EP3922854A1 - Rotary compressor, method for manufacturing rotary compressor, and refrigeration cycle device - Google Patents
Rotary compressor, method for manufacturing rotary compressor, and refrigeration cycle device Download PDFInfo
- Publication number
- EP3922854A1 EP3922854A1 EP19914314.0A EP19914314A EP3922854A1 EP 3922854 A1 EP3922854 A1 EP 3922854A1 EP 19914314 A EP19914314 A EP 19914314A EP 3922854 A1 EP3922854 A1 EP 3922854A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotary shaft
- hole
- balancer
- rotary compressor
- rotary
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/023—Lubricant distribution through a hollow driving shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2230/00—Manufacture
- F04C2230/60—Assembly methods
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
- F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/807—Balance weight, counterweight
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/809—Lubricant sump
Definitions
- Embodiments of the present invention relate to a rotary compressor, a method for manufacturing a rotary compressor, and a refrigeration cycle apparatus.
- a rotary compressor is used in a refrigeration cycle apparatus such as an air conditioner.
- a refrigerant is compressed in such a manner that an eccentric portion of a rotary shaft is eccentrically rotated by a compression mechanism.
- the rotary shaft has a supply channel for supplying a lubricating oil stored inside a case to a sliding portion between the rotary shaft and a bearing.
- a lubricating oil stored inside a case to a sliding portion between the rotary shaft and a bearing.
- An object of the present invention is to provide a rotary compressor, a method for manufacturing a rotary compressor, and a refrigeration cycle apparatus which are capable of obtaining desired lubrication performance.
- a rotary compressor includes a case, a rotary shaft, a compression mechanism, a balancer, and a balancer cover.
- a lubricating oil is stored in the case.
- the rotary shaft is disposed inside the case, and has an eccentric portion.
- the compression mechanism has a cylinder, a main bearing, and an auxiliary bearing.
- the cylinder accommodates the eccentric portion.
- the main bearing rotatably supports the rotary shaft from above the cylinder.
- the auxiliary bearing rotatably supports the rotary shaft from below the cylinder.
- a through-hole is formed at a position of the balancer cover facing the rotary shaft in the axial direction.
- the rotary shaft has a thrust sliding portion, a protruding portion, and a supply channel.
- the thrust sliding portion of the rotary shaft comes into contact with a seal located around the through-hole of the balancer cover, in the axial direction.
- the protruding portion is located on an inner peripheral side of the thrust sliding portion, and protrudes downward from the through-hole through the through-hole.
- the supply channel is open on a lower end surface of the protruding portion to guide the lubricating oil.
- FIG. 1 is a schematic configuration diagram of the refrigeration cycle apparatus 1 including a sectional view of a rotary compressor 2 according to a first embodiment.
- the refrigeration cycle apparatus 1 includes the rotary compressor 2, a condenser 3 serving as a radiator connected to the rotary compressor 2, an expansion device 4 connected to the condenser 3, and an evaporator 5 serving as a heat absorber connected between the expansion device 4 and the rotary compressor 2.
- the rotary compressor 2 is a so-called rotary-type compressor.
- the rotary compressor 2 compresses an internally fetched low-pressure gas refrigerant and obtains a high-temperature and high-pressure gas refrigerant. A specific configuration of the rotary compressor 2 will be described later.
- the condenser 3 dissipates heat from the high-temperature and high-pressure gas refrigerant fed from the rotary compressor 2, and obtains a high-pressure liquid refrigerant.
- the expansion device 4 lowers a pressure of the high-pressure liquid refrigerant fed from the condenser 3 and obtains a low-temperature and low-pressure liquid refrigerant.
- the evaporator 5 vaporizes the low-temperature and low-pressure liquid refrigerant fed from the expansion device 4 and changes the low-temperature and low-pressure liquid refrigerant into a low-pressure gas refrigerant.
- the low-pressure liquid refrigerant vaporizes, heat of vaporization is taken from surroundings, and the surroundings are cooled.
- the low-pressure gas refrigerant passing through the evaporator 5 is fetched into the above-described rotary compressor 2.
- the refrigerant serving as a working fluid circulates while changing a phase between the gas refrigerant and the liquid refrigerant.
- the refrigerant it is possible to use an HFC-based refrigerant such as R410A and R32, an HFO-based refrigerant such as R1234yf and R1234ze, or a natural refrigerant such as CO 2 .
- the rotary compressor 2 includes a compressor body 11 and an accumulator 12.
- the accumulator 12 is a so-called gas-liquid separator.
- the accumulator 12 is provided between the above-described evaporator 5 and the compressor body 11.
- the accumulator 12 is connected to the compressor body 11 through a suction pipe 21.
- the accumulator 12 supplies only the gas refrigerant to the compressor body 11, out of the gas refrigerant vaporized by the evaporator 5 and the liquid refrigerant not vaporized by the evaporator 5.
- the compressor body 11 includes a rotary shaft 31, an electric motor unit 32, a compression mechanism 33, and a case 34 for accommodating the rotary shaft 31, the electric motor unit 32, and the compression mechanism 33.
- the compressor body 11 according to the present embodiment is disposed in a state where an axial direction of the rotary shaft 31 is an upward-downward direction.
- the case 34 is formed in a cylindrical shape, and both end portions in the axial direction are closed.
- a lubricating oil J is accommodated inside the case 34.
- a portion of the compression mechanism 33 is immersed into the lubricating oil J.
- the rotary shaft 31 is disposed coaxially with an axis line O of the case 34.
- a direction extending along the axis line O will simply be referred to as the axial direction
- a direction orthogonal to the axial direction will be referred to as a radial direction
- a direction turning around the axis line O will be referred to as a circumferential direction.
- the electric motor unit 32 is disposed on a first side inside the case 34 in the axial direction.
- the compression mechanism 33 is disposed on a second side inside the case 34 in the axial direction.
- the electric motor unit 32 side along the axial direction will be referred to as an upper side, and the compression mechanism 33 side will be referred to as a lower side.
- the electric motor unit 32 is a so-called inner rotor type DC brushless motor. Specifically, the electric motor unit 32 includes a stator 35 and a rotor 36.
- the stator 35 is fixed to an inner wall surface of the case 34 by means of shrink fitting.
- the rotor 36 is fixed to an upper portion of the rotary shaft 31 in a state where an interval is formed inside the stator 35 in the radial direction.
- a counter bore 37 is formed in an inner peripheral portion on a lower surface of the rotor 36.
- the counter bore 37 is an annular recess portion recessed upward from the lower surface of the rotor 36, and formed over an entire periphery of the rotor 36.
- a balancer 39 is provided in an outer peripheral portion on the lower surface of the rotor 36.
- the balancer 39 is formed in an arc shape in a plan view when viewed in the axial direction.
- the balancer 39 is provided in a portion in the circumferential direction on the lower surface of the rotor 36.
- the compression mechanism 33 includes a cylinder 41 having a cylindrical shape through which the rotary shaft 31 penetrates, and a main bearing 42 and an auxiliary bearing 43 which individually close both end opening portions of the cylinder 41 and rotatably support the rotary shaft 31.
- a space formed by the cylinder 41, the main bearing 42, and the auxiliary bearing 43 forms a cylinder chamber 46.
- An eccentric portion 51 eccentric in the radial direction with respect to the axis line O is formed in a portion located inside the cylinder chamber 46 in the above-described rotary shaft 31.
- an eccentric direction of the eccentric portion 51 is set on a side opposite to the balancer 39 across the axis line O.
- a roller 53 is externally inserted into the eccentric portion 51.
- the roller 53 is configured to be eccentrically rotatable with respect to the axis line O while an outer peripheral surface is in sliding contact with an inner peripheral surface of the cylinder 41 as the rotary shaft 31 is rotated.
