferential surface of the cylinder decreases. When the rigidity of the cylinder against external force is lowered, the cylinder tends to be distorted. Therefore, there is a possibility that friction occurs between the vane groove and the vane due to the distortion of the vane groove, and the sliding motion of the vane is deteriorated. On the other hand, if the clearance between the vane groove and the vane is increased, the leakage of the refrigerant gas from the clearance increases and the compression efficiency decreases, so it is necessary to keep the clearance small. Therefore, in the rotary compressor of Patent Document 1, when the compression amount of the gas refrigerant is increased while maintaining the outer dimension of the cylinder, noise or slide motion loss increases due to deterioration of the sliding motion of the vane, thereby increasing durability and reliability. The problem is that there is a possibility that it cannot be secured.

An object of the present invention is to provide a rotary compressor capable of solving the above-mentioned problems, avoiding deterioration of vane sliding mobility, and ensuring durability and reliability of the rotary compressor.

The rotary compressor of the present invention includes an inner surface extending between a piston rotating eccentrically by rotation of the crankshaft, a pair of hollow disc surfaces, and an inner edge portion of the pair of hollow disc surfaces, and the pair of hollow discs A cylinder having an outer surface extending between the outer edges of the disk surface, and having a cylinder accommodated in the space surrounded by the inner surface, the cylinder extending radially from the inner surface toward the outer surface , A vane groove accommodating the vane reciprocating by the eccentric rotation of the piston, and a vane groove opening penetrating the pair of hollow disc surfaces and communicating with the vane groove, wherein the vane groove opening is made of A pair of first convex-shaped bends having a radius of curvature of 1 and the pair of first convex-shaped bends are disposed on the outer surface side of the cylinder than the pair of first convex-shaped bends, and the pair of It is formed in a space enclosed between the first convex-shaped bends and surrounded by the wall surface portion having the second convex-shaped bends, and the second radius of curvature is smaller than the first radius of curvature. .

In the present invention, since the opening area of the vane groove opening can be configured to be smaller than that of the conventional vane groove opening, the occurrence of distortion of the vane groove can be avoided. In the present invention, the durability of the cylinder can be improved by avoiding the occurrence of distortion of the vane groove. In addition, by avoiding the occurrence of distortion of the vane groove, friction between the vane groove and the vane can be avoided, and the sliding movement of the vane can be avoided. Therefore, according to the present invention, it is possible to provide a rotary compressor capable of avoiding deterioration of vane sliding mobility and securing durability and reliability.

1 is a longitudinal sectional view schematically showing an example of a rotary compressor 1 according to Embodiment 1 of the present invention.
2 is a schematic diagram showing an example of an internal structure in a side view of a compressor mechanism 30 of a rotary compressor 1 according to Embodiment 1 of the present invention.
3 is a schematic diagram showing an example of an internal structure in a top view of a compressor mechanism 30 of a rotary compressor 1 according to Embodiment 1 of the present invention.
FIG. 4 is a partially enlarged view showing an example of a schematic structure of a vane groove opening 318 of the cylinder 31 in the compressor mechanism 30 of the rotary compressor 1 according to Embodiment 1 of the present invention. .
5 is a schematic diagram showing a method of fixing the cylinder 31 to the sealed container 2 at the time of manufacture of the rotary compressor 1 according to Embodiment 1 of the present invention.
Fig. 6 is a schematic diagram showing an external force applied to the vane groove 316 when the cylinder 31 is fixed to the sealed container 2 in the rotary compressor 1 according to the first embodiment of the present invention.
Fig. 7 is a schematic diagram showing the structure of a vane groove opening 318a in the rotary compressor 1 of the prior art.
Fig. 8 is a schematic diagram comparing the shape of the vane groove opening 318 in the rotary compressor 1 according to the first embodiment of the present invention to the vane groove opening 318a of the prior art having a circular shape.

Embodiment 1.

The configuration of the rotary compressor 1 according to the first embodiment of the present invention will be described with reference to FIG. 1. 1 is a longitudinal sectional view schematically showing an example of the rotary compressor 1 according to the first embodiment. In addition, the rotary compressor 1 is used for a refrigeration cycle device, such as an air conditioner, and is a component constituting a refrigerant circuit of the refrigeration cycle device.

