WO2022080179A1

WO2022080179A1 - Compressor and refrigeration cycle apparatus

Info

Publication number: WO2022080179A1
Application number: PCT/JP2021/036763
Authority: WO
Inventors: 勝吾志田; 卓也平山
Original assignee: 東芝キヤリア株式会社
Priority date: 2020-10-14
Filing date: 2021-10-05
Publication date: 2022-04-21
Also published as: CN115943259A; JPWO2022080179A1

Abstract

Provided are a compressor and a refrigeration cycle apparatus having a lubricating structure capable of stably lubricating a sliding portion between a rotary shaft and each bearing.　A compression mechanism portion (13) of a compressor (2) is provided with: a main bearing (16) rotatably supporting a main shaft portion (15a) of a rotary shaft (15); a sub-bearing (17) rotatably supporting a sub-shaft portion (15b) of the rotary shaft (15); three or more annular cylinders (42) stacked on each other and arranged between the main bearing (16) and the sub-bearing (17); vanes (44) each arranged in each of the cylinders (42) and reciprocating in the radial direction of the cylinder (42); and a plurality of partition plates (45A, 45B) serving as partitions between the cylinders (42, 42) adjacent to each other. The partition plate (45B), which is one of the plurality of partition plates (45A, 45B), includes an intermediate bearing (45Bb) rotatably supporting an intermediate shaft portion (15A) of the rotary shaft (15). The intermediate bearing (45Bb) has a first oil supply groove (81) provided in an inner peripheral surface (45Bc), along which the rotary shaft (15) is to be inserted, and extending toward a second cylinder (42B).

Description

Compressor and refrigeration cycle equipment

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

A compressor housing having a vertically placed cylindrical airtight container in which lubricating oil is stored, a compression mechanism unit arranged at the bottom of the airtight container, and an electric motor unit arranged at the top of the airtight container to drive the compression mechanism unit. A rotary compressor is known to be equipped with a motor and a rotating shaft. The rotation axis is provided along a center line extending vertically in the compressor housing. The compression mechanism portion is connected to the motor via a rotating shaft.

The compression mechanism 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 provided on the upper end plate, and an auxiliary bearing provided on the lower end plate. , Is equipped. Further, the compression mechanism portion includes an annular piston that is fitted to the eccentric portion of the rotating shaft and revolves along the inner peripheral surface of the cylinder. The piston is located in the cylinder chamber inside the cylinder. The main shaft portion of the rotating shaft is rotatably supported by the main bearing, and the sub-shaft portion of the rotating shaft is rotatably supported by the sub-bearing.

The inner peripheral surface of the shaft hole of the auxiliary bearing is provided with a spiral lubrication groove that supplies lubricating oil from the lower end to the upper end of the shaft hole. 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.

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 by the rotation of the rotating shaft. The sucked-up lubricating oil lubricates the sliding portion between the rotating shaft and the auxiliary bearing.

Japanese Unexamined Patent Publication No. 2019-183768

In the conventional rotary compressor, a gas load (compression load) is generated during compression. The direction in which the peak of the gas load occurs is determined, for example, with respect to the eccentric direction of the eccentric portion of the rotating shaft. In particular, in the case of a multi-cylinder rotary compressor, the eccentric directions of the plurality of eccentric portions of the rotating shaft face different directions depending on the number of cylinders. Specifically, the eccentric directions of the three eccentric portions of the rotation shaft of the three-cylinder rotary compressor are directed to three directions at every 120 °, for example. Therefore, there are three peak positions of the gas load of the three-cylinder rotary compressor on the outer peripheral surface of the rotating shaft.

In addition, the multi-cylinder rotary compressor is equipped with a partition plate between the main bearing and the auxiliary bearing. This partition plate functions as an intermediate bearing that rotatably supports the eccentric portion of the rotating shaft. Therefore, for example, the position where the gas load peaks in the intermediate bearing of the three-cylinder rotary compressor is determined by the position in each of the three compression chambers.

Furthermore, in the case of a multi-cylinder rotary compressor that has a refueling groove in the sliding part between the intermediate bearing and the rotating shaft, the position where the gas load peaks overlaps with the part where the refueling groove is arranged due to the rotation of the rotating shaft. In this case, it becomes difficult to form an oil film of the lubricating oil supplied through the lubrication groove, and the lubrication reliability is lowered. Therefore, in a multi-cylinder rotary compressor, it is difficult to lubricate the sliding portion between the intermediate bearing and the rotating shaft.