- Fig. 2 is a sectional view of the compression mechanism 33 corresponding to line II-II in Fig. 1 .
- a blade groove 54 recessed outward in the radial direction is formed in a portion in the circumferential direction.
- the blade groove 54 is formed over in the axial direction (upward-downward direction) of the cylinder 41.
- the blade groove 54 communicates with the inside of the case 34 in an outer end portion in the radial direction.
- a blade 55 is provided in the blade groove 54.
- the blade 55 is configured to be slidable in the radial direction with respect to the cylinder 41.
- the blade 55 is biased inward in the radial direction by a biasing member (not shown).
- An inner end surface of the blade 55 in the radial direction is in contact with an outer peripheral surface of the roller 53 inside the cylinder chamber 46. In this manner, the blade 55 moves forward and rearward inside the cylinder chamber 46 as the roller 53 is eccentrically rotated.
- the cylinder chamber 46 is divided into a suction chamber 46a and a compression chamber 46b by the roller 53 and the blade 55.
- a compression operation is performed inside the cylinder chamber 46 by a rotation operation of the roller 53 and a forward/rearward operation of the blade 55.
- a suction hole 56 that penetrates the cylinder 41 in the radial direction is formed in a portion located on an inner side (left side of the blade groove 54 in Fig. 2 ) of the blade groove 54 along a rotation direction of the roller 53 (refer to an arrow in Fig. 2 ).
- the above-described suction pipe 21 (refer to Fig. 1 ) is connected to the suction hole 56 from an outer end portion in the radial direction.
- an inner end portion of the suction hole 56 in the radial direction is open into the cylinder chamber 46 (suction chamber 46a).
- the main bearing 42 closes an upper end opening portion of the cylinder 41.
- the main bearing 42 rotatably supports a portion located above the cylinder 41 in the rotary shaft 31.
- the main bearing 42 includes a cylinder portion 61 into which the rotary shaft 31 is inserted, and a flange portion 62 protruding outward in the radial direction from a lower end portion of the cylinder portion 61.
- a main bearing discharge hole 64 that penetrates the flange portion 62 in the axial direction is formed in a portion of the flange portion 62 in the circumferential direction.
- the main bearing discharge hole 64 communicates with the inside of the cylinder chamber 46 (compression chamber 46b).
- a discharge valve mechanism 67 is disposed in the flange portion 62. The discharge valve mechanism 67 opens the main bearing discharge hole 64 as the pressure inside the cylinder chamber 46 (compression chamber 46b) increases, and discharges the refrigerant outward of the cylinder chamber 46.
- the main bearing 42 is provided with a muffler 65 that covers the main bearing 42 from above.
- a communication hole 66 that causes the inside and the outside of the muffler 65 to communicate with each other is formed in a central portion of the muffler 65 in the radial direction.
- the high-temperature and high-pressure gas refrigerant discharged through the above-described discharge hole 64 is discharged into the case 34 through the communication hole 66.
- the auxiliary bearing 43 closes a lower end opening portion of the cylinder 41.
- the auxiliary bearing 43 rotatably supports a portion located below the cylinder 41 in the rotary shaft 31.
- the auxiliary bearing 43 includes a cylinder portion 71 into which the rotary shaft 31 is inserted, and a flange portion 72 protruding outward in the radial direction from the upper end portion of the cylinder portion 71.
- An auxiliary bearing discharge hole 73 that penetrates the flange portion 72 in the axial direction is formed in a portion of the flange portion 72 in the circumferential direction.
- the auxiliary bearing discharge hole 73 communicates with the inside of the cylinder chamber 46 (compression chamber 46b).
- a discharge valve mechanism 75 is provided in the flange portion 72. The discharge valve mechanism 75 opens the auxiliary bearing discharge hole 73 as the pressure inside the cylinder chamber 46 (compression chamber 46b) increases and discharges the refrigerant outward of the cylinder chamber 46.
- the auxiliary bearing 43 is provided with a balancer cover 81 that covers the auxiliary bearing 43 from below.
- the balancer cover 81 is formed in a bottomed cylindrical shape that is open upward.
- a seal 82 is formed in a central portion in the radial direction in a bottom portion of the balancer cover 81.
- the seal 82 is formed to bulge upward with respect to an outer peripheral portion in the bottom portion of the balancer cover 81. However, the seal 82 may not bulge from the bottom portion of the balancer cover 81.
- An upper surface of the seal 82 is formed to have a flat surface orthogonal to the axis line O.
- a through-hole 84 that penetrates the seal 82 in the axial direction is formed in a central portion (portion located on the axis line O) of the seal 82.
- the main bearing 42, the cylinder 41, and the auxiliary bearing 43 have a communication hole 85 for causing the inside of the inside of the muffler 65 and the inside of the balancer cover 81 to communicate with each other.
- the communication hole 85 penetrates the main bearing 42, the cylinder 41, and the auxiliary bearing 43 in the axial direction at a position where the communication hole 85 faces the above-described discharge holes 64 and 73 across the axis line O in the radial direction.
- Fig. 3 is an enlarged view of a main part in Fig. 1 .
- the rotary shaft 31 has a thrust sliding portion 90 and a protruding portion 87 located on an inner peripheral side of the thrust sliding portion 90 and protruding downward.
- the rotary shaft 31 further has the above-described eccentric portion 51, a main shaft portion 88, and an auxiliary shaft portion 89.
- the main shaft portion 88 is a portion located above the eccentric portion 51 in the above-described rotary shaft 31.
- the main shaft portion 88 is connected to an upper side of the eccentric portion 51 via a connecting portion 51a.
- the main shaft portion 88 is supported by the main bearing 42, and the rotor 36 is fixed to the main shaft portion 88.
- the auxiliary shaft portion 89 is a portion located below the eccentric portion 51 in the rotary shaft 31.
- the auxiliary shaft portion 89 is connected to a lower side of the eccentric portion 51 via a connecting portion 51b.
- the auxiliary shaft portion 89 is supported by the auxiliary bearing 43.
- an outer diameter ⁇ Ds of the auxiliary shaft portion 89 is smaller than an outer diameter ⁇ Dm of the main shaft portion 88.
- at least a portion protruding downward from the auxiliary bearing 43 may have a diameter smaller than that of the main shaft portion 88. That is, a portion located inside the auxiliary bearing 43 in the auxiliary shaft portion 89 may have an outer diameter the same as that of the main shaft portion 88.
- the seal 82 of the balancer cover 81 receives an axial load acting on the rotary shaft 31 and supports the thrust sliding portion 90 of the rotary shaft 31 to be slidable.
- the thrust sliding portion 90 and the seal 82 come into contact with each other in the axial direction, thereby blocking communication between the inside and the outside of the balancer cover 81 through the through-hole 84.
- the thrust sliding portion 90 according to the present embodiment is a lower end surface of the auxiliary shaft portion 89.
- the thrust sliding portion 90 is a flat surface orthogonal to the axial direction. It is preferable that the thrust sliding portion 90 is pressed against the seal 82 by the weight of the rotary shaft 31 and the rotor 36, or a magnetic force generated between the stator 35 and the rotor 36.
- the base shaft portion is configured to include the eccentric portion 51, the main bearing 88, and the auxiliary bearing 89.
- a balancer 91 is attached to a portion protruding downward from the auxiliary bearing 43 in the auxiliary shaft portion 89.
- the balancer 91 is formed in a disk shape.
- An attachment hole 92 that penetrates the balancer 91 in the axial direction is formed at a position eccentric with respect to the center of the balancer 91.
- the auxiliary shaft portion 89 of the rotary shaft 31 is fixed inside the attachment hole 92 by means of press-fitting.
