JP2021173211A - Compressor and refrigeration cycle device - Google Patents

Abstract

To provide a compressor having a lubrication structure which may stably lubricate a slide portion between a rotary shaft and a sub bearing, and to provide a refrigeration cycle device.SOLUTION: A rotary shaft 15 of a compressor 2 has a first oil supply groove 81 provided on an outer peripheral surface 77 of a portion supported by a sub bearing 17 and extending in a reverse direction of a rotation direction of the rotary shaft 15 and toward a third cylinder 42C. The sub bearing 17 has a second oil supply groove 82 which is provided on an inner peripheral surface 78 of the sub bearing 17, extends in the rotation direction of the rotary shaft 15 which is a direction away from the third cylinder 42C, and is connected to the first oil supply groove 81 constantly or temporarily in conjunction with rotation of the rotary shaft 15.SELECTED DRAWING: Figure 2

Description

The present invention relates to a compressor and a refrigeration cycle device.

It includes a vertically placed cylindrical compressor housing in which lubricating oil is stored, a compression unit arranged in the lower part of the compressor housing, and a motor arranged in the upper part of the compressor housing to drive the compression unit. Rotary compressors are known.

The compression portion includes an annular cylinder, an upper end plate that closes the upper side of the cylinder, a lower end plate that closes the lower side of the cylinder, a main bearing portion provided on the upper end plate, and an auxiliary bearing portion provided on the lower end plate. The rotating shaft supported by the main bearing and the auxiliary bearing and rotated by the motor, and the annular shape that is fitted to the eccentric part of the rotating shaft and revolves along the inner peripheral surface of the cylinder to form a cylinder chamber in the cylinder. It is equipped with a cylinder.

A spiral oil supply groove for supplying lubricating oil from the lower end to the upper end of the shaft hole is formed on the inner peripheral surface of the shaft hole of the auxiliary bearing portion. The refueling groove is inclined with respect to the rotation direction of the rotation shaft and extends from the lower end to the upper end in the rotation direction of the rotation shaft.

Japanese Unexamined Patent Publication No. 2019-183768

In the conventional rotary compressor, the lubricating oil stored in the compressor housing is sucked up along the lubrication groove extending from the lower end to the upper end of the shaft hole of the auxiliary bearing portion by the rotation of the rotating shaft.

By the way, the multi-cylinder type rotary compressor may include a main muffler that covers the main bearing and a sub muffler that covers the sub bearing. In such a multi-cylinder rotary compressor, a first cylinder that discharges the refrigerant compressed in the cylinder chamber into the main muffler, a second cylinder that discharges the refrigerant compressed in the cylinder chamber into the sub-muffler, and the like. Includes. That is, the lower end of the shaft hole of the auxiliary bearing is covered with the auxiliary muffler. The lower end of the shaft hole of the auxiliary bearing is not submerged in the lubricating oil stored in the compressor housing.

Therefore, in a multi-cylinder rotary compressor, unlike a conventional rotary compressor, the sliding portion between the rotating shaft and the auxiliary bearing is lubricated with an oil supply groove that penetrates the shaft hole of the auxiliary bearing from the lower end to the upper end. Is difficult.

Therefore, an object of the present invention is to provide a compressor and a refrigeration cycle device having a lubrication structure capable of stably lubricating a sliding portion between a rotating shaft and an auxiliary bearing.

In order to solve the above problems, the compressor according to the embodiment of the present invention includes a cylindrical closed container having a center line extending in the vertical direction and a refrigerant contained in the closed container and introduced into the closed container. An electric motor having a compression mechanism for compressing the container, a cylindrical stator fixed to the inner surface of the closed container, and a rotor arranged inside the stator to generate a rotational driving force of the compression mechanism. It is provided with a refueling mechanism for supplying the lubricating oil stored in the closed container to the compression mechanism. The compression mechanism rotates integrally with the rotor, a rotating shaft extending downward from the rotor, a main bearing that rotatably supports an intermediate portion of the rotating shaft, and a lower end portion of the rotating shaft. An auxiliary bearing that can be supported, a cylinder having a cylinder chamber that is closed by the auxiliary bearing, an auxiliary muffler that covers the auxiliary bearing and partitions a space for discharging a refrigerant compressed by the cylinder, and the auxiliary bearing. It is provided with a balancer provided in a protruding portion of the rotating shaft protruding from the side and housed in the sub muffler. The rotating shaft is provided on the outer peripheral surface of a portion supported by the auxiliary bearing, and has a first oil supply groove extending in the direction opposite to the rotating direction of the rotating shaft and toward the cylinder. The auxiliary bearing is provided on the inner peripheral surface of the auxiliary bearing, extends in the direction of rotation of the rotary shaft and away from the cylinder, and is constantly or temporarily in the first oil filler groove as the rotary shaft rotates. It has a second refueling groove that leads to.

Further, the refrigeration cycle device according to the embodiment of the present invention connects the compressor, the radiator, the expander, the heat absorber, the compressor, the radiator, the expander, and the heat absorber. It is equipped with a refrigerant pipe for circulating the refrigerant.

The schematic diagram of the refrigeration cycle apparatus and the compressor which concerns on embodiment of this invention. An enlarged view of a vertical sectional view of a compressor according to an embodiment of the present invention. The vertical sectional view of the auxiliary bearing of the compressor which concerns on embodiment of this invention.