In addition, in the following drawings including FIG. 1, the refrigerant circuit and other components constituting the refrigerant circuit such as, for example, a radiator, an evaporator, a pressure reducing device, and an oil separator are not illustrated. In addition, in the following drawings, the relationship and shape of the dimension of each structural member may differ from an actual thing. In the following drawings, the same or similar members are assigned the same reference numerals or the same reference numerals are omitted. In addition, in the following description, the positional relationship between each component member of the rotary compressor 1, for example, a vertical relationship, etc., is a principle when the rotary compressor 1 is installed in a usable state. We do with location relations.

The rotary compressor 1 is a rolling piston type compressor, and is a fluid machine that discharges a low-pressure gas refrigerant sucked into the rotary compressor 1 as a high-pressure gas refrigerant. The body of the rotary compressor 1 is configured as a cylinder-shaped sealed container 2. The closed container 2 is composed of a U-shaped body portion 2a having a longitudinal cross-section and a reverse U-shaped cover portion 2b having a longitudinal cross-section, and the outer surface of the opening of the cover 2b has a body portion ( It is fixed to the inner side of the opening in 2a). The fixed portions of the body portion 2a and the cover portion 2b are joined by welding or the like, for example. In addition, on the outer surface of the bottom surface of the main body portion 2a, a stage 3 for arranging the rotary compressor 1 in a vertical type is provided. In addition, in FIG. 1, the rotary compressor 1 is configured as a vertical type compressor, but may be configured as a horizontal compressor.

The body 4a of the suction muffler 4 is fixed to the outer surface of the main body portion 2a of the sealed container 2 to the support member 5 disposed on the outer surface of the sealed container 2. The support member 5 is, for example, an annular band portion 5a that fixes the outer surface of the suction muffler 4, and a holder that is fixed to the outer surface of the sealed container 2 and supports the band portion 5a. It can be set as a structure having a portion 5b. At the top of the body 4a of the suction muffler 4, the inlet pipe 4b is fixed through the body 4a. The inlet pipe 4b, for example, introduces a low pressure gas refrigerant discharged from an evaporator of a refrigeration cycle device or a two-phase refrigerant having high dryness into the body 4a of the suction muffler 4. It is a refrigerant pipe. In addition, one end of the suction pipe 6 is fixed to the bottom of the body 4a of the suction muffler 4, and the other end of the suction pipe 6 is of the body portion 2a of the sealed container 2 It is fixed through the side portion.

The suction muffler 4 is a silencer that reduces or eliminates the noise generated by the refrigerant flowing from the inlet pipe 4b. In addition, the suction muffler 4 also has an accumulator function, a refrigerant storage function for storing excess refrigerant, and a gas-liquid separation function by retaining a liquid refrigerant temporarily generated when the operating state changes. By the gas-liquid separation function of the suction muffler 4, it is possible to prevent a large amount of liquid refrigerant from flowing into the sealed container 2 and performing liquid compression in the rotary compressor 1.

The suction pipe 6 is a refrigerant pipe that sucks low-pressure gas refrigerant into the sealed container 2. The fixed portion between the suction pipe 6 and the body portion 2a is joined by soldering or the like, for example. In addition, although not shown in FIG. 1, the suction pipe 6 is provided with an oil return hole in the side portion, and the lubricant component contained in the high-pressure gas refrigerant separated from the oil separator of the refrigeration cycle device is sealed through the suction pipe 6 It may be configured to return to the inside of the container 2.

On the upper surface of the cover portion 2b of the sealed container 2, a discharge pipe 7 is penetrated and fixed. The discharge pipe 7 is a refrigerant pipe that discharges a high-pressure gas refrigerant to the outside of the sealed container 2. The fixed portion between the discharge pipe 7 and the cover portion 2b is joined by soldering or the like, for example.

Moreover, the charge pipe 8 is penetrated and fixed to the upper surface of the cover portion 2b of the sealed container 2. The charge pipe 8 can be configured to vacuum-suction the inside of the sealed container 2 so that the gas refrigerant can be sealed inside the sealed container 2. In addition, the charge pipe 8 may be configured so that lubricant can be sealed inside the sealed container 2.

Moreover, the glass terminal 9 is arrange | positioned at the upper surface of the cover part 2b of the sealed container 2. The glass terminal 9 provides an interface for connecting an external power supply. The external power supply is a power supply device that supplies electric power to the rotary compressor 1, and a general commercial AC power supply having an AC frequency of 50 Hz or 60 Hz or an inverter power supply capable of changing the AC frequency is used. When a frequency-converter inverter power source is used, the number of revolutions of the rotary compressor 1 can be changed, so that the rotary compressor 1 can control the discharge amount of the high-pressure gas refrigerant from the discharge pipe 7. In the following description, in the following drawings including FIG. 1, an external power supply connected to the glass terminal 9 is not shown.