- the center of the balancer 91 is eccentric with respect to the axis line O in a direction opposite to an eccentric direction of the eccentric portion 51 (direction the same as that of the balancer 39). That is, the balancer 91 and the eccentric portion 51 are disposed with a phase difference of 180° in the circumferential direction.
- the shape of the balancer 91 is not limited to the disc shape.
- the balancer 91 is provided in the auxiliary shaft portion 89. Accordingly, for example, compared to a case where the balancer is provided on an upper surface of the rotor 36, a distance between the balancer 91 and the bearing (in the present embodiment, the auxiliary bearing 43) can be shortened. In this manner, it is possible to suppress bending of the rotor 36.
- a centrifugal force acting on the eccentric portion 51 is defined as F0
- a centrifugal force acting on the balancer 91 is defined as F1
- a centrifugal force acting on the balancer 39 is defined as F2.
- F0, F1, and F2 it is preferable that a resultant force of the respective centrifugal forces F0, F1, and F2 becomes 0 (refer to Equation (1) below).
- the respective centrifugal forces F0, F1, and F2 can be calculated by mr ⁇ 2 (m: mass, r: distance in the radial direction from the axis line O, and ⁇ : angular velocity).
- F 0 ⁇ F 1 ⁇ F 2 0
- the center of action of the centrifugal force F0 is defined as a reference point, a distance in the axial direction from the reference point to the center of action of the centrifugal force F1 is defined as L1, and a distance in the axial direction from the reference point to the center of action of the centrifugal force F2 is defined as L2.
- a sum of moments acting on the rotary shaft 31 due to the centrifugal forces F1 and F2 becomes 0 (refer to Equation (2) below).
- the distance L1 in the axial direction from the reference point to the center of action of the centrifugal force F1 is equal to or longer than the distance L2 in the axial direction from the reference point to the center of action of the centrifugal force F2 (L1 ⁇ L2).
- the balancer 91 can be miniaturized, and the amount of eccentricity can be reduced.
- the protruding amount of the balancer 91 in the radial direction with respect to the axis line O can be particularly suppressed, and the compressor body 11 in the radial direction can be miniaturized.
- the protruding portion 87 protrudes downward from an inner peripheral portion of the thrust sliding portion 90.
- the protruding portion 87 protrudes downward from a lower end opening edge of the through-hole 84 through the through-hole 84.
- the protruding portion 87 according to the present embodiment protrudes downward from a lowest point (lower surface of the seal 82) of the balancer cover 81.
- the rotary shaft 31 can be displaced (backlash in the upward-downward direction) by a predetermined distance in the axial direction with respect to the compression mechanism 33, due to a difference between the height of the cylinder chamber 46 and the length in the axial direction of the connecting portions 51a and 51b provided upward and downward of the eccentric portion 51 and the eccentric portion 51.
- the protruding amount from the lower end opening edge of the through-hole 84 of the protruding portion 87 is larger than the predetermined distance which is a displacement amount of the rotary shaft 31. That is, even when the rotary shaft 31 is displaced in the upward-downward direction by the amount of backlash, the protruding amount of the protruding portion 87 is set so that the protruding portion 87 always protrudes downward from the lower end opening edge of the through-hole 84 of the balancer cover 81.
- the rotary shaft 31 has a supply channel 94 for supplying the lubricating oil J to each sliding portion in the compression mechanism 33 (for example, a portion between the eccentric portion 51 and the roller 53, and a portion between the rotary shaft 31 and the bearings 42 and 43).
- the supply channel 94 has a main flow path 95 extending coaxially with the axis line O, and sub-flow paths 96 and 97 extending in the radial direction from the main flow path 95.
- a lower end portion of the main flow path 95 is open on a lower end surface of the rotary shaft 31 (protruding portion 87). In this manner, the lubricating oil J inside the case 34 can flow into the main flow path 95.
- An upper end portion of the main flow path 95 is terminated in a lower end portion of the main shaft portion 88.
- the length in the axial direction of the main flow path 95 can appropriately be changed as long as the length reaches at least the cylinder 41.
- the main flow path 95 may penetrate the rotary shaft 31 in the axial direction.
- a twist plate that promotes the lubricating oil J to rise as the rotary shaft 31 is rotated may be provided on an inner peripheral surface of the main flow path 95.
- the first sub-flow path 96 is formed in a connecting portion (connecting portion 51a) between the main shaft portion 88 and the eccentric portion 51 in the rotary shaft 31.
- An inner end portion in the radial direction of the first sub-flow path 96 communicates with the inside of the above-described main flow path 95.
- an outer end portion in the radial direction of the first sub-flow path 96 is open outward in the radial direction on an outer peripheral surface of the rotary shaft 31.
- the second sub-flow path 97 is formed in a portion located inside the auxiliary bearing 43 in the auxiliary shaft portion 89. An inner end portion in the radial direction of the second sub-flow path 97 communicates with the inside of the above-described main flow path 95. On the other hand, an outer end portion in the radial direction of the second sub-flow path 97 is open outward in the radial direction on the outer peripheral surface of the rotary shaft 31.
- a lower circulation path 99 is formed on the outer peripheral surface of the rotary shaft 31 (auxiliary shaft portion 89).
- the lower circulation path 99 is formed by a spiral groove formed on the outer peripheral surface of the rotary shaft 31.
- a lower end portion of the lower circulation path 99 communicates with the inside of the second sub-flow path 97.
- an upper end portion of the lower circulation path 99 is located in the upper end portion of the auxiliary shaft portion 89.
- the lower circulation path 99 guides the lubricating oil J upward from below when the rotary shaft 31 is rotated.
- the lower circulation path 99 may be configured so that the lubricating oil J can be supplied between the outer peripheral surface of the auxiliary shaft portion 89 and the inner peripheral surface of the auxiliary bearing 43 (cylinder portion 71). In this case, for example, a groove may be formed on the inner peripheral surface of the cylinder portion 71.
- a shape or a layout of the lower circulation path 99 can appropriately be changed.
- an upper circulation path (not shown) is formed on the inner peripheral surface of the cylinder portion 61.
- the upper circulation path is formed in a spiral groove.
- the lower end portion of the upper circulation path communicates with the inside of the first sub-flow path 96.
- the upper end portion of the upper circulation path communicates with the inside of the case 34.
- the upper circulation path guides the lubricating oil J upward from below when the rotary shaft 31 is rotated.
- the upper circulation path may be formed on the outer peripheral surface of the main shaft portion 88.
- the gas refrigerant is suctioned into the suction chamber 46a through the suction hole 56, and the gas refrigerant previously suctioned from the suction hole 56 is compressed in the compression chamber 46b.
- the gas refrigerant discharged into the muffler 65 through the main bearing discharge hole 64 is discharged into the case 34 through the communication hole 66 of the muffler 65.
- the gas refrigerant discharged into the balancer cover 81 through the auxiliary bearing discharge hole 73 flows into the muffler 65 through the communication hole 85, and thereafter, is discharged into the case 34 through the communication hole 66 of the muffler 65.
- the gas refrigerant discharged into the case 34 is fed to the condenser 3 as described above.
- a pressure equivalent to a discharge pressure of the gas refrigerant acts on the lubricating oil J inside the case 34. Therefore, the lubricating oil J flows into the main flow path 95, and rises inside the main flow path 95 as the rotary shaft 31 is rotated. The lubricating oil J rising inside the main flow path 95 is distributed to each of the sub-flow paths 96 and 97 by the centrifugal force generated by the rotation of the rotary shaft 31.
- the lubricating oil J distributed to each of the sub-flow paths 96 and 97 is discharged on the outer peripheral surface of the rotary shaft 31 and is supplied to each sliding portion.
- the lubricating oil J discharged from the first sub-flow path 96 rises inside the upper circulation path as the rotary shaft 31 is rotated and is supplied to a portion between the main shaft portion 88 and the main bearing 42.
