CZ2018394A3 - A rotary compressor - Google Patents

Abstract

A rotary compressor (1) is provided comprising a piston (26) which is eccentrically rotated when the crankshaft (20) is rotated, and a cylinder (31) having a pair of circular disk surfaces (31a) with a hole, an inner surface (31b) which extends between the inner edge portions of a pair of circular disk surfaces (31a) with a hole, and an outer surface (31c) that extends between the outer edge portions of a pair of circular disk surfaces (31a) with a hole, wherein the piston (26) is located in the cylinder ( 31) in the space bounded by the inner surface (31b). The cylinder (31) has a lamella groove (316) that extends in a radial direction from the inner surface (31b) towards the outer surface (31c) and in which the lamella (32) and the resilient member (33) are located. The lamella (32) moves reciprocatingly during eccentric rotation of the piston (26), the resilient member (33) pressing the lamella (32) against the piston (26). The lamella groove opening portion (318) is formed in a space bounded by a wall surface portion (319) that includes a pair of first convexly curved portions (319a) having a first curvature radius (R1) and a second convex curved portion (319b) positioned closer to the outer surface (31c) of the roller (31) than the pair of first convexly curved portions (319a) and extending between a pair of first convexly curved portions (319a) and having a second radius of curvature (R2). The second curvature radius (R2) is less than the first curvature radius (R1).

Description

Technical field

The invention relates to a rotary compressor comprising a vane groove.

BACKGROUND OF THE INVENTION

Patent Literature 1: Japanese Patent Application No. 2014-070596.

As a conventional rotary compressor which includes a vane groove, patent literature 1 discloses a rotary compressor in which an annular cylinder is provided with a vane groove in which the vane is located and a pressure supply path connected to an extreme end portion of the outer side of the circumferential surface of the vane groove. In the rotary compressor described in patent literature 1, the pressure supply path includes a circular opening and extends through the cylinder in a vertical direction.

SUMMARY OF THE INVENTION

In order to increase the compression amount of gaseous refrigerant while rotating the piston while maintaining the outer dimensions of the cylinder, the cylinder needs, in the rotary compressor of patent literature 1, an arrangement with a larger cylinder inner diameter, greater eccentric piston distance and greater blade sliding distance.

In order to increase the eccentric distance of the piston while maintaining the outer dimensions of the cylinders, the inner diameter of the cylinder needs to be increased in a rotary compressor according to patent literature 1. Further, if, in a rotary compressor according to Patent Literature 1, the inner diameter of the cylinder is increased while maintaining the outer dimensions of the cylinder, the distance between the position of each vane groove and the pressure inlet path and the outer peripheral surface of the cylinder is reduced.

Further, in order to increase the sliding distance of the lamella while maintaining the outer dimensions of the cylinder, it is necessary, in the rotary compressor according to patent literature 1, to increase the length of the lamella groove. If, in the rotary compressor of patent literature 1, the length of the lamella groove is increased while maintaining the outer dimensions of the cylinder, the distance between the pressure inlet path and the outer peripheral surface of the cylinder is reduced.

In the rotary compressor described in patent literature 1, in the manufacture of the rotary compressor according to patent literature 1, there occurs a situation where external pressure is applied from the outer surface of the sealed container towards the center of the cylinder to secure the outer surface of the cylinder to the inner surface of the sealed container. When, in the rotary compressor described in Patent Literature 1, the distance between the pressure inlet path and the outer peripheral surface of the cylinder is reduced, the resistance of the cylinder to the external force acting from the outer peripheral surface of the cylinder is reduced. If the resistance of the roller to external forces is reduced, the roller may become more deformed. As a result, there is a possibility that due to deformation of the lamella groove, friction will develop between the lamella groove and the lamella, which will impair the sliding of the lamella. On the other hand, if a greater clearance is created between the lamella groove and the lamella, a larger amount of coolant escapes from such a gap, which reduces the compression efficiency. For this reason, it is necessary to keep the clearance small. Accordingly, in the case where the compressive amount of gaseous refrigerant is increased while maintaining the outer diameter of the cylinder, the sliding of the lamella will deteriorate, leading to more noise or greater frictional losses. As a result, there is a possibility that durability and reliability cannot be assured.

The present invention is intended to solve the above problem and it is an object of the present invention to provide a rotary compressor that does not impair the slip of the slat and can provide a long life

- 1 GB 2018 - 394 A3 reliability.