Inside the sealed container 2, an electric motor part 10, a crankshaft 20, and a compression mechanism part 30 are accommodated. The electric motor part 10 is disposed above the fixed part between the main body part 2a and the suction pipe 6. The crankshaft 20 is arranged in the vertical direction between the electric motor part 10 and the compression mechanism part 30 in the center of the hermetic container 2. The compressor mechanism portion 30 is configured such that the side portion of the compressor mechanism portion 30 covers a fixed portion between the main body portion 2a and the suction pipe 6, and the inside of the compression mechanism portion 30 communicates with the suction pipe 6. . That is, inside the sealed container 2, the electric motor part 10 is arranged above the compressor mechanism part 30. In addition, the hollow space inside the sealed container 2 above the compression mechanism 30 is filled with a high-pressure gas refrigerant compressed by the compression mechanism 30.

The electric motor unit 10 is configured as a motor that generates a rotational driving force using electric power supplied from an external power source and transmits the rotational driving force to the compressor mechanism 30 through the crankshaft 20. The electric motor unit 10 includes a stator 12 having a hollow cylindrical appearance in the upper surface and a cylindrical rotor 14 rotatably disposed inside the inner surface of the stator 12. The stator 12 is fixed to the inner surface of the body portion 2a of the hermetic container 2 and is connected to the glass terminal 9 through a conducting wire 16. The electric motor unit 10 rotates the rotor 14 from the inside of the inner surface of the stator 12 by supplying electric power from an external power source to the coil wound on the stator 12 through the conducting wire 16. You can. In the rotary compressor 1, for example, a DC brushless motor or the like is used as the electric motor unit 10.

In the center of the rotor 14, a crankshaft 20 is fixed through the rotor 14 and fixed. The crankshaft 20 is fixed to the rotor 14 on a fixed surface 20a which is a part of the outer surface of the crankshaft 20, and a rotating shaft for transmitting the rotational driving force of the rotor 14 to the compression mechanism 30 to be. The crankshaft 20 extends from the fixed surface 20a in the vertical direction, that is, in the direction of the cover portion 2b of the sealed container 2 and in the direction of the bottom of the body portion 2a of the sealed container 2 have. The oil separation plate 22 is provided above the fixed surface 20a. The oil separating plate 22 separates the lubricating oil contained in the high-pressure gas refrigerant discharged from the compressor mechanism part 30 by centrifugal force by rotation of the crankshaft 20, and the body part 2a by gravity action It is configured to be dropped at the bottom of the.

In addition, the crankshaft 20 is located below the fixed surface 20a and has a cylindrical eccentric portion 24 disposed inside the compression mechanism portion 30. On the outer surface of the eccentric portion 24, a piston 26 that is rotatably mounted along the outer surface of the eccentric portion 24 is disposed.

In addition, an oil hole is provided in the center of the crankshaft 20 to extend upward from the lower end of the crankshaft 20 and the lubricant oil, which is the refrigerating oil 40 sucked up from the lower end of the crankshaft 20, flows. . The outer surface of the crankshaft 20 is provided with a plurality of oil supply ports communicating with the above-described oil holes and supplying lubricant to the compressor mechanism section 30. In addition, a configuration in which a centrifugal pump is disposed at the lower end of the oil hole of the crankshaft 20 can be employed. The above-described centrifugal pump is configured, for example, as a helical centrifugal pump so as to suck up the refrigerating machine oil 40 stored at the bottom of the main body portion 2a of the sealed container 2. Further, as the refrigerating machine oil 40, for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, polyol ester-based lubricants, and the like are used. In addition, the oil hole provided in the crankshaft 20, the oil supply port, and the centrifugal pump arrange | positioned at the lower end part of an oil hole are not shown in the following drawings including FIG.

Next, the structure of the compressor mechanism 30 of the rotary compressor 1 will be described with reference to FIGS. 2 and 3 together with FIG. 1. 2 is a schematic diagram showing an example of an internal structure in a side view of the compressor mechanism 30 of the rotary compressor 1 according to the first embodiment. 3 is a schematic diagram showing an example of an internal structure in the upper surface of the compressor mechanism 30 of the rotary compressor 1 according to the first embodiment.

