JP6652623B2 - Rotary compressor, refrigeration cycle device, and method of manufacturing rotary compressor - Google Patents

Description

Embodiments of the present invention relate to a rotary compressor, a refrigeration cycle device, and a method for manufacturing a rotary compressor.

As a rotary compressor used in a refrigeration cycle device such as an air conditioner, a cylindrical cylinder, a closing plate closing an opening of the cylinder, and a roller eccentrically rotating in a cylinder chamber formed by the cylinder and the closing plate. Are known. A blade for dividing the cylinder chamber into a compression chamber and a suction chamber is provided in a blade groove formed in the cylinder. The blade comes into contact with the roller and moves in and out of the cylinder chamber with the eccentric rotation of the roller.

By the way, it is preferable that the above-mentioned blade slides with respect to the closing plate with lubricating oil interposed between the blade and the closing plate. Thus, it is considered that, while reducing the wear between the blade and the closing plate, the sealing property between the blade and the closing plate can be ensured.

However, in the rotary compressor described above, there is still room for improvement in interposing a desired amount of lubricating oil between the blade and the closing plate. Specifically, a load is applied to the side surface of the blade (the surface facing the rotation direction of the roller) due to the differential pressure between the compression chamber and the suction chamber. In particular, in an operation region in which the blade shifts from bottom dead center (the state most protruding into the cylinder chamber) to top dead center (a state most retracted from the cylinder chamber) (hereinafter, referred to as the latter half of the compression stroke), the pressure in the compression chamber increases. Is big. Therefore, in the latter half of the compression stroke, the load applied to the side surface of the blade is large. Therefore, a large amount of lubricating oil is required between the blade and the closing plate. In this case, if the lubricating oil between the blade and the closing plate is insufficient and the oil film is broken, abrasion between the blade and the closing plate increases. As a result, operation reliability may be reduced. In addition, if the sealing performance between the blade and the closing plate is reduced and the refrigerant leaks between the compression chamber and the suction chamber, the compression performance may be reduced.

On the other hand, in an operation region in which the blade shifts from the top dead center to the bottom dead center (hereinafter, referred to as the first half of the compression stroke), the pressure increase in the compression chamber is smaller than in the second half of the compression stroke. Therefore, in the first half of the compression stroke, the load applied to the side surface of the blade is relatively small. Therefore, less lubricating oil is required between the blade and the closing plate.

Japanese Unexamined Patent Publication No. 4-191149

The problem to be solved by the present invention is to provide a rotary compressor, a refrigeration cycle device, and a method for manufacturing a rotary compressor that can improve the operation reliability and the compression performance.

The rotary compressor of the embodiment has a container, a cylinder, a closing plate, a roller, a blade, and an oil supply groove. The container stores lubricating oil. The cylinder has a cylindrical shape housed in a container. The closing plate closes the opening of the cylinder and forms a cylinder chamber together with the cylinder. The rollers rotate eccentrically in the cylinder chamber. The blade divides the cylinder chamber in the rotation direction of the roller, and is capable of moving back and forth into the cylinder chamber with the eccentric rotation of the roller. The oil supply groove is formed on the opposing surface of the blade facing the closing plate, extends along the moving direction of the blade, has a first end communicating with the container, and is located on the opposite side to the first end. A second end terminates in the blade. The refueling groove is located on the first end side, and has a straight extending portion having the same groove depth over the entirety. It has an inclined portion which becomes shallower toward the second end and which inclines and terminates at the second end, and the second end is located in the cylinder chamber when the blade projects most into the cylinder chamber.

FIG. 1 is a schematic configuration diagram of a refrigeration cycle device including a cross-sectional view of a rotary compressor according to a first embodiment. FIG. 2 is a cross-sectional view of the compression mechanism along the line II-II in FIG. 1. FIG. 2 is a schematic configuration diagram illustrating a blade groove forming apparatus according to the first embodiment. FIG. 10 is a side view of the blade according to the second embodiment. FIG. 5 is a schematic configuration diagram illustrating a blade groove forming apparatus according to a second embodiment. FIG. 10 is a side view of the blade according to the third embodiment. FIG. 9 is a schematic configuration diagram illustrating a blade groove forming apparatus according to a third embodiment.