A rotary compressor according to an embodiment of the present invention comprises: a piston arranged to rotate eccentrically when the crankshaft rotates; and a cylinder comprising a pair of circular disk surfaces with a hole, an inner surface and an outer surface, the inner surface extending between the inner edge portions of the pair of circular disk surfaces with the hole, the outer surface extending between the outer edge portions of the pair of circular disc surfaces with the hole. arranged in the space bounded by the inner surface. The cylinder comprises a vane groove and an aperture portion of the vane groove, wherein the vane groove extends in a radial direction from the inner surface towards the outer surface and accommodates a vane arranged to reciprocate when the piston eccentrically rotates, the vane groove opening through a pair of circular disk surfaces and is connected to a vane groove. The aperture portion of the lamella groove is formed in a space bounded by a wall sheet portion comprising a pair of first convexly curved portions and a second convexly curved portion, the pair of first convexly curved portions having a first curvature radius, the second convexly curved portion having a second curvature radius closer to the outer surface of the cylinder than the pair of first convexly curved portions and extends between the pair of first convexly curved portions. The second radius of curvature is smaller than the first radius of curvature.

In an embodiment of the invention, the aperture portion of the vane groove may be designed to have a surface area of the aperture portion smaller than the aperture portion of the vane groove of a conventional rotary compressor. Therefore, deformations of the lamella groove can be avoided. Since, in the embodiment of the invention, deformation of the lamella groove can be avoided, the service life of the roller can be improved and, moreover, friction between the lamella groove and the lamella can be prevented, thereby also deteriorating the sliding of the lamella. Thus, an embodiment of the invention can provide a rotary compressor which can avoid deteriorating the sliding of the slat and thus ensure durability and reliability.

BRIEF DESCRIPTION OF THE DRAWINGS [FIG. 1] FIG. 1 is a vertical sectional view schematically showing an example of a rotary compressor 1 according to Embodiment 1 of the invention.

[Giant. 2] FIG. 2 is a schematic view showing an example of the internal structure of the rotary compressor compression unit 30 according to Embodiment 1 of the invention, shown in side view.

[Giant. 3] FIG. 3 is a schematic view showing an example of the internal structure of the compressor mechanism 30 of the rotary compressor 1 according to Embodiment 1 of the invention, shown in plan view.

[Giant. 4] FIG. 4 is a partially enlarged diagram showing an example of a schematic structure of the aperture portion 318 of the vane groove of the cylinder 31 in the compressor mechanism 30 of the rotary compressor 1 according to embodiment 1 of the invention.

[Giant. 5] FIG. 5 is a schematic view showing a method of attaching a cylinder 31 to a tight container 2 in the manufacture of a rotary compressor 1 according to embodiment 1 of the invention.

[Giant. 6] FIG. 6 is a schematic view showing the external force exerted on the vane groove 316 when fastening the cylinder 31 to a tight container 2 in a rotary compressor 1 according to embodiment 1 of the invention.

[Giant. 7] FIG. 7 is a schematic view showing the structure of the aperture portion 318a of the vane groove in a conventional rotary compressor 1.

[Giant. 8] FIG. 8 is a schematic diagram comparing the shape of the aperture portion 318 of the vane groove v

The rotary compressor 1 according to Embodiment 1 of the invention having a circular shape of a vane slot portion 318a of a conventional rotary compressor.

DETAILED DESCRIPTION OF THE INVENTION

Embodiment 1

The rotary compressor arrangement 1 according to Embodiment 1 of the invention will be described with reference to FIG. 1. FIG. 1 is a vertical section schematically showing an example of a rotary compressor 1 according to Embodiment 1. The rotary compressor 1 is used in a refrigeration circulator, such as an air conditioner, and is a structural element of a refrigeration circuit of a refrigeration circulator.

Giant. 1 and the figures referred to below do not show the refrigerant circuit or other components included in the refrigerant circuit, such as a radiator, an evaporator, a decompressor and an oil separator. In the drawings, there is a case where the dimensional relationships between the structural members and the shapes of the structural members are different from the actual ones. All identical or similar members or parts in the drawings are designated with the same reference numerals, or for some members or parts the reference numeral or symbols are omitted. The positional relationship, such as the vertical relationship between the rotary compressor 1 components, is in the following description a positional relationship established when the rotary compressor J is installed in a usable state, unless otherwise stated.

The rotary compressor 1 is of the rolling-piston type and is a fluidized-bed engine arranged to eject, as a high-pressure gaseous refrigerant, the low-pressure gaseous fuel introduced into the rotary compressor J. The rotary compressor housing J is a cylindrical tight container 2. which has a U-shaped vertical section and a lid unit 2b having an inverted U vertical section. The outer surface of the opening portion of the lid unit 2b is fixed to the inner surface of the opening portion of the body unit 2a. In this fastened part, the body unit 2a and the lid unit 2b are joined together, for example by welding. Further, the outer surface of the lower surface of the body unit 2a is provided with a pedestal 3 for use to vertically deploy the rotary compressor J. The rotary compressor J is shown in Figs. 1 may be arranged as a vertically mounted compressor, but may be arranged as a horizontally mounted compressor.