The compression mechanism 30 compresses the low-pressure gas refrigerant sucked into the low-pressure space of the sealed container 2 from the suction pipe 6 with the high-pressure gas refrigerant by the rotational driving force supplied from the electric motor unit 10, and compresses it. A high-pressure gas refrigerant is discharged above the compressor mechanism (30).

The compression mechanism 30 includes an inner surface 31b extending between a pair of hollow disc faces 31a and an inner edge portion of the pair of hollow disc faces 31a, and a pair of hollow disc faces 31a. It is provided with a hollow cylindrical cylinder 31 having an outer surface 31c extending between the outer edges. The outer surface 31c of the cylinder 31 is fixed to the inner surface of the body portion 2a of the sealed container 2. The hollow portion 310 of the cylinder 31 is composed of a space surrounded by the inner surface 31b of the cylinder 31, and the eccentric portion 24 and the piston 26 of the crankshaft 20 are accommodated. That is, in the hollow portion 310 of the cylinder 31, the eccentric portion 24 and the piston 26 of the crankshaft 20 rotate eccentrically by the rotation of the crankshaft 20 in the hollow portion 310 of the cylinder 31. It is configured to be.

In the cylinder 31, a suction port communicating between the suction pipe 6 and the hollow portion 310 of the cylinder 31 and introducing a low-pressure gas refrigerant into the hollow portion 310 of the cylinder 31 from the suction pipe 6 312 is provided. In addition, a semicircular discharge passage 314 extending in the vertical direction is provided on the inner surface of the cylinder 31. Further, the cylinder 31 is provided with vane grooves 316 extending in the radial direction from the inner surface 31b of the cylinder 31 to the outer surface 31c of the cylinder 31 in the upper surface. The vane groove 316 is formed between two parallel plate-shaped side walls 317 in the upper surface.

The vane 32 is accommodated in the vane groove 316 of the cylinder 31. The vane 32 is a sliding motion member configured to reciprocate the inside of the vane groove 316 in the radial direction by an eccentric motion of the piston 26. The tip portion 32a of the vane 32 disposed in the hollow portion 310 of the cylinder 31 is the restoring force of an elastic body 33 such as a spring provided inside the vane groove 316 or the upper side of the compression mechanism portion 30 By the pressure from the high-pressure portion of the, it is pressed and pasted to the outer surface of the piston 26. As shown in Fig. 3, during the rotational drive of the piston 26, the hollow portion 310 of the cylinder 31 is a low-pressure space communicating with the suction port 312 by the vane 32 and the piston 26. It is divided into a portion 310a and a high-pressure space portion 310b communicating with the discharge passage 314. The low-pressure space portion 310a and the high-pressure space portion 310b serve as a space constituting the compression chamber of the compression mechanism portion 30 to be described later.

In addition, the cylinder 31 is provided with a vane groove opening 318 communicating with the vane groove 316 and penetrating through the pair of hollow disc faces 31a of the cylinder 31. In the compression mechanism portion 30, the pressure from the high pressure portion above the compression mechanism portion 30 can be applied to the distal end portion 32b of the vane 32 through the vane groove opening 318. Moreover, the movement of the vane 32 in the direction of the outer surface of the cylinder 31 can be restricted by the vane groove opening 318. In addition, through the vane groove opening 318, the lubricant separated from the high-pressure gas refrigerant can be supplied between the vane groove 316 and the vane 32 to smoothly reciprocate the vane 32. The detailed structure of the vane groove opening 318 will be described later.

In addition, although not shown in the following drawings including FIG. 1, clearance is provided between the vane groove 316 and the vane 32 so that friction does not occur between the vane groove 316 and the vane 32. Consists of. On the other hand, when the clearance between the vane groove 316 and the vane 32 increases, the refrigerant gas compressed in the hollow portion 310 of the cylinder 31, through the clearance and the vane groove opening 318, the compression mechanism ( 30), there is a possibility that the compression efficiency may decrease. Therefore, the clearance is configured to be so small that friction does not occur between the vane groove 316 and the vane 32. By making the clearance small, leakage of compressed refrigerant gas can be suppressed, leakage loss can be reduced, and compression efficiency can be improved.

The main shaft 34 is disposed on the hollow disc face 31a on the upper side of the cylinder 31, that is, on the hollow disc face 31a on the side of the lid portion 2b of the sealed container 2. On the hollow disk surface 31a on the lower side of the cylinder 31, that is, the hollow disk surface 31a on the bottom surface side of the body portion 2a of the hermetic container 2, the auxiliary shaft 35 is arranged. The main shaft support 34 and the auxiliary shaft support 35 are slide bearings that support the crankshaft 20 so that it can slide.

