Compressor and refrigeration cycle device

Abstract

The present invention relates to a compressor and a refrigeration cycle device, which can reduce the supply amount of lubricating oil to a space formed by a sub-bearing and a sub-muffler mounted to the sub-bearing, and improve performance and reliability. A rotary compressor (2) has a through passage (91) that connects an accumulation space (90) with an inside of a hermetic container (11), the accumulation space (90) being surrounded by a lower surface of an eccentric portion (36), an inner peripheral surface of a roller (43), and an upper surface of a sub-bearing (17), and accumulates lubricating oil (21) supplied to a compression mechanism portion (13) by an oil supply mechanism portion (22).

Description

TECHNICAL FIELD

[0001] The present application relates to a compressor and a refrigeration cycle apparatus. BACKGROUND

[0002] A rotary compressor is known that includes a compressor housing having a vertically disposed cylindrical closed container that stores lubricating oil, a compression mechanism portion disposed in a lower portion of the closed container, a motor as a motor portion that is disposed in an upper portion of the closed container and drives the compression mechanism portion, and a rotary shaft. The rotary shaft is disposed along a center line that extends in a vertical direction of the compressor housing. The compression mechanism portion is coupled to the motor via the rotary shaft.

[0003] The compression mechanism portion includes a ring-shaped cylinder, an upper end plate that closes an upper side of the cylinder, a lower end plate that closes a lower side of the cylinder, a main bearing provided to the upper end plate, and a sub bearing provided to the lower end plate. Further, the compression mechanism portion includes a ring-shaped piston that is fitted to an eccentric portion of the rotary shaft and revolves along an inner peripheral surface of the cylinder. The piston is disposed in a cylinder chamber inside the cylinder. A main shaft portion of the rotary shaft is rotatably supported by the main bearing, and a sub shaft portion of the rotary shaft is rotatably supported by the sub bearing.

[0004] A spiral oil supply groove that supplies lubricating oil from a lower end to an upper end of a shaft hole of the sub bearing is provided to an inner peripheral surface of the shaft hole. The oil supply groove is inclined with respect to a rotation direction of the rotary shaft and extends from the lower end toward the upper end in the rotation direction of the rotary shaft.

[0005] The conventional rotary compressor is configured to suck up the lubricating oil stored in the compressor housing along the oil supply groove that extends from the lower end to the upper end of the shaft hole of the sub bearing by rotation of the rotary shaft. The sucked-up lubricating oil lubricates sliding portions of the rotary shaft and the sub bearing.

[0006] PRIOR ART DOCUMENTS

[0007] PATENT DOCUMENTS

[0008] Patent Document 1: Japanese Patent Application Publication No. 2019-183768 SUMMARY

[0009] PROBLEMS TO BE SOLVED BY THE INVENTION

[0010] A multi-cylinder type rotary compressor is known that includes a main muffler that covers the main bearing and a sub muffler that covers the sub bearing. This multi-cylinder type rotary compressor includes a first cylinder that discharges refrigerant compressed in a first cylinder chamber to the inside of the main muffler and a second cylinder that discharges refrigerant compressed in a second cylinder chamber to the inside of the sub muffler. The sub muffler covers a lower end of a shaft hole of the sub bearing. The lower end of the shaft hole of the sub bearing is not immersed in the lubricating oil stored in the compressor housing.

[0011] Further, a balancer that adjusts the unbalance of the rotating body is provided to a protruding portion of the rotating shaft that protrudes from the sub bearing. The balancer is disposed in a space divided by the sub bearing and a sub muffler mounted to the sub bearing.

[0012] However, the sucked lubricating oil moves downward due to gravity. Therefore, sometimes the lubricating oil flows from the gap of the parts into the space divided by the sub bearing and the sub muffler. However, the balancer provided to the rotating shaft is disposed in this space. When the lubricating oil is stored in this space, the lubricating oil sometimes becomes a resistance of the balancer. From the aspect of achieving improvement of the performance and reliability of the compressor, an increase in the resistance of the balancer is not preferable.

[0013] Therefore, an object of the present application is to provide a compressor and a refrigeration cycle device that can reduce the supply amount of lubricating oil to a space divided by a sub bearing and a sub muffler mounted to the sub bearing, and can improve the performance and reliability.

[0014] Means for solving the problem

[0015] To solve the above problem, the compressor of the embodiment of the present application includes: a cylindrical hermetic container having a center line extending in the up-down direction; a compression mechanism housed in the hermetic container and compressing a refrigerant introduced into the hermetic container; a motor having a cylindrical stator fixed to the inner surface of the hermetic container and a rotor disposed inside the stator to generate a rotational driving force of the compression mechanism; and an oil supply mechanism that supplies lubricating oil stored in the hermetic container to the compression mechanism. The compression mechanism includes: a rotating shaft that rotates integrally with the rotor, extends downward from the rotor, and has an eccentric portion; a roller that is fitted to the eccentric portion and has a lower surface positioned lower than the lower surface of the eccentric portion; a sub bearing that rotatably supports the lower end portion of the rotating shaft; a cylinder body having a cylinder chamber that is plugged by the sub bearing and houses the eccentric portion and the roller; a sub muffler that covers the sub bearing and separates a space in which a refrigerant compressed in the cylinder body is discharged; and a balancer that is provided to a protruding portion of the rotating shaft that protrudes from the sub bearing, is housed in the sub muffler, and has an accumulation space in which the lubricating oil supplied to the compression mechanism by the oil supply mechanism is accumulated, the accumulation space being formed at a position surrounded by the lower surface of the eccentric portion, the inner peripheral surface of the roller, and the upper surface of the sub bearing. The sub bearing has a through path that is formed through the sub bearing to communicate the accumulation space with the hermetic container.

[0016] Preferably, the rotating shaft of the compressor of the embodiment of the present application has an oil supply hole that supplies the lubricating oil guided to the compression mechanism portion by the oil supply mechanism portion to the gap between the sub bearing and the cylinder chamber, and an oil supply groove that is provided on the outer circumferential surface of the portion supported by the sub bearing and extends toward the cylinder chamber.