Hereinafter, a rotary compressor and a refrigeration cycle device of an embodiment will be described with reference to the drawings. First Embodiment First, a refrigeration cycle apparatus will be briefly described. As shown in FIG. 1, a refrigeration cycle device 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, 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 inside thereof to produce a high-temperature and high-pressure gas refrigerant. The specific configuration of the rotary compressor 2 will be described later. The condenser 3 radiates 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 lowers the pressure of the high-pressure liquid refrigerant sent from the condenser 3 to convert the high-pressure liquid refrigerant into a low-temperature and low-pressure liquid refrigerant. The evaporator 5 vaporizes the low-temperature and low-pressure liquid refrigerant sent from the expansion device 4 and converts the low-temperature and low-pressure liquid refrigerant into a low-pressure gas refrigerant. Then, in the evaporator 5, when the low-pressure liquid refrigerant evaporates, it takes away heat of vaporization from the surroundings, and the surroundings are cooled. The low-pressure gas refrigerant that has passed through the evaporator 5 is taken into the rotary compressor 2 described above.

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

Next, the rotary compressor 2 described above will be described. The rotary compressor 2 according to 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 main body 11 described above. The accumulator 12 is connected to a later-described cylinder 41 of the compressor body 11 through the suction pipe 21. The accumulator 12 supplies only the gas refrigerant to the compressor main body 11 among the gas refrigerant vaporized by the evaporator 5 and the liquid refrigerant not vaporized by the evaporator 5.

The compressor body 11 includes a rotating shaft 31, an electric motor unit 32, a compression mechanism unit 33, and a closed container (container) 34. The motor 32 rotates the rotating shaft 31. The compression mechanism 33 compresses the gas refrigerant by the rotation of the rotating shaft 31. The closed container 34 houses the rotating shaft 31, the electric motor 32, and the compression mechanism 33. Note that the closed container 34 has a cylindrical shape. The lubricating oil J is contained in the closed container 34. A part of the compression mechanism 33 is immersed in the lubricating oil J.

The closed container 34 and the rotating shaft 31 are arranged coaxially along the axis O. In the following description, the direction along the axis O is simply referred to as the axial direction, and the portion closer to the electric motor portion 32 in the axial direction is referred to as the upper side, and the portion closer to the compression mechanism portion 33 is referred to as the lower side. The direction orthogonal to the axial direction is called a radial direction, and the direction around the axis O is called a circumferential direction.

The motor section 32 is a so-called inner rotor type DC brushless motor. Specifically, the electric motor unit 32 includes a cylindrical stator 35 and a columnar rotor 36 disposed inside the stator 35. The stator 35 is fixed to the inner wall surface of the sealed container 34 by shrink fitting or the like. The rotor 36 is fixed on the upper part of the rotating shaft 31. The rotors 36 are arranged inside the stator 35 at intervals in the radial direction.

The compression mechanism 33 includes a cylindrical cylinder 41, and a main bearing (blocking plate) 42 and a sub-bearing (blocking plate) 43 for respectively closing the openings at both ends of the cylinder 41. The rotating shaft 31 passes through the cylinder 41. The main bearing 42 and the sub bearing 43 rotatably support the rotating shaft 31. The space defined by the cylinder 41, the main bearing 42, and the sub-bearing 43 constitutes a cylinder chamber 46 (see FIG. 2). The gas refrigerant separated into gas and liquid by the accumulator 12 is taken into the cylinder chamber 46 through the suction pipe 21 described above.

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 located in the cylinder chamber 46. A roller 53 is externally fitted to the eccentric part 51. The roller 53 is configured to be eccentrically rotatable with respect to the axis O while the outer peripheral surface is in sliding contact with the inner peripheral surface of the cylinder 41 as the rotation shaft 31 rotates.

As shown in FIGS. 1 and 2, the cylinder 41 has a blade groove 54 that is depressed outward in the radial direction. The blade groove 54 is formed over the entirety of the cylinder 41 in the axial direction. The blade groove 54 communicates with the inside of the closed container 34 at the radially outer end (rear end).

