CN107076148B

CN107076148B - Rotary compressor and refrigeration cycle device

Info

Publication number: CN107076148B
Application number: CN201580057254.XA
Authority: CN
Inventors: 平山卓也; 渡边哲永
Original assignee: Toshiba Carrier Corp
Current assignee: Toshiba Carrier Corp
Priority date: 2015-03-06
Filing date: 2015-09-29
Publication date: 2020-06-16
Anticipated expiration: 2035-09-29
Also published as: JPWO2016143177A1; WO2016143177A1; JP6652623B2; CN107076148A; JP2019049267A

Abstract

The rotary compressor of the embodiment has a container, a cylinder, a blocking plate, a roller, a blade, and an oil supply groove. The container stores lubricating oil. The cylinder is a cylinder housed in the container. The blocking plate blocks an opening portion of the cylinder, and forms a cylinder chamber together with the cylinder. The roller eccentrically rotates within the cylinder chamber. The vane is divided into cylinder chambers in the rotation direction of the roller, and can advance and retreat in the cylinder chambers in accordance with eccentric rotation of the roller. The oil supply groove is formed in the opposite surface of the vane to the blocking plate, extends in the moving direction of the vane, and has a 1 st end communicating with the inside of the container and a 2 nd end terminating inside the vane. The oil supply groove is such that the 2 nd end portion is located in the cylinder chamber when the vane projects to the maximum extent in the cylinder chamber, and the portion closer to the 2 nd end portion becomes shallower as it goes toward the 2 nd end surface.

Description

Rotary compressor and refrigeration cycle device

Technical Field

Embodiments of the present invention relate to a rotary compressor and a refrigeration cycle apparatus.

Background

As a rotary compressor used in a refrigeration cycle apparatus such as an air conditioner, there is known a rotary compressor including a cylindrical cylinder, a blocking plate for blocking an opening of the cylinder, and a roller eccentrically rotating in a cylinder chamber formed by the cylinder and the blocking plate. Further, a vane that divides the cylinder chamber into a compression chamber and a suction chamber is disposed in a vane groove formed in the cylinder. The vane abuts against the roller and moves forward and backward in the cylinder chamber in accordance with eccentric rotation of the roller.

However, the vane described above preferably slides relative to the blocking plate with the lubricating oil interposed therebetween. Thus, it is considered that the abrasion between the vane and the clogging plate can be reduced and the sealing property between the vane and the clogging plate can be ensured.

However, in the rotary compressor described above, there is room for improvement in that a desired amount of lubricating oil is interposed between the vane and the closing plate. Specifically, a load is applied to a side surface (surface facing the rotation direction of the roller) of the vane by a differential pressure between the compression chamber and the suction chamber. In particular, in an operating region (hereinafter, referred to as a second half of a compression stroke) in which the vane transitions from a bottom dead center (a state of being maximally protruded in the cylinder chamber) to a top dead center (a state of being maximally retreated from the cylinder chamber), a pressure increase in the compression chamber is large. Therefore, in the latter half of the compression stroke, the load applied to the side surface of the vane is large. Therefore, a large amount of lubricating oil is required between the vane and the blocking plate. In this case, if the lubricating oil between the vane and the clogging plate is insufficient and the oil film is broken, the wear between the vane and the clogging plate increases. As a result, the operation reliability may be lowered. Further, if the sealing property between the vane and the blocking plate is lowered, and refrigerant leakage or the like occurs between the compression chamber and the suction chamber, there is a possibility that the compression performance is lowered.

On the other hand, in an operating region where the vane shifts from the top dead center to the bottom dead center (hereinafter, referred to as the first half of the compression stroke), the pressure rise in the compression chamber is smaller than in the second half of the compression stroke. Thus, the load applied to the side of the vane in the first half of the compression stroke is relatively small. Therefore, less lubricating oil is required between the vane and the plug plate.

Documents of the prior art

Patent document

Patent document 1: japanese laid-open patent publication No. 4-191491

Disclosure of Invention

Problems to be solved by the invention

The present invention addresses the problem of providing a rotary compressor and a refrigeration cycle device that can improve operational reliability and compression performance.

Means for solving the problems

Drawings

Fig. 1 is a schematic configuration diagram of a refrigeration cycle apparatus including a cross-sectional view of the rotary compressor according to embodiment 1.

Fig. 2 is a sectional view of the compression mechanism section taken along line II-II of fig. 1.