The main shaft 34 has a shape of a hollow disk in the upper surface. The main shaft support 34 includes a fixing portion 34a fixed to the hollow disc face 31a on the upper side of the cylinder 31, and a shaft support portion 34b for slidingly supporting the outer surface of the crankshaft 20 Have In addition, in the longitudinal cross-sectional view of FIG. 1, the main shaft 34 is shown as two L-shaped members. In addition, the main spindle 34 is fixed to the hollow disc face 31a above the cylinder 31, for example, by bolts or the like.

The supporting shaft 35 has a hollow disk-shaped shape when viewed from the bottom. The auxiliary shaft support 35 is fixed to the hollow disk surface 31a below the cylinder 31, a fixed portion 35a, and a support portion 35b for slidingly supporting the outer surface of the crankshaft 20 Have In addition, in the longitudinal cross-sectional view of FIG. 1, the auxiliary bearing 35 is shown as two L-shaped members. In addition, the auxiliary bearing 35 is fixed to the hollow disc face 31a on the lower side of the cylinder 31 by, for example, bolts.

In the compression mechanism section 30, the piston 26, the cylinder 31, the vane 32, the fixed portion 34a of the main shaft 34 and the fixed portion 35a of the auxiliary shaft 35 surrounded by a sealed free space The silver constitutes a compression chamber that compresses the low-pressure gas refrigerant sucked from the suction pipe 6. The gas refrigerant of high pressure compressed in the compression chamber is discharged from the discharge port provided in the main shaft 34. In addition, the discharge port provided in the main shaft 34 is not illustrated in the following drawings including FIG. 1.

A silencer 36 is disposed on the upper surface side of the fixing portion 34a of the main shaft 34. The silencer 36 is configured to remove or reduce noise generated during compression of the refrigerant in the compression mechanism portion 30 by covering a part of the fixing portion 34a and the bearing portion 34b of the main shaft 34. It is done. In addition, although not shown, the silencer 36 is provided with a plurality of openings for discharging the high-pressure gas refrigerant flowing from the discharge port provided in the main shaft 34 into the sealed container 2. Further, the silencer 36 is fixed to the hollow disc face 31a above the cylinder 31 through the main shaft 34, for example, by a bolt or the like.

Next, the detailed structure of the vane groove opening 318 of the cylinder 31 in the compression mechanism 30 of the rotary compressor 1 of the first embodiment will be described with reference to FIG. 4. FIG. 4 is a partially enlarged view showing an example of a schematic structure of a vane groove opening 318 of the cylinder 31 in the compressor mechanism 30 of the rotary compressor 1 according to the first embodiment. .

As described above, the cylinder 31 is provided with a vane groove opening 318 communicating with the vane groove 316 and penetrating through the pair of hollow disc faces 31a of the cylinder 31. The vane groove opening 318 is a space surrounded by a wall surface portion 319 having, for example, a pair of first convex-shaped bent portions 319a and second convex-shaped bent portions 319b, as shown in FIG. 4. It is formed of. The pair of first convex-shaped bent portions 319a is disposed on the inner surface 31b side of the cylinder 31 and has a first radius of curvature R1. The second convex-shaped bent portion 319b is disposed on the outer surface 31c side of the cylinder 31 than the pair of first convex-shaped bent portions 319a, and between the pair of first convex-shaped bent portions 319a. And a second radius of curvature R2. 4, in the first convex-shaped bend 319a, the center of the first radius of curvature R1 is located on the vane groove opening 318 side, and the second convex-shaped bend 319b ), The center of the second radius of curvature R2 is located on the vane groove opening 318 side.

The vane groove opening 318, for example, drills a hole having a first radius of curvature R1 through the hollow disc surface 31a with a drilling tool such as a drill, and then penetrates through the hollow disc surface 31a. It is formed by drilling a hole of the second radius of curvature R2. Therefore, since the vane groove opening 318 can be formed by a simple drilling operation, the manufacturing cost of the rotary compressor 1 can be reduced.