A blade 55 that is slidable in the radial direction is provided in the blade groove 54. The blade 55 is biased radially inward by a biasing means 57 (biasing device). A radially inner end surface of the blade 55 (hereinafter, referred to as a front end surface (second end surface)) is in contact with the outer peripheral surface of the roller 53 in the cylinder chamber 46. Thereby, the blade 55 is configured to be able to advance and retreat into the cylinder chamber 46 in accordance with the rotation operation of the roller 53. In a plan view seen from the axial direction, the distal end surface of the blade 55 has a circular arc shape that is convex toward the inside in the radial direction. The specific configuration of the blade 55 will be described later.

The cylinder chamber 46 is partitioned (divided) by a roller 53 and a blade 55 into a suction chamber and a compression chamber. The compression mechanism 33 performs a compression operation in the cylinder chamber 46 by the rotation operation of the roller 53 and the advance / retreat operation of the blade 55.

A suction hole 56 is formed in a portion of the cylinder 41 that is located on the inner side (left side of the blade groove 54 in FIG. 2) of the blade groove 54 along the rotation direction of the roller 53 (see the arrow in FIG. 2). I have. The suction hole 56 penetrates the cylinder 41 in the radial direction. The above-described suction pipe 21 (see FIG. 1) is connected to a radially outer end of the suction hole 56. On the other hand, a radially inner end of the suction hole 56 opens into the cylinder chamber 46. On the inner peripheral surface of the cylinder 41, a discharge groove 58 is formed at a portion located on the near side (to the right of the blade groove 54 in FIG. 2) of the blade groove 54 along 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 plan view when viewed from the axial direction.

As shown in FIG. 1, the main bearing 42 closes an upper end opening of the cylinder 41 and rotatably supports a portion of the rotating shaft 31 located above the cylinder 41. Specifically, the main bearing 42 includes a tubular portion 61 into which the rotating shaft 31 is inserted, and a flange portion 62 protruding radially outward from the lower end of the tubular portion 61. The flange portion 62 closes the cylinder chamber 46 from above.

A discharge hole 64 (see FIG. 2) that communicates with the inside and outside of the cylinder chamber 46 through the discharge groove 58 described above is formed in a part of the flange 62 in the circumferential direction. The discharge hole 64 passes through the flange 62 in the axial direction. The flange 62 is provided with a discharge valve mechanism (not shown) that opens and closes the discharge hole 64 in accordance with a rise in the pressure in the cylinder chamber 46 (compression chamber) and discharges the refrigerant to the outside of the cylinder chamber 46.

The main bearing 42 is provided with a muffler 65 that covers the main bearing 42 from above. The muffler 65 has a communication hole 66 that communicates the inside and outside of the muffler 65. The high-temperature and high-pressure gaseous refrigerant discharged through the discharge hole 64 described above is discharged into the closed container 34 through the communication hole 66.

The auxiliary bearing 43 closes an opening at the lower end of the cylinder 41 and rotatably supports a portion of the rotating shaft 31 located below the cylinder 41. Specifically, the auxiliary bearing 43 includes a cylindrical portion 71 through which the rotating shaft 31 is inserted, and a flange portion 72 protruding from the upper end portion of the cylindrical portion 71 toward the outside in the radial direction. The flange portion 72 closes the cylinder chamber 46 from below.

The above-described blade 55 is formed in a rectangular parallelepiped shape extending along the radial direction. Lubricating oil J is interposed between the blade 55 and the inner wall surface of the blade groove 54 and the flange portions 62 and 72 of the bearings 42 and 43. Therefore, the side faces of the blade 55 facing both sides in the circumferential direction can slide on the inner wall surface of the blade groove 54 via the oil film. Further, the upper end surface of the blade 55 is slidable on the lower surface of the flange portion 62 via an oil film. The lower end surface of the blade 55 can slide on the upper surface of the flange portion 72 via an oil film.