Fig. 3 is a schematic configuration diagram illustrating a groove forming apparatus for a blade according to embodiment 1.

Fig. 4 is a side view of the blade of embodiment 2.

Fig. 5 is a schematic configuration diagram showing a groove forming apparatus for a blade according to embodiment 2.

Fig. 6 is a side view of the blade of embodiment 3.

Fig. 7 is a schematic configuration diagram showing a groove forming apparatus for a blade according to embodiment 3.

Detailed Description

Hereinafter, a rotary compressor and a refrigeration cycle apparatus according to an embodiment will be described with reference to the drawings.

(embodiment 1)

First, the refrigeration cycle apparatus will be briefly described.

As shown in fig. 1, a refrigeration cycle apparatus 1 of the present embodiment includes a rotary compressor 2, a condenser 3 connected to the rotary compressor 2, an expansion device 4 connected to the condenser 3, and an evaporator 5 connected between the expansion device 4 and the rotary compressor 2.

The rotary compressor 2 is a so-called rotary compressor. The rotary compressor 2 compresses a low-pressure gas refrigerant taken into the interior thereof to turn the refrigerant into a high-temperature and high-pressure gas refrigerant. The specific structure of the rotary compressor 2 will be described later.

The condenser 3 discharges heat from the high-temperature and high-pressure gas refrigerant sent from the rotary compressor 2, and turns the high-temperature and high-pressure gas refrigerant into a high-pressure liquid refrigerant.

The expansion device 4 reduces the pressure of the high-pressure liquid refrigerant sent from the condenser 3, and turns the high-pressure liquid refrigerant into a low-temperature low-pressure liquid refrigerant.

The evaporator 5 vaporizes the low-temperature low-pressure liquid refrigerant sent from the expansion device 4, and turns the low-temperature low-pressure liquid refrigerant into a low-pressure gas refrigerant. In the evaporator 5, the low-pressure liquid refrigerant takes vaporization heat from the surroundings when vaporized, and the surroundings are cooled. The low-pressure gas refrigerant having passed through the evaporator 5 is taken into the rotary compressor 2.

As described above, in the refrigeration cycle apparatus 1 of the present embodiment, the refrigerant as the working fluid circulates while being phase-changed into the gas refrigerant and the liquid refrigerant.

Next, the rotary compressor 2 will be described.

The rotary compressor 2 of the present embodiment includes a compressor main body 11 and an accumulator 12.

The accumulator 12 is a so-called gas-liquid separator. The accumulator 12 is provided between the evaporator 5 and the compressor body 11. The accumulator 12 is connected to a later-described cylinder 41 of the compressor main body 11 via a suction pipe 21. The accumulator 12 supplies only the gas refrigerant of the gas refrigerant vaporized by the evaporator 5 and the liquid refrigerant not vaporized by the evaporator 5 to the compressor body 11.

The compressor body 11 includes a rotary shaft 31, a motor portion 32, a compression mechanism portion 33, and a closed container (container) 34.

The motor unit 32 rotates the rotary shaft 31. The compression mechanism 33 compresses the gas refrigerant as the rotary shaft 31 rotates. The hermetic container 34 houses the rotary shaft 31, the motor unit 32, and the compression mechanism unit 33. The closed casing 34 is formed in a cylindrical shape. The lubricant oil J is contained in the closed casing 34. A part of the compression mechanism 33 is immersed in the lubricating oil J.

The closed casing 34 and the rotary shaft 31 are coaxially arranged along the axis O. In the following description, the direction along the axis O is simply referred to as the axial direction, and the side closer to the motor unit 32 in the axial direction is referred to as the upper side, and the side closer to the compression mechanism unit 33 is referred to as the lower side. The direction perpendicular to the axial direction is referred to as a radial direction, and the direction around the axis O is referred to as a circumferential direction.

The motor unit 32 is a so-called inner rotor type DC brushless motor. Specifically, the motor unit 32 includes a cylindrical stator 35 and a cylindrical rotor 36 disposed inside the stator 35.

The stator 35 is fixed to an inner wall surface of the closed casing 34 by shrink fitting or the like. The rotor 36 is fixed to an upper portion of the rotary shaft 31. The rotor 36 is disposed inside the stator 35 at intervals in the radial direction.

The compression mechanism 33 includes a cylindrical cylinder 41, a main bearing (a closing plate) 42 and a sub bearing (a closing plate) 43 that close openings at both ends of the cylinder 41.