- the lubricating oil J discharged from the second sub-flow path 97 rises inside the lower circulation path 99 as the rotary shaft 31 is rotated and is supplied to a portion between the auxiliary shaft portion 89 and the auxiliary bearing 43 and a portion between the eccentric portion 51 and the roller 53.
- the lubricating oil J supplied to each sliding portion is discharged from the compression mechanism 33 through a portion between the main shaft portion 88 and the main bearing 42 and through the cylinder chamber 46.
- the present embodiment adopts a configuration as follows.
- the thrust sliding portion 90 of the rotary shaft 31 and the seal 82 of the balancer cover 81 are brought into contact with each other to seal a portion in the axial direction between the rotary shaft 31 and the balancer cover 81.
- the portion in the axial direction between the rotary shaft 31 and the balancer cover 81 is sealed by the seal 82. Accordingly, it is possible to suppress a possibility that the lubricating oil J accommodated inside the case 34 may enter the inside of the balancer cover 81. The possibility that the lubricating oil J may enter the inside of the balancer cover 81 is suppressed. Accordingly, even when the balancer 91 is provided in the auxiliary shaft portion 89, it is possible to suppress a possibility that the eccentric rotation of the balancer 91 may be hindered by the lubricating oil J when the rotary shaft 31 is rotated. In this manner, rotational resistance acting on the balancer 91 can be reduced when the rotary shaft 31 is rotated. As a result, the rotary shaft 31 can efficiently be rotated, and compression performance can be improved.
- the thrust sliding portion 90 and the seal 82 may be separated from each other in some cases.
- the gas refrigerant discharged into the balancer cover 81 through the auxiliary bearing discharge hole 73 may leak outward of the balancer cover 81 through the through-hole 84.
- the present embodiment adopts a configuration as follows.
- the protruding portion 87 protrudes downward from the lower end opening edge of the through-hole 84 of the balancer cover 81 more than the predetermined distance which is the displacement amount of the rotary shaft 31.
- the gas refrigerant discharged into the balancer cover 81 leaks outward of the balancer cover 81 through the through-hole 84, it is possible to suppress a possibility that the gas refrigerant may flow into the main flow path 95 after turning around the protruding portion 87.
- the lubricating oil J can effectively be supplied to the sliding portion, and the desired lubrication performance can be obtained.
- the refrigeration cycle apparatus 1 includes the above-described rotary compressor 2. Accordingly, it is possible to provide the refrigeration cycle apparatus 1 capable of improving operation reliability and compression performance over a long period of time.
- Fig. 4 is a partial sectional view of a rotary compressor 200 according to a second embodiment.
- the same reference numerals will be assigned to configurations the same as those of the above-described embodiment, and description thereof will be omitted.
- the rotary compressor 200 according to the present embodiment is different from the above-described first embodiment in that a plurality of (for example, three) cylinders (upper cylinder 201, intermediate cylinder 202, and lower cylinder 203) are aligned in the axial direction.
- the upper cylinder 201 and the intermediate cylinder 202 abut each other in the axial direction while an upper partitioning portion 210 is interposed therebetween.
- the intermediate cylinder 202 and the lower cylinder 203 abut each other in the axial direction while a lower partitioning portion 211 is interposed therebetween.
- a configuration of each of the cylinders 201 to 203 is the same as that of the above-described embodiment.
- the upper cylinder 201, the lower cylinder 203, the main bearing 42, the auxiliary bearing 43, and the partitioning portions 210 and 211 form a compression mechanism 212 according to the present embodiment.
- An upper end opening portion of the upper cylinder 201 is closed by the main bearing 42.
- a space defined by the upper cylinder 201, the main bearing 42, and the upper partitioning portion 210 forms an upper cylinder chamber 221.
- a lower end opening portion of the lower cylinder 203 is closed by the auxiliary bearing 43.
- a space defined by the lower cylinder 203, the auxiliary bearing 43, and the lower partitioning portion 211 forms a lower cylinder chamber 223.
- the rotary shaft 225 includes a base shaft portion 226 provided with the thrust sliding portion 90, and a supplementary shaft portion 228 fixed to the base shaft portion 226 and forming a protruding portion 227.
- the base shaft portion 226 includes a plurality of eccentric portions 231 to 233 accommodated in the respective cylinder chambers 221 to 223.
- the upper eccentric portion 231 is formed in a portion located inside the upper cylinder chamber 221 in the base shaft portion 226.
- the intermediate eccentric portion 232 is formed in a portion located inside the intermediate cylinder chamber 222 in the base shaft portion 226.
- the lower eccentric portion 233 is formed in a portion located inside the lower cylinder chamber 223 in the base shaft portion 226.
- Each of the eccentric portions 231 to 233 has the same outer shape and the same size when viewed in the axial direction.
- Each of the eccentric portions 231 to 233 is eccentric with respect to the axis line O by the same amount in the radial direction while having a phase difference of 120° in the circumferential direction. That is, eccentric directions of the respective eccentric portions 231 to 233 are set to be equal to each other in the circumferential direction.
- a roller 53 is fitted to each of the eccentric portions 231 to 233.
- the lower end surface of the base shaft portion 226 serves as the thrust sliding portion 90.
- a base flow path 235 is formed in the base shaft portion 226.
- the base flow path 235 extends coaxially with the axis line O.
- a lower end portion of the base flow path 235 is open on a lower end surface (thrust sliding portion 90) of the base shaft portion 226.
- the base flow path 235 communicates with each of the sub-flow paths 96 and 97.
- the sub-flow path may be provided at a position corresponding to each of the partitioning portions 210 and 211.
- the protruding portion 227 including the supplementary shaft portion 228 is formed in a cylindrical shape extending coaxially with the axis line O. That is, the inside of the protruding portion 227 forms a protruding portion flow path 236 that penetrates the protruding portion 227 in the axial direction.
- An upper end portion of the protruding portion 227 is fixed inside the base flow path 235 by means of press-fitting. That is, the protruding portion 227 is fixed to the base shaft portion 226 in a state where the protruding portion 227 protrudes downward from the thrust sliding portion 90, and the base flow path 235 and the protruding portion flow path 236 communicate with each other.
- the base flow path 235 and the protruding portion flow path 236 form a main flow path 237 according to the present embodiment.
- a method of fixing the base shaft portion 226 of the protruding portion 227 may be any desired method other than the press-fitting.
- a balancer cover 240 includes a cover body 241 that covers the auxiliary bearing 43 from below, and a thrust plate 242 attached to the cover body 241. Even in the present embodiment, the inside of the balancer cover 240 communicates with the inside of the muffler 65 through a communication hole (not shown).
- the cover body 241 is formed in a bottomed cylindrical shape. An upper end portion of the cover body 241 is attached to the flange portion 72 of the auxiliary bearing 43. An accommodation hole 243 is formed in a bottom portion of the cover body 241. The accommodation hole 243 penetrates the bottom portion of the cover body 241 in the axial direction. A lower end portion of the base shaft portion 226 is accommodated inside the accommodation hole 243. In the illustrated example, it is preferable that the thrust sliding portion 90 and the bottom portion (lower surface) of the cover body 241 are disposed flush with each other.
- the thrust plate 242 is formed in a disk shape having a diameter larger than that of the above-described accommodation hole 243.
- the thrust plate 242 closes the accommodation hole 243 from below in a state where an outer peripheral portion is fixed to the bottom portion of the cover body 241 by a screw 244.
- a through-hole 245 is formed in a portion that overlaps the main flow path 237 of the rotary shaft 225 when viewed in the axial direction.
- the inner diameter of the through-hole 245 is smaller than the inner diameter of the accommodation hole 243 and is larger than the outer diameter of the protruding portion 227.