At upper and lower end surfaces of the blade 55 (surfaces facing the flange portions 62 and 72), an oil supply groove 81 which is depressed inward in the axial direction is provided in a radially central portion of the blade 55 in the width direction. The oil supply groove 81 is formed in a linear shape extending along the radial direction (the moving direction of the blade 55) in plan view as viewed from the axial direction. The width of the oil supply groove 81 is uniform (same) throughout. Specifically, the oil supply groove 81 includes a linearly extending portion 82 located on a radially outer end (first end) side, and a radially inner end (second end) of the linearly extending portion 82. And an inclined portion 83 which is continuous with. The linear extension 82 has a uniform groove depth throughout. The groove depth of the inclined portion 83 is gradually reduced toward the tip end surface of the blade 55.

A first end of the linear extension 82 opens on the rear end surface of the blade 55. A first end of the linear extension 82 communicates with the closed container 34 through the blade groove 54. The lubricating oil J stored in the closed container 34 is supplied into the oil supply groove 81 through the blade groove 54. The bottom of the inclined portion 83 has an arcuate shape that protrudes inward in the axial direction when viewed from the side when viewed from the circumferential direction. The radius of curvature of the inclined portion 83 is R. The second end of the inclined portion 83 terminates in the blade 55 in a state close to the tip end surface of the blade 55. That is, the oil supply groove 81 does not reach the tip end surface of the blade 55 and does not communicate with the inside of the cylinder chamber 46. The oil supply groove 81 is formed so as to be located in the cylinder chamber 46 when the blade 55 projects most into the cylinder chamber 46.

In the upper and lower end surfaces of the blade 55, portions other than the oil supply groove 81 function as seal surfaces that surround the oil supply groove 81 on three sides except the outside in the radial direction. The sealing surface of the blade 55 faces each of the flange portions 62 and 72 via an oil film. In this case, communication between the compression chamber and the suction chamber passing between the sealing surface of the blade 55 and the flange portions 62 and 72 is blocked by the oil film. In the present embodiment, the width dimensions S1 and S2 of portions of the seal surface located on both sides in the circumferential direction with respect to the oil supply groove 81, and the diameter between the other end edge of the oil supply groove 81 and the tip end surface of the blade 55. The widths S3 along the directions are set to be equal.

Here, the capacity of the oil supply groove 81 is set in accordance with the capacity of the lubricating oil J required in the latter half of the compression stroke. Moreover, the dimension of the maximum groove depth E of the oil supply groove 81 (the depth of the linearly extending portion 82 in the present embodiment) is deeper than H. The width dimension H of the oil supply groove 81 is smaller than the minimum width dimension of the sealing surface.

Next, a method of forming the oil supply groove 81 in the above-described 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 device 90 shown in FIG. 3 has a pair of cutters 91 and 92 rotatable around rotation axes parallel to each other, and a transport mechanism (not shown) for transporting the blade 55.

The cutters 91 and 92 have the same configuration. The cutters 91 and 92 are disposed with a gap between them both smaller than the height of the blade 55. 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 transport mechanism moves between a processing position where the blade 55 has entered between the cutters 91 and 92 and a retreat position where the blade 55 retreats from between the cutters 91 and 92.

When forming the oil supply groove 81 using the above-described groove forming device 90, first, the blade 55 is held by the transport mechanism at the retracted position, and the cutters 91 and 92 and the blade 55 are aligned. Then, the cutters 91 and 92 are rotated in opposite directions, and the transport mechanism transports the blade 55 from the first end toward the processing position. Then, as the blade 55 enters the gap between the cutters 91 and 92, the upper and lower end surfaces of the blade 55 are cut.

Then, after the blade 55 is advanced by a predetermined amount, the transport mechanism is moved to the retreat position again, and the blade 55 is retreated from the cutters 91 and 92. At this time, the entering amount of the blade 55 is set so that the cutters 91 and 92 do not reach the tip end surface of the blade 55. Thus, an arc-shaped inclined portion 83 is formed at the tip of the blade 55 so as to follow the radius of curvature of the cutters 91 and 92. Thus, the blade 55 of the present embodiment is completed.