The rotary shaft 31 penetrates the cylinder 41. The main bearing 42 and the sub bearing 43 rotatably support the rotary shaft 31. The space formed by the cylinder 41, the main bearing 42, and the sub-bearing 43 constitutes a cylinder chamber 46 (see fig. 2). The gas refrigerant gas-liquid-separated by the accumulator 12 is taken into the cylinder chamber 46 through the suction pipe 21.

An eccentric portion 51 that is eccentric in the radial direction with respect to the axis O is formed in a portion of the rotary shaft 31 that is located in the cylinder chamber 46.

A roller 53 is fitted outside the eccentric portion 51. The roller 53 is configured to be capable of rotating eccentrically with respect to the axis O while the outer peripheral surface thereof is in sliding contact with the inner peripheral surface of the cylinder 41 as the rotary shaft 31 rotates.

As shown in fig. 1 and 2, the cylinder 41 is formed with vane grooves 54 that are recessed outward in the radial direction. The vane grooves 54 are formed integrally in the axial direction of the cylinder 41. The vane groove 54 communicates with the inside of the closed casing 34 at the outer end (rear end) in the radial direction.

A vane 55 slidably movable in the radial direction is provided in the vane groove 54. The blade 55 is biased radially inward by a biasing unit 57 (biasing means). The radially inner end surface (hereinafter referred to as a leading end surface (2 nd end surface)) of the vane 55 abuts against the outer peripheral surface of the roller 53 in the cylinder chamber 46. Thus, the vane 55 is configured to be able to advance and retreat in the cylinder chamber 46 in accordance with the rotation operation of the roller 53. In addition, in a plan view taken from the axial direction, the tip end surface of the blade 55 is formed in an arc shape protruding inward in the radial direction. The specific structure of the blade 55 will be described later.

The cylinder chamber 46 is divided (divided) into a suction chamber and a compression chamber by the roller 53 and the vane 55. In the compression mechanism 33, the compression operation is performed in the cylinder chamber 46 by the rotation operation of the roller 53 and the advancing and retreating operation of the vane 55.

In the cylinder 41, a suction hole 56 is formed in a portion located on the back side of the vane groove 54 (left side of the vane groove 54 in fig. 2) in the rotation direction of the roller 53 (see the arrow in fig. 2). The suction hole 56 penetrates the cylinder 41 in the radial direction. The suction pipe 21 (see fig. 1) is connected to the outer end of the suction hole 56 in the radial direction. On the other hand, the radially inner end of the suction hole 56 opens in the cylinder chamber 46.

A discharge groove 58 is formed in the inner circumferential surface of the cylinder 41 at a portion located on the front side of the vane groove 54 (the right side of the vane groove 54 in fig. 2) in the rotation direction of the roller 53. The discharge groove 58 communicates with a discharge hole 64 described later. The discharge groove 58 is formed in a semicircular shape in a plan view seen from the axial direction.

As shown in fig. 1, main bearing 42 closes the upper end opening of cylinder 41, and rotatably supports a portion of rotary shaft 31 located above cylinder 41. Specifically, the main bearing 42 includes a cylinder portion 61 through which the rotating shaft 31 is inserted, and a flange portion 62 provided to protrude radially outward from a lower end portion of the cylinder portion 61. The flange portion 62 closes the cylinder chamber 46 from above.

A discharge hole 64 (see fig. 2) for communicating the inside and outside of the cylinder chamber 46 through the discharge groove 58 is formed in a part of the circumferential direction of the flange portion 62. The discharge hole 64 penetrates the flange 62 in the axial direction. Further, a discharge valve mechanism (not shown) that opens and closes a discharge hole 64 in accordance with a pressure increase in the cylinder chamber 46 (compression chamber) and discharges the refrigerant to the outside of the cylinder chamber 46 is disposed in the flange portion 62.

The main bearing 42 is provided with a muffler 65 covering the main bearing 42 from above. Muffler 65 is provided with communication hole 66 for communicating the inside and outside of muffler 65. The high-temperature and high-pressure gas refrigerant discharged through the discharge hole 64 is discharged into the closed casing 34 through the communication hole 66.

The sub-bearing 43 closes the lower end opening of the cylinder 41, and rotatably supports a portion of the rotary shaft 31 located below the cylinder 41. Specifically, the sub-bearing 43 includes a cylindrical portion 71 through which the rotating shaft 31 is inserted, and a flange portion 72 provided to protrude radially outward from an upper end portion of the cylindrical portion 71. The flange portion 72 closes the cylinder chamber 46 from below.