Furthermore, the multi-cylinder rotary compressor may be equipped with a balancer provided in a portion protruding from the auxiliary bearing of the rotating shaft in order to reduce the imbalance during the compression operation of the compression mechanism. However, the auxiliary bearing receives a load due to the centrifugal force of the balancer over the entire circumference of the inner peripheral surface due to the rotation of the rotating shaft. Therefore, when the oil supply groove is provided on the inner peripheral surface of the auxiliary bearing, the load due to this centrifugal force may overlap with the oil supply groove, and it becomes difficult to form an oil film. Therefore, in a multi-cylinder rotary compressor, it is difficult to lubricate the sliding portion between the rotating shaft and the auxiliary bearing by the oil supply groove provided on the inner peripheral surface of the auxiliary bearing.

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 the sliding portion between the rotating shaft and the 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, a compression mechanism unit for compressing the refrigerant introduced into the closed container, and a compression mechanism unit. An electric motor unit having a main shaft portion, an intermediate shaft portion, and a sub-shaft portion, connected to a rotating shaft provided along the center line via the rotating shaft, and driving the compression mechanism portion. A main bearing that rotatably supports the main shaft portion and a sub-shaft that rotatably supports the main shaft portion. An auxiliary bearing that rotatably supports the portion, an annular cylinder arranged by stacking three or more between the main bearing and the auxiliary bearing, and an annular cylinder arranged in each of the cylinders and reciprocating in the radial direction of the cylinder. An intermediate that includes a moving vane and a plurality of partition plates that partition between adjacent cylinders, and one of the plurality of partition plates functions as a bearing that rotatably supports the intermediate shaft portion. The intermediate bearing includes a bearing, and the intermediate bearing has a first oil supply groove extending in the vertical direction and allowing the lubricating oil to flow on an inner peripheral surface through which the rotating shaft is inserted.

The vanes of the compressor according to the embodiment of the present invention are arranged in a straight line in the vertical direction, and the rotary shaft is provided on the outer peripheral surface of the sub-shaft portion and extends in the vertical direction to flow the lubricating oil. It is preferable to have a second lubrication groove and a protruding portion protruding from the auxiliary bearing, and the compression mechanism portion is provided with a balancer provided in the protruding portion.

The compression mechanism portion of the compressor according to the embodiment of the present invention sequentially drives the refrigerant from the cylinders arranged above to the cylinders arranged below among the cylinders stacked in the vertical direction. It is preferable to compress it.

Further, the refrigerating 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.

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

An explanatory diagram schematically showing a refrigerating cycle apparatus and a compressor according to an embodiment. The cross-sectional view which shows the compression mechanism part of the compressor which concerns on embodiment. The cross-sectional view which shows the intermediate bearing of the compressor which concerns on embodiment. The cross-sectional view which shows the auxiliary bearing of the compressor which concerns on embodiment.

An embodiment of the compressor and the refrigeration cycle apparatus according to the present invention will be described with reference to FIGS. 1 to 4. In the plurality of drawings, the same or corresponding configurations are designated by the same reference numerals.

FIG. 1 is a schematic diagram of a refrigeration cycle device and a compressor according to an embodiment of the present invention. In FIG. 1, the compressor is shown in a vertical cross section.

FIG. 2 is a cross-sectional view of the compression mechanism portion of the compressor according to the embodiment of the present invention as viewed from below.

As shown in FIG. 1, the refrigerating cycle device 1 according to the present embodiment is, for example, an air conditioner. The refrigeration cycle device 1 includes a closed-type rotary compressor 2 (hereinafter, simply referred to as “compressor 2”), a radiator 3 (radiator), an expansion device 5, a heat absorber 6 (heat absorber), and the like. It includes an accumulator 7 and a refrigerant pipe 8. 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 referred to as 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 to the radiator 3 through the refrigerant pipe 8.

The compressor 2 includes a cylindrical airtight container 11 placed vertically, an open winding type motor unit 12 (hereinafter, simply referred to as “motor unit 12”) housed in the upper half of the airtight container 11. The compression mechanism unit 13 housed in the lower half of the closed container 11, the rotary shaft 15 that transmits the rotational driving force of the motor unit 12 to the compression mechanism unit 13, and the main bearing 16 that rotatably supports the rotary shaft 15. A sub-bearing 17 that rotatably supports the rotary shaft 15 in cooperation with the main bearing 16, and a refueling mechanism 22 that refuels the lubricating oil 21 (refrigerator oil) stored in the closed container 11 to the compression mechanism unit 13. And have.