[0017] Preferably, the sub bearing of the compressor of the embodiment of the present application has a recessed step portion that is provided on the upper surface of the sub bearing and communicates with the accumulation space, and the through path connects the step portion and the inside of the closed container.

[0018] Preferably, the sub bearing of the compressor of the embodiment of the present application has an annular groove portion that is provided so as to have a diameter larger than the diameter of the portion that supports the rotating shaft, is open toward the upper portion of the sub bearing, and communicates with the accumulation space, and the through path connects the annular groove portion and the inside of the closed container.

[0019] Further, the refrigeration cycle device of the embodiment of the present application is provided with the compressor, a radiator, an expansion device, a heat absorber, and refrigerant piping that connects the compressor, the radiator, the expansion device, and the heat absorber and makes the refrigerant flow.

[0020] Effects of the Invention

[0021] According to the present application, it is possible to provide a compressor and a refrigeration cycle device that can reduce the amount of lubricating oil supplied to the space divided by the sub bearing and the sub muffler mounted to the sub bearing, and can improve performance and reliability. BRIEF DESCRIPTION OF DRAWINGS

[0022] Figure 1 is a schematic view of a refrigeration cycle device and a compressor of an embodiment of the present application.

[0023] Figure 2 is an enlarged view of a longitudinal sectional view of a compressor of the first embodiment of the present application.

[0024] Figure 3 is a longitudinal sectional view of a sub bearing of a compressor of the first embodiment of the present application.

[0025] Figure 4 is a transverse sectional view of a sub bearing of a compressor of the first embodiment of the present application.

[0026] Figure 5 is an enlarged view of a longitudinal sectional view of a compressor of the first embodiment of the present application.

[0027] Figure 6 is a longitudinal sectional view of a sub bearing of a compressor of the second embodiment of the present application. DETAILED DESCRIPTION

[0028] Reference Figures 1 to 6 Embodiments of the compressor and the refrigeration cycle apparatus of the present application will be described. In addition, the same reference symbols are used for the same or equivalent constituent elements throughout the drawings.

[0029] (1st Embodiment)

[0030] Figure 1 is a schematic view of the refrigeration cycle apparatus and the compressor of the 1st embodiment of the present application.

[0031] As shown in Figure 1 , the refrigeration cycle apparatus 1 of the present embodiment is, for example, an air conditioner. The refrigeration cycle apparatus 1 is provided with a hermetic rotary compressor 2 (hereinafter, simply referred to as "compressor"), a radiator 3, an expansion device 5, a heat absorber 6, a reservoir 7, and a refrigerant pipe 8. The refrigerant pipe 8 connects the compressor 2, the radiator 3, the expansion device 5, the heat absorber 6, and the reservoir 7 in this order to circulate the refrigerant. The radiator 3 is also referred to as a condenser. The heat absorber 6 is also referred to as an evaporator.

[0032] The compressor 2 sucks in the refrigerant that has passed through the heat absorber 6 through the refrigerant pipe 8 and compresses it, and discharges the high-temperature and high-pressure refrigerant to the radiator 3 through the refrigerant pipe 8.

[0033] The compressor 2 is provided with a vertically disposed cylindrical hermetic container 11, an open-winding type motor portion 12 (hereinafter, simply referred to as "motor portion 12") housed in the upper half portion inside the hermetic container 11, a compression mechanism portion 13 housed in the lower half portion inside the hermetic container 11, a rotating shaft 15 that transmits the rotational driving force of the motor portion 12 to the compression mechanism portion 13, a main bearing 16 that rotatably supports the rotating shaft 15, a sub bearing 17 that rotatably supports the rotating shaft 15 in cooperation with the main bearing 16, and an oil supply mechanism portion 22 that supplies the lubricating oil 21 (refrigerator oil) accumulated inside the hermetic container 11 to the compression mechanism portion 13.

[0034] The center line of the vertically disposed hermetic container 11 extends in the vertical direction. The hermetic container 11 is provided with a cylindrical main body portion 11a that extends in the vertical direction, an end panel 11b that plugs the upper end portion of the main body portion, and an end panel 11c that plugs the lower end portion of the main body portion.

[0035] An exhaust pipe 8a that discharges refrigerant outside the sealed container 11 is connected to an end panel 11b on the upper side of the sealed container 11. The exhaust pipe 8a is connected to the refrigerant pipe 8. Further, a pair of sealed terminals 25, 26 that guide electric power supplied to the motor portion 12 from the outside to the inside of the sealed container 11, and a pair of terminal plates 27, 28 are provided on the end panel 11b on the upper side of the sealed container 11. Each of the terminal plates 27, 28 is provided to each of the sealed terminals 25, 26. A plurality of electric power lines 29 that are electrically connected to each of the sealed terminals 25, 26 to supply electric power are fixed to each of the terminal plates 27, 28. The electric power lines 29 are so-called wires.

[0036] The motor portion 12 generates driving force that rotates the compression mechanism portion 13. The motor portion 12 is disposed at a position higher than the compression mechanism portion 13. The motor portion 12 includes a cylindrical stator 31 fixed to the inner surface of the sealed container 11, a rotor 32 disposed inside the stator 31 and generating rotational driving force of the compression mechanism portion 13, and a plurality of lead wires 33 drawn from the stator 31 and electrically connected to the pair of sealed terminals 25, 26.

[0037] The rotor 32 includes a rotor core 35 having a magnet receiving hole (not shown) and a permanent magnet (not shown) received in the magnet receiving hole. The rotor 32 is fixed to the rotary shaft 15. The rotational center line C of the rotor 32 and the rotary shaft 15 substantially coincides with the center line of the stator 31. Further, the rotational center line C of the rotor 32 and the rotary shaft 15 substantially coincides with the center line of the sealed container 11.