A suction damper housing 4a is fastened to a portion of the outer surface of the sealed container body unit 2a to the support member 5 located on the outer surface of the sealed container 2. The support member 5 may be formed to include, for example, an annular belt unit 5a configured to secure the outer surface of the intake silencer 4, and a bracket unit 5b secured to the outer surface of the sealed container 2 and configured to support the belt unit 5a. The supply line 4b, which extends through the housing 4a, is fixed to the upper part of the housing 4a of the intake silencer 4. The inlet conduit 4b is, for example, a refrigerant conduit through which a low pressure gaseous refrigerant or a high-quality two-phase refrigerant flows into the housing 4a of the intake silencer 4, which flows from the refrigerant circulator. One end of the inlet pipe 6 is fixed to the bottom of the housing 4a of the intake silencer 4 in such a way as to permeate it, while the other end of the inlet pipe 6 is fixed to the lateral surface of the body unit 2a of the sealed container 2 in such a way.

The intake silencer 4 is a silencer arranged to reduce or eliminate the noise caused by the refrigerant flowing from the supply line 4b. The intake silencer 4 also functions as a reservoir having the function of a refrigerant storage and accumulating refrigerant surplus, and a function of separating liquid and steam from the storage of the liquid refrigerant temporarily formed when the operating conditions change. Due to the liquid / steam separation function of the intake silencer 4, a large amount of liquid refrigerant can be prevented from flowing into the tight container 2, thereby preventing liquid compression in the rotary compressor T

-3 EN 2018 - 394 A3

The inlet conduit 6 is a refrigerant conduit through which the low pressure gaseous refrigerant flows into the tight container 2. The inlet conduit 6 and the body unit 2a are connected together in a fixed portion therebetween, for example by soldering. Although not shown in FIG. 1, the inlet conduit 6 may be provided with an oil return hole in a portion of its side surface through which the lubricating component contained in the high pressure gaseous refrigerant that is separated in the oil separator of the refrigeration circulator can be returned to the tight container 2 through the inlet conduit 6.

The discharge line 7 is fastened to the upper surface of the lid unit 2b of the sealed container 2 in such a way as to pass therethrough. The discharge line 7 is a refrigerant line through which the high pressure gaseous refrigerant is forced out of the tight container 2. The discharge line 7 and the lid unit 2b are connected together in a fixed part therebetween, for example by soldering.

The filling line 8 is fixed to the top surface of the lid unit 2b of the sealed container 2 in such a way as to pass through it. The filling line 8 may be arranged to allow a vacuum to be formed in the tight container 2 as well as to seal the tight container 2, with the gaseous refrigerant inside. The filling line 8 may also be arranged to allow sealing of the sealed container 2 with the lubricant contained therein.

In addition, an insulated terminal block 9 ("glass terminal") is located on the top surface of the lid unit 2b of the sealed container 2. The insulated terminal block 9 provides an interface for connecting an external power supply. The external power supply is a power supply device configured to provide power to the rotary compressor 1 and is either a commercial general purpose AC power supply having a 50 Hz or 60 Hz alternating current power supply or a variable frequency AC power supply. If a variable frequency converter power supply is used, the rotational speed of the rotary compressor 1 can be varied so that the amount of high pressure gaseous refrigerant to be discharged from the discharge line 7 can be controlled in the rotary compressor 1. including FIG. 1, the external power supply connected to the insulated terminal block 9 is not shown.

In the tight container 2 is provided an electric motor unit 10, a crankshaft 20 and a compression mechanism unit 30. The electric motor unit 10 is located at a higher position than the fixed portion between the body unit 2a and the inlet pipe 6. In the central part of the tight container 2 is a crankshaft 20 that extends vertically between the electric motor unit 10 and the compression mechanism unit 30. The compression unit 30 is configured such that a portion of the side surface of the compression unit 30 covers the fixed portion between the body unit 2a and the inlet conduit 6 so that the interior of the compression unit 30 is connected to the inlet conduit 6. engine located above the compression unit 30. Also, the hollow space above the compression mechanism unit 30 in the tight container 2 is filled with high pressure gaseous refrigerant compressed on the compression mechanism unit 30.

The electric motor unit 10 is configured as a motor configured to generate a rotational driving force using the power supplied from an external power supply, and to transmit the rotational driving force to the compression mechanism unit 30 via the crankshaft 20. The electric motor unit 10 comprises a stator 12 having the form a hollow cylinder, as seen in plan view, and a cylindrical rotor 14 rotatably positioned within the inner surface of the stator 12, the stator 12 is fixed to the inner surface of the body unit 2a of the tight container 2 and connected to the insulated terminal block 9 by conductor 16. can cause the rotor 14 to rotate at a position within the inner surface of the stator 12 when supplying power from an external power supply via conductor 16 to a coil that is wrapped around the stator 12. engine for example, a brushless DC motor.