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, on the end plate 11b on the upper side of the closed container 11, 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 unit 12 from the outside to the inside of the closed container 11 are provided. It is provided. 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 motor unit 12 generates a driving force for rotating the compression mechanism unit 13. The electric motor unit 12 is arranged above the compression mechanism unit 13. The electric motor unit 12 is composed of a tubular stator 31 fixed to the inner surface of the closed container 11, a rotor 32 arranged inside the stator 31 to generate a rotational driving force of the compression mechanism unit 13, and a stator 31. It is provided with a plurality of outlet wires 33 that are drawn out and 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 accommodated in the magnet accommodating hole (not shown). 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 sealed terminals 25 and 26, and are so-called lead wires. A plurality of outlet wires 33 are wired according to the type of the motor unit 12. In this embodiment, six outlet wires 33 are wired.

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

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

The spindle portion 15a located in the middle portion of the rotating shaft 15 connects the motor portion 12 and the compression mechanism portion 13, and is rotatably supported by the main bearing 16. The sub-shaft portion 15b located at the lower end portion of the rotating shaft 15 is rotatably supported by the sub-bearing 17. The main bearing 16 and the auxiliary bearing 17 are also a part of the compression mechanism portion 13. In other words, the rotating shaft 15 is arranged so as to penetrate the compression mechanism portion 13.

Further, the rotary shaft 15 is provided with a plurality, for example, three eccentric portions 36 between the spindle portion 15a supported by the main bearing 16 and the sub-shaft portion 15b supported by the sub-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 at a protruding portion of the rotating shaft 15 protruding from the auxiliary bearing 17.

The compression mechanism unit 13 compresses the refrigerant introduced into the closed container 11. When the motor unit 12 rotates and drives the rotary shaft 15, the compression mechanism unit 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 unit 13 is a multi-cylinder type, for example, a 3-cylinder rotary type. As shown in FIGS. 1 and 2, the compression mechanism unit 13 includes a plurality of cylinders 42 each having a circular cylinder chamber 41, a plurality of annular rollers 43 arranged in each cylinder chamber 41, and each of them. The cylinder 42 includes vanes 44 arranged in the radial direction of the cylinder chamber 41. The roller 43 is fitted to the eccentric portion 36 of the rotating shaft 15.

The rotation shaft 15 is assumed to rotate counterclockwise in the plan view of the compressor 2. That is, when the rotating shaft 15 is rotating, the eccentric portion 36 shown in FIG. 2 viewed from below the rotating shaft 15 is counterclockwise indicated by a solid arrow R about the rotation center line C (see FIG. 1). Rotate around.

The roller 43 rotates eccentrically with respect to the central axis of the cylinder 42 and the rotating shaft 15 while being in contact with the inner wall of the cylinder 42 by the rotation of the rotating shaft 15 joined to the motor portion 12 (indicated by the solid line arrow R in FIG. 2). do. At this time, the direction indicated by the solid arrow in FIG. 2 is the eccentric direction X of the roller 43. The roller 43 is also called a rolling piston. The vanes 44 are arranged in a straight line in the vertical direction in the compression mechanism unit 13. In other words, the vanes 44 are arranged at substantially the same position in the circumferential direction of the cylinder 42. Further, the vane 44 reciprocates in the radial direction of the cylinder chamber 41 while being pressed against the roller 43 by a vane spring (not shown). Therefore, the vane 44 divides the space between the cylinder 42 and the roller 43 into two in this radial direction.

Here, the cylinder 42 closest to the motor unit 12 is the first cylinder 42A, the cylinder 42 farthest from the motor unit 12 is the third cylinder 42C, and the cylinder is arranged between the first cylinder 42A and the third cylinder 42C. Let 42 be the second cylinder 42B. In the following, the first cylinder 42A, the second cylinder 42B, and the third cylinder 42C may be collectively referred to as a cylinder 42.

The compression mechanism portion 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 and the third of the second cylinder 42B. It includes a second partition plate 45B that closes the upper surface of the cylinder 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 discharges 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 unit 13. The port (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) connecting 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 (a discharge port () 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 unit 13. (Not shown) is opened, and the compressed refrigerant is discharged 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. Although details will be described later, in the case of the present embodiment, the second partition plate 45B includes a partition plate portion 45Ba and an intermediate bearing 45Bb that functions as a bearing that rotatably supports the intermediate shaft portion 15A of the rotating shaft 15. Is configured to include.