In addition, the vane groove opening 318 is not limited to the example of FIG. 4, and may be formed as a space surrounded by the wall surface portion 319 having a plurality of convex-shaped bent portions. For example, the vane groove opening 318 may have an elliptical shape, may have a spindle shape such as a shape of a rugby ball, or may have a long shape such as a shape of a capsule. At this time, the wall surface portion 319 is configured to be disposed inside the imaginary circle having the maximum width of the vane groove opening 318 in the radial direction of the cylinder 31 as a diameter. Further, the maximum width of the vane groove opening 318 described above is a vane in the radial direction of the cylinder 31 formed by a drilling tool such as a drill, assuming that the vane groove 316 is not formed in the cylinder 31. Let the groove opening 318 be the maximum width. Further, the plurality of convex-shaped bent portions described above may have different radii of curvature.

Next, the operation of the rotary compressor 1 of the first embodiment will be described.

When the crankshaft 20 is rotated by the drive of the electric motor unit 10, the eccentric part 24 and the piston 26 accommodated in the interior of the cylinder 31 together with the crankshaft 20 rotate eccentrically at high speed. . In conjunction with the eccentric rotation of the piston 26, the vane 32 provided inside the vane groove 316 of the cylinder 31 moves in a piston. The low-pressure gas refrigerant flowing into the compressor mechanism 30 from the intake pipe 6 through the intake 312 includes a fixed portion 34a of the piston 26, the cylinder 31, the vane 32, and the main shaft 34. ) And the compression chamber, which is an enclosed space surrounded by the fixing part 35a of the supporting shaft 35. The low-pressure gas refrigerant flowing into the compression chamber is compressed with a high-pressure gas refrigerant as the volume of the compression chamber is reduced by eccentric rotation of the piston 26.

In addition, the refrigerating machine oil 40 stored at the bottom of the main body portion 2a in the sealed container 2 is sucked up from the lower end portion of the crankshaft 20. The sucked freezer oil 40 is lubricating oil, between the bearing part 34b and the crankshaft 20 of the main spindle 34 and between the bearing part 35b and the crankshaft 20 of the auxiliary bearing 35. Inflow. By lubricating oil entering the sliding portion between the crankshaft 20 and the axle portion 34b of the main shaft 34 or the axle portion 35b of the sub-axis 35, the crankshaft 20 smoothly rotates the driving force. It can be delivered to the piston 26. In addition, the lubricating oil flows between the fixed portion 34a of the main shaft 34 and the upper surface of the piston 26 and also between the fixed portion 35a of the auxiliary shaft 35 and the lower surface of the piston 26. do. The lubricating oil is used to smoothly rotate the piston 26, but a part of the lubricating oil is compressed simultaneously with the low-pressure gas refrigerant and is discharged while being contained in the high-pressure gas refrigerant.

The high-pressure gas refrigerant containing lubricating oil flows into the silencer 36 from the cylinder 31 through the discharge passage 314 and the discharge port provided in the main shaft 34. The high-pressure gas refrigerant inside the silencer 36 is discharged from a plurality of openings provided in the silencer 36 to the high-pressure portion inside the sealed container 2 located between the electric motor part 10 and the compression mechanism part 30. do.

The high-pressure gas refrigerant discharged to the high-pressure portion passes through the gap provided in the stator 12 and the rotor 14 and flows in the upper direction of the crankshaft 20. At the upper part of the crankshaft 20, the lubricating oil component is separated from the high-pressure gas refrigerant by centrifugal force by rotation of the oil separation plate 22. The lubricating oil separated from the oil separation plate 22 is attached to the inner surface of the sealed container 2, passes through the outer groove provided in the stator 12, and falls downward by gravity. The lubricating oil that has fallen downward is recovered, for example, through the vane groove opening 318 at the bottom of the body portion 2a of the hermetic container 2, but a portion of the vane is reciprocated smoothly. The clearance between the groove 316 and the vane 32 is supplied. The high-pressure gas refrigerant from which the lubricating oil component is separated from the oil separation plate 22 reaches the lid portion 2b of the sealed container 2 and is discharged out of the sealed container 2 through the discharge pipe 7.