- the above-described protruding portion 227 penetrates into the through-hole 245. In this manner, a lower end opening portion of the main flow path 95 communicates with the inside of the case 34 below the balancer cover 81 (lower surface of the thrust plate 242).
- the above-described thrust sliding portion 90 is in contact with a portion (seal 242a) located around the through-hole 245 in the axial direction, on the upper surface of the thrust plate 242. In this manner, communication between the inside of the balancer cover 81 and the inside of the case 34 is blocked.
- a gap S1 in the radial direction between the inner peripheral surface of the accommodation hole 243 and the outer peripheral surface of the base shaft portion 226 is larger than a gap S2 in the radial direction between the inner peripheral surface of the through-hole 245 and the outer peripheral surface of the protruding portion 227.
- the gaps S1 and S2 do may not be uniform in the entire circumferential direction due to dimensional variations.
- the gap S1 may be equal to or smaller than the gap S2.
- Fig. 5 is a process drawing for describing the assembly process.
- the assembly process of the thrust plate 242 includes a positioning process and a fixing process.
- a jig 250 is used to position the thrust plate 242 with respect to the protruding portion 227.
- the jig 250 is formed in a cylindrical shape disposed coaxially with the axis line O.
- the jig 250 has an operation portion 251 located in a lower portion and a plate holding portion 252 located in an upper portion.
- the outer diameter of the operation portion 251 is larger than the inner diameter of the through-hole 245.
- the plate holding portion 252 is connected to an upper side of the operation portion 251.
- the plate holding portion 252 is formed in a tapered shape whose outer diameter gradually decreases upward.
- a minimum outer diameter of the plate holding portion 252 is smaller than the inner diameter of the through-hole 245.
- the inside of the jig 250 forms an insertion hole 253 into which the protruding portion 227 can be inserted.
- the jig 250 is not limited to a cylindrical shape as long as a configuration has a plate holding portion for holding the inner peripheral surface of the through-hole 245 and an accommodation portion capable of accommodating the protruding portion 227.
- the plate holding portion 252 is inserted into the through-hole 245 of the thrust plate 242. Then, a lower end opening edge of the through-hole 245 is held by the outer peripheral surface of the plate holding portion 252. It is preferable that the plate holding portion 252 holds the thrust plate 242 in a state where the plate holding portion 252 does not protrude upward from the through-hole 245.
- the jig 250 is disposed coaxially with the axis line O below the rotary shaft 225 (cover body 241), and the thrust plate 242 and the jig 250 are raised. Then, the thrust plate 242 moves close to the cover body 241 while the protruding portion 227 is inserted into the insertion hole 253 of the jig 250. The thrust plate 242 is raised until the thrust plate 242 abuts the lower surface of the cover body 241.
- the size of the gap between the through-hole 245 of the thrust plate 242 and the outer peripheral surface of the protruding portion 227 becomes substantially uniform in the circumferential direction, and the thrust plate 242 is positioned in the radial direction with respect to the protruding portion 227.
- the thrust plate 242 may be rotated in the circumferential direction with respect to the cover body 241 to align a fixing portion between the thrust plate 242 and the cover body 241.
- the thrust plate 242 is fixed to the cover body 241 by a screw 244 (refer to Fig. 4 ). Thereafter, the jig 250 is retreated to complete the assembly process of the thrust plate 242.
- the base shaft portion 226 and the protruding portion 227 are separately formed.
- the rotary shaft does not need to be processed into a stepped shape as in a case where the base shaft portion and the protruding portion are integrally formed. Therefore, the accurate thrust sliding portion 90 can easily be manufactured, and it is possible to provide the low cost rotary compressor 200 having excellent manufacturing efficiency. Since the base shaft portion 226 and the protruding portion 227 are separately formed, an optimum material can be selected for each component. Therefore, design can more freely be selected.
- the present embodiment adopts a configuration as follows.
- the gap S1 in the radial direction between the inner peripheral surface of the accommodation hole 243 and the outer peripheral surface of the base shaft portion 226 is larger than the gap S2 in the radial direction between the inner peripheral surface of the through-hole 245 and the outer peripheral surface of the protruding portion 227.
- the gap S1 is enlarged, the lubricating oil J existing inside the balancer cover 240 can easily be accommodated inside the gap S1.
- the lubricating oil J is likely to be interposed between the outer peripheral surface of the base shaft portion 226 and the inner peripheral surface of the accommodation hole 243, and between the thrust sliding portion 90 and the seal 242a. Therefore, it is possible to improve lubrication performance.
- the present embodiment adopts a configuration as follows.
- the jig 250 having the plate holding portion 252 for holding the inner peripheral surface of the through-hole 245 and the insertion hole 253 into which the protruding portion 227 is inserted is used so that the thrust plate 242 is positioned with respect to the protruding portion 227.
- the gap S1 is enlarged as described above. In this manner, it is easy to avoid contact between the base shaft portion 226 having a large turning radius in the rotary shaft 225 and the cover body 241. In this manner, it is also possible to suppress the friction during the operation.
- each of the rotary shaft 225 and the balancer cover 240 is separately formed.
- any one of the rotary shaft 225 and the balancer cover 240 may separately be formed.
- the thrust plate 242 is assembled in a state where the rotary shaft 225 and the cover body 241 are assembled.
- the present invention is not limited only to this configuration.
- the cover body 241 may be assembled to the auxiliary bearing 43 in a state where the cover body 241 and the thrust plate 242 are assembled in advance.
- desired lubrication performance can be obtained.
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Abstract
Description
- Embodiments of the present invention relate to a rotary compressor, a method for manufacturing a rotary compressor, and a refrigeration cycle apparatus.
- Priority is claimed on
Japanese Patent Application No. 2019-020870, filed on February 7, 2019 - A rotary compressor is used in a refrigeration cycle apparatus such as an air conditioner. In the rotary compressor, a refrigerant is compressed in such a manner that an eccentric portion of a rotary shaft is eccentrically rotated by a compression mechanism.
- In this type of the rotary compressor, the rotary shaft has a supply channel for supplying a lubricating oil stored inside a case to a sliding portion between the rotary shaft and a bearing. However, when the refrigerant compressed by the compression mechanism enters the supply channel, there is a possibility that desired lubrication performance may not be obtained.
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Japanese Unexamined Patent Application, First Publication No. 2018-165502 - An object of the present invention is to provide a rotary compressor, a method for manufacturing a rotary compressor, and a refrigeration cycle apparatus which are capable of obtaining desired lubrication performance.
- A rotary compressor according to an embodiment includes a case, a rotary shaft, a compression mechanism, a balancer, and a balancer cover. A lubricating oil is stored in the case. The rotary shaft is disposed inside the case, and has an eccentric portion. The compression mechanism has a cylinder, a main bearing, and an auxiliary bearing. The cylinder accommodates the eccentric portion. The main bearing rotatably supports the rotary shaft from above the cylinder. The auxiliary bearing rotatably supports the rotary shaft from below the cylinder. A through-hole is formed at a position of the balancer cover facing the rotary shaft in the axial direction. The rotary shaft has a thrust sliding portion, a protruding portion, and a supply channel. The thrust sliding portion of the rotary shaft comes into contact with a seal located around the through-hole of the balancer cover, in the axial direction. The protruding portion is located on an inner peripheral side of the thrust sliding portion, and protrudes downward from the through-hole through the through-hole. The supply channel is open on a lower end surface of the protruding portion to guide the lubricating oil.