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 discharges 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 unit 13. The port (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.

In such a compression step, on the outer peripheral surface of each eccentric portion 36, the maximum compression load that maximizes the compression load received from the gas is approximately orthogonal to the eccentric direction X, specifically, from the eccentric direction X. It occurs in the direction advanced by 90 degrees in the direction of rotation. Therefore, on the outer peripheral surface of the eccentric portion 36 in each cylinder 42, the maximum compression load is generated in the range indicated by the solid line arrow P1 in FIG.

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 by welding at a plurality of places, for example, to the frame 58 fixed by spot welding with a fastening member 59 such as a bolt. That is, the frame 58 supports the rotor 32 of the motor unit 12, the compression mechanism unit 13, and the rotating shaft 15 to the closed container 11 via the first cylinder 42A. The center of gravity of the rotor 32 of the motor unit 12, the compression mechanism unit 13, and the airtight container 11 of the rotating shaft 15 in the height direction 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 do.

The balancer 38 is housed in the 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 portion 13 during the compression operation.

By the way, when a balancer is provided at the upper end of the rotating shaft 15 protruding above 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. Therefore, compared to this distance, when the balancer 38 is provided at the lower end of the rotating shaft 15 protruding from the auxiliary bearing 17 as in the present embodiment, the bearing supporting the balancer 38 and the rotating shaft 15 (auxiliary bearing 17). The distance to and from 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 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 may be 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 portion 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 portion 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 portion 13.

Here, the "sliding portion of the compression mechanism portion 13" is, for example, a gap between the eccentric portion 36 and the roller 43, a gap between the main bearing 16 and the rotary shaft 15, and a gap between the intermediate bearing 45Bb and the rotary shaft 15. It also includes a gap between the auxiliary bearing 17 and the rotating shaft 15.

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 portion of the rotary shaft 15 and extends toward the upper end portion 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. The rotor 71 rotates together with the rotary shaft 15 to continuously pump the lubricating oil 21 from the opening at the lower end of the rotary shaft 15 into the pump arrangement hole 69 of the rotary shaft 15.

The pump 65 is not limited to the rotor 71 as long as it is provided in the closed container 11 and can continuously supply the lubricating oil 21 into the pump arrangement hole 69 of the rotary shaft 15. The pump 65 may be a turbo pump driven by utilizing the rotational driving force of the rotary 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 up into the pump arrangement hole 69 of the rotary shaft 15 by the pump 65 that is rotationally integrated with the rotary shaft 15 to the sliding portion of the compression mechanism portion 13 for lubrication.

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 housed in the first cylinder 42A and the roller 43, and the pump arrangement hole 69. The second cylinder refueling hole 73B for refueling the gap between the eccentric portion 36 and the roller 43 in which the lubricating oil 21 is housed in the second cylinder 42B, and the lubricating oil 21 in the pump arrangement hole 69 are housed 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 rotary shaft 15 and the lubricating oil 21 in the pump arrangement hole 69 are used as 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 between the rotary shaft 15 and the intermediate bearing 45Bb will be described.

FIG. 3 is an enlarged view showing a cross section of an intermediate bearing of a compressor according to an embodiment of the present invention in the field of view of AA in FIG.

As shown in FIGS. 1 and 3, in the compression mechanism portion 13, the intermediate bearing 45Bb faces the inner peripheral surface 45Bc through which the rotating shaft 15 is inserted in the vertical direction, that is, from the second cylinder 42B side to the third cylinder 42C side. It has a first lubrication groove 81 extending through the cylinder.

The first refueling groove 81 is recessed from the inner peripheral surface 45Bc toward the outer peripheral surface side of the intermediate bearing 45Bb, communicates with the second cylinder refueling hole 73B on the upper side, and reaches the second cylinder 42B. Further, the first refueling groove 81 reaches the partition plate portion 45Ba on the lower side and communicates with the third cylinder refueling hole 73C via the partition plate portion 45Ba. The lubricating oil 21 is supplied to the sliding portion between the intermediate shaft portion 15A of the rotary shaft 15 and the intermediate bearing 45Bb through the first lubrication groove 81.

Specifically, in the lubrication structure of the intermediate shaft portion 15A of the rotary shaft 15 and the intermediate bearing 45Bb having such a configuration, the pump 65 is pumped into the pump arrangement hole 69 of the rotary shaft 15 by the pump 65 which is integrally rotated with the rotary shaft 15. The lubricating oil 21 flowing out from the second cylinder oil supply hole 73B and the third cylinder oil supply hole 73C flows into the first oil supply groove 81 of the intermediate shaft portion 15A to lubricate the gap between the intermediate shaft portion 15A and the intermediate bearing 45Bb. ..