According to this configuration, the oil supply groove 81 can be formed on the upper and lower end surfaces of the blade 55 only by moving the blade 55 forward and backward with respect to the pair of cutters 91 and 92. In this case, the lead time for forming the oil supply groove 81 can be reduced as compared with, for example, milling using an end mill. As a result, it is possible to improve manufacturing efficiency and reduce costs.

Next, the operation of the rotary compressor 2 will be described. When electric power is supplied to the stator 35 of the electric motor unit 32 as shown in FIG. 1, the rotating shaft 31 rotates around the axis O together with the rotor 36. The eccentric part 51 and the roller 53 rotate eccentrically in the cylinder chamber 46 with the rotation of the rotating shaft 31. At this time, when the rollers 53 are in sliding contact with the inner peripheral surface of the cylinder 41, the gas refrigerant is taken into the cylinder chamber 46 through the suction pipe 21, and the gas refrigerant taken into the cylinder chamber 46 is compressed.

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

Here, the inside of the oil supply groove 81 of the blade 55 is filled with the lubricating oil J because it communicates with the inside of the closed container 34 through the blade groove 54. The lubricating oil J in the oil supply groove 81 flows between the seal surface and each of the flange portions 62 and 72, and forms an oil film between the two. Therefore, the blade 55 moves radially with respect to the cylinder chamber 46 with the eccentric rotation of the roller 53 in a state where the direct contact with the flange portions 62 and 72 is suppressed.

In the process of moving the blade 55 forward and backward, the lubricating oil J interposed between the blade 55 and the flange portions 62 and 72 has a speed difference between a portion located closer to the blade 55 and a portion located closer to the flange portions 62 and 72. . When a speed difference occurs, a shear force due to viscosity acts on the lubricating oil J. In particular, since the inclined portion 83 is formed at the second end of the oil supply groove 81, the gap between the blade 55 and the flange portions 62 and 72 becomes narrower toward the rear in the moving direction of the blade 55 in the latter half of the compression stroke. Therefore, the lubricating oil J in the oil supply groove 81 is dragged inward in the radial direction by the viscous action of the lubricating oil J and the inclination of the inclined portion 83 (a so-called wedge effect occurs). As a result, the lubricating oil J enters between the upper and lower end surfaces of the blade 55 and the flange portions 62 and 72 to the tip end surface side of the blade 55. Thereby, the lubricating oil J can be effectively supplied between the blade 55 and the flange portions 62 and 72.

On the other hand, since the first end of the oil supply groove 81 is opened through the linearly extending portion 82, the above-described wedge effect hardly occurs in the first half of the compression stroke. Therefore, the lubricating oil J is less likely to flow radially inward in the first half of the compression stroke than in the second half of the compression stroke. Accordingly, it is possible to suppress a large amount of the lubricating oil J in the oil supply groove 81 from flowing into the tip end surface of the blade 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 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 between the blade 55 (seal surface) and the flange portions 62 and 72 near the front end surface. Therefore, breakage of the oil film between the blade 55 and the flange portions 62 and 72 can be suppressed, and direct contact between the blade 55 and the flange portions 62 and 72 can be suppressed. Thereby, the wear between the blade 55 and the flange portions 62 and 72 can be reduced, and the operation reliability can be improved. Further, since the oil supply groove 81 is formed so as to be located in the cylinder chamber 46 when the blade 55 projects most into the cylinder chamber 46, the compression chamber and the compression chamber that pass between the blade 55 and the flange portions 62 and 72 are formed. The communication in the suction chamber is blocked by the oil film. Therefore, the sealing performance between the blade 55 and the flange portions 62 and 72 can be ensured. Therefore, the leakage of the refrigerant between the compression chamber and the suction chamber passing between the blade 55 and the flange portions 62 and 72 can be suppressed, and the compression performance can be improved. Further, since the first end of the oil supply groove 81 is opened through the linearly extending portion 82 as described above, it is possible to suppress a large amount of the lubricating oil J from flowing toward the tip end surface of the blade 55 in the first half of the compression stroke. Therefore, in the first half of the compression stroke, the lubricating oil J is prevented from being excessively interposed between the blade 55 and the flange portions 62 and 72, and the sealing performance between the blade 55 and the flange portions 62 and 72 can be maintained. Accordingly, it is possible to prevent the surplus lubricating oil J interposed between the blade 55 and the flange portions 62 and 72 from flowing into the cylinder chamber 46, and to prevent the refrigerant from flowing into the cylinder chamber 46 together with the lubricating oil J, A decrease in compression performance can be suppressed.