The crankshaft 20 is mounted in the central part of the rotor 14 in such a way that the rotor 14

-4GB 2018 - 394 A3 passed. The crankshaft 20 is a rotary shaft that secures the rotor 14 to a mounting surface 20a that is part of the outer surface of the crankshaft 20 and transmits the rotational drive force of the rotor 14 to the compression unit 30. The crankshaft 20 extends from the mounting surface 20a in the vertical direction, i.e. towards the lid unit 2b of the tight container 2 and in the direction of the bottom of the body unit 2a of the tight container 2. An oil separator plate 22 is provided above the mounting surface 20a. The oil separator plate 22 is arranged to separate the lubricant contained in the high pressure gaseous refrigerant extruded from the compression mechanism unit 30 by centrifugal force when the crankshaft 20 rotates so that the lubricant falls into the lower part of the body unit 2a by gravity.

The crankshaft 20 comprises a cylindrical eccentric unit 24 which is situated below the mounting surface 20a and is located in the compression mechanism unit 30. The piston 26 pivotally connected along the outer surface of the eccentric unit 24 is located on the outer surface of the eccentric unit 24.

The center portion of the crankshaft 20 is provided with an oil passage extending upwardly from the lower end of the crankshaft 20. A lubricant flows through the oil passage through which coolant oil 40 is sucked from the lower end of the crankshaft 20. The outer surface of the crankshaft 20 is provided with a plurality of lubrication holes. which are connected to the oil hole above and through which the lubricant is supplied to the compression mechanism unit 30. A centrifugal pump may be provided at the lower end portion of the crankshaft oil channel. For example, a centrifugal pump is a helical centrifugal pump arranged to suck up cooling engine oil 40 accumulated at the bottom of the body unit 2a of the tight container 2. The cooling engine oil 40 may be, for example, a mineral lubricant, an alkyl benzene lubricant, a polyalkylene glycol lubricant, a polyvinyl ether lubricant, or a polyol-ester lubricant. The oil passage and lubrication holes provided by the crankshaft 20 and the centrifugal pump located at the lower end portion of the oil passage are not shown in the drawings, including Figs. 1, shown.

The arrangement of the compressor mechanism unit 30 of the rotary compressor 1 will be adjacent to FIG. 1 described with reference to FIG. 2 and 3. In FIG. 2 is a schematic view showing an example of the internal structure of the rotary compressor compression unit 30 of the embodiment 1 shown in side view. In FIG. 3 is a schematic view showing an exemplary internal structure of the rotary compressor compression unit 1 of the embodiment 1 shown in plan view.

The compression mechanism unit 30 utilizes the rotational driving force supplied by the electric motor unit 10 to compress the low pressure gaseous refrigerant sucked from the low pressure space of the tight container 2 through the inlet conduit 6 into the high pressure gaseous refrigerant. The pressurized high-pressure gaseous refrigerant expels to a region located above the compression unit 30.

The compression mechanism unit 30 comprises a cylinder 31 having a hollow cylindrical shape. The cylinder 31 includes a pair of circular disk surfaces 31a with a hole, an inner surface 31b that extends between the inner edge portions of the pair of circular disk surfaces 31a with a hole, and an outer surface 31c that extends between the outer edge portions of the pair of circular disk surfaces 31a with the hole. The outer surface 31c of the cylinder 31 is fixed to the inner surface of the body unit 2a of the sealed container 2. The cylinder 31 comprises a hollow portion 310 which is provided in the space bounded by the inner surface 31b of the cylinder 31 and the eccentric unit 24 and the piston 26 of the crankshaft 20. That is, the cylinder 31 is arranged to allow eccentric unit 24 and the piston 26 of the crankshaft 20 to eccentrically rotate in the hollow portion 310 of the cylinder 3k when the crankshaft 20 is rotated.

The cylinder 31 is provided with an inlet opening 312 which is positioned between the inlet duct 6 and the hollow portion 310 of the cylinder 31 to interconnect them and through which the hollow portion 310 of the cylinder 31 flows from

Inlet pipe 6 low pressure gaseous refrigerant. Also, the inner surface of the cylinder 31 is provided with a semicircular discharge path 314 that extends vertically. The cylinder 31 is also provided with a vane groove 316 that extends in a radial direction from the inner surface 31b of the cylinder 31 towards the outer surface of the cylinder 31c of the cylinder 31, as seen in plan view. The lamella groove 316 is formed between two flat plate side walls 317 that are parallel to each other when viewed in plan view.