[0038] The plurality of lead wires 33 are electric power lines that supply electric power to the stator 31 through the sealed terminals 25, 26, and are so-called wires. The plurality of lead wires 33 are wired depending on the type of the motor portion 12. In the present embodiment, six lead wires 33 are wired.

[0039] In addition, the motor portion 12 can be a motor portion having a plurality of systems, for example, two systems, in addition to the open winding type.

[0040] The rotary shaft 15 links the motor portion 12 and the compression mechanism portion 13. The rotary shaft 15 transmits rotational driving force generated by the motor portion 12 to the compression mechanism portion 13. The rotary shaft 15 rotates integrally with the rotor 32 and extends downward from the rotor 32.

[0041] The middle portion 15a of the rotary shaft 15 links the motor portion 12 and the compression mechanism portion 13 and is rotatably supported by a main bearing 16. The lower end portion 15b of the rotary shaft 15 is rotatably supported by a sub bearing 17. The main bearing 16 and the sub bearing 17 are also a part of the compression mechanism portion 13. In other words, the rotary shaft 15 penetrates the compression mechanism portion 13.

[0042] Further, the rotating shaft 15 has 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 sub bearing 17.

[0043] A balancer 38 is provided to the protruding portion of the rotating shaft 15 protruding from the sub bearing 17.

[0044] The compression mechanism portion 13 compresses the refrigerant introduced into the closed container 11. The motor portion 12 rotationally drives the rotating shaft 15, whereby the compression mechanism portion 13 sucks in the gaseous refrigerant from the refrigerant pipe 8 to compress it, and discharges the compressed high-temperature and high-pressure refrigerant into the closed container 11.

[0045] The compression mechanism portion 13 is a rotary type having a plurality of, for example, three cylinders. The compression mechanism portion 13 has a plurality of cylinder bodies 42 each having a circular cylinder chamber 41, and a plurality of ring-shaped rollers 43 disposed in each cylinder chamber 41. Alternatively, the compression mechanism portion 13 can be a rotary type having a single cylinder.

[0046] Here, the cylinder body 42 closest to the motor portion 12 is referred to as the first cylinder body 42A, the cylinder body 42 farthest from the motor portion 12 is referred to as the third cylinder body 42C, and the cylinder body 42 disposed between the first cylinder body 42A and the third cylinder body 42C is referred to as the second cylinder body 42B.

[0047] The compression mechanism portion 13 has the main bearing 16 that closes the upper surface of the first cylinder body 42A, the first partition plate 45A that closes the lower surface of the first cylinder body 42A and the upper surface of the second cylinder body 42B, the second partition plate 45B that closes the lower surface of the second cylinder body 42B and the upper surface of the third cylinder body 42C, and the sub bearing 17 that closes the lower surface of the third cylinder body 42C.

[0048] In other words, the upper surface of the first cylinder body 42A is closed by the main bearing 16. The lower surface of the first cylinder body 42A is closed by the first partition plate 45A. The upper surface of the second cylinder body 42B is closed by the first partition plate 45A. The lower surface of the second cylinder body 42B is closed by the second partition plate 45B. The upper surface of the third cylinder body 42C is closed by the second partition plate 45B. The lower surface of the third cylinder body 42C is closed by the sub bearing 17.

[0049] That is, the first cylinder body 42A is sandwiched between the main bearing 16 and the first partition plate 45A. The second cylinder body 42B is sandwiched between the first partition plate 45A and the second partition plate 45B. The third cylinder body 42C is sandwiched between the second partition plate 45B and the sub bearing 17.

[0050] The main bearing 16 and the first partition plate 45A are fixed to the second cylinder block 42B by a fastening member 46 such as a bolt. That is, the main bearing 16 and the first partition plate 45A are fastened to the second cylinder block 42B by the fastening member 46. The main bearing 16 is provided with a first discharge valve mechanism 51A that discharges the refrigerant compressed in the cylinder chamber 41 of the first cylinder block 42A, and a first discharge muffler 52 (main muffler) that covers the first discharge valve mechanism 51A. The first discharge valve mechanism 51A is opened to discharge the compressed refrigerant into the first discharge muffler 52 when the pressure difference between the pressure in the cylinder chamber 41 of the first cylinder block 42A and the pressure in the first discharge muffler 52 reaches a predetermined value due to the compression action of the compression mechanism 13.

[0051] The first discharge muffler 52 separates the space in which the refrigerant compressed in the cylinder block 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 hole.

[0052] The second partition plate 45B is provided with a second discharge valve mechanism 51B that discharges the refrigerant compressed in the cylinder chamber 41 of the second cylinder block 42B, and a discharge chamber 53. The main bearing 16, the first cylinder block 42A, the first partition plate 45A, and the second cylinder block 42B have a first hole (not shown) that connects the discharge chamber 53 of the second partition plate 45B and the inside of the first discharge muffler 52. The second discharge valve mechanism 51B is opened to discharge the compressed refrigerant into the discharge chamber 53 when the pressure difference between the pressure in the cylinder chamber 41 of the second cylinder block 42B and the pressure in the discharge chamber 53 reaches a predetermined value due to the compression action of the compression mechanism 13. 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 is combined with the refrigerant compressed in the first cylinder block 42A.