The blade 55 is formed in a rectangular parallelepiped shape extending in the radial direction. Lubricating oil J is interposed between vane 55 and the inner wall surface of vane groove 54 and

flange portions

62 and 72 of

bearings

42 and 43. Therefore, the side surfaces of the vane 55 on both sides in the circumferential direction can slide on the inner wall surface of the vane groove 54 via an oil film. Further, the upper end surface of the vane 55 is slidable with respect to the lower surface of the flange portion 62 via an oil film. The lower end surface of the vane 55 is slidable on the upper surface of the flange portion 72 via an oil film.

An oil supply groove 81 recessed inward in the axial direction is provided in the upper and lower end surfaces (facing surfaces facing the flange portions 62, 72) of the vane 55 so as to extend radially at the center in the width direction of the vane 55. The oil supply groove 81 is formed in a straight line shape extending in a radial direction (a moving direction of the blade 55) in a plan view seen from the axial direction. The oil supply groove 81 is formed to have the same width over the entire surface. Specifically, the oil supply groove 81 includes a linearly extending portion 82 located on the outer end (1 st end) side in the radial direction, and an inclined portion 83 connected to the inner end (2 nd end) in the radial direction of the linearly extending portion 82. The groove depth of the linear extension 82 is formed uniformly throughout the entirety. The inclined portion 83 has a groove depth gradually becoming shallower as it goes toward the tip end surface of the blade 55.

The 1 st end of the linearly extending portion 82 is open on the rear end surface of the blade 55. The 1 st end of the linear extension 82 communicates with the inside of the sealed container 34 through the vane groove 54. Lubricating oil J stored in sealed container 34 is supplied into oil supply groove 81 through vane groove 54.

The bottom of the inclined portion 83 is formed in an arc shape protruding inward in the axial direction in a side view seen in the circumferential direction. The inclined portion 83 has a radius of curvature R. The 2 nd end of the inclined portion 83 terminates inside the blade 55 in a state of approaching the front end surface of the blade 55. That is, the oil supply groove 81 does not reach the tip end surface of the vane 55 and does not communicate with the cylinder chamber 46.

Further, the oil supply groove 81 is formed so as to be located in the cylinder chamber 46 when the vane 55 protrudes to the maximum extent in the cylinder chamber 46.

The portions of the upper and lower end surfaces of the vane 55 other than the oil supply groove 81 function as sealing surfaces surrounding the oil supply groove 81 with three sides except the outer side in the radial direction. The seal surface of the vane 55 faces the

flange portions

62 and 72 with an oil film therebetween. In this case, the communication between the compression chamber and the suction chamber between the seal surface of the vane 55 and the

flange portions

62 and 72 is blocked by an oil film. In the present embodiment, the widths S1, S2 of the portions of the sealing surface located on both sides in the circumferential direction with respect to the oil supply groove 81, and the width S3 along the radial direction between the other end edge of the oil supply groove 81 and the leading end surface of the vane 55 are formed to be equal to each other.

Here, the volume of the oil supply groove 81 is set to match the volume of the lubricating oil J required in the latter half of the compression stroke. The maximum groove depth E of the oil supply groove 81 (the depth of the linear extension 82 in the present embodiment) is deeper than H. Further, the width H of the oil supply groove 81 is smaller than the minimum width of the sealing surface.

Next, a method of forming the oil supply groove 81 in the blade 55 will be described. In the present embodiment, the oil supply groove 81 is formed by cutting using the disk-shaped

cutters

91 and 92.

The groove forming apparatus 90 shown in fig. 3 includes a pair of

cutters

91 and 92 rotatable about mutually parallel rotation axes, and a conveying mechanism, not shown, for conveying the blade 55.

The

disconnectors

91 and 92 have the same structure. The

disconnectors

91 and 92 are disposed with a gap smaller than the height of the blade 55 therebetween. In the present embodiment, the gap between the

cutters

91 and 92 is set to the difference between the height of the blade 55 and the maximum groove depth E of each oil supply groove 81.

The transport mechanism moves the blade 55 forward and backward with respect to the gap between the

cutters

91 and 92. Specifically, the conveying mechanism moves between a processing position where the blade 55 enters between the

cutters

91 and 92 and a retracted position where the blade 55 is retracted from between the

cutters

91 and 92.