A lamella 32 is provided in the vane groove 316 of the cylinder 31. The vane 32 is a sliding member arranged to reciprocate in the vane groove 316 in the radial direction due to the eccentric movement of the piston 26. The front end portion 32a of the lamella 32, which is located in the hollow portion 310 of the cylinder 31, is pressed against the outer surface of the piston 26 by the restoring force of a resilient member 33 such as a spring provided in the vane groove 316 or pressure from the high pressure portion above the unit. 30 of the compression mechanism. As shown in FIG. 3, during the rotation of the piston 26, the hollow portion 310 of the cylinder 31 through the lamella 32 and the piston 26 is located in the low pressure chamber portion 310a that communicates with the inlet port 312, and the high pressure chamber portion 310b that communicates with the discharge path 314. the low pressure space and the high pressure part 310b serve as compression sections of the compression mechanism unit 30 as will be described below.

The cylinder 31 is also provided with a vane groove aperture 318 that communicates with the vane groove 316 and extends with a pair of circular disk surfaces 31a with a cylinder bore 31. In the compression unit 30, pressure from the high pressure portion above the compression unit 30 acts through the aperture portion 318 The groove aperture 318 may limit the movement of the lamella 32 toward the outer surface of the cylinder 31. Through the aperture 318 of the lamella groove, lubricant that has been separated may also be fed between the lamella groove 316 and the lamella 32. of high pressure gaseous coolant, allowing blade 32 to move smoothly reciprocally. The arrangement of the aperture portion 318 of the vane groove will be described in more detail below.

Although it is not in the figures referred to below, including FIG. 1, a clearance is provided between the vane groove 316 and the vane 32 to prevent friction between the vane groove 316 and the vane 32, but if the clearance between the vane groove 316 and the vane 32 is greater, the gaseous refrigerant compressed in the hollow portion 310 of the cylinder 31 through this clearance and through the aperture portion 318 of the vane groove to escape out of the compression mechanism unit 30, which reduces the compression efficiency. The clearance must therefore only be so small as to prevent friction between the vane groove 316 and the vane 32. Due to the small clearance, the leakage of compressed gaseous refrigerant can be prevented and leakage loss can be reduced, thereby improving compression efficiency.

On the upper circular disk surface 31a with the cylinder bore 31, i.e. ^{on the} circular disk surface 31a with the bore which is located closer to the lid unit 2b of the sealed container 2, there is a main bearing 34. A sub-bearing 35 is located on a circular disk surface 31a with a hole that is located closer to the bottom surface of the body unit 2a of the sealed container 2. so that he can slide in them.

The main bearing 34 has, as shown in plan view, the shape of a circular plate with a hole. The main bearing 34 includes a fixed portion 34a that is fixed to the upper circular disk surface 31a with the cylinder bore 31, and a bearing 34b that carries the outer surface of the crankshaft 20 so as to be slidable therein. In the vertical section of FIG. 1, the main bearing 34 is shown as two L-shaped members. The main bearing 34 is attached to the upper circular disk surface 31a with the cylinder bore 31, for example, by a screw.

The sub-bearing 35 has the shape of a circular plate with a hole when viewed from below. The sub-bearing 35 includes a fixed portion 35a that is fixed to the lower annular disk surface 31a with the cylinder bore 31, and a bearing 35b that carries the outer surface of the crankshaft 20 so as to be slidable therein.

-6GB 2018 - 394 A3 Move. In the vertical section of FIG. 1, the sub-bearing 35 is shown as two L-shaped members. The sub-bearing 35 is secured to the lower circular disk surface 31a with the cylinder bore 31, for example by a screw.

In the unit 30 of the compression mechanism, the sealed space enclosed by the piston 26, the cylinder 31, the vane 32, the fixed portion 34a of the main bearing 34 and the fixed portion 35a of the auxiliary bearing 35 serve as the compression section for compressing the low pressure gaseous coolant. the refrigerant which is compressed in the compression compartment is extruded through the discharge port provided with the main bearing 34. The discharge port with which the main bearing 34 is provided is not shown in the figures to which reference is made below, including FIG. 1, shown.

A damper 36 is located on the upper surface of the fixed portion 34a of the main bearing 34. The damper 36 covers part of the fixed portion 34a and the bearing 34b of the main bearing 34 and is arranged to eliminate or reduce the refrigerant compression noise in the compression mechanism unit 30. Although not shown, the damper 36 is provided with a plurality of orifices for extruding high pressure gaseous coolant entering through the discharge port provided with the main bearing 34 into the tight container 2. The damper 36 is secured to the upper circular disk surface 31a with the cylinder bore 31 for example the main bearing 34 being interposed therebetween.