[0053] The sub bearing 17, the third cylinder block 42C, and the second partition plate 45B are fixed to the second cylinder block 42B by a fastening member 55 such as a bolt. That is, the sub bearing 17, the third cylinder block 42C, and the second partition plate 45B are collectively fastened to the second cylinder block 42B by the fastening member 55. The sub bearing 17 is provided with a third discharge valve mechanism 51C that discharges refrigerant compressed in the cylinder chamber 41 of the third cylinder block 42C, and a second discharge muffler 56 (sub muffler) that covers the third discharge valve mechanism 51C. The second discharge muffler 56 separates a space in which refrigerant compressed in the third cylinder block 42C is discharged. The main bearing 16, the first cylinder block 42A, the first partition plate 45A, the second cylinder block 42B, the second partition plate 45B, and the third cylinder block 42C have a second hole 57 that connects a space in the second discharge muffler 56 with a space in the first discharge muffler 52. The third discharge valve mechanism 51C is a mechanism that, when a pressure difference between a pressure in the cylinder chamber 41 of the third cylinder block 42C and a pressure in the second discharge muffler 56 reaches a predetermined value due to compression by the compression mechanism 13, opens a discharge port (not shown) to discharge compressed refrigerant into the second discharge muffler 56. Refrigerant discharged into the second discharge muffler 56 is discharged into the first discharge muffler 52 through the second hole 57. Refrigerant discharged into the first discharge muffler 52 is combined with refrigerant compressed in the first cylinder block 42A and refrigerant compressed in the second cylinder block 42B.

[0054] In addition, the first hole can be part of the second hole 57. Further, the discharge chamber 53 of the second partition plate 45B can be connected to the second discharge muffler 56. That is, the first hole can be connected to the second discharge muffler 56.

[0055] The first cylinder block 42A is fixed to a frame 58 by a fastening member 59 such as a bolt. The frame 58 is fixed to the hermetic container 11 at a plurality of points by welding, for example, spot welding. That is, the frame 58 supports the rotor 32 of the motor portion 12, the compression mechanism 13, and the rotary shaft 15 to the hermetic container 11 via the first cylinder block 42A. In addition, the center of gravity of the rotor 32 of the motor portion 12, the compression mechanism 13, and the rotary shaft 15 in the height direction of the hermetic container 11 is preferably within the thickness (dimension in the height direction of the compressor 2) of the frame 58.

[0056] The balancer 38 is housed in the 2nd discharge muffler 56 that covers the sub bearing 17. The balancer 38 is, for example, a circular plate having a center line parallel to the direction of the rotational center line C of the rotating shaft 15, or a sector plate having the rotational center line C of the rotating shaft 15 as a base point. The balancer 38 is provided at a position eccentric from the center line of the balancer 38 and has a through-hole 38a that penetrates the balancer 38. The lower end portion of the rotating shaft 15 is pressed into the through-hole 38a of the balancer 38. The amount of eccentricity of the through-hole 38a is adjusted so that the unbalance of the rotating body of the compression mechanism portion 13 at the time of compression operation can be reduced.

[0057] However, in the case where the balancer is provided at the upper end portion of the rotating shaft 15 that protrudes upward of the rotor 32, the distance between the balancer and the bearing (main bearing 16) that supports the rotating shaft 15 depends on the axial dimension of the rotor 32. As in the present embodiment, by providing the balancer 38 at the lower end portion of the rotating shaft 15 that protrudes from the sub bearing 17, the distance between the balancer 38 and the bearing (sub bearing 17) that supports the rotating shaft 15 is greatly shortened as compared with the case where the balancer is provided at the upper end portion of the rotating shaft 15. Therefore, by disposing the balancer 38 as in the present embodiment, the deflection of the rotating shaft 15 and the rotor 32 can be suppressed.

[0058] A plurality of suction pipes 61 penetrate the sealed container 11 and are connected to the cylinder chambers 41 of the respective cylinder blocks 42. Each of the cylinder blocks 42 has a suction hole that reaches the cylinder chamber 41 in connection with each of the suction pipes 61. The 1st suction pipe 61A is connected to the cylinder chamber 41 of the 1st cylinder block 42A. The 2nd suction pipe 61B is connected to the cylinder chamber 41 of the 2nd cylinder block 42B. The 3rd suction pipe 61C is connected to the cylinder chamber 41 of the 3rd cylinder block 42C. In addition, as to the number of the plurality of suction pipes 61, the number can be the same as the number of the plurality of cylinder blocks 42 as in the present embodiment, or the number can be less than the number of the plurality of cylinder blocks 42 by being shared by two of the cylinder blocks 42. For example, the 2nd suction pipe 61B can also be connected to the 2nd partition plate 45B. The 2nd partition plate 45B is provided with a refrigerant passage (not shown) that is connected to the 2nd partition plate 45B and branches to the cylinder chamber 41 of the 2nd cylinder block 42B and the cylinder chamber 41 of the 3rd cylinder block 42C to be connected to both of the cylinder chambers 41.

[0059] The lower portion of the sealed container 11 is filled with the lubricating oil 21. Also, the majority of the compression mechanism portion 13 is immersed in the lubricating oil 21 in the sealed container 11.

[0060] The oil supply mechanism portion 22 sucks up the lubricating oil 21 in the sealed container 11 and supplies it to the sliding portion of the compression mechanism portion 13. The oil supply mechanism portion 22 includes a pump 65 that sucks up the lubricating oil 21 in the sealed container 11 and an oil passage 66 that sends the lubricating oil 21 sucked up by the pump 65 to the sliding portion of the compression mechanism portion 13.

[0061] Here, the sliding portion of the compression mechanism portion 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 sub bearing 17 and the rotating shaft 15.

[0062] The pump 65 is, for example, a screw pump (Archimedes screw, Archimedes spiral). The suction port of the screw pump is immersed in the lubricating oil 21 accumulated in the closed container 11.

[0063] Here, the 2nd discharge muffler 56 has an oil supply mechanism insertion hole 68 through which the lower end portion of the rotating shaft 15 is exposed to the outside of the 2nd discharge muffler 56. The lower end portion of the rotating shaft 15 is immersed in the lubricating oil 21 in the closed container 11 through the oil supply mechanism insertion hole 68. Further, the rotating shaft 15 has a pump arrangement hole 69 that opens at the lower end portion of the rotating shaft 15 and extends toward the upper end portion of the rotating shaft 15.