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Fig. 1 is a schematic configuration diagram of a refrigeration cycle apparatus including a sectional view of a rotary compressor according to a first embodiment. -
Fig. 2 is a sectional view of a compression mechanism corresponding to line 11-II inFig. 1 . -
Fig. 3 is an enlarged view of a main part inFig. 1 . -
Fig. 4 is a partial sectional view of a rotary compressor according to a second embodiment. -
Fig. 5 is a process drawing for describing an assembly process. - Hereinafter, a rotary compressor according to an embodiment, a method for manufacturing a rotary compressor, and a refrigeration cycle apparatus will be described with reference to the drawings.
- First, a refrigeration cycle apparatus 1 will briefly be described.
Fig. 1 is a schematic configuration diagram of the refrigeration cycle apparatus 1 including a sectional view of arotary compressor 2 according to a first embodiment. - As shown in
Fig. 1 , the refrigeration cycle apparatus 1 according to the present embodiment includes therotary compressor 2, acondenser 3 serving as a radiator connected to therotary compressor 2, anexpansion device 4 connected to thecondenser 3, and anevaporator 5 serving as a heat absorber connected between theexpansion device 4 and therotary compressor 2. - The
rotary compressor 2 is a so-called rotary-type compressor. Therotary compressor 2 compresses an internally fetched low-pressure gas refrigerant and obtains a high-temperature and high-pressure gas refrigerant. A specific configuration of therotary compressor 2 will be described later. - The
condenser 3 dissipates heat from the high-temperature and high-pressure gas refrigerant fed from therotary compressor 2, and obtains a high-pressure liquid refrigerant. - The
expansion device 4 lowers a pressure of the high-pressure liquid refrigerant fed from thecondenser 3 and obtains a low-temperature and low-pressure liquid refrigerant. - The
evaporator 5 vaporizes the low-temperature and low-pressure liquid refrigerant fed from theexpansion device 4 and changes the low-temperature and low-pressure liquid refrigerant into a low-pressure gas refrigerant. In theevaporator 5, when the low-pressure liquid refrigerant vaporizes, heat of vaporization is taken from surroundings, and the surroundings are cooled. The low-pressure gas refrigerant passing through theevaporator 5 is fetched into the above-describedrotary compressor 2. - In this way, in the refrigeration cycle apparatus 1 according to the present embodiment, the refrigerant serving as a working fluid circulates while changing a phase between the gas refrigerant and the liquid refrigerant. In the refrigeration cycle apparatus 1 according to the present embodiment, as the refrigerant, it is possible to use an HFC-based refrigerant such as R410A and R32, an HFO-based refrigerant such as R1234yf and R1234ze, or a natural refrigerant such as CO2.
- Next, the above-described
rotary compressor 2 will be described. - The
rotary compressor 2 according to the present embodiment includes acompressor body 11 and anaccumulator 12. - The
accumulator 12 is a so-called gas-liquid separator. Theaccumulator 12 is provided between the above-describedevaporator 5 and thecompressor body 11. Theaccumulator 12 is connected to thecompressor body 11 through asuction pipe 21. Theaccumulator 12 supplies only the gas refrigerant to thecompressor body 11, out of the gas refrigerant vaporized by theevaporator 5 and the liquid refrigerant not vaporized by theevaporator 5. - The
compressor body 11 includes arotary shaft 31, anelectric motor unit 32, acompression mechanism 33, and acase 34 for accommodating therotary shaft 31, theelectric motor unit 32, and thecompression mechanism 33. Thecompressor body 11 according to the present embodiment is disposed in a state where an axial direction of therotary shaft 31 is an upward-downward direction. - The
case 34 is formed in a cylindrical shape, and both end portions in the axial direction are closed. A lubricating oil J is accommodated inside thecase 34. A portion of thecompression mechanism 33 is immersed into the lubricating oil J. - The
rotary shaft 31 is disposed coaxially with an axis line O of thecase 34. In the following description, a direction extending along the axis line O will simply be referred to as the axial direction, a direction orthogonal to the axial direction will be referred to as a radial direction, and a direction turning around the axis line O will be referred to as a circumferential direction. - The
electric motor unit 32 is disposed on a first side inside thecase 34 in the axial direction. Thecompression mechanism 33 is disposed on a second side inside thecase 34 in the axial direction. In the following description, theelectric motor unit 32 side along the axial direction will be referred to as an upper side, and thecompression mechanism 33 side will be referred to as a lower side. - The
electric motor unit 32 is a so-called inner rotor type DC brushless motor. Specifically, theelectric motor unit 32 includes astator 35 and arotor 36. - The
stator 35 is fixed to an inner wall surface of thecase 34 by means of shrink fitting. - The
rotor 36 is fixed to an upper portion of therotary shaft 31 in a state where an interval is formed inside thestator 35 in the radial direction. - A counter bore 37 is formed in an inner peripheral portion on a lower surface of the
rotor 36. The counter bore 37 is an annular recess portion recessed upward from the lower surface of therotor 36, and formed over an entire periphery of therotor 36. Abalancer 39 is provided in an outer peripheral portion on the lower surface of therotor 36. For example, thebalancer 39 is formed in an arc shape in a plan view when viewed in the axial direction. Thebalancer 39 is provided in a portion in the circumferential direction on the lower surface of therotor 36. - The
compression mechanism 33 includes acylinder 41 having a cylindrical shape through which therotary shaft 31 penetrates, and amain bearing 42 and anauxiliary bearing 43 which individually close both end opening portions of thecylinder 41 and rotatably support therotary shaft 31. A space formed by thecylinder 41, themain bearing 42, and theauxiliary bearing 43 forms acylinder chamber 46. - An
eccentric portion 51 eccentric in the radial direction with respect to the axis line O is formed in a portion located inside thecylinder chamber 46 in the above-describedrotary shaft 31. In the present embodiment, an eccentric direction of theeccentric portion 51 is set on a side opposite to thebalancer 39 across the axis line O. - A
roller 53 is externally inserted into theeccentric portion 51. Theroller 53 is configured to be eccentrically rotatable with respect to the axis line O while an outer peripheral surface is in sliding contact with an inner peripheral surface of thecylinder 41 as therotary shaft 31 is rotated. -
Fig. 2 is a sectional view of thecompression mechanism 33 corresponding to line II-II inFig. 1 . - As shown in
Fig. 2 , in thecylinder 41, ablade groove 54 recessed outward in the radial direction is formed in a portion in the circumferential direction. Theblade groove 54 is formed over in the axial direction (upward-downward direction) of thecylinder 41. Theblade groove 54 communicates with the inside of thecase 34 in an outer end portion in the radial direction. - A
blade 55 is provided in theblade groove 54. Theblade 55 is configured to be slidable in the radial direction with respect to thecylinder 41. Theblade 55 is biased inward in the radial direction by a biasing member (not shown). An inner end surface of theblade 55 in the radial direction is in contact with an outer peripheral surface of theroller 53 inside thecylinder chamber 46. In this manner, theblade 55 moves forward and rearward inside thecylinder chamber 46 as theroller 53 is eccentrically rotated. - The
cylinder chamber 46 is divided into asuction chamber 46a and acompression chamber 46b by theroller 53 and theblade 55. In thecompression mechanism 33, a compression operation is performed inside thecylinder chamber 46 by a rotation operation of theroller 53 and a forward/rearward operation of theblade 55. - In the
cylinder 41, asuction hole 56 that penetrates thecylinder 41 in the radial direction is formed in a portion located on an inner side (left side of theblade groove 54 inFig. 2 ) of theblade groove 54 along a rotation direction of the roller 53 (refer to an arrow inFig. 2 ). The above-described suction pipe 21 (refer toFig. 1 ) is connected to thesuction hole 56 from an outer end portion in the radial direction. On the other hand, an inner end portion of thesuction hole 56 in the radial direction is open into the cylinder chamber 46 (suction chamber 46a). - The