An embodiment of the compressor and the refrigeration cycle apparatus according to the present invention will be described with reference to FIGS. 1 to 3. In the plurality of drawings, the same or corresponding configurations are designated by the same reference numerals.

FIG. 1 is a schematic view of a refrigeration cycle apparatus and a compressor according to an embodiment of the present invention.

As shown in FIG. 1, the refrigeration cycle device 1 according to the present embodiment is, for example, an air conditioner. The refrigeration cycle device 1 includes a closed rotary compressor 2 (hereinafter, simply referred to as “compressor 2”), a radiator 3, an expansion device 5, a heat absorber 6, an accumulator 7, and a refrigerant pipe. 8 and. The refrigerant pipe 8 sequentially connects the compressor 2, the radiator 3, the expansion device 5, the heat absorber 6, and the accumulator 7 to circulate the refrigerant. The radiator 3 is also called a condenser. The endothermic absorber 6 is also called an evaporator.

The compressor 2 sucks in the refrigerant that has passed through the heat absorber 6 through the refrigerant pipe 8, compresses it, and discharges the high-temperature and high-pressure refrigerant through the refrigerant pipe 8 to the radiator 3.

The compressor 2 includes a cylindrical airtight container 11 placed vertically, an open winding type electric motor 12 (hereinafter, simply referred to as “motor 12”) housed in the upper half of the airtight container 11, and the airtight container. A compression mechanism 13 housed in the lower half of the interior 11, a rotating shaft 15 that transmits the rotational driving force of the motor 12 to the compression mechanism 13, a main bearing 16 that rotatably supports the rotating shaft 15, and a main bearing 16 It is provided with an auxiliary bearing 17 that rotatably supports the rotating shaft 15 in cooperation with the compressor, and a refueling mechanism 22 that supplies the lubricating oil 21 (refrigerating machine oil) stored in the closed container 11 to the compression mechanism 13. ..

The center line of the vertically placed closed container 11 extends in the vertical direction. The closed container 11 includes a cylindrical body portion 11a extending in the vertical direction, a end plate 11b that closes the upper end portion of the body portion, and a end plate 11c that closes the lower end portion of the body portion.

A discharge pipe 8a for discharging the refrigerant to the outside of the closed container 11 is connected to the end plate 11b on the upper side of the closed container 11. The discharge pipe 8a is connected to the refrigerant pipe 8. Further, the end plate 11b on the upper side of the closed container 11 is provided with a pair of sealed terminals 25 and 26 and a pair of terminal blocks 27 and 28 that guide the electric power supplied to the electric motor 12 from the outside to the inside of the closed container 11. Has been done. The terminal blocks 27 and 28 are provided on the sealed terminals 25 and 26, respectively. A plurality of power lines 29 that are electrically connected to the sealed terminals 25 and 26 to supply electric power are fixed to the terminal blocks 27 and 28, respectively. The power line 29 is a so-called lead wire.

The electric motor 12 generates a driving force for rotating the compression mechanism 13. The electric motor 12 is arranged above the compression mechanism 13. The electric motor 12 is pulled out from the tubular stator 31 fixed to the inner surface of the closed container 11, the rotor 32 arranged inside the stator 31 to generate the rotational driving force of the compression mechanism 13, and the stator 31. It is provided with a plurality of outlet wires 33 that are electrically connected to the pair of sealed terminals 25 and 26.

The rotor 32 includes a rotor core 35 having a magnet accommodating hole (not shown) and a permanent magnet (not shown) accommodated in the magnet accommodating hole. The rotor 32 is fixed to the rotating shaft 15. The rotation center line C of the rotor 32 and the rotation shaft 15 substantially coincides with the center line of the stator 31. Further, the rotation center line C of the rotor 32 and the rotation shaft 15 substantially coincides with the center line of the closed container 11.

The plurality of outlet wires 33 are power lines that supply electric power to the stator 31 through the sealing terminals 25 and 26, and are so-called lead wires. A plurality of outlet wires 33 are wired according to the type of the electric motor 12. In this embodiment, six outlet wires 33 are wired.

The motor 12 may be a motor having a plurality of systems, for example, two systems of three-phase windings, in addition to the open winding type.

The rotating shaft 15 connects the electric motor 12 and the compression mechanism 13. The rotating shaft 15 transmits the rotational driving force generated by the electric motor 12 to the compression mechanism 13. The rotation shaft 15 is rotationally integrated with the rotor 32 and extends downward from the rotor 32.

The intermediate portion 15a of the rotating shaft 15 connects the electric motor 12 and the compression mechanism 13 and is rotatably supported by the main bearing 16. The lower end portion 15b of the rotating shaft 15 is rotatably supported by the auxiliary bearing 17. The main bearing 16 and the auxiliary bearing 17 are also a part of the compression mechanism 13. In other words, the rotating shaft 15 penetrates the compression mechanism 13.

Further, the rotating shaft 15 is provided with a plurality of, for example, three eccentric portions 36 between the intermediate portion 15a supported by the main bearing 16 and the lower end portion 15b supported by the auxiliary bearing 17. Each eccentric portion 36 is a disk or a cylinder having a center that does not match the rotation center line C of the rotation axis 15.

A balancer 38 is provided on the protruding portion of the rotating shaft 15 protruding from the auxiliary bearing 17.