Here, the load generated when the gas is compressed by the cylinder 42 will be described. The compression mechanism unit 13 compresses the gas in the space partitioned by the cylinder 42, the roller 43, and the vane 44. The maximum compressive load generated in the cylinder 42 occurs at a position corresponding to the position of the vane 44. Specifically, the maximum compression load generated between each cylinder 42 and the eccentric portion 36 is generated at a position on the counter-rotation direction side from the position of the vane 44. Further, the vanes 44 of the three cylinders 42 are arranged on the same straight line in the vertical direction. Therefore, the maximum compression load generated in each cylinder 42 is generated on the same straight line in the vertical direction of the compression mechanism unit 13, that is, is generated in the same direction range of the cylinder 42.

As a reaction force of the maximum compression load of the cylinder 42, a maximum load is generated on the inner peripheral surface 45Bc of the intermediate bearing 45Bb. The maximum load of the inner peripheral surface 45Bc of the intermediate bearing 45Bb is, for example, the oil passage 66 from the position facing the position where the maximum compression load of the cylinder 42 is generated (solid arrow P1 in FIG. 2), that is, the position where the maximum compression load of the cylinder 42 is generated. It occurs at a position separated by (solid arrow P3 in FIG. 3). Further, as a reaction of the maximum load on the inner peripheral surface 45Bc of the intermediate bearing 45Bb, the maximum load is also generated on the outer peripheral surface of the intermediate shaft portion 15A of the rotating shaft 15. The maximum load on the outer peripheral surface of the intermediate shaft portion 15A is generated at a position (solid line arrow P2 in FIG. 3) that overlaps with the maximum load on the inner peripheral surface 45Bc of the intermediate bearing 45Bb.

When the gas is compressed by the cylinder 42, the rotating shaft 15 is rotating. Therefore, as shown in FIG. 3 when viewed from below the rotating shaft 15, the outer peripheral surface of the intermediate shaft portion 15A of the rotating shaft 15 is inside the intermediate bearings 45Bb facing the rotating center line C (see FIG. 1). It moves so as to cross the peripheral surface 45Bc counterclockwise indicated by the solid line arrow R. Further, in the compressor 2 of the present embodiment, since the compression mechanism portion 13 is a rotary type having three cylinders, the eccentric direction X of the rotating shaft 15 is directed at equal intervals at an angle corresponding to the number of cylinders (that is, 120 °). Has been done. As a result, the maximum load on the outer peripheral surface of the intermediate shaft portion 15A is the position corresponding to the eccentric portion 36 of each of the first cylinder 42A, the second cylinder 42B, and the third cylinder 42C (three points indicated by arrows P2 in FIG. 3). ) Occurs one after another.

Therefore, if the first lubrication groove 81 is provided on the outer peripheral surface of the intermediate shaft portion 15A, the first lubrication groove 81 becomes a solid line on the inner peripheral surface 45Bc of the intermediate bearing 45Bb which becomes the maximum load as the rotating shaft 15 rotates. Cross the range of arrow P3. That is, if the first lubrication groove 81 is provided on the outer peripheral surface of the intermediate shaft portion 15A, the first lubrication groove 81 is susceptible to a compression load. Further, when the compression mechanism portion 13 is a multi-cylinder rotary type, the range in which the maximum load is received on the outer peripheral surface of the intermediate shaft portion 15A (arrow P2 in FIG. 3) increases, and the first lubrication groove 81 receives a further compression load. Cheap. When the first lubrication groove 81 is arranged on the outer peripheral surface of the intermediate shaft portion 15A in this way, the lubrication reliability of the sliding portion between the rotating shaft 15 and the intermediate bearing 45Bb is lowered.

Therefore, in the present embodiment, the first lubrication groove 81 is arranged outside the range of the inner peripheral surface 45Bc of the intermediate bearing 45Bb, more specifically, the solid line arrow P3 at which the compression load by each cylinder 42 is maximized. ..

The lubrication structure between the rotating shaft 15 and the intermediate bearing 45Bb includes 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 first oil supply groove 81 and the oil passage 66 on the upstream side thereof. Rotation is performed by appropriately setting at least one of the cross-sectional area of the second cylinder refueling hole 73B to be connected and the cross-sectional area of the third cylinder refueling hole 73C connecting the first refueling groove 81 and the oil passage 66 on the downstream side thereof. The amount of oil supplied at the sliding portion between the shaft 15 and the intermediate bearing 45Bb is adjusted.