main bearing 42 closes an upper end opening portion of thecylinder 41. Themain bearing 42 rotatably supports a portion located above thecylinder 41 in therotary shaft 31. Specifically, themain bearing 42 includes acylinder portion 61 into which therotary shaft 31 is inserted, and aflange portion 62 protruding outward in the radial direction from a lower end portion of thecylinder portion 61. - An upper end portion of the
cylinder portion 61 is accommodated inside the above-described counter bore 37. In this manner, the rotary compressor 2 (compressor body 11) is miniaturized in the axial direction. - A main
bearing discharge hole 64 that penetrates theflange portion 62 in the axial direction is formed in a portion of theflange portion 62 in the circumferential direction. The mainbearing discharge hole 64 communicates with the inside of the cylinder chamber 46 (compression chamber 46b). Adischarge valve mechanism 67 is disposed in theflange portion 62. Thedischarge valve mechanism 67 opens the mainbearing discharge hole 64 as the pressure inside the cylinder chamber 46 (compression chamber 46b) increases, and discharges the refrigerant outward of thecylinder chamber 46. - The
main bearing 42 is provided with amuffler 65 that covers themain bearing 42 from above. Acommunication hole 66 that causes the inside and the outside of themuffler 65 to communicate with each other is formed in a central portion of themuffler 65 in the radial direction. The high-temperature and high-pressure gas refrigerant discharged through the above-describeddischarge hole 64 is discharged into thecase 34 through thecommunication hole 66. - The
auxiliary bearing 43 closes a lower end opening portion of thecylinder 41. Theauxiliary bearing 43 rotatably supports a portion located below thecylinder 41 in therotary shaft 31. Specifically, theauxiliary bearing 43 includes acylinder portion 71 into which therotary shaft 31 is inserted, and aflange portion 72 protruding outward in the radial direction from the upper end portion of thecylinder portion 71. - An auxiliary
bearing discharge hole 73 that penetrates theflange portion 72 in the axial direction is formed in a portion of theflange portion 72 in the circumferential direction. The auxiliarybearing discharge hole 73 communicates with the inside of the cylinder chamber 46 (compression chamber 46b). Adischarge valve mechanism 75 is provided in theflange portion 72. Thedischarge valve mechanism 75 opens the auxiliarybearing discharge hole 73 as the pressure inside the cylinder chamber 46 (compression chamber 46b) increases and discharges the refrigerant outward of thecylinder chamber 46. - The
auxiliary bearing 43 is provided with abalancer cover 81 that covers theauxiliary bearing 43 from below. Thebalancer cover 81 is formed in a bottomed cylindrical shape that is open upward. Aseal 82 is formed in a central portion in the radial direction in a bottom portion of thebalancer cover 81. Theseal 82 is formed to bulge upward with respect to an outer peripheral portion in the bottom portion of thebalancer cover 81. However, theseal 82 may not bulge from the bottom portion of thebalancer cover 81. An upper surface of theseal 82 is formed to have a flat surface orthogonal to the axis line O. A through-hole 84 that penetrates theseal 82 in the axial direction is formed in a central portion (portion located on the axis line O) of theseal 82. - The
main bearing 42, thecylinder 41, and theauxiliary bearing 43 have acommunication hole 85 for causing the inside of the inside of themuffler 65 and the inside of thebalancer cover 81 to communicate with each other. Thecommunication hole 85 penetrates themain bearing 42, thecylinder 41, and theauxiliary bearing 43 in the axial direction at a position where thecommunication hole 85 faces the above-described discharge holes 64 and 73 across the axis line O in the radial direction. -
Fig. 3 is an enlarged view of a main part inFig. 1 . - As shown in
Fig. 3 , therotary shaft 31 according to the present embodiment has athrust sliding portion 90 and a protrudingportion 87 located on an inner peripheral side of thethrust sliding portion 90 and protruding downward. - The
rotary shaft 31 further has the above-describedeccentric portion 51, amain shaft portion 88, and anauxiliary shaft portion 89. - The
main shaft portion 88 is a portion located above theeccentric portion 51 in the above-describedrotary shaft 31. Themain shaft portion 88 is connected to an upper side of theeccentric portion 51 via a connectingportion 51a. Themain shaft portion 88 is supported by themain bearing 42, and therotor 36 is fixed to themain shaft portion 88. - On the other hand, the
auxiliary shaft portion 89 is a portion located below theeccentric portion 51 in therotary shaft 31. Theauxiliary shaft portion 89 is connected to a lower side of theeccentric portion 51 via a connectingportion 51b. Theauxiliary shaft portion 89 is supported by theauxiliary bearing 43. In the present embodiment, an outer diameter ϕDs of theauxiliary shaft portion 89 is smaller than an outer diameter ϕDm of themain shaft portion 88. However, in theauxiliary shaft portion 89, at least a portion protruding downward from theauxiliary bearing 43 may have a diameter smaller than that of themain shaft portion 88. That is, a portion located inside theauxiliary bearing 43 in theauxiliary shaft portion 89 may have an outer diameter the same as that of themain shaft portion 88. - The
seal 82 of thebalancer cover 81 receives an axial load acting on therotary shaft 31 and supports thethrust sliding portion 90 of therotary shaft 31 to be slidable. Thethrust sliding portion 90 and theseal 82 come into contact with each other in the axial direction, thereby blocking communication between the inside and the outside of thebalancer cover 81 through the through-hole 84. Thethrust sliding portion 90 according to the present embodiment is a lower end surface of theauxiliary shaft portion 89. Thethrust sliding portion 90 is a flat surface orthogonal to the axial direction. It is preferable that thethrust sliding portion 90 is pressed against theseal 82 by the weight of therotary shaft 31 and therotor 36, or a magnetic force generated between thestator 35 and therotor 36. In the present embodiment, the base shaft portion is configured to include theeccentric portion 51, themain bearing 88, and theauxiliary bearing 89. - A
balancer 91 is attached to a portion protruding downward from theauxiliary bearing 43 in theauxiliary shaft portion 89. For example, thebalancer 91 is formed in a disk shape. Anattachment hole 92 that penetrates thebalancer 91 in the axial direction is formed at a position eccentric with respect to the center of thebalancer 91. Theauxiliary shaft portion 89 of therotary shaft 31 is fixed inside theattachment hole 92 by means of press-fitting. In this case, the center of thebalancer 91 is eccentric with respect to the axis line O in a direction opposite to an eccentric direction of the eccentric portion 51 (direction the same as that of the balancer 39). That is, thebalancer 91 and theeccentric portion 51 are disposed with a phase difference of 180° in the circumferential direction. The shape of thebalancer 91 is not limited to the disc shape. - In this way, in the present embodiment, the
balancer 91 is provided in theauxiliary shaft portion 89. Accordingly, for example, compared to a case where the balancer is provided on an upper surface of therotor 36, a distance between thebalancer 91 and the bearing (in the present embodiment, the auxiliary bearing 43) can be shortened. In this manner, it is possible to suppress bending of therotor 36. - Here, in the
compressor body 11, a centrifugal force is generated in theeccentric portion 51 and therespective balancers rotary shaft 31 is rotated. In this case, in order to stabilize rotational balance of therotary shaft 31, it is preferable to satisfy two Equations ((1) and (2)) below. - Specifically, a centrifugal force acting on the
eccentric portion 51 is defined as F0, a centrifugal force acting on thebalancer 91 is defined as F1, and a centrifugal force acting on thebalancer 39 is defined as F2. In this case, it is preferable that a resultant force of the respective centrifugal forces F0, F1, and F2 becomes 0 (refer to Equation (1) below). The respective centrifugal forces F0, F1, and F2 can be calculated by mrω2 (m: mass, r: distance in the radial direction from the axis line O, and ω: angular velocity). - The center of action of the centrifugal force F0 is defined as a reference point, a distance in the axial direction from the reference point to the center of action of the centrifugal force F1 is defined as L1, and a distance in the axial direction from the reference point to the center of action of the centrifugal force F2 is defined as L2. In this case, it is preferable that a sum of moments acting on the