The compression mechanism 13 compresses the refrigerant introduced into the closed container 11. When the electric motor 12 rotationally drives the rotating shaft 15, the compression mechanism 13 sucks the gaseous refrigerant from the refrigerant pipe 8 and compresses it, and discharges the compressed high-temperature and high-pressure refrigerant into the closed container 11.

The compression mechanism 13 is a rotary type having a plurality of cylinders, for example, three cylinders. The compression mechanism 13 includes a plurality of cylinders 42, each having a circular cylinder chamber 41, and a plurality of annular rollers 43 arranged in the respective cylinder chambers 41. The compression mechanism 13 may be a single-cylinder rotary type.

Here, the cylinder 42 closest to the motor 12 is the first cylinder 42A, the cylinder 42 farthest from the motor 12 is the third cylinder 42C, and the cylinder 42 arranged between the first cylinder 42A and the third cylinder 42C is The second cylinder is 42B.

The compression mechanism 13 includes a main bearing 16 that closes the upper surface of the first cylinder 42A, a first partition plate 45A that closes the lower surface of the first cylinder 42A and the upper surface of the second cylinder 42B, and the lower surface of the second cylinder 42B and the third cylinder. It includes a second partition plate 45B that closes the upper surface of the 42C, and an auxiliary bearing 17 that closes the lower surface of the third cylinder 42C.

In other words, the upper surface of the first cylinder 42A is closed by the main bearing 16. The lower surface of the first cylinder 42A is closed by the first partition plate 45A. The upper surface of the second cylinder 42B is closed by the first partition plate 45A. The lower surface of the second cylinder 42B is closed by the second partition plate 45B. The upper surface of the third cylinder 42C is closed by the second partition plate 45B. The lower surface of the third cylinder 42C is closed by the auxiliary bearing 17.

That is, the first cylinder 42A is sandwiched between the main bearing 16 and the first partition plate 45A. The second cylinder 42B is sandwiched between the first partition plate 45A and the second partition plate 45B. The third cylinder 42C is sandwiched between the second partition plate 45B and the auxiliary bearing 17.

The main bearing 16 and the first partition plate 45A are collectively fixed to the second cylinder 42B by a fastening member 46 such as a bolt. That is, the main bearing 16 and the first partition plate 45A are co-tightened to the second cylinder 42B by the fastening member 46. The main bearing 16 includes a first discharge valve mechanism 51A that discharges the compressed refrigerant in the cylinder chamber 41 of the first cylinder 42A, and a first discharge muffler 52 (main muffler) that covers the first discharge valve mechanism 51A. , Are provided. The first discharge valve mechanism 51A has a discharge port when the pressure difference between the pressure in the cylinder chamber 41 of the first cylinder 42A and the pressure in the first discharge muffler 52 reaches a predetermined value due to the compression action of the compression mechanism 13. (Not shown) is opened to discharge the compressed refrigerant into the first discharge muffler 52.

The first discharge muffler 52 partitions the space where the refrigerant compressed by the cylinder 42 is discharged. The first discharge muffler 52 has a discharge hole (not shown) that connects the inside and outside of the first discharge muffler 52. The compressed refrigerant discharged into the first discharge muffler 52 is discharged into the closed container 11 through the discharge holes.

The second partition plate 45B is provided with a second discharge valve mechanism 51B for discharging the compressed refrigerant in the cylinder chamber 41 of the second cylinder 42B, and a discharge chamber 53. The main bearing 16, the first cylinder 42A, the first partition plate 45A, and the second cylinder 42B have a first hole (not shown) for connecting the discharge chamber 53 of the second partition plate 45B into the first discharge muffler 52. ing. The second discharge valve mechanism 51B has a discharge port (not shown) when the pressure difference between the pressure in the cylinder chamber 41 and the pressure in the discharge chamber 53 of the second cylinder 42B reaches a predetermined value due to the compression action of the compression mechanism 13. (Omitted) is opened to discharge the compressed refrigerant into the discharge chamber 53. The refrigerant discharged into the discharge chamber 53 is discharged into the first discharge muffler 52 through the first hole. The refrigerant discharged into the first discharge muffler 52 through the first hole joins the refrigerant compressed by the first cylinder 42A.

The auxiliary bearing 17, the third cylinder 42C, and the second partition plate 45B are collectively fixed to the second cylinder 42B by a fastening member 55 such as a bolt. That is, the auxiliary bearing 17, the third cylinder 42C, and the second partition plate 45B are co-tightened to the second cylinder 42B by the fastening member 55. The auxiliary bearing 17 includes a third discharge valve mechanism 51C that discharges the compressed refrigerant in the cylinder chamber 41 of the third cylinder 42C, and a second discharge muffler 56 (secondary muffler) that covers the third discharge valve mechanism 51C. , Are provided. The second discharge muffler 56 partitions the space where the refrigerant compressed by the third cylinder 42C is discharged. The main bearing 16, the first cylinder 42A, the first partition plate 45A, the second cylinder 42B, the second partition plate 45B, and the third cylinder 42C connect the space in the second discharge muffler 56 into the first discharge muffler 52. It has a second hole 57. The third discharge valve mechanism 51C has a discharge port when the pressure difference between the pressure in the cylinder chamber 41 of the third cylinder 42C and the pressure in the second discharge muffler 56 reaches a predetermined value due to the compression action of the compression mechanism 13. (Not shown) is opened to discharge the compressed refrigerant into the second discharge muffler 56. The refrigerant discharged into the second discharge muffler 56 is discharged into the first discharge muffler 52 through the second hole 57. The refrigerant discharged into the first discharge muffler 52 joins the refrigerant compressed by the first cylinder 42A and the refrigerant compressed by the second cylinder 42B.