As described above, the rotary compressor 1 according to the first embodiment includes a piston 26 that rotates eccentrically by rotation of the crankshaft 20, a pair of hollow disc faces 31a, and It has an inner surface 31b extending between the inner edges of the pair of hollow disc surfaces 31a, and an outer surface 31c extending between the outer edges of the pair of hollow disc surfaces 31a, and the inner surface 31b. ) Is provided with a cylinder 31 in which the piston 26 is accommodated in a space surrounded by, and the cylinder 31 extends radially from the inner surface 31b toward the outer surface 31c, and the piston 26 It has a vane groove 316 accommodating the vane 32 reciprocating by eccentric rotation, and a vane groove opening 318 penetrating the pair of hollow disc faces 31a and communicating with the vane groove 316. The vane groove opening 318 includes a pair of first convex-shaped bent portions 319a having a first radius of curvature R1, and a pair of first convex-shaped bent portions ( 319a), the second convex-shaped bent portion disposed on the outer surface 31c side of the cylinder 31, extending between the pair of first convex-shaped bent portions 319a, and having the second radius of curvature R2 It is formed of a space surrounded by the wall surface portion 319 having the 319b, and the second radius of curvature R2 is configured to be smaller than the first radius of curvature R1.

Effects of the above-described configuration will be described below.

5 is a schematic diagram showing a method of fixing the cylinder 31 to the sealed container 2 at the time of manufacture of the rotary compressor 1 according to the first embodiment. As shown in FIG. 5, the outer surface 31c of the cylinder 31 is pressed by three caulking load mechanisms 50, and taps and attaches the jig 55 from the outside of the sealed container 2, and taps three caulking portions. By forming it is fixed to the inner surface of the sealed container (2). At this time, as shown by the three black block arrows, pressure is applied to the cylinder 31 in the radial direction from the outer surface 31c to the inner surface 31b.

6 is a schematic diagram showing an external force applied to the vane groove 316 when the cylinder 31 is fixed to the sealed container 2 in the rotary compressor 1 according to the first embodiment. As pressure is applied in the radial direction from the outer surface 31c of the cylinder 31 toward the inner surface 31b, as shown by the black block arrow in FIG. 6, the vane groove 316 includes a cylinder 31 ), The external force acts in the direction perpendicular to the radial direction and also in the direction of narrowing the width of the vane groove 316.

7 is a schematic view showing the structure of a vane groove opening 318a in the rotary compressor 1 of the prior art. In the prior art, the vane groove opening 318a is formed as a space surrounded by a circular wall portion 319. In the rotary compressor 1, in order to increase the discharge amount of refrigerant gas while maintaining the outer dimension of the cylinder 31, that is, the thickness and outer diameter of the cylinder 31, the inner diameter of the cylinder 31 is, for example, 44 mm. It is thought to increase from 46 mm. In this case, when the radial distance of the vane groove 316 is made 2 mm smaller, the sliding distance of the vane 32 becomes 2 mm smaller, and the amount of gas refrigerant compressed in the cylinder 31 decreases, so that the vane groove It is necessary to maintain the radial distance of 316. Maintaining the radial distance of the vane groove 316, the position of the vane groove opening 318 moves 2 mm in the direction of the hollow white block arrow, between the outer surface 31c and the vane groove opening 318. The distance D decreases. When the distance D between the outer surface 31c and the vane groove opening 318 decreases, the rigidity of the cylinder 31 against pressure by the caulking load mechanism 50 decreases, so that the vane groove 316 The external force acting in the direction of narrowing becomes large, and there is a case where distortion occurs in the vane groove 316. When distortion occurs in the vane groove 316, friction occurs between the vane groove 316 and the vane 32, and the sliding mobility of the vane 32 deteriorates.

On the other hand, in the vane groove opening 318 in the rotary compressor 1 according to the first embodiment, even when the distance D between the outer surface 31c and the vane groove opening 318 decreases, the vane groove opening The opening area of 318 can be configured to be smaller than that of the prior art. 8 is a schematic diagram comparing the shape of the vane groove opening 318 in the rotary compressor 1 according to the first embodiment with the vane groove opening 318a of the prior art having a circular shape. As shown by the hatched area A in FIG. 8, since the opening area of the vane groove opening 318 can be configured to be smaller than that of the conventional vane groove opening 318a, the caulking load mechanism 50 A decrease in the rigidity of the cylinder 31 against pressure due to) can be avoided.

Therefore, according to the above-described configuration, since the occurrence of distortion of the vane groove 316 can be avoided, the durability of the cylinder 31 can be improved. In addition, by avoiding the occurrence of distortion of the vane groove 316, friction between the vane groove 316 and the vane 32 is generated, and it is possible to avoid that the sliding mobility of the vane 32 deteriorates. Therefore, according to the above-described configuration, it is possible to provide the rotary compressor 1 capable of avoiding deterioration of the sliding mobility of the vane 32 and securing durability and reliability.