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

FIG. 4 is a cross-sectional view showing the auxiliary bearing of the compressor according to the embodiment of the present invention in the BB field of view in FIG.

As shown in FIG. 4, the outer peripheral surface of the sub-shaft portion 15b supported by the sub-bearing 17 of the rotating shaft 15 (see FIG. 1) of the compressor 2 according to the present embodiment has a rotation direction of the rotating shaft 15 on the outer peripheral surface. A second refueling groove 82 extending in the opposite direction and toward the third cylinder 42C is provided. That is, the second lubrication groove 82 faces the inner peripheral surface 78 of the auxiliary bearing 17. The second refueling groove 82 is recessed toward the rotation center line C of the rotary 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 second lubrication groove 82 extends spirally along the outer peripheral surface of the sub-shaft portion 15b. In the compressor 2 that rotates the rotating shaft 15 counterclockwise in a plan view, the second lubrication groove 82 draws a clockwise spiral from the connection portion with the auxiliary bearing lubrication hole 75B toward the third cylinder 42C. .. The lubricating oil 21 is supplied to the sliding portion between the sub-shaft portion 15b of the rotary shaft 15 and the sub-bearing 17 through the second lubrication groove 82.

Here, with the rotation of the rotating shaft 15, the sub-shaft portion 15b receives the maximum compression load within the range of the solid line arrow P4 shown in FIG. Further, since the auxiliary bearing 17 receives only the compression load from the third cylinder 42C, the position where the compression load becomes maximum receives the maximum compression load within the range of the solid line arrow P5 shown in FIG. In addition, the auxiliary bearing 17 is loaded over the entire circumference of the inner peripheral surface 78 due to the centrifugal force of the balancer 38. Therefore, when the oil supply groove is provided on the auxiliary bearing 17 side (that is, the inner peripheral surface 78 of the auxiliary bearing 17), a load due to centrifugal force acts on the oil supply groove, and it becomes difficult to form an oil film on the sliding portion.

Therefore, in the compressor 2 of the present embodiment, the second oil supply groove 82 is provided on the outer peripheral surface of the sub-shaft portion 15b. In the range of the solid line arrow P5 of the auxiliary bearing 17, the compression load becomes the maximum value when the P4 portion which is the maximum compression load in the auxiliary shaft portion 15b of the rotary shaft 15 passes, and when the second lubrication groove 82 passes through. The compression load is lower than the maximum value. That is, in the range of the solid line arrow P5 of the auxiliary bearing 17, the compression load fluctuates with increasing or decreasing with the rotation of the rotating shaft 15. On the other hand, the inner peripheral surface 78 of the auxiliary bearing 17 passes through the P4 portion, which is the maximum compression load in the auxiliary shaft portion 15b, over the entire circumference. Therefore, it is preferable to provide the second oil supply groove 82 on the outer peripheral surface of the sub-shaft portion 15b that can pass through when the compression load is low in the range of the solid line arrow P5 of the sub-bearing 17.

Further, in such a compression mechanism portion 13, the direction in which the balancer 38 is arranged is determined according to the eccentric direction in which the eccentric portion 36 of the rotating shaft 15 is arranged. Therefore, there are cases where the compression process is performed from the first cylinder 42A located above to the third cylinder 42C sequentially located below, and the compression process is performed from the third cylinder 42C located below to the first cylinder 42A sequentially located upward. The direction in which the centrifugal force generated by the balancer 38 is generated differs depending on the case where the process is performed. In the case of the present embodiment, the former (compression from upper to lower) is in the direction indicated by the solid arrow M1 in FIG. 4, and the latter (compression from lower to upper) is in the direction indicated by the solid arrow M2 in FIG. Then, the sub-shaft portion 15b rotates with the driving of the rotating shaft 15 without changing the relative positions of the position of the second oil supply groove 82 and the directions M1 and M2 of the centrifugal force. At this time, the closer the position where the compression load is maximized to the direction of the centrifugal force, the more the second lubrication groove 82 is provided in the direction opposite to the position, so that the influence of these compression load and the centrifugal force can be avoided. It is in. Therefore, in the compression mechanism unit 13, it is preferable to perform the compression step from the first cylinder 42A located above to the third cylinder 42C sequentially located below.