When the oil supply groove 81 is formed using the groove forming device 90 described above, first, the blade 55 is held by the conveying mechanism located at the retracted position, and the

cutters

91 and 92 are aligned with the blade 55. Then, the

cutters

91 and 92 are rotated in opposite directions to each other, and the blade 55 is conveyed from the 1 st end toward the machining position by the conveying mechanism. Then, the upper and lower end faces of the blade 55 are cut as the blade 55 enters the gap between the

cutters

91, 92.

After the blade 55 is advanced by a predetermined amount, the conveyance mechanism is moved to the retreat position again, and the blade 55 is retreated from the

cutters

91 and 92. At this time, the amount of the blade 55 entering is set to such an extent that the

cutters

91 and 92 do not reach the tip end surface of the blade 55. Thereby, the tip end of the blade 55 is formed with an arc-shaped inclined portion 83 which follows the curvature radius of the

cutters

91 and 92.

As described above, the blade 55 of the present embodiment is completed.

According to this configuration, the oil supply groove 81 can be formed in the upper and lower end surfaces of the blade 55 simply by moving the blade 55 forward and backward relative to the pair of

cutters

91 and 92. In this case, for example, the machining period for forming the oil supply groove 81 can be shortened as compared with the milling machining using an end mill. As a result, the manufacturing efficiency can be improved and the cost can be reduced.

Next, the operation of the rotary compressor 2 will be described.

As shown in fig. 1, when electric power is supplied to the stator 35 of the motor unit 32, the rotary shaft 31 rotates about the axis O together with the rotor 36. The eccentric portion 51 and the roller 53 eccentrically rotate in the cylinder chamber 46 with the rotation of the rotary shaft 31. At this time, the rollers 53 are in sliding contact with the inner circumferential surfaces of the cylinders 41, respectively, thereby introducing the gas refrigerant into the cylinder chambers 46 through the suction pipes 21 and compressing the gas refrigerant introduced into the cylinder chambers 46.

Specifically, the gas refrigerant is sucked into the suction chamber of the cylinder chamber 46 through the suction hole 56, and the gas refrigerant sucked from the suction hole 56 is compressed in the compression chamber. The compressed gas refrigerant is discharged to the outside of the cylinder chamber 46 (into the muffler 65) through the discharge hole 64 of the main bearing 42, and then discharged into the sealed container 34 through the communication hole 66 of the muffler 65. The gas refrigerant discharged into the closed casing 34 is sent to the condenser 3 as described above.

Here, the inside of the oil supply groove 81 of the vane 55 communicates with the inside of the closed casing 34 through the vane groove 54, and is filled with the lubricating oil J. The lubricating oil J in the oil supply groove 81 flows into between the seal surface and each of the

flange portions

62, 72, and forms an oil film therebetween. Therefore, the vane 55 moves forward and backward in the radial direction with respect to the cylinder chamber 46 in accordance with the eccentric rotation of the roller 53 while suppressing direct contact with the

flange portions

62 and 72.

In the process of advancing and retracting the vane 55, a speed difference is generated between the portion closer to the vane 55 and the portions closer to the

flange portions

62 and 72 in the lubricating oil J interposed between the vane 55 and the

flange portions

62 and 72. If a speed difference occurs, a shearing force accompanied by viscosity acts on the lubricating oil J. In particular, since the inclined portion 83 is formed at the 2 nd end portion of the oil supply groove 81, the clearance between the vane 55 and the

flange portions

62 and 72 becomes narrower toward the rear in the moving direction of the vane 55 in the second half of the compression stroke. Therefore, the lubricating oil J in the oil supply groove 81 is drawn inward in the radial direction (so-called wedge effect is generated) by the viscosity action of the lubricating oil J and the inclination of the inclined portion 83. Thereby, the lubricating oil J enters the front end surface side of the vane 55 between the upper and lower end surfaces of the vane 55 and the

flange portions

62 and 72. This enables lubricating oil J to be efficiently supplied between vane 55 and

flange portions

62 and 72.

On the other hand, since the 1 st end of the oil supply groove 81 is opened by the linear extension 82, the above-described wedge effect is hardly generated in the first half of the compression stroke. Therefore, in the first half of the compression stroke, the lubricating oil J is less likely to flow radially inward than in the second half of the compression stroke. This can suppress a large amount of the lubricating oil J in the oil feed groove 81 from flowing into the tip end surface side of the vane 55 in the first half of the compression stroke.