[0064] Further, the pump 65 has a rotary body 71 that is arranged in the pump arrangement hole 69 of the rotating shaft 15 and extends in a spiral shape along the center line C of the rotation of the rotating shaft 15. The rotary body 71 is rotationally integrated with the rotating shaft 15. The rotary body 71 rotates together with the rotating shaft 15, thereby continuously sucking up the lubricating oil 21 from the opening of the lower end portion of the rotating shaft 15 into the pump arrangement hole 69 of the rotating shaft 15.

[0065] In addition, the pump 65 is not limited to the rotary body 71 as long as it can be arranged in the closed container 11 and continuously supply the lubricating oil 21 into the pump arrangement hole 69 of the rotating shaft 15. The pump 65 can be a turbine pump that is driven by the rotational driving force of the rotating shaft 15, or can be a positive displacement pump. In this case, the pump arrangement hole 69 functions as a part of the oil passage 66.

[0066] The oil passage 66 delivers and lubricates the lubricating oil 21 sucked up into the pump arrangement hole 69 of the rotating shaft 15 by the pump 65 that rotates integrally with the rotating shaft 15 to the sliding portions of the compression mechanism portion 13.

[0067] The oil passage 66 has a 1st cylinder body oil supply hole 73A that supplies the lubricating oil 21 in the pump arrangement hole 69 to the gap between the eccentric portion 36 and the roller 43 accommodated in the 1st cylinder body 42A, a 2nd cylinder body oil supply hole 73B that supplies the lubricating oil 21 in the pump arrangement hole 69 to the gap between the eccentric portion 36 and the roller 43 accommodated in the 2nd cylinder body 42B, and a 3rd cylinder body oil supply hole 73C that supplies the lubricating oil 21 in the pump arrangement hole 69 to the gap between the eccentric portion 36 and the roller 43 accommodated in the 3rd cylinder body 42C.

[0068] Further, the oil passage 66 has a main bearing oil supply hole 75A that supplies the lubricating oil 21 in the pump arrangement hole 69 to a gap between the main bearing 16 and the rotating shaft 15, and a sub bearing oil supply hole 75B that supplies the lubricating oil 21 in the pump arrangement hole 69 to a gap between the sub bearing 17 and the rotating shaft 15.

[0069] The liquid reservoir 7 prevents liquid refrigerant that has not completely vaporized in the heat absorber 6 from being drawn into the compressor 2.

[0070] Next, the configuration around the rotating shaft 15 and the sub bearing 17 will be described in detail.

[0071] Figure 2 is an enlarged view of the longitudinal sectional view of the compressor of the first embodiment of the present application.

[0072] Figure 3 is a longitudinal sectional view of the sub bearing of the compressor of the first embodiment of the present application.

[0073] Figure 4 is a transverse sectional view of the compressor of the first embodiment of the present application.

[0074] Further, in the plan view of the compressor 2, the rotating shaft 15 rotates counterclockwise. That is, when the rotating shaft 15 rotates, Figure 2 the outer peripheral surface 77 of the rotating shaft 15 depicted in the center moves in a manner that cuts the rotation center line C from left to right as the solid arrow R. Further, when the rotating shaft 15 rotates, Figure 3 the outer peripheral surface 77 of the rotating shaft 15 faced by the inner peripheral surface 78 of the sub bearing 17 depicted in the center moves in a manner that cuts the rotation center line C from right to left as the solid arrow R.

[0075] As shown in Figure 2 , the size of the eccentric portion 36 of the compressor 2 of the present embodiment in the up-down direction is shorter than the size of the roller 43 in the up-down direction. Also, the upper surface of the eccentric portion 36 is positioned lower than the upper surface of the roller 43, and the lower surface of the eccentric portion 36 is positioned higher than the lower surface of the roller 43. That is, the eccentric portion 36 is arranged in the central portion in the up-down direction of the roller 43.

[0076] Further, the lower surface of the roller 43 and the upper surface of the sub bearing 17 meet within a range in which the roller 43 can move smoothly in rotation. Therefore, a gap 90 is provided between the lower surface of the eccentric portion 36 and the upper surface of the sub bearing 17. The side surface of the gap 90 is demarcated by the inner peripheral surface of the roller 43. That is, the gap 90 is surrounded by the lower surface of the eccentric portion 36, the inner peripheral surface of the roller 43, and the upper surface of the sub bearing 17.

[0077] Hereinafter, a portion of the inner circumferential surface of the roller 43 defining the gap 90 will be referred to as the sidewall portion of the gap 90. The inner diameter of the sidewall portion of the gap 90 is larger than the outer diameter of the eccentric portion 36. Furthermore, the upper half of the sidewall portion of the gap 90 slopes downwards, gradually widening towards the bottom, while the lower half of the sidewall portion of the gap 90 hangs vertically downwards. Therefore, the lubricating oil 21 supplied to the gap between the eccentric portion 36 and the roller 43 gradually flows downwards due to gravity and reaches the upper end of the sidewall portion of the gap 90. The lubricating oil 21 that reaches the upper end of the sidewall portion of the gap 90 flows to the lower end of the sidewall portion of the gap 90 and accumulates in the gap 90. Hereinafter, this gap 90 will be referred to as the storage space 90 for temporarily storing the lubricating oil 21.

[0078] The auxiliary bearing 17 has a through passage 91 that connects the storage space 90 to the sealed container 11. That is, the storage space 90 in the compression mechanism section 13 and the sealed container 11 that houses the compression mechanism section 13 are connected through the through passage 91 of the auxiliary bearing 17.

[0079] Furthermore, the through passage 91 has an L-shape when viewed in longitudinal section. The opening at one end of the through passage 91 opens towards the storage space 90. The opening at the other end of the through passage 91 opens towards the side of the secondary bearing 17. The through passage 91 is formed, for example, by a drill bit. Additionally, the secondary bearing 17 may have multiple through passages 91. The multiple through passages 91 are preferably arranged at intervals in the circumferential direction of the secondary bearing 17. The intervals between the multiple through passages 91 can be equal or different. Furthermore, multiple through passages 91 can increase the flow rate of lubricating oil 21 and easily prevent dust blockage.