Referring to FIG. 4, the arrangement of the aperture portion 318 of the vane groove of the cylinder 31 in the compressor mechanism 30 of the rotary compressor 1 according to the embodiment 1 will be described. 4 is a partially enlarged diagram showing an example of a schematic arrangement of the aperture portion 318 of the vane groove of the cylinder 31 in the compressor mechanism 30 of the rotary compressor 1 according to embodiment 1.

As described above, the roller 31 includes a vane groove aperture 318 that communicates with the vane groove 316 and extends through a pair of circular disk surfaces 31a with the cylinder bore 31. The vane groove aperture 318 is formed in the space delimited by the wall surface portion 319, which, as shown in FIG. 4, includes a pair of first convexly curved portions 319a and a second convexly curved portion 319b. The pair of first convexly curved portions 319a has a first curvature radius R1 and is located closer to the inner surface 31b of the roller 31. The second convexly curved portion 319b has a second curvature radius R2. The second convexly curved portion 319 is located closer to the outer surface 31c of the roller 31 than the pair of the first convexly curved portions 319a and extends between the pair of the first convexly curved portions 319a. As shown in FIG. 4, the center of the first curvature radius R1 in the first convexly curved portion 319a is located on the side closer to the aperture portion 318 of the vane groove, and also the center of the second curvature radius R2 in the second convexly curved portion 319b is located on the side closer to the aperture portion 318 of the vane groove.

The aperture groove portion 318 is formed by making, by means of a perforating tool such as a drill, a hole having a first curvature radius R1 and extending with circular disk surfaces 31a with a hole, and subsequently making a hole having a second curvature radius R2 and extending circular disk surfaces 31a with a hole. Thus, the aperture portion 318 of the vane groove can be formed by easy perforation work. Thus, the manufacturing cost of a rotary compressor 1 may be lower.

The aperture portion 318 of the vane groove is not limited to the example shown in FIG. 4, but may be formed in a space bounded by a wall surface portion 319 that includes a plurality of convexly curved portions. For example, the aperture portion 318 of the vane groove may have an elliptical shape, a spindle shape such as a rugby ball shape, or an oval shape such as a capsule shape. In such an arrangement, the wall surface portion 319 is located within a virtual circle having a diameter equal to the maximum width of the aperture portion 318 of the vane groove in the radial direction of the roller 31. The maximum width of the aperture portion 318 of the vane groove is lamella grooves formed using a perforation tool such as a drill, provided that no lamella groove is formed in the cylinder 31

-7 GB 2018 - 394 A3

31. The plurality of convexly curved portions may have different radii of curvature.

Next, the operation of the rotary compressor 1 according to Embodiment 1 will be described.

When the crankshaft 20 is rotated by the electric motor unit 10, the eccentric unit 24 and the piston 26 provided in the cylinder 31 are eccentrically rotated together with the crankshaft 20. The plate 32 provided in the vane groove 316 of the cylinder 31 moves the piston in conjunction with the eccentric rotating the piston 26. After flowing into the compression mechanism unit 30 from the inlet pipe 6 through the inlet port 312, low pressure gaseous refrigerant flows into the compression compartment, which is the sealed space bounded by the piston 26, cylinder 31, fin 32, fixed portion 34a of main bearing 34 and fixed. The low pressure gaseous refrigerant flowed into the compression compartment is compressed to the high pressure gaseous refrigerant because the volume of the compression compartment decreases by eccentric rotation of the piston 26.

Cooling machine oil 40, which is collected at the bottom of the body unit 2a in the tight container 2, is sucked from the lower end of the crankshaft 20. The sucked cooling machine oil 40 flows as a lubricant into the sliding portion between the main bearing 34b and the crank. When the lubricant flows into the sliding portion between the crankshaft 20 and the main bearing 34b or the bearing 35b of the sub-bearing 35, the crankshaft 20 can smoothly transmit the rotary drive. The lubricant also flows between the fixed portion 34a of the main bearing 34 and the upper surface of the piston 26, and also between the fixed portion 35a of the sub-bearing 35 and the lower surface of the piston 26. The lubricant serves to smoothly rotate the piston 26 part of the lubricant is compressed together with the low pressure gaseous refrigerant and is extruded when contained in the high pressure gas coolant gas coolant.

The high pressure gaseous refrigerant containing the lubricant flows from the cylinder 31 via the discharge path 314 and the discharge port provided with the main bearing 34 to the silencer 36. The high pressure gaseous refrigerant is discharged from the silencer 36 through a plurality of holes provided with the silencer 36 into a high pressure portion in a tight container 2 that is located between the electric motor unit 10 and the compression mechanism unit 30.