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 made to flow into the second lubrication groove 82 of the rotating shaft 15. The lubricating oil 21 that has flowed into the second lubrication groove 82 of the rotary shaft 15 flows from the auxiliary bearing lubrication hole 75B toward the third cylinder 42C as the rotary shaft 15 rotates, and the gap between the rotary shaft 15 and the auxiliary bearing 17 is reached. Lubricate.

The lubrication structure of the rotary shaft 15 and the auxiliary bearing 17 includes the flow path cross-sectional area of the second lubrication groove 82, the flow path length of the second lubrication groove 82, and the second lubrication groove 82 with respect to the rotation center line C of the rotary shaft 15. By appropriately setting at least one of the cross-sectional areas of the auxiliary bearing oil supply hole 75B that is tilted and connects the second oil supply groove 82 and the oil passage 66 on the upstream side thereof, the sliding portion between the rotary shaft 15 and the auxiliary bearing 17 The amount of refueling in is adjusted.

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

Further, the length of the second refueling groove 82 according to the present embodiment is shorter than that around the outer peripheral surface of the rotating shaft 15. That is, the second lubrication groove 82 does not go around the rotating shaft 15 once. Therefore, the compressor 2 and the refrigeration cycle device 1 can easily process the second refueling groove 82. The lubricating oil 21 pumped by the pump 65 is constantly supplied to the second oil supply groove 82 of the rotary shaft 15.

The second refueling groove 82 is open to the inside of the roller 43 of the third cylinder 42C. That is, the second lubrication groove 82 causes the lubricating oil 21 to flow out to the inside of the roller 43 of the third cylinder 42C while suppressing the amount of the lubricating oil 21 flowing out from the opening on the lower end side of the auxiliary bearing 17.

As described above, the compressor 2 and the refrigerating cycle device 1 according to the present embodiment are provided on one of the plurality of

partition plates

45A and 45B, and rotate the intermediate shaft portion 15A of the rotating shaft 15. It has an intermediate bearing 45Bb that functions as a bearing that can support it. The intermediate bearing 45Bb has a first oil supply groove 81 extending in the vertical direction and allowing the lubricating oil 21 to flow through the inner peripheral surface 45Bc through which the intermediate shaft portion 15A of the rotating shaft 15 is inserted.

Therefore, the compressor 2 and the refrigerating cycle device 1 do not overlap with the portion (solid line arrows P2, P3) where the maximum value of the compression load is obtained by the rotation of the rotating shaft 15 as in the conventional compressor, and the first lubrication groove 81 Is provided. The lubricating oil 21 flowing into the first lubrication groove 81 can reliably lubricate the entire gap between the rotating shaft 15 and the intermediate bearing 45Bb.

Further, the compressor 2 and the refrigerating cycle device 1 according to the present embodiment are provided with vanes provided on the plurality of cylinders 42 and arranged in a straight line in the vertical direction, and the outer periphery of the sub-shaft portion 15b of the rotating shaft 15. It is provided with a second lubrication groove 82 provided on the surface and extending in the vertical direction to circulate the lubricating oil 21, and a balancer 38 provided on the protruding portion of the rotating shaft 15 protruding from the auxiliary bearing 17.

The compressor 2 and the refrigerating cycle device 1 suppress the bending of the rotating shaft 15 by arranging the balancer 38 in the protruding portion of the rotating shaft 15 protruding from the auxiliary bearing 17, that is, the second discharge muffler 56. The imbalance of the rotating body of the compression mechanism unit 13 can be easily adjusted.

Further, by providing the second oil supply groove 82 on the outer peripheral surface of the sub-shaft portion 15b that can pass when the compression load is low in the range of the solid line arrow P5 of the sub-bearing 17, the sub-shaft portion 15b has a constant interval with the centrifugal force. Since the rotation is maintained, it is possible to prevent the second lubrication groove 82 from overlapping with the position where the maximum value of the compression load is reached. Therefore, the lubricating oil 21 flowing into the second lubrication groove 82 can form an oil film in the gap between the rotary shaft 15 and the auxiliary bearing 17, and the entire gap can be reliably lubricated.

In this way, the compressor 2 and the refrigerating cycle device 1 ensure the entire gap between the rotary shaft 15 and each bearing (intermediate bearing 45Bb, auxiliary bearing 17) by the first lubrication groove 81 and the second lubrication groove 82. Can be lubricated to.