The first hole may be a part of the second hole 57. Further, the discharge chamber 53 of the second partition plate 45B may be connected to the inside of the second discharge muffler 56. That is, the first hole may be connected to the inside of the second discharge muffler 56.

The first cylinder 42A is fixed to the closed container 11 at a plurality of locations, for example, to a frame 58 fixed by spot welding with fastening members 59 such as bolts. That is, the frame 58 supports the rotor 32, the compression mechanism 13, and the rotating shaft 15 of the electric motor 12 in the closed container 11 via the first cylinder 42A. The center of gravity of the rotor 32, the compression mechanism 13, and the rotating shaft 15 of the electric motor 12 in the height direction of the closed container 11 is located within the range of the thickness of the frame 58 (dimensions in the height direction of the compressor 2). It is preferable to have.

The balancer 38 is housed in a second discharge muffler 56 that covers the auxiliary bearing 17. The balancer 38 is, for example, a disk having a center line parallel to the rotation center line C of the rotation shaft 15 or a fan-shaped plate requiring the rotation center line C of the rotation shaft 15. The balancer 38 is provided at an eccentric position away from the center line of the balancer 38, and has a through hole 38a penetrating the balancer 38. The lower end of the rotating shaft 15 is press-fitted into the through hole 38a of the balancer 38. The amount of eccentricity of the through hole 38a is adjusted so as to reduce the imbalance of the rotating body of the compression mechanism 13 during the compression operation.

By the way, when a balancer is provided at the upper end of the rotating shaft 15 projecting upward of the rotor 32, the distance between the balancer and the bearing (main bearing 16) supporting the rotating shaft 15 is the axial dimension of the rotor 32. Depends on. By providing the balancer 38 at the lower end of the rotating shaft 15 protruding from the auxiliary bearing 17 as in the present embodiment, the balancer 38 and the rotating shaft 15 are supported as compared with the case where the balancer is provided at the upper end of the rotating shaft 15. The distance from the bearing (secondary bearing 17) is extremely shortened. Therefore, by arranging the balancer 38 as in the present embodiment, the bending of the rotating shaft 15 and the rotor 32 is suppressed.

The plurality of suction pipes 61 penetrate the closed container 11 and are connected to the cylinder chamber 41 of each cylinder 42. Each cylinder 42 has a suction hole that is connected to each suction pipe 61 and reaches the cylinder chamber 41. The first suction pipe 61A is connected to the cylinder chamber 41 of the first cylinder 42A. The second suction pipe 61B is connected to the cylinder chamber 41 of the second cylinder 42B. The third suction pipe 61C is connected to the cylinder chamber 41 of the third cylinder 42C. The number of the plurality of suction pipes 61 may be the same as that of the plurality of cylinders 42 as in the present embodiment, or may be shared by the two cylinders 42 and smaller than the number of the plurality of cylinders 42. good. For example, the second suction pipe 61B may be connected to the second partition plate 45B. The second partition plate 45B is connected to the second partition plate 45B, and is branched into the cylinder chamber 41 of the second cylinder 42B and the cylinder chamber 41 of the third cylinder 42C, and is connected to the two cylinder chambers 41. (Not shown) is provided.

The lower part of the closed container 11 is filled with the lubricating oil 21. Most of the compression mechanism 13 is immersed in the lubricating oil 21 in the closed container 11.

The lubrication mechanism 22 pumps up the lubricating oil 21 in the closed container 11 and supplies it to the sliding portion of the compression mechanism 13. The refueling mechanism 22 includes a pump 65 that pumps the lubricating oil 21 in the closed container 11, and an oil passage 66 that sends the lubricating oil 21 pumped by the pump 65 to the sliding portion of the compression mechanism 13.

Here, the "sliding portion of the compression mechanism 13" includes, for example, a gap between the eccentric portion 36 and the roller 43, a gap between the main bearing 16 and the rotating shaft 15, and a gap between the auxiliary bearing 17 and the rotating shaft 15. I'm out.

The pump 65 is, for example, a screw pump (Archimedean screw, Archimedes' spiral). The suction port of the screw pump is immersed in the lubricating oil 21 stored in the closed container 11.

Here, the second discharge muffler 56 has a refueling mechanism insertion hole 68 that exposes the lower end portion of the rotating shaft 15 to the outside of the second discharge muffler 56. The lower end of the rotating shaft 15 is immersed in the lubricating oil 21 in the closed container 11 through the lubrication mechanism insertion hole 68. Further, the rotary shaft 15 has a pump arrangement hole 69 that opens at the lower end of the rotary shaft 15 and extends toward the upper end of the rotary shaft 15.

The pump 65 is arranged in the pump arrangement hole 69 of the rotation shaft 15 and includes a rotor 71 that extends spirally along the rotation center line C of the rotation shaft 15. The rotor 71 is rotationally integrated with the rotating shaft 15. By rotating together with the rotating shaft 15, the rotor 71 continuously pumps the lubricating oil 21 from the opening at the lower end of the rotating shaft 15 into the pump arrangement hole 69 of the rotating shaft 15.