Upon extrusion into the high pressure portion, the high pressure gaseous coolant flows towards the upper portion of the crankshaft 20 through the gap between the stator 12 and the rotor 14. At the upper portion of the crankshaft 20, the lubricant component separates from the high pressure gaseous coolant under centrifugal force due to rotation of the oil separator plate 22. The lubricant separated by the oil separator plate 22 adheres to the inner surface of the sealed container 2, and under gravity flows down the outer groove provided in the stator 12. When it flows down, lubricant collects, for example, in the lower part of the sealed container body 2a through the aperture 318. and a portion of the lubricant enters the gap between the vane groove 316 and the vane 32 so that the vane 32 can move smoothly reciprocally. The high-pressure gaseous refrigerant from which the lubricant component has been separated on the oil separator plate 22 reaches the lid unit 2b of the tight container 2 and is forced out of the tight container 2 via the discharge line 7.

As described above, the rotary compressor 1 according to Embodiment 1 comprises: a piston 26 arranged to rotate eccentrically when the crankshaft 20 rotates; and a cylinder 31 20 that includes a pair of circular disk surfaces 31 and with a hole, an inner surface 31b that extends between the inner edge portions of the pair of circular disk surfaces 31a with a hole, and an outer surface 31c that extends between the outer edge portions of the pair of circular disc surfaces. 31a with a hole, and in which the piston 26 is arranged in a space bounded by the inner surface 31b. The roller 31 further comprises a vane groove 316 and an aperture portion 318 of a vane groove. The vane groove 316 extends in a radial direction from the inner surface 31b towards the outer surface 31c, and includes a vane 32 that is configured to reciprocate when the piston 26 is eccentrically rotated. The aperture groove portion 318 extends through a pair of circular disk surfaces 31a with a hole and communicates with the aperture groove 316. The aperture groove portion 318 is formed in a space delimited by a wall planar portion 319 that includes a pair of first convex

2018 - 394 A3 of the curved portion 319a and the second convexly curved portion 319b. The pair of first convexly curved portions 319a have a first curvature radius R1. The second convexly curved portion 319b has a second curvature radius R2. The second convexly curved portion 319b is located closer to the outer surface 31c of the cylinder 31 than the pair of the first convexly curved portions 319a, and extends between the pair of the first convexly curved portions 319a. The second curvature radius R2 is smaller than the first curvature radius R1.

The advantages obtained by the above arrangement will be described below.

In FIG. 5 is a schematic view showing a method of fastening a cylinder 31 to a sealed container 2 in the manufacture of a rotary compressor 1 according to embodiment 1. As shown in FIG. 5, with three indentation mechanisms 50, the compression tools 55 are impinged on the outer surface 31c of the cylinder 31 from the outside of the sealed container 2, thereby forming three indented portions thereby securing the outer surface 31c to the inner surface of the sealed container 2. In this case in a radial direction from the outer surface 31c towards the inner surface 31b, as indicated by the three black block arrows.

In FIG. 6 is a schematic view showing an external force that acts on a vane groove 316 when a cylinder 31 is attached to a tight container 2 in a rotary compressor 1 according to Embodiment 1. When pressure is applied radially away from the outer surface 31c of the cylinder 31, an external force is exerted on the vane groove 316 in a direction perpendicular to the radial direction of the roller 31 and in which the width of the vane groove 316 narrows, as indicated by the black block arrows in FIG. 6.

In FIG. 7 is a schematic view showing the arrangement of the aperture portion 318a of the vane groove in a conventional rotary compressor. In a conventional rotary compressor, the aperture portion 318a of the vane groove is formed in a space bounded by a wall surface portion 319 having a circular shape. Suppose that in the rotary compressor 1, the inner diameter of the cylinder 31 increases from, for example, 44 mm to 46 mm to increase the extruded amount of gaseous refrigerant in the rotary compressor 1, while maintaining the outer dimensions of the cylinder 31, i.e. the thickness and outer diameter of the cylinder 31. In this case, if the length of the vane groove 316 in the radial direction decreases by 2 mm, the distance the blade 32 slides by 2 mm decreases by 2 mm and the compressed amount of gaseous refrigerant in the cylinder 31 is reduced accordingly. maintain the required length of the groove 316 in the radial direction. If the length of the vane groove 316 in the radial direction is maintained, the position of the vane groove hole portion 318 is shifted by 2 mm in the direction indicated by the white block arrow, and the distance D between the outer surface 31c and the vane groove hole 318 is correspondingly reduced. As the distance D between the outer surface 31c and the aperture portion 318 of the vane groove decreases, the stiffness of the roller 31 against the pressure of the press mechanisms 50 also decreases, and thus a greater external force is applied in the direction in which the vane groove width narrows. thus, the vane groove 316 may deform. If the vane groove 316 deforms, friction occurs between the vane groove 316 and the vane 32, i.e., the sliding performance of the vane 32 is impaired,

On the other hand, the aperture portion 318 of the vane groove in the rotary compressor 1 according to embodiment 1 may be formed to have a smaller area of the aperture portion than that of a conventional rotary compressor, even if the distance D between the outer surface 31c and the aperture portion 318 of the vane groove is reduced. In FIG. 8 is a diagram comparing the shape of a vane slot portion 318 of a rotary compressor 1 according to embodiment 1 to a circular shape of a vane slot portion 318a of a conventional rotary compressor. Since the aperture portion 318 of the vane groove may have a smaller area of the aperture portion than the aperture portion 318a of the conventional rotary compressor, as shown in FIG. 8, the reduction in stiffness of the cylinder 31 against the pressure exerted by the indentation mechanisms 50 can be prevented.