As described above, in the present embodiment, since the inclined portion 83 is formed at the other end portion of the oil supply groove 81, the wedge effect is easily generated in the latter half of the compression stroke. Therefore, the lubricating oil J is effectively supplied toward the distal end surface between the vane 55 (seal surface) and the

flange portions

62, 72. Therefore, the oil film between the vane 55 and the

flange portions

62 and 72 can be prevented from being broken, and the vane 55 and the

flange portions

62 and 72 can be prevented from directly contacting each other. This reduces wear of the vane 55 and the

flanges

62 and 72, and improves operational reliability.

Further, since the oil supply groove 81 is formed so as to be located in the cylinder chamber 46 when the vane 55 protrudes to the maximum extent in the cylinder chamber 46, the communication between the vane 55 and the

flange portions

62 and 72 in the compression chamber and the suction chamber is blocked by an oil film. Therefore, the sealing performance between the blade 55 and the

flanges

62 and 72 can be ensured. Therefore, leakage of refrigerant passing through the compression chamber and the suction chamber between the vane 55 and the

flanges

62 and 72 can be suppressed, and the compression performance can be improved.

Further, as described above, the 1 st end of the oil supply groove 81 is opened by the linearly extending portion 82, and therefore, in the first half of the compression stroke, a large amount of the lubricating oil J can be suppressed from flowing into the tip end surface side of the vane 55. Therefore, excessive insertion of lubricating oil J between vane 55 and

flange portions

62 and 72 can be suppressed in the first half of the compression stroke, and the sealing performance between vane 55 and

flange portions

62 and 72 can be maintained. This can suppress the excessive lubricating oil J interposed between the vane 55 and the

flange portions

62 and 72 from flowing into the cylinder chamber 46, or suppress the refrigerant from flowing into the cylinder chamber 46 together with the lubricating oil J, thereby suppressing a reduction in compression performance.

In the present embodiment, since the maximum groove depth E of the oil supply groove 81 is deeper than the width H, the volume in the oil supply groove 81 can be secured, and the width of the sealing surface can be secured. Therefore, the capacity of lubricating oil J in oil supply groove 81 can be ensured, and the sealing property between blade 55 and

flange portions

62 and 72 can be ensured. This can further improve the operational reliability and the compression performance.

In the present embodiment, the width H of the oil supply groove 81 is smaller than the minimum width of the sealing surface, so that the width of the sealing surface can be ensured. In this case, the sealing performance between the blade 55 and the

flange portions

62 and 72 can be ensured (so-called robustness can be improved) regardless of the variation in the gap between the blade 55 and the

flange portions

62 and 72 due to the tolerance. As a result, the operational reliability and the compression performance can be further improved.

Further, since the refrigeration cycle apparatus 1 of the present embodiment includes the rotary compressor 2 described above, the refrigeration cycle apparatus 1 having high performance and excellent reliability can be provided.

(embodiment 2)

In the blade 155 shown in fig. 4, the bottom of the oil supply groove 181 is formed in an arc shape that is convex toward the inside in the axial direction as a whole. Therefore, the oil supply groove 181 has a gradually shallower groove depth as it goes to both the 1 st end portion and the 2 nd end portion. The 1 st end of the oil supply groove 181 opens to the rear end surface of the vane 155. The 2 nd end of the oil supply groove 181 is terminated in the vane 155.

As shown in fig. 5, in the groove forming apparatus 190 of the present embodiment, a pair of

cutters

191 and 192 are configured to be able to approach or separate from each other. Specifically, the

cutters

191 and 192 move between a machining position where the blade 155 positioned between the

cutters

191 and 192 is machined and a retracted position where the blade 155 positioned between the

cutters

191 and 192 is separated.

The conveying mechanism causes the blade 155 to pass through the gap between the pair of

cutters

191, 192 in order from upstream to downstream.

In order to form the oil supply groove 81 using the groove forming device 190, first, the blade 155 is conveyed between the

cutters

191 and 192 by the conveying mechanism in a state where the

cutters

191 and 192 are located at the retracted positions. Next, the

cutters

191, 192 are rotated in opposite directions to each other, and the

cutters

191, 192 are moved toward the machining position. Then, the

cutters

191 and 192 enter the upper and lower end surfaces of the blade 155, and cut the upper and lower end surfaces of the blade 155. At this time, the amount of penetration of the

cutters

191 and 192 into the vane 155 is set to the maximum groove depth E of each oil supply groove 181. Thus, the oil feed groove 181 is formed in an arc shape following the curvature radius of the

cutters

191 and 192.