[0080] like Figure 3 As shown, the auxiliary bearing 17 of the compressor 2 in this embodiment has a recessed stepped portion 92 disposed on the upper surface of the auxiliary bearing 17 and communicating with the gap 90. The vertical dimension of the stepped portion 92 is shorter than the radial dimension of the auxiliary bearing 17, and it is recessed into a disc shape. The stepped portion 92 is located below the storage space 90, thus dividing a space that is integral with the storage space 90. That is, the stepped portion 92, together with the gap 90, functions as the storage space 90 for lubricating oil 21.

[0081] like Figure 4 As shown, the stepped portion 92 of the compressor 2 in this embodiment is circular in plan view. The outer periphery of the stepped portion 92 is sized such that it is blocked by the rollers 43 and not connected to the cylinder chamber 41. In other words, the stepped portion 92 is sized and positioned such that it is located inside the trajectory of the eccentric portion 36 and the rollers 43 during eccentric rotation. The rollers 43, which engage with the eccentric portion 36, move eccentrically around the center of the secondary bearing 17. Figure 4 The double-dotted lines in the diagram indicate the positions of rollers 43 at each 90-degree rotational position of the eccentric portion 36. (As per...)Figure 4 As can be seen, the stepped portion 92 is located inside the roller 43 throughout the entire process of the roller 43's eccentric motion. In other words, the stepped portion 92 is located on the upper surface of the secondary bearing 17 within the area blocked by the roller 43 and not connected to the cylinder chamber 41.

[0082] The passageway 91 connects the stepped portion 92 to the inside of the sealed container 11. That is, the opening at one end of the passageway 91, which opens to the storage space 90, is provided at the stepped portion 92 and opens toward the gap 90.

[0083] Furthermore, the auxiliary bearing 17 has an annular groove 93 with a larger diameter than the lower end portion 15b of the supporting rotating shaft 15, i.e., the inner circumferential surface 78. This annular groove 93 opens upward toward the auxiliary bearing 17 and communicates with the clearance 90 and the step portion 92. Similar to the step portion 92, the groove 93, together with the clearance 90, functions as a storage space 90 for lubricating oil 21. That is, the groove 93 defines a space that is integral with the storage space 90. In addition, the groove 93 is located on the inner circumferential side of the auxiliary bearing 17, closer to the through passage 91. That is, the groove 93 is connected to the through passage 91 via the step portion 92. The through passage 91 can also be directly connected to the groove 93. Furthermore, the groove 93 also provides flexibility to the auxiliary bearing 17.

[0084] like Figure 2 As indicated by the solid arrow, lubricating oil 21, drawn from the sealed container 11 by pump 65, is supplied from the oil supply port 73C of the third cylinder to the gap between the eccentric portion 36 and the roller 43 housed in the third cylinder 42C. Furthermore, the lubricating oil 21 gathers downwards due to gravity, flowing into the gap 90 from the gap between the eccentric portion 36 and the roller 43. The lubricating oil 21 reaching the upper end of the sidewall of the gap 90 flows to the lower end of the sidewall of the gap 90 and temporarily accumulates in the gap 90. The gap 90 defines an accumulation space 90 integral with the stepped portion 92 and the annular groove 93, thus lubricating oil 21 also accumulates in the stepped portion 92 and the annular groove 93. Furthermore, the accumulation space 90 only needs to have at least the gap 90. The accumulation space 90 may have the gap 90 and the groove 93 in addition to the stepped portion 92.

[0085] The lubricating oil 21 accumulated in the gap 90, the step portion 92, and the groove portion 93 is branched to the gap between the rotating shaft 15 and the auxiliary bearing 17 and the through passage 91, and discharged from the compression mechanism portion 13. The lubricating oil 21 flowing into the gap between the rotating shaft 15 and the auxiliary bearing 17 moves downward due to gravity and flows out into the sealed container 11 through the oil supply mechanism insertion hole 68. The lubricating oil 21 flowing into the through passage 91 flows out into the sealed container 11 through the through passage 91. That is, the lubricating oil 21 sucked up by the oil supply mechanism portion 22 is branched to the gap between the rotating shaft 15 and the auxiliary bearing 17 and the through passage 91 and returns to the sealed container 11 side, generating a circulating flow F1 while lubricating the third cylinder 42C and its surroundings.

[0086] Figure 5 This is an enlarged view of the longitudinal cross-section of the compressor according to the first embodiment of the present invention.

[0087] like Figure 5 As shown, the compressor 2 of this embodiment has a rotating shaft 15 with an oil supply groove 81. This oil supply groove 81 is provided on the outer peripheral surface 77 of the portion supported by the auxiliary bearing 17, and extends toward the third cylinder 42C in a direction opposite to the rotation direction of the rotating shaft 15. That is, the oil supply groove 81 faces the inner peripheral surface 78 of the auxiliary bearing 17. The oil supply groove 81 is recessed toward the rotation center line C of the rotating shaft 15 and is connected to the auxiliary bearing oil supply hole 75B, and extends from the portion connected to the auxiliary bearing oil supply hole 75B to the third cylinder 42C. The oil supply groove 81 extends spirally along the outer peripheral surface 77 of the rotating shaft 15. In the compressor 2 with the rotating shaft 15 rotating counterclockwise when viewed from above, the oil supply groove 81 traces a clockwise spiral from the portion connected to the auxiliary bearing oil supply hole 75B toward the third cylinder 42C.

[0088] When the lower end of the secondary bearing 17 is taken as a reference, the oil supply groove 81 traces a clockwise spiral from the lower end of the secondary bearing 17 toward the upper end. When the upper end of the secondary bearing 17 is taken as a reference, the oil supply groove 81 traces a counterclockwise spiral from the upper end of the secondary bearing 17 toward the lower end.