Thus, due to the arrangement described above, deformation of the vane groove 316 can be prevented, thereby improving the service life of the roller 31. Since the deformation of the vane groove 316 can be prevented, friction between the vane groove 316 and the vane 32 can be prevented as well as deterioration of sliding.

Thus, through the above-mentioned arrangement, a rotary compressor can be provided in which the sliding movement of the slat 32 can be prevented from deteriorating and durability and reliability can be assured.

In addition, due to the arrangement described above, the aperture groove portion 318 can be formed by making, by means of a perforation tool such as a drill, a hole having a first radius of curvature R1 and extending to the circular disk surfaces 31a with a hole and subsequently making a hole having a second radius R2 curves and extends with circular disk surfaces 31 with a hole. Thus, the aperture portion 318 of the vane groove can be formed by easy perforation work, thereby reducing the manufacturing cost of the rotary compressor 1.

In Embodiment 1, the rotary compressor 1 is configured as a rolling-piston type compressor, but may also be configured as a swinging vane type compressor. The rotary vane-type compressor comprises in the cylinder 31 a piston unit in which a roller piston unit corresponding to the piston 26 of embodiment 1 is formed as one part and a vane unit which corresponds to the vane 32 of embodiment 1. Also, the rotary-type compressor of the pendulum type the lamella comprises a sleeve arranged to cause the piston unit to perform a rocking motion. The sleeve is provided as a pair of cylindrical members in the form of cylinder halves that are disposed on the cylinder 31 and support the vane unit of the piston unit, with the vane unit disposed therebetween. Also, in the case where the rotary compressor 1 is configured as a swinging compressor, the aperture portion 318 of the vane groove may be designed to have a surface area of the aperture portion smaller than the aperture portion 318a of the vane groove of conventional technique. Thus, even in the case where the rotary compressor 1 is configured as a rotary compressor, the stiffness of the cylinder 31 can be reduced, thus providing a rotary compressor 1 that can avoid deteriorating the sliding of the vane unit and thus ensure durability and reliability.

Other embodiments

The above-described embodiment can be modified in many ways without departing from the scope of the invention. For example, in the embodiment 1 described above, the rotary compressor 1 is arranged as a tight type compressor, but may also be arranged as a semi-tight type or an open type compressor.

Further, according to embodiment 1 described above, the rotary compressor 1 is arranged as a single cylinder compressor, but may be arranged as a compressor comprising two or more cylinders 31.

PATENT CLAIMS

Claims (1)

A rotary compressor (1) comprising: a piston (26) configured to eccentrically rotate when the crankshaft (20) rotates; and a cylinder (31) comprising a pair of circular disk surfaces (31a) with a hole, an inner surface (31b) and an outer surface (31c), the inner surface (31b) extending between the inner edge portions of the pair of circular disk surfaces (31a) with the hole. the outer surface (31c) extends between the outer edge portions of the pair of circular disk surfaces (31a) with the bore, the piston (26) being provided in a space bounded by the inner surface (31b), characterized in that the cylinder (31) comprises: a lamella groove (316) extending in a radial direction from the inner surface (31b) towards the outer surface (31c) and in which the lamella (32) and the resilient member (33) are located, the lamella (32) being configured to perform a reversible moving the eccentric rotation of the piston (26), the resilient member - 10GB 2018 - 394 A3 (33) is arranged to pressurize the vane (32) against the piston (26) by the restoring force of the resilient member (33); and a vane groove aperture (318) extending through a pair of circular disc surfaces 5 (31a) with a hole and connected to the vane groove (316), the vane groove aperture (318) being formed in a space bounded by the wall surface portion (319) wherein the wall surface portion (319) comprises: a pair of first convexly curved portions (319a) having a first curvature radius (R1); and a second convexly curved portion (319b) having a second curvature radius (R2), wherein the second convexly curved portion (319b) is located closer to the outer surface (31c) of the cylinder (31) than the pair of first convexly curved portions (319a) and extends between the pair of first convexly 15 curved portions (319a), and the second curvature radius (R2) is smaller than the first curvature radius (R1).