Thereafter, the

cutters

191 and 192 are moved again to the retracted positions, and the

cutters

191 and 192 are separated from the blade 155. Then, the conveying mechanism is driven to convey the processed blade 155 downstream of the

cutters

191 and 192, and to convey the blade 155 to be processed next between the

cutters

191 and 192 in sequence. Thereafter, the blade 155 conveyed between the

cutters

191 and 192 is cut by the same method as described above. Thereby, the oil supply groove 181 is formed in order for the blade 155 fed between the

cutters

191, 192.

According to this configuration, since the entire oil feed groove 181 is formed in an arc shape that protrudes inward in the axial direction, the oil feed groove 181 can be formed by reciprocating the

cutters

191 and 192 with respect to the blade 155 that conveys in one direction. This can further improve the manufacturing efficiency and reduce the cost.

(embodiment 3)

In the vane 255 shown in fig. 6, the bottom of the oil supply groove 281 extends linearly outward in the axial direction from the 1 st end toward the 2 nd end. The 1 st end of the oil supply groove 281 opens at one end surface of the vane 255. The 2 nd end of the oil supply groove 281 terminates within the vane 255.

As shown in fig. 7, in the groove forming device 290 of the present embodiment, the cutter 291 is rotatably supported.

The conveying mechanism 292 conveys the blade 255 from upstream to downstream with respect to the cutter 291. The conveyance mechanism 292 holds the blade 255 in a state inclined with respect to the conveyance direction. Specifically, the conveyance mechanism 292 holds the blade 255 in a state in which the 1 st end surface of the blade 255 is directed downstream and one end surface is inclined upward (in the direction toward the cutter 291).

In order to form the oil supply groove 281 using the groove forming device 290, the blade 255 is conveyed downstream by the conveying mechanism 292 while the cutter 291 is rotated. Then, the cutter 291 enters one end surface of the blade 255 from the 1 st end of the blade 255. Then, the vane 255 passes downstream of the cutter 291, and an oil supply groove 281 is formed in one end surface of the vane 255. When the processed blade 255 passes through the cutter 291, the blade 255 to be processed next is sequentially conveyed to the cutter 291. Then, the blade 255 to be machined next is cut by the same method as the above-described method. Thereby, the oil supply groove 281 is formed in order with respect to one end surface of the blade 255 conveyed toward the cutter 291.

Next, the vane 255 having the oil supply groove 281 formed in one end surface thereof is turned upside down, and the oil supply groove 281 is formed in the other end surface thereof by the same method as that described above. This completes the blade 255 of the present embodiment described above.

According to this configuration, since the oil supply groove 281 can be formed only by passing the vane 255 through one cutter 291, simplification and cost reduction of the groove forming device 290 can be achieved. Since the blade 255 is processed by the cutter 291 while being conveyed, the conveyance of the blade 255 is not stopped. Therefore, further shortening of the processing period can be achieved.

In the above-described embodiment, the case where the main bearing 42 and the sub bearing 43 are used as the clogging plate has been described, but the present invention is not limited to this. For example, a bearing portion that closes the upper end opening of the cylinder 41 and through which the rotary shaft 31 is inserted, and a cylinder plate that closes the lower end opening of the cylinder 41 and slidably supports the axial lower end surface of the rotary shaft 31 may be used as the blocking plate.

In the above-described embodiment, the description has been given of the structure in which one cylinder chamber 46 is provided, but the present invention is not limited to this, and a plurality of cylinder chambers 46 may be provided.

In the above-described embodiment, the case where the axial direction is aligned with the vertical direction has been described, but the present invention is not limited thereto, and the axial direction may be aligned with the horizontal direction.

Further, in the above-described embodiment, the case where the roller 53 is formed separately from the blade has been described, but the present invention is not limited thereto, and the roller 53 may be formed integrally with the blade.

In the above-described embodiment, the case where the oil supply groove is formed in each of the upper and lower end surfaces of the vane has been described, but the present invention is not limited to this, and the oil supply groove may be formed in at least one of the end surfaces.

Further, in the above-described embodiment, the case where the oil supply groove is formed in 1 row with respect to the end surface of the blade has been described, but the present invention is not limited thereto, and the oil supply grooves may be formed in a plurality of rows.