Moreover, in the present embodiment, since the maximum groove depth dimension E of the oil supply groove 81 is larger than the width dimension H, the width of the seal surface can be ensured while securing the volume in the oil supply groove 81. Therefore, while ensuring the capacity of the lubricating oil J in the oil supply groove 81, the sealing performance between the blade 55 and the flange portions 62 and 72 can be ensured. Thereby, the operational reliability and the compression performance can be further improved.

In the present embodiment, the width H of the oil supply groove 81 is smaller than the minimum width of the seal surface, so that the width of the seal surface can be secured. In this case, the sealability 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 clearance between the blade 55 and the flange portions 62 and 72 due to tolerance. . As a result, the operational reliability and the compression performance can be further improved.

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

Second Embodiment In the blade 155 shown in FIG. 4, the bottom of the oil supply groove 181 is formed in an arc shape that protrudes inward in the axial direction throughout. Therefore, the groove depth of the oil supply groove 181 is gradually reduced toward both the first end and the second end. The first end of the oil supply groove 181 is open on the rear end surface of the blade 155. The second end of the oil supply groove 181 terminates in the blade 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 and separate from each other. Specifically, the cutters 191 and 192 move between a processing position where processing is performed on the blade 155 located between the cutters 191 and 192 and a retracted position that is separated from the blade 155 located between the cutters 191 and 192. Moving. The transport mechanism sequentially passes the blades 155 from upstream to downstream through a gap between the pair of cutters 191 and 192.

In order to form the oil supply groove 81 using the above-described groove forming apparatus 190, first, the blade 155 is transported between the cutters 191 and 192 by the transport mechanism with the cutters 191 and 192 at the retracted position. Next, the cutters 191 and 192 are rotated in opposite directions, and the cutters 191 and 192 are moved toward the processing position. Then, the cutters 191 and 192 enter the upper and lower end surfaces of the blade 155, and the upper and lower end surfaces of the blade 155 are cut. At this time, the amount of the cutters 191 and 192 entering the blade 155 is set to the maximum groove depth E of each oil supply groove 181. Thereby, the oil supply groove 181 is formed in an arc shape following the radius of curvature of the cutters 191 and 192.

Thereafter, the cutters 191 and 192 are moved to the retracted position again, and the cutters 191 and 192 are separated from the blade 155. Then, the transport mechanism is driven to transport the processed blade 155 downstream with respect to the cutters 191 and 192, and the blade 155 to be processed next is sequentially transported between the cutters 191 and 192. After that, the blade 155 conveyed between the cutters 191 and 192 is cut by the same method as described above. Thereby, an oil supply groove 181 is sequentially formed on the blade 155 conveyed between the cutters 191 and 192.

According to this configuration, since the entire oil supply groove 181 is formed in a convex arc shape toward the inside in the axial direction, the cutters 191 and 192 can reciprocate with respect to the blade 155 conveyed in one direction. Thus, the oil supply groove 181 can be formed. Thereby, it is possible to further improve the manufacturing efficiency and reduce the cost.

Third Embodiment In the blade 255 shown in FIG. 6, the bottom of the oil supply groove 281 extends linearly outward in the axial direction from the first end to the second end. A first end of the oil supply groove 281 is open on one end surface of the blade 255. The second end of the oil supply groove 281 terminates in the blade 255.

As shown in FIG. 7, in the groove forming apparatus 290 of the present embodiment, the cutter 291 is rotatably supported. The transport mechanism 292 transports the blade 255 from upstream to downstream with respect to the cutter 291. The transport mechanism 292 holds the blade 255 in a state inclined with respect to the transport direction. Specifically, the transport mechanism 292 holds the blade 255 in a state where the first end face of the blade 255 is directed downstream and one end face is tilted upward (toward the cutter 291).