Further, the compression mechanism unit 13 can sequentially drive the first cylinder 42A arranged above the cylinders 42 stacked in the vertical direction to the third cylinder 42C arranged below to compress the refrigerant. preferable. The sub-shaft portion 15b rotates with the driving of the rotating shaft 15 without changing the relative positions of the position of the second oil supply groove 82 and the directions M1 and M2 of the centrifugal force. At this time, the closer the position where the compression load is maximized to the direction of the centrifugal force, the more the second oil supply groove 82 is provided in the direction opposite to the position, so that the influence of the compression load and the centrifugal force can be avoided.

Further, the compressor 2 and the refrigeration cycle device 1 include a compression mechanism unit 13 having three or more cylinders. Therefore, the compressor 2 and the refrigerating cycle device 1 are intermediate with the rotating shaft 15 even in the compression mechanism unit 13 having three or more cylinders, in which the adjustment of the imbalance of the rotating body of the compression mechanism unit 13 becomes more serious. The gap between the bearing 45Bb and the auxiliary bearing 17 can be lubricated.

Therefore, according to the refrigerating 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 portions of the rotating shaft 15 and the intermediate bearing 45Bb and the auxiliary bearing 17. can.

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 ... body Part, 11b ... End plate, 11c ... End plate, 12 ... Open winding type electric motor part, 13 ... Compression mechanism part, 15 ... Rotating shaft, 15a ... Main shaft part, 15b ... Sub-shaft part, 15A ... Intermediate shaft part, 16 ... Main bearing , 17 ... auxiliary bearing, 21 ... lubricating oil, 22 ... lubrication mechanism, 25, 26 ... sealed terminal, 27, 28 ... terminal block, 29 ... power line, 31 ... stator, 32 ... rotor, 33 ... outlet wire, 35 ... Rotor core, 36 ... Eccentric part, 38 ... Balancer, 38a ... Through hole, 41 ... Cylinder chamber, 42 ... Cylinder, 42A ... First cylinder, 42B ... Second cylinder, 42C ... Third cylinder, 43 ... Roller , 44 ... vane, 45A ... first partition plate, 45B ... second partition plate, 45Ba ... partition plate part, 45Bb ... intermediate bearing, 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 ... 1st suction pipe, 61B ... 2nd suction pipe, 61C ... 3rd suction pipe, 65 ... pump, 66 ... oil passage, 68 ... refueling mechanism insertion hole, 69 ... pump placement hole, 71 ... rotor, 73A ... 1st cylinder refueling hole, 73B ... 2nd cylinder refueling hole, 73C ... 3rd cylinder refueling hole, 75A ... main bearing refueling hole, 75B ... sub-bearing refueling hole, 78 ... sub-bearing inner peripheral surface, 81 ... One refueling groove, 82 ... Second refueling groove.

Claims

A cylindrical closed container with a center line extending in the vertical direction,
A compression mechanism that compresses the refrigerant introduced into the closed container,
A rotating shaft having a main shaft portion, an intermediate shaft portion, and a sub shaft portion and provided along the center line,
An electric motor unit that is connected to the compression mechanism unit via the rotation shaft and drives the compression mechanism unit.
A lubrication mechanism unit for supplying the lubricating oil stored in the airtight container to the compression mechanism unit is provided.
The compression mechanism unit
A main bearing that rotatably supports the spindle and
A sub-bearing that rotatably supports the sub-shaft and
An annular cylinder arranged by stacking three or more between the main bearing and the auxiliary bearing,
A vane placed in each cylinder and reciprocating in the radial direction of the cylinder,
It is equipped with a plurality of partition plates that partition between adjacent cylinders.
One of the plurality of partition plates includes an intermediate bearing that functions as a bearing that rotatably supports the intermediate shaft portion.
The intermediate bearing is a compressor having a first lubrication groove extending in the vertical direction and allowing the lubricating oil to flow on the inner peripheral surface through which the rotating shaft is inserted.
The vanes are arranged in a straight line in the vertical direction.
The rotary shaft has a second lubrication groove provided on the outer peripheral surface of the sub-shaft portion and extending in the vertical direction to circulate the lubricating oil, and a protruding portion protruding from the sub-bearing.
The compression mechanism portion includes a balancer provided on the protruding portion, and the compression mechanism portion includes a balancer.
The compressor according to claim 1.
The compressor according to claim 2, wherein the compression mechanism unit is sequentially driven from the cylinder arranged above the cylinders stacked in the vertical direction to the cylinders arranged below to compress the refrigerant. ..
The compressor according to any one of claims 1 to 3 and
With a radiator,
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.