[0089] The lubrication mechanism of this rotating shaft 15 and auxiliary bearing 17 is such that lubricating oil 21, drawn up by a pump 65 rotating integrally with the rotating shaft 15 through the pump mounting hole 69 of the rotating shaft 15 and flowing out from the auxiliary bearing oil supply hole 75B, flows into the oil supply groove 81 of the rotating shaft 15 to lubricate the gap between the rotating shaft 15 and the auxiliary bearing 17. The lubricating oil 21 flowing into the oil supply groove 81 of the rotating shaft 15 flows F2 from the auxiliary bearing oil supply hole 75B toward the third cylinder block 42C as the rotating shaft 15 rotates, while lubricating the area S1 above the auxiliary bearing oil supply hole 75B.

[0090] The lubrication structure of the rotating shaft 15 and the sub bearing 17 is configured to adjust the oil supply amount of the sliding portion between the rotating shaft 15 and the sub bearing 17 by appropriately setting at least any one of the flow passage cross-sectional area of the oil supply groove 81, the flow passage length of the oil supply groove 81, the inclination of the oil supply groove 81 with respect to the center line C of the rotation of the rotating shaft 15, and the cross-sectional area of the sub bearing oil supply hole 75B connecting the oil supply groove 81 and the oil passage 66 on the upstream side thereof.

[0091] Further, the flow passage cross-sectional area of the oil supply groove 81 is set by the combination of the groove depth and the groove width of the oil supply groove 81.

[0092] Furthermore, the length of the oil supply groove 81 of the present embodiment is shorter than the length of the outer peripheral surface 77 surrounding the rotating shaft 15. That is, the oil supply groove 81 does not surround the rotating shaft 15 by one revolution. Further, the oil supply groove 81 of the rotating shaft 15 is always supplied with the lubricating oil 21 sucked up by the pump 65.

[0093] However, when the lubricating oil 21 excessively leaks into the 2nd discharge muffler 56, the function of the balancer 38 in the 2nd discharge muffler 56 to adjust the unbalance of the rotating body of the compression mechanism portion 13 can sometimes be reduced. Therefore, the oil supply groove 81 is open to the inside (accumulation space 90) of the roller 43 of the 3rd cylinder block 42C. That is, the oil supply groove 81 causes the lubricating oil 21 to flow out to the inside of the roller 43 of the 3rd cylinder block 42C.

[0094] As described above, the compressor 2 and the refrigeration cycle device 1 of the present embodiment have the through passage 91 connecting the accumulation space 90 (gap 90) surrounded by the lower surface of the eccentric portion 36 of the rotating shaft 15, the inner peripheral surface of the roller 43, and the upper surface of the sub bearing 17 with the inside of the closed container 11 through the sub bearing 17, which accumulates the lubricating oil 21 guided by the oil supply mechanism portion 22 and supplied to the compression mechanism portion 13. Therefore, the lubricating oil 21 sucked up by the oil supply mechanism portion 22 is supplied from the 3rd cylinder oil supply hole 73C and temporarily accumulated in the accumulation space 90 (gap 90). The accumulation space 90 reduces the lubricating oil 21 flowing from the gap of the parts into the space divided by the sub bearing 17 and the 2nd discharge muffler 56. Furthermore, the through passage 91 discharges the lubricating oil 21 temporarily accumulated in the accumulation space 90 (gap 90) into the inside of the closed container 11. Thus, it is more difficult for the lubricating oil 21 to flow into the space divided by the sub bearing 17 and the 2nd discharge muffler 56. That is, the through passage 91 can reduce the supply amount of the lubricating oil 21 to the space divided by the sub bearing 17 and the 2nd discharge muffler 56. Thus, it is possible to reduce the possibility that the operation of the balancer 38 housed in the 2nd discharge muffler 56 is hindered by the lubricating oil 21 and maintain the function of the balancer 38 to adjust the unbalance of the rotating body. As a result, it is possible to improve the performance and the reliability of the compressor 2 and the refrigeration cycle device 1.

[0095] Further, the compressor 2 and the refrigeration cycle apparatus 1 have an oil passage 66 including a third cylinder oil supply hole 73C that supplies the lubricating oil 21 guided by the oil supply mechanism portion 22 to the gap between the sub bearing 17 and the rotating shaft 15, and an oil supply groove 81 that is provided on the outer peripheral surface 77 of the portion supported by the sub bearing 17 and extends toward the cylinder chamber 41. Thus, the amount of oil supplied from the oil passage 66 and the oil supply groove 81 to the storage space 90 is increased. Also, if the amount of oil supplied to the storage space 90 is increased, the discharge of the lubricating oil 21 stored in the storage space 90 can be promoted, and the reliability of the compressor 2 and the refrigeration cycle apparatus 1 can be improved.

[0096] Further, the compressor 2 and the refrigeration cycle apparatus 1 of the present embodiment have a recessed step portion 92 provided on the upper surface of the sub bearing 17 and communicating with the gap 90, and a through passage 91 connecting the step portion 92 with the inside of the closed container 11. Thus, the compressor 2 and the refrigeration cycle apparatus 1 can collect the lubricating oil 21 guided downward by gravity to the step portion 92, and smoothly discharge the lubricating oil 21 collected to the step portion 92 through the through passage 91, and thus the reliability of the compressor 2 and the refrigeration cycle apparatus 1 can be improved.

[0097] (Second Embodiment)

[0098] Figure 6 is a longitudinal sectional view of a sub bearing of a compressor according to the second embodiment of the present application.

[0099] As Figure 6 shown, the sub bearing 17A of the compressor 2 and the refrigeration cycle apparatus 1 of the present embodiment has a ring-shaped groove portion 93A provided with a larger diameter than the portion supporting the rotating shaft 15, i.e., the inner peripheral surface 78 of the sub bearing 17A, and opened toward the upper portion of the sub bearing 17A to communicate with the gap 90, and a through passage 91A connecting the ring-shaped groove portion 93A with the inside of the closed container 11. Further, the through passage 91A connects the lower end portion of the ring-shaped groove portion 93A with the inside of the closed container 11. That is, the lubricating oil 21 stored in the ring-shaped groove portion 93A is discharged to the closed container 11 side through the through passage 91A.