The pump 65 is not limited to the rotor 71 as long as it is provided in the closed container 11 and the lubricating oil 21 can be continuously supplied into the pump arrangement hole 69 of the rotating shaft 15. The pump 65 may be a turbo type pump driven by utilizing the rotational driving force of the rotating shaft 15, or may be a positive displacement pump. In this case, the pump arrangement hole 69 plays a part of the oil passage 66.

The oil passage 66 sends the lubricating oil 21 pumped into the pump arrangement hole 69 of the rotating shaft 15 by the pump 65 that is rotationally integrated with the rotating shaft 15 to the sliding portion of the compression mechanism 13 to lubricate the oil passage 66.

The oil passage 66 has a first cylinder oil supply hole 73A for supplying the lubricating oil 21 in the pump arrangement hole 69 to the gap between the eccentric portion 36 and the roller 43 housed in the first cylinder 42A, and the pump arrangement hole 69. The second cylinder oil supply hole 73B for supplying the lubricating oil 21 to the gap between the eccentric portion 36 and the roller 43 housed in the second cylinder 42B, and the lubricating oil 21 in the pump arrangement hole 69 are stored in the third cylinder 42C. It has a third cylinder oil supply hole 73C for supplying oil to the gap between the eccentric portion 36 and the roller 43.

Further, in the oil passage 66, the main bearing oil supply hole 75A for supplying the lubricating oil 21 in the pump arrangement hole 69 to the gap between the main bearing 16 and the rotating shaft 15 and the lubricating oil 21 in the pump arrangement hole 69 are supplied to the auxiliary bearing 17. It has an auxiliary bearing oil supply hole 75B for supplying oil to the gap between the rotary shaft 15 and the rotary shaft 15.

The accumulator 7 prevents the liquid refrigerant that could not be completely gasified by the heat absorber 6 from being sucked into the compressor 2.

Next, the lubrication structure of the rotating shaft 15 and the auxiliary bearing 17 will be described.

FIG. 2 is an enlarged view of a vertical cross-sectional view of the compressor according to the embodiment of the present invention.

FIG. 3 is a vertical cross-sectional view of the auxiliary bearing of the compressor according to the embodiment of the present invention.

The rotation shaft 15 is assumed to rotate counterclockwise in the plan view of the compressor 2. That is, when the rotation shaft 15 is rotating, the outer peripheral surface 77 of the rotation shaft 15 drawn in FIG. 2 moves so as to cross the rotation center line C from left to right as shown by the solid line arrow R. Further, when the rotating shaft 15 is rotating, the outer peripheral surface 77 of the rotating shaft 15 facing the inner peripheral surface 78 of the auxiliary bearing 17 depicted in FIG. 3 has a rotation center line C as shown by a solid arrow R. Move across from right to left.

As shown in FIG. 2, the rotary shaft 15 of the compressor 2 according to the embodiment of the present invention is provided on the outer peripheral surface 77 of the portion supported by the auxiliary bearing 17, and is in the direction opposite to the rotation direction of the rotary shaft 15. Moreover, it has a first oil supply groove 81 extending toward the third cylinder 42C. That is, the first oil supply groove 81 faces the inner peripheral surface 78 of the auxiliary bearing 17. The first refueling groove 81 is recessed toward the rotation center line C of the rotating shaft 15, is connected to the sub-bearing refueling hole 75B, and extends from the connection portion with the sub-bearing refueling hole 75B to reach the third cylinder 42C. The first oil supply groove 81 extends spirally along the outer peripheral surface 77 of the rotating shaft 15. In the compressor 2 that rotates the rotating shaft 15 counterclockwise in a plan view, the first lubrication groove 81 draws a clockwise spiral from the connection portion with the auxiliary bearing lubrication hole 75B toward the third cylinder 42C. ..

Further, as shown in FIG. 3, the auxiliary bearing 17 of the compressor 2 according to the embodiment of the present invention is provided on the inner peripheral surface 78 of the auxiliary bearing 17 in the rotation direction of the rotating shaft 15 and from the third cylinder 42C. It has a second refueling groove 82 extending in the direction away from it. The second refueling groove 82 faces the outer peripheral surface 77 of the rotating shaft 15. The second oil supply groove 82 is recessed toward the outer side in the radial direction of the auxiliary bearing 17. The second oil supply groove 82 spirally extends along the inner peripheral surface 78 of the auxiliary bearing 17. In the compressor 2 that rotates the rotating shaft 15 counterclockwise in a plan view, the second refueling groove 82 draws a counterclockwise spiral from the upper end side to the lower end side of the auxiliary bearing 17. That is, the second refueling groove 82 draws a clockwise spiral from the lower end side to the upper end side of the auxiliary bearing 17. Therefore, the first refueling groove 81 and the second refueling groove 82 each form a clockwise spiral from the lower end to the upper end of the sub bearing 17 with reference to the lower end side of the sub bearing 17. The first refueling groove 81 and the second refueling groove 82 each form a counterclockwise spiral from the upper end to the lower end of the sub bearing 17 with reference to the upper end side of the sub bearing 17.