In addition, according to the above-described configuration, the vane groove opening 318, for example, drills a hole of the first radius of curvature R1 through the hollow disc face 31a with a drilling tool such as a drill, followed by It can be formed by drilling a hole of the second radius of curvature R2 penetrating through the hollow disk surface 31a. Therefore, since the vane groove opening 318 can be formed by a simple drilling operation, the manufacturing cost of the rotary compressor 1 can be reduced.

Further, in the first embodiment, the rotary compressor 1 is configured as a rolling piston type compressor, but it may also be configured as a swing vane type swing compressor. In the swing vane type swing compressor, the rolling piston portion corresponding to the piston 26 of the first embodiment and the piston portion incorporating the vane portion corresponding to the vane 32 of the first embodiment of the cylinder 31 It is equipped inside. Moreover, the swing vane type swing compressor is equipped with the bush which swings a piston part. The bush is a pair of semi-cylindrical rocking members that are arranged on the cylinder 31 and are supported by sandwiching the vane portion of the piston. Even when the rotary compressor 1 is configured as a swing compressor, the opening area of the vane groove opening 318 can be configured to be smaller than that of the conventional vane groove opening 318a. Therefore, even when the rotary compressor 1 is configured as a swing compressor, since the stiffness of the cylinder 31 can be avoided, it is possible to avoid deterioration of the sliding movement of the vane portion and to ensure durability and reliability. 1) can be provided.

Other embodiments.

Various modifications can be made to the above-described embodiment without departing from the gist of the present invention. For example, in the first embodiment described above, the rotary compressor 1 is configured as a hermetic compressor, but it may be configured as a semi-hermetic or open compressor.

Further, in the first embodiment described above, the rotary compressor 1 is configured as a one-cylinder compressor, but may be configured as a compressor having two or more cylinders 31.

1: rotary compressor 2: sealed container
2a: Body portion 2b: Cover portion
3: VS 4: Suction muffler
4a: body 4b: inlet pipe
5: support member 5a: band portion
5b: holder portion 6: suction pipe
7: discharge pipe 8: charge pipe
9: Glass terminal 10: Electric motor part
12: stator 14: rotor
16: Conductor 20: Crankshaft
20a: fixed surface 22: oil separation plate
24: eccentric part 26: piston
30: compression mechanism 31: cylinder
31a: hollow disc face 31b: inner face
31c: outer surface 32: vane
32a: distal end 32b: distal end
33: elastic 34: spindle
34a: Fixing part 34b: Shaft part
35: side support 35a: fixing part
35b: bearing unit 36: silencer
40: refrigerator oil 50: load mechanism
55: pressing jig 310: hollow part
310a: low pressure space portion 310b: high pressure space portion
312: inlet 314: discharge passage
316: vane groove 317: side wall
318: vane groove opening 318a: prior art vane groove opening
319: wall surface portion 319a: first convex shape bent portion
319b: second convex-shaped bend

Claims (3)

A piston rotated eccentrically by the rotation of the crankshaft,
A pair of hollow disc surfaces, an inner surface extending between the inner edges of the pair of hollow disc surfaces, and an outer surface extending between the outer edges of the pair of hollow disc surfaces, and the inner surface to the others. A vane groove extending radially toward the side and accommodating a vane reciprocating by eccentric rotation of the piston; a vane groove opening penetrating through the pair of hollow disc surfaces and communicating with the vane groove; and A cylinder provided on a side of the outer surface of the vane groove opening, having a groove to which an elastic body is pressed against the piston by a restoring force, and receiving the piston in a space surrounded by the inner surface;
A method of manufacturing a rotary compressor having a sealed container accommodating the cylinder,
By punching a hole having a first radius of curvature on the pair of hollow disc surfaces, a pair of first convex-shaped bends having the first radius of curvature is formed, and the pair of first convex-shaped bends By punching a hole of a second radius of curvature smaller than the first radius of curvature on the pair of hollow disc surfaces on the outer surface side of the cylinder, the gap between the pair of first convex-shaped bends is extended, Forming a second convex-shaped bend having the second radius of curvature, and forming the vane groove opening in a space surrounded by a wall surface portion having the pair of first convex-shaped bend and the second convex-shaped bend and,
And forming a caulking portion in the hermetic container, thereby fixing the cylinder to the hermetic container. According to claim 1,
The caulking portion, a rotary compressor manufacturing method characterized in that it is formed in the closed container by applying pressure from the outer surface toward the inner surface of the cylinder. delete

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