[0100] Further, like the sub bearing 17 of the first embodiment, the sub bearing 17A of the present embodiment has a step portion 92. The ring-shaped groove portion 93A is provided to the step portion 92. Thus, the lubricating oil 21 guided downward by gravity is collected to the step portion 92, and further collected to the ring-shaped groove portion 93A from the step portion 92. Then, the lubricating oil 21 stored in the groove bottom of the ring-shaped groove portion 93A is discharged to the closed container 11 side through the through passage 91A.

[0101] As explained above, the compressor 2 and the refrigeration cycle device 1 of the present embodiment have the annular groove portion 93A provided with a larger diameter than the portion supporting the rotating shaft 15, which is open toward the upper side of the sub bearing 17A to communicate with the accumulation space 90, and the through path 91 connecting the annular groove portion 93A with the inside of the closed container 11. Therefore, the compressor 2 and the refrigeration cycle device 1 can collect the lubricating oil 21 directed downward by gravity to the annular groove portion 93A and smoothly discharge the lubricating oil 21 collected to the groove portion 93A through the through path 91. Also, the annular groove portion 93A also has a function of imparting flexibility to the sub bearing 17A, so the reliability of the compressor 2 and the refrigeration cycle device 1 can be improved.

[0102] The embodiments of the present application have been described, but these embodiments are suggested as examples and are not intended to limit the scope of the application. These new embodiments can be implemented in other various ways, and various omissions, substitutions, and changes can be made within the scope of the gist of the application. These embodiments and modifications thereof are included in the scope and gist of the application, and are included in the scope of the application and the equivalent thereof recited in the patent claim.

[0103] Explanation of Symbols

[0104] 1: refrigeration cycle device; 2: rotary compressor; 3: heat sink; 5: expansion device; 6: heat absorber; 7: accumulator; 8: refrigerant piping; 8a: discharge pipe; 11: closed container; 11a: main body portion; 11b: end panel; 11c: end panel; 12: open-winding type motor portion; 13: compression mechanism portion; 15: rotary shaft; 15a: middle portion; 15b: lower end portion; 16: main bearing; 17, 17A: auxiliary bearing; 21: lubricating oil; 22: oil supply mechanism portion; 25, 26: seal terminal; 27, 28: terminal plate; 29: electric power line; 31: stator; 32: rotor; 33: lead wire; 35: rotor core; 36: eccentric portion; 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: oil supply mechanism insertion hole; 69: pump arrangement hole; 71: swivel body; 73A: first cylinder oil supply hole; 73B: second cylinder oil supply hole; 73C: third cylinder oil supply hole; 75A: main bearing oil supply hole; 75B: auxiliary bearing oil supply hole; 77: outer peripheral surface of rotary shaft; 78: inner peripheral surface of auxiliary bearing; 81: oil supply groove; 90: accumulation space; 91, 91A: through passage; 92: step portion; 93, 93A: annular groove portion.

Claims

1. A compressor, comprising: A cylindrical, sealed container with a center line extending in the vertical direction; The compression mechanism is housed in the aforementioned sealed container and compresses the refrigerant introduced into the sealed container. The motor section includes a cylindrical stator fixed to the inner surface of the sealed container, and a rotor disposed inside the stator and generating the rotational driving force of the compression mechanism section; and The oil supply mechanism supplies the lubricating oil stored in the sealed container to the compression mechanism. The aforementioned compression mechanism includes: The rotating shaft rotates integrally with the rotor, extends downwards compared to the rotor, and has an eccentric portion; The roller has a lower surface located below the lower surface of the eccentric portion, and engages with the eccentric portion. A secondary bearing supports the lower end of the aforementioned rotating shaft, enabling it to rotate. The cylinder body, blocked by the aforementioned auxiliary bearing, has a cylinder chamber for accommodating the aforementioned eccentric portion and the aforementioned roller; A secondary muffler, covering the aforementioned secondary bearing, separates the space where the compressed refrigerant discharged within the aforementioned cylinder block; and The balancer, located on the protruding portion of the rotating shaft that extends from the aforementioned secondary bearing, is housed within the aforementioned secondary muffler. The aforementioned auxiliary bearing has a through passage that connects the storage space to the interior of the sealed container. The storage space is surrounded by the lower surface of the eccentric portion, the inner circumferential surface of the roller, and the upper surface of the auxiliary bearing. The storage space contains the lubricating oil supplied to the compression mechanism by the oil supply mechanism. The aforementioned through passage has a first opening located on the side of the aforementioned secondary bearing and opening into the aforementioned sealed container, and a second opening located on the upper surface of the aforementioned secondary bearing and opening into the aforementioned storage space. The aforementioned through passage is L-shaped and passes through the aforementioned secondary bearing. The aforementioned rotating shaft has: The oil supply port supplies lubricating oil, guided by the aforementioned oil supply mechanism to the aforementioned compression mechanism, to the gap between the lubricating oil supply port and the aforementioned auxiliary bearing; and An oil supply groove is provided on the outer peripheral surface of the portion supported by the aforementioned auxiliary bearing, extends toward the aforementioned cylinder chamber, and reaches the aforementioned cylinder body. The aforementioned secondary bearing has a recessed stepped portion disposed on the upper surface of the secondary bearing and communicating with the aforementioned storage space. The aforementioned passageway connects the aforementioned stepped section to the interior of the aforementioned sealed container. The aforementioned stepped recess is disc-shaped and located inside the rotational trajectory traced by the rotor as the aforementioned rotating shaft rotates.

2. A refrigeration cycle device, comprising: The compressor according to claim 1; heat sink; Expansion device; Heat absorber; and The refrigerant piping connects the compressor, radiator, expansion device, and absorber to allow the refrigerant to circulate.

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