Further, the second oil supply groove 82 is arranged at a position closer to the opening on the lower end side than the opening on the upper end side of the auxiliary bearing 17. Therefore, in the direction of the rotation center line C of the rotating shaft 15, the range S2 in which the second refueling groove 82 exists is narrower than the range S1 in which the first refueling groove 81 exists.

Then, the second refueling groove 82 is constantly or temporarily connected to the first refueling groove 81 as the rotating shaft 15 rotates.

For example, when the groove end 82t on the upper side of the second refueling groove 82 is connected to face the auxiliary bearing refueling hole 75B each time the rotating shaft 15 makes one rotation, the second refueling groove 82 is connected with the rotation of the rotating shaft 15. It is temporarily connected to the first refueling groove 81. When the second refueling groove 82 extends toward the upper opening of the auxiliary bearing 17 to such an extent that it always intersects the first refueling groove 81 of the rotating shaft 15, the second refueling groove 82 is the second It is always connected to one oil supply groove 81.

The lubricating structure of the rotating shaft 15 and the auxiliary bearing 17 having such a configuration is pumped into the pump arrangement hole 69 of the rotating shaft 15 by the pump 65 which is integrally rotated with the rotating shaft 15, and the lubricating oil flows out from the auxiliary bearing oil supply hole 75B. 21 is allowed to flow into the first lubrication groove 81 of the rotary shaft 15 and the second lubrication groove 82 of the auxiliary bearing 17 to lubricate the gap between the rotary shaft 15 and the auxiliary bearing 17. The lubricating oil 21 that has flowed into the first oil supply groove 81 of the rotary shaft 15 is above the auxiliary bearing oil supply hole 75B while generating a flow F1 from the auxiliary bearing oil supply hole 75B to the third cylinder 42C as the rotary shaft 15 rotates. Lubricate the range S1 of. Further, the lubricating oil 21 that has flowed into the second oil supply groove 82 of the auxiliary bearing 17 generates a flow F2 from the auxiliary bearing oil supply hole 75B toward the lower opening of the auxiliary bearing 17 with the rotation of the rotating shaft 15, and is secondary. Lubricate the range S2 below the bearing lubrication hole 75B.

The lubrication structure of the rotary shaft 15 and the auxiliary bearing 17 is the cross-sectional area of the flow path of the first oil supply groove 81, the flow path length of the first oil supply groove 81, and the first oil supply groove 81 with respect to the rotation center line C of the rotary shaft 15. Tilt, cross-sectional area of auxiliary bearing oil supply hole 75B connecting the first oil supply groove 81 and the oil passage 66 on the upstream side, the flow path cross-sectional area of the second oil supply groove 82, the flow path length of the second oil supply groove 82, rotation. By appropriately setting at least one of the inclination of the second lubrication groove 82 with respect to the rotation center line C of the shaft 15 and the amount of overlap between the first lubrication groove 81 and the second lubrication groove 82, the rotary shaft 15 and the auxiliary bearing The amount of oil supplied at the sliding portion with 17 is adjusted.

The flow path cross-sectional area of the refueling grooves 81 and 82 is set by a combination of the groove depth and the groove width of the refueling grooves 81 and 82.

Further, the amount of overlap between the first oil supply groove 81 and the second oil supply groove 82 does not have to extend to the entire opening of the auxiliary bearing oil supply hole 75B. For example, the first refueling groove 81 is connected to the entire sub-bearing refueling hole 75B, and the second refueling groove 82 is heavy on a part of the sub-bearing refueling hole 75B, for example, a semicircle in the process of rotation of the rotating shaft 15. It should be.

Further, the length of the first refueling groove 81 according to the present embodiment is shorter than that orbiting the outer peripheral surface 77 of the rotating shaft 15, and the length of the second refueling groove 82 according to the present embodiment is within the auxiliary bearing 17. It is shorter than orbiting the peripheral surface 78. That is, the first refueling groove 81 does not go around the rotating shaft 15 once. Further, the second oil supply groove 82 does not go around the auxiliary bearing 17 once. The lubricating oil 21 pumped by the pump 65 is constantly supplied to the first lubrication groove 81 of the rotating shaft 15, while the first lubrication groove 81 and the second lubrication groove 81 of the auxiliary bearing 17 are supplied. The lubricating oil 21 is supplied only when the lubrication groove 82 is connected. Therefore, in order to ensure lubrication by the second refueling groove 82, the second refueling groove 82 has a wider angle than the first refueling groove 81 in the size of the central angle centered on the rotation center line C of the rotating shaft 15. It is provided in the range. For example, the first refueling groove 81 is provided in a range of a central angle of 90 degrees centered on the rotation center line C of the rotation shaft 15, and the second refueling groove 82 is centered on the rotation center line C of the rotation shaft 15. It is provided in a range of a central angle of 180 degrees.

By the way, when the lubricating oil 21 that has flowed into the second oil supply groove 82 leaks excessively into the second discharge muffler 56, the balancer 38 in the second discharge muffler 56 adjusts the imbalance of the rotating body of the compression mechanism 13. There is a risk of losing the function to do. Therefore, the second oil supply groove 82 is a closed groove that is not open at the opening on the lower end side of the auxiliary bearing 17. In other words, the upper groove end 82t and the lower groove end 82b of the second refueling groove 82 are both closed. The first refueling groove 81 is open to the inside of the roller 43 of the third cylinder 42C. That is, the second lubrication groove 82 suppresses the amount of the lubricating oil 21 flowing out from the opening on the lower end side of the auxiliary bearing 17, while the entire lubrication grooves 81 and 82 move the lubricating oil 21 to the inside of the roller 43 of the third cylinder 42C. Let it leak.