In the above-described embodiment, the case where the 2 nd end portion of the oil supply groove is formed in the arc shape or the linear shape has been described, but the invention is not limited thereto. The blade may be stepped, for example, as long as it has a structure that becomes gradually shallower as it goes toward the tip end surface of the blade. The oil supply groove may be formed such that at least the 2 nd end portion (the 2 nd end portion of the oil supply groove from the middle portion in the extending direction) is shallower toward the 2 nd end.

In the above-described embodiment, the case where the oil supply groove is formed in a straight line shape extending along the moving direction (radial direction) of the blade in a plan view seen from the axial direction has been described, but the invention is not limited to this. For example, the oil supply groove may be formed in a wave shape or inclined with respect to the moving direction as long as it extends along the moving direction of the blade.

In the above-described embodiment, the structure in which the width of the oil supply groove is the same over the entire structure has been described, but the width of the oil supply groove may be appropriately designed and changed. In this case, the minimum width of the seal surface is preferably smaller than the maximum width of the oil supply groove.

According to at least one embodiment described above, since the oil supply groove becomes shallower from the 1 st end toward the 2 nd end, the wedge effect is likely to occur in the latter half of the compression stroke. Therefore, the lubricating oil is effectively supplied between the vane and the clogging plate toward the 2 nd end surface side.

Therefore, the oil film between the vane and the blocking plate can be prevented from being broken, and the vane and the blocking plate can be prevented from directly contacting. This can reduce wear of the vane and the blocking plate. As a result, the operational reliability can be improved.

Further, since the communication between the compression chamber and the suction chamber between the vane and the closing plate is blocked by an oil film, the sealing property between the vane and the closing plate can be ensured. Therefore, the refrigerant leakage between the compression chamber and the suction chamber between the vane and the blocking plate can be suppressed, and the compression performance can be improved.

Further, since the other end portion of the oil supply groove communicates with the inside of the closed casing, a large amount of inflow of the lubricating oil to the 2 nd end surface side of the roller can be suppressed in the first half of the compression stroke. Therefore, in the first half of the compression stroke, excessive lubricant oil is prevented from being interposed between the vane and the blocking plate, and the sealing performance between the vane and the blocking plate can be maintained. This can suppress the excessive lubricating oil interposed between the vane and the closing plate from flowing into the cylinder chamber, or suppress the refrigerant from flowing into the cylinder chamber together with the lubricating oil, thereby suppressing the reduction in compression performance.

Several embodiments of the present invention have been described, but these embodiments are shown as examples and are not intended to limit the scope of the present invention. These embodiments can be implemented in other various ways, and various omissions, substitutions, and changes can be made without departing from the spirit of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the scope equivalent thereto.

Claims

1. A rotary compressor is provided with:

a cylindrical container for storing lubricating oil;

a cylindrical cylinder housed in the container;

a blocking plate for blocking an opening of the cylinder and forming a cylinder chamber together with the cylinder;

a roller eccentrically rotating in the cylinder chamber;

a vane which is divided into the cylinder chamber in a rotation direction of the roller and can advance and retreat in the cylinder chamber along with eccentric rotation of the roller; and

an oil supply groove formed in an opposed surface of the blade opposed to the clogging plate, extending in a moving direction of the blade, and having a 1 st end portion communicating with the inside of the container and a 2 nd end portion terminating in the inside of the blade,

the oil supply groove is formed such that the 2 nd end portion is positioned in the cylinder chamber when the vane is protruded to the maximum extent in the cylinder chamber, and a portion closer to the 2 nd end portion has a shallower groove depth as it goes toward the 2 nd end surface,

the oil supply groove has a linear extension portion located on the 1 st end portion side and having the same groove depth, and an inclined portion continuous with the linear extension portion, the inclined portion having a gradually shallower groove depth as it goes toward the 2 nd end surface, and the inclined portion having an arc shape protruding in an axial direction along the axis toward a side away from the facing surface in a circumferential direction of the container viewed from the axis.

2. The rotary compressor of claim 1,

the maximum groove depth of the oil supply groove is deeper than the width of the oil supply groove.

3. The rotary compressor of claim 1 or 2,

the minimum width of the portion other than the oil supply groove on the opposed surface of the vane is wider than the width of the oil supply groove.

4. A refrigeration cycle device is provided with:

the rotary compressor of any one of claims 1 to 3;

a condenser connected to the rotary compressor;

an expansion device connected to the condenser; and

and an evaporator connected between the expansion device and the rotary compressor.