To form the oil supply groove 281 using the above-described groove forming device 290, the blade 255 is transported downstream by the transport mechanism 292 while the cutter 291 is rotated. Then, the cutter 291 enters one end surface of the blade 255 from the first end of the blade 255. Then, by passing the blade 255 downstream of the cutter 291, an oil supply groove 281 is formed on one end surface of the blade 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, a cutting process is performed on the blade 255 to be processed next by the same method as described above. Thereby, an oil supply groove 281 is sequentially formed on one end surface of the blade 255 conveyed toward the cutter 291.

Next, the blade 255 having the oil supply groove 281 formed on one end surface is turned upside down, and the oil supply groove 281 is formed on the other end surface by the same method as described above. Thereby, the above-described blade 255 of the present embodiment is completed.

According to this configuration, the oil supply groove 281 can be formed only by passing the blade 255 to one cutter 291, so that the groove forming device 290 can be simplified and the cost can be reduced. Further, since the processing by the cutter 291 is performed while the blade 255 is being conveyed, the conveyance of the blade 255 is not stopped. Therefore, the lead time can be further reduced.

In the above embodiment, the case where the main bearing 42 and the sub-bearing 43 are used as the closing plate has been described, but the present invention is not limited to this. For example, the upper end opening of the cylinder 41 is closed, and the bearing portion through which the rotating shaft 31 is inserted and the lower end opening of the cylinder 41 are closed to slidably support the lower end surface of the rotating shaft 31 in the axial direction. May be used as a closing plate.

Further, in the above-described embodiment, the configuration in which the number of the cylinder chambers 46 is one has been described. Further, in the above-described embodiment, a case has been described in which the axial direction coincides with the vertical direction. However, the present invention is not limited to this, and the axial direction may coincide with the horizontal direction. Further, in the above-described embodiment, a case has been described in which the roller 53 and the blade are formed separately, but the invention is not limited thereto, and the roller 53 and the blade may be formed integrally.

Further, in the above-described embodiment, the case where the oil supply grooves are separately formed on the upper and lower end surfaces of the blade has been described. Further, in the above-described embodiment, the case where one line of the oil supply groove is formed on the end face of the blade has been described. However, the present invention is not limited to this, and a plurality of lines of the oil supply groove may be formed.

Further, in the above-described embodiment, the case where the second end of the oil supply groove is formed in an arc shape or a straight line is described, but the present invention is not limited to this. For example, a step shape may be used as long as the depth gradually decreases toward the tip surface of the blade. Further, the oil supply groove may be such that at least the second end (the portion located closer to the second end than the intermediate portion in the extending direction in the oil supply groove) is shallower toward the second end.

Further, in the above-described embodiment, a case has been described where the oil supply groove is a straight line extending along the moving direction (radial direction) of the blade in plan view as viewed from the axial direction. However, the present invention is not limited to this. For example, if the oil supply groove extends along the moving direction of the blade, the oil supply groove may be, for example, corrugated or may be inclined with respect to the moving direction. Further, in the above-described embodiment, the configuration in which the width of the oil supply groove is uniform throughout is described, but the design of the width of the oil supply groove can be changed as appropriate. In this case, it is preferable that the minimum width dimension of the sealing surface is smaller than the maximum width dimension of the oil supply groove.

According to at least one embodiment described above, the oil supply groove is shallower from the first end to the second end, so that the wedge effect is likely to occur in the latter half of the compression stroke. Therefore, the lubricating oil is effectively supplied between the blade and the closing plate toward the second end face. Therefore, breakage of the oil film between the blade and the closing plate can be suppressed, and direct contact between the blade and the closing plate can be suppressed. Thereby, abrasion between the blade and the closing plate can be reduced. As a result, operation reliability can be improved. In addition, since communication between the blade and the closing plate and between the compression chamber and the suction chamber is blocked by the oil film, the sealing property between the blade and the closing plate can be ensured. Therefore, leakage of the refrigerant between the compression chamber and the suction chamber passing between the blade and the closing plate can be suppressed, and the compression performance can be improved. Furthermore, since the other end of the oil supply groove communicates with the inside of the closed container, it is possible to suppress a large amount of lubricating oil from flowing toward the second end face of the roller in the first half of the compression stroke. Therefore, in the first half of the compression stroke, it is possible to suppress the excessive interposition of the lubricating oil between the blade and the closing plate, and to maintain the sealing property between the blade and the closing plate. Thereby, it is possible to suppress the surplus lubricating oil interposed between the blade and the closing plate from flowing into the cylinder chamber, and to suppress the refrigerant from flowing into the cylinder chamber together with the lubricating oil, thereby suppressing a decrease in compression performance.