As described above, the compressor 2 and the refrigerating cycle device 1 according to the present embodiment have a rotating shaft 15 having a first oil supply groove 81 extending in the direction opposite to the rotating direction of the rotating shaft 15 and toward the third cylinder 42C. And, which is provided on the inner peripheral surface 78 of the auxiliary bearing 17, extends in the direction of rotation of the rotating shaft 15 and in the direction away from the third cylinder 42C, and constantly or temporarily fills the first oil supply groove 81 with the rotation of the rotating shaft 15. It is provided with an auxiliary bearing 17 having a second oil supply groove 82 connected to the engine.

Therefore, the compressor 2 and the refrigerating cycle device 1 use the lubricating oil 21 that flows into the lubrication grooves 81 and 82 without immersing the lower end of the auxiliary bearing 17 in the lubricating oil 21 as in the conventional compressor. The entire gap between the bearing 17 and the auxiliary bearing 17 can be reliably lubricated. Further, in the compressor 2 and the refrigeration cycle device 1, the balancer 38 is arranged in the second discharge muffler 56, and the imbalance of the rotating body of the compression mechanism 13 can be easily adjusted while suppressing the bending of the rotating shaft 15. .. Further, the compressor 2 and the refrigerating cycle device 1 ensure that the entire gap between the rotating shaft 15 and the auxiliary bearing 17 is lubricated by the oil supply grooves 81 and 82, and the lubrication flows out from the opening on the lower end side of the auxiliary bearing 17. It is possible to suppress the oil 21 and prevent the balancer 38 in the second discharge muffler 56 from being immersed in the lubricating oil 21 and losing its function. In other words, the compressor 2 and the refrigeration cycle device 1 can easily balance the lubrication of the gap between the rotating shaft 15 and the auxiliary bearing 17 and the function of the balancer 38 in the second discharge muffler 56.

Further, the compressor 2 and the refrigeration cycle device 1 cover the main bearing 16, the auxiliary bearing 17, and the second hole 57 penetrating the third cylinder 42C, and the main bearing 16, and the space in the second discharge muffler 56 and the space inside the second discharge muffler 56. It includes a first discharge muffler 52 that partitions a space in which the refrigerant compressed by the third cylinder 42C is discharged through the second hole 57. Therefore, regardless of whether the compressor 2 and the refrigeration cycle device 1 are provided with a single-cylinder or multi-cylinder compression mechanism 13, the gap between the rotating shaft 15 and the auxiliary bearing 17 is lubricated and the second discharge is performed. The function of the balancer 38 in the muffler 56 can be easily compatible with the function of the balancer 38.

Further, in the compressor 2 and the refrigeration cycle device 1, the lubrication structure of the rotating shaft 15 and the auxiliary bearing 17 is the flow path cross-sectional area of the first oil supply groove 81, the flow path length of the first oil supply groove 81, and the rotary shaft. The inclination of the first oil supply groove 81 with respect to the rotation center line C of 15, the cross-sectional area of the auxiliary bearing oil supply hole 75B connecting the first oil supply groove 81 and the oil passage 66 on the upstream side thereof, and the flow path cross-sectional area of the second oil supply groove 82. , At least one of the length of the flow path of the second oil supply groove 82, the inclination of the second oil supply groove 82 with respect to the rotation center line C of the rotating shaft 15, and the amount of overlap between the first oil supply groove 81 and the second oil supply groove 82. The amount of oil supplied at the sliding portion between the rotating shaft 15 and the auxiliary bearing 17 is adjusted. Therefore, the compressor 2 and the refrigerating cycle device 1 reliably lubricate the entire gap between the rotating shaft 15 and the auxiliary bearing 17, while suppressing the lubricating oil 21 flowing out from the opening on the lower end side of the auxiliary bearing 17. (Ii) It is possible to reliably prevent the balancer 38 in the discharge muffler 56 from being immersed in the lubricating oil 21 and losing its function.

Further, the compressor 2 and the refrigeration cycle device 1 have a shorter first lubrication groove 81 that orbits the outer peripheral surface 77 of the rotary shaft 15 and a shorter second lubrication groove 82 that orbits the inner peripheral surface 78 of the auxiliary bearing 17. And have. Therefore, the compressor 2 and the refrigeration cycle device 1 can easily process the refueling grooves 81 and 82.

Further, the compressor 2 and the refrigeration cycle device 1 include a compression mechanism 13 having three or more cylinders. Therefore, the compressor 2 and the refrigeration cycle device 1 have the rotating shaft 15 and the auxiliary bearing 17 even in the compression mechanism 13 having three or more cylinders, in which the adjustment of the imbalance of the rotating body of the compression mechanism 13 becomes more serious. The lubrication of the gap and the function of the balancer 38 in the second discharge muffler 56 can be easily achieved at the same time.

Therefore, according to the refrigeration cycle device 1 and the compressor 2 according to the present embodiment, it is possible to provide a lubrication structure capable of stably lubricating the sliding portion between the rotating shaft 15 and the auxiliary bearing 17.

Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the gist of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are also included in the scope of the invention described in the claims and the equivalent scope thereof.

1 ... refrigeration cycle device, 2 ... rotary compressor, 3 ... radiator, 5 ... expansion device, 6 ... heat absorber, 7 ... accumulator, 8 ... refrigerant pipe, 8a ... discharge pipe, 11 ... closed container, 11a ... cylinder Part, 11b ... End plate, 11c ... End plate, 12 ... Open winding type electric motor, 13 ... Compression mechanism, 15 ... Rotor shaft, 15a ... Intermediate part, 15b ... Lower end part, 16 ... Main bearing, 17 ... Sub bearing, 21 ... Lubrication Oil, 22 ... refueling mechanism, 25, 26 ... sealed terminals, 27, 28 ... terminal bases, 29 ... power lines, 31 ... stators, 32 ... rotors, 33 ... outlet lines, 35 ... rotor cores, 36 ... eccentricity Part, 38 ... Balancer, 38a ... Through hole, 41 ... Cylinder chamber, 42 ... Cylinder, 42A ... First cylinder, 42C ... Third cylinder, 42B ... Second cylinder, 43 ... Roller, 45A ... First partition plate, 45B ... Second partition plate, 46 ... Fastening member, 51A ... First discharge valve mechanism, 51B ... Second discharge valve mechanism, 51C ... Third discharge valve mechanism, 52 ... First discharge muffler, 53 ... Discharge chamber, 55 ... Fastening Member, 56 ... Second discharge muffler, 57 ... Second hole, 58 ... Frame, 59 ... Fastening member, 61 ... Suction pipe, 61A ... First suction pipe, 61B ... Second suction pipe, 61C ... Third suction pipe, 65 ... Pump, 66 ... Oil passage, 68 ... Refueling mechanism insertion hole, 69 ... Pump placement hole, 71 ... Rotor, 73A ... First cylinder refueling hole, 73B ... Second cylinder refueling hole, 73C ... Third cylinder refueling hole, 75A ... Main bearing refueling hole, 75B ... Sub-bearing refueling hole, 77 ... Rotor shaft outer peripheral surface, 78 ... Sub-bearing inner peripheral surface, 81 ... First refueling groove, 82 ... Second refueling groove, 82t, 82b ... (Ii) The end of the refueling groove.

Claims (6)

A cylindrical closed container with a center line extending in the vertical direction,
A compression mechanism that compresses the refrigerant contained in the closed container and introduced into the closed container.
An electric motor having a tubular stator fixed to the inner surface of the closed container and a rotor arranged inside the stator to generate a rotational driving force of the compression mechanism.
A lubrication mechanism for supplying lubricating oil stored in the closed container to the compression mechanism is provided.
The compression mechanism
A rotation shaft that is integrally rotated with the rotor and extends downward from the rotor,
A main bearing that rotatably supports the middle part of the rotating shaft,
An auxiliary bearing that rotatably supports the lower end of the rotating shaft,
A cylinder having a cylinder chamber closed by the auxiliary bearing and
An auxiliary muffler that covers the auxiliary bearing and partitions the space where the refrigerant compressed by the cylinder is discharged.
A balancer provided in a protruding portion of the rotating shaft protruding from the auxiliary bearing and housed in the auxiliary muffler is provided.
The rotating shaft is provided on the outer peripheral surface of a portion supported by the auxiliary bearing, and has a first oil supply groove extending in the direction opposite to the rotating direction of the rotating shaft and toward the cylinder.
The auxiliary bearing is provided on the inner peripheral surface of the auxiliary bearing, extends in the direction of rotation of the rotary shaft and away from the cylinder, and constantly or temporarily fills the first oil supply groove with the rotation of the rotary shaft. A compressor with a second refueling groove that connects to. The main bearing, the sub-bearing, and the hole penetrating the cylinder,
The compressor according to claim 1, further comprising a main muffler that covers the main bearing and partitions a space in the sub muffler and a space in which the refrigerant compressed by the cylinder is discharged through the hole. The cross-sectional area of the flow path of the first supply groove, the flow path length of the first supply groove, the inclination of the first oil supply groove with respect to the rotation center line of the rotation shaft, the first oil supply groove and the oil passage on the upstream side thereof. The cross-sectional area of the opening connecting the two, the cross-sectional area of the flow path of the second supply groove, the flow path length of the second supply groove, the inclination of the second oil supply groove with respect to the rotation center line of the rotation axis, and the first The compressor according to claim 1 or 2, wherein the amount of oil supplied at the sliding portion between the rotating shaft and the auxiliary bearing is adjusted by at least one of the overlapping amounts of the supply groove and the second supply groove. The length of the first refueling groove is shorter than that orbiting the outer peripheral surface of the rotating shaft.
The compressor according to any one of claims 1 to 3, wherein the length of the second oil filler groove is shorter than that around the inner peripheral surface of the auxiliary bearing. The compressor according to any one of claims 1 to 4, wherein the compression mechanism is a compression mechanism having three or more cylinders including the cylinder between the main bearing and the sub bearing. The compressor according to any one of claims 1 to 4, and the compressor.
With a heat sink
Inflator and
With a heat absorber,
A refrigerating cycle device including the compressor, the radiator, the expansion device, and a refrigerant pipe for connecting the heat absorber and circulating the refrigerant.

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