Although several embodiments of the present invention have been described, these embodiments are provided by way of example and are not intended to limit the scope of the invention. These embodiments can be implemented in other various forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the scope and gist of the invention, and are also included in the invention described in the claims and equivalents thereof. ?

Claims (7)

A container in which lubricating oil is stored,
A cylindrical cylinder housed in the container,
A closing plate that closes an opening of the cylinder and forms a cylinder chamber together with the cylinder;
A roller eccentrically rotating in the cylinder chamber,
A blade that divides the cylinder chamber in the rotation direction of the roller, and is configured to be able to advance and retreat into the cylinder chamber with eccentric rotation of the roller,
The blade is formed on a facing surface facing the closing plate, extends linearly along a moving direction of the blade, has a first end communicating with the container, and is opposite to the first end. A refueling groove, the second end of which is located on the side, terminating in the blade.
The refueling groove is located on the first end side, and has a straight extending portion having the same groove depth throughout, and a continuous groove portion extending from the straight extending portion to the second end portion and having a groove depth. An inclined portion which becomes shallower toward the second end portion and which is inclined and terminates at the second end portion, wherein the second end portion is in the cylinder chamber when the blade projects most into the cylinder chamber; Located in
Rotary compressor. The lubrication groove has an arc shape in which a groove depth gradually decreases toward the second end.
The rotary compressor according to claim 1. The maximum groove depth dimension of the oil groove is larger than the width dimension of the oil groove,
The rotary compressor according to claim 1. On the facing surface of the blade, a minimum width dimension of a portion other than the oil supply groove is wider than a width dimension of the oil supply groove,
The rotary compressor according to any one of claims 1 to 3. The oil supply groove is provided on both end surfaces of the blade, which are opposing surfaces facing the closing plate,
The rotary compressor according to any one of claims 1 to 4. A rotary compressor according to any one of claims 1 to 5,
A condenser connected to the rotary compressor;
An expansion device connected to the condenser;
An evaporator connected between the expansion device and the rotary compressor,
Refrigeration cycle device. A container in which lubricating oil is stored, a cylindrical cylinder housed in the container, a closing plate that closes an opening of the cylinder to form a cylinder chamber with the cylinder, and eccentric rotation in the cylinder chamber. A roller that divides the cylinder chamber in the direction of rotation of the roller, a blade that can advance and retreat into the cylinder chamber with the eccentric rotation of the roller, and an opposing surface of the blade that faces the closing plate. Formed in a straight line along the direction of movement of the blade, a first end communicates with the container, and a second end opposite to the first end has a second end within the blade. A refueling groove that terminates, wherein the refueling groove is located on the first end side and has the same groove depth throughout the entire length of the refueling groove; When connected to the end With a groove depth becomes shallower toward the second end portion has an inclined portion which terminates inclined at said second end, said second end when said blade is the most prominent in the cylinder chamber Part is located in the cylinder chamber, in the method of manufacturing a rotary compressor,
Spaced apart one another axis of rotation, are relatively moved in a direction and the pair of disk-shaped cutter between them are spaced narrower gap than the height of the blade blade approaches, the By moving the contact surface of the cutter and the blade so that the contact surface does not reach the tip end surface of the blade, simultaneously forming an oil supply groove on both end surfaces of the blade,
The pair of cutters and the blade, comprising a step of relatively moving in a direction away from,
Manufacturing method of rotary compressor.