rotary shaft 31 due to the centrifugal forces F1 and F2 becomes 0 (refer to Equation (2) below). - In the present embodiment, it is preferable that the distance L1 in the axial direction from the reference point to the center of action of the centrifugal force F1 is equal to or longer than the distance L2 in the axial direction from the reference point to the center of action of the centrifugal force F2 (L1≥L2). In this manner, the
balancer 91 can be miniaturized, and the amount of eccentricity can be reduced. As a result, the protruding amount of thebalancer 91 in the radial direction with respect to the axis line O can be particularly suppressed, and thecompressor body 11 in the radial direction can be miniaturized. - The protruding
portion 87 protrudes downward from an inner peripheral portion of thethrust sliding portion 90. The protrudingportion 87 protrudes downward from a lower end opening edge of the through-hole 84 through the through-hole 84. Specifically, the protrudingportion 87 according to the present embodiment protrudes downward from a lowest point (lower surface of the seal 82) of thebalancer cover 81. Therotary shaft 31 can be displaced (backlash in the upward-downward direction) by a predetermined distance in the axial direction with respect to thecompression mechanism 33, due to a difference between the height of thecylinder chamber 46 and the length in the axial direction of the connectingportions eccentric portion 51 and theeccentric portion 51. Therefore, in the present embodiment, the protruding amount from the lower end opening edge of the through-hole 84 of the protrudingportion 87 is larger than the predetermined distance which is a displacement amount of therotary shaft 31. That is, even when therotary shaft 31 is displaced in the upward-downward direction by the amount of backlash, the protruding amount of the protrudingportion 87 is set so that the protrudingportion 87 always protrudes downward from the lower end opening edge of the through-hole 84 of thebalancer cover 81. - The
rotary shaft 31 has asupply channel 94 for supplying the lubricating oil J to each sliding portion in the compression mechanism 33 (for example, a portion between theeccentric portion 51 and theroller 53, and a portion between therotary shaft 31 and thebearings 42 and 43). Thesupply channel 94 has a main flow path 95 extending coaxially with the axis line O, andsub-flow paths - A lower end portion of the main flow path 95 is open on a lower end surface of the rotary shaft 31 (protruding portion 87). In this manner, the lubricating oil J inside the
case 34 can flow into the main flow path 95. - An upper end portion of the main flow path 95 is terminated in a lower end portion of the
main shaft portion 88. However, the length in the axial direction of the main flow path 95 can appropriately be changed as long as the length reaches at least thecylinder 41. For example, the main flow path 95 may penetrate therotary shaft 31 in the axial direction. A twist plate that promotes the lubricating oil J to rise as therotary shaft 31 is rotated may be provided on an inner peripheral surface of the main flow path 95. - The first
sub-flow path 96 is formed in a connecting portion (connectingportion 51a) between themain shaft portion 88 and theeccentric portion 51 in therotary shaft 31. An inner end portion in the radial direction of the firstsub-flow path 96 communicates with the inside of the above-described main flow path 95. On the other hand, an outer end portion in the radial direction of the firstsub-flow path 96 is open outward in the radial direction on an outer peripheral surface of therotary shaft 31. - The second
sub-flow path 97 is formed in a portion located inside theauxiliary bearing 43 in theauxiliary shaft portion 89. An inner end portion in the radial direction of the secondsub-flow path 97 communicates with the inside of the above-described main flow path 95. On the other hand, an outer end portion in the radial direction of the secondsub-flow path 97 is open outward in the radial direction on the outer peripheral surface of therotary shaft 31. - A
lower circulation path 99 is formed on the outer peripheral surface of the rotary shaft 31 (auxiliary shaft portion 89). Thelower circulation path 99 is formed by a spiral groove formed on the outer peripheral surface of therotary shaft 31. A lower end portion of thelower circulation path 99 communicates with the inside of the secondsub-flow path 97. On the other hand, an upper end portion of thelower circulation path 99 is located in the upper end portion of theauxiliary shaft portion 89. Thelower circulation path 99 guides the lubricating oil J upward from below when therotary shaft 31 is rotated. Thelower circulation path 99 may be configured so that the lubricating oil J can be supplied between the outer peripheral surface of theauxiliary shaft portion 89 and the inner peripheral surface of the auxiliary bearing 43 (cylinder portion 71). In this case, for example, a groove may be formed on the inner peripheral surface of thecylinder portion 71. A shape or a layout of thelower circulation path 99 can appropriately be changed. - In the
main bearing 42, an upper circulation path (not shown) is formed on the inner peripheral surface of thecylinder portion 61. The upper circulation path is formed in a spiral groove. The lower end portion of the upper circulation path communicates with the inside of the firstsub-flow path 96. On the other hand, the upper end portion of the upper circulation path communicates with the inside of thecase 34. The upper circulation path guides the lubricating oil J upward from below when therotary shaft 31 is rotated. The upper circulation path may be formed on the outer peripheral surface of themain shaft portion 88. - Next, an operation of the above-described
rotary compressor 2 will be described. - As shown in
Fig. 1 , when electric power is supplied to thestator 35 of theelectric motor unit 32, therotary shaft 31 is rotated around the axis line O together with therotor 36. As therotary shaft 31 is rotated, theeccentric portion 51 and theroller 53 are eccentrically rotated inside thecylinder chamber 46. In this case, each of therollers 53 comes into sliding contact with the inner peripheral surface of thecylinder 41. In this manner, the gas refrigerant is fetched into thecylinder chamber 46 through thesuction pipe 21, and the gas refrigerant fetched into thecylinder chamber 46 is compressed. - Specifically, in the
cylinder chamber 46, the gas refrigerant is suctioned into thesuction chamber 46a through thesuction hole 56, and the gas refrigerant previously suctioned from thesuction hole 56 is compressed in thecompression chamber 46b. In the compressed gas refrigerant, the gas refrigerant discharged into themuffler 65 through the mainbearing discharge hole 64 is discharged into thecase 34 through thecommunication hole 66 of themuffler 65. On the other hand, in the compressed gas refrigerant, the gas refrigerant discharged into thebalancer cover 81 through the auxiliarybearing discharge hole 73 flows into themuffler 65 through thecommunication hole 85, and thereafter, is discharged into thecase 34 through thecommunication hole 66 of themuffler 65. The gas refrigerant discharged into thecase 34 is fed to thecondenser 3 as described above. - Incidentally, a pressure equivalent to a discharge pressure of the gas refrigerant acts on the lubricating oil J inside the
case 34. Therefore, the lubricating oil J flows into the main flow path 95, and rises inside the main flow path 95 as therotary shaft 31 is rotated. The lubricating oil J rising inside the main flow path 95 is distributed to each of thesub-flow paths rotary shaft 31. - The lubricating oil J distributed to each of the
sub-flow paths rotary shaft 31 and is supplied to each sliding portion. For example, the lubricating oil J discharged from the firstsub-flow path 96 rises inside the upper circulation path as therotary shaft 31 is rotated and is supplied to a portion between themain shaft portion 88 and themain bearing 42. On the other hand, the lubricating oil J discharged from the secondsub-flow path 97 rises inside thelower circulation path 99 as therotary shaft 31 is rotated and is supplied to a portion between theauxiliary shaft portion 89 and theauxiliary bearing 43 and a portion between theeccentric portion 51 and theroller 53. The lubricating oil J supplied to each sliding portion is discharged from thecompression mechanism 33 through a portion between themain shaft portion 88 and themain bearing 42 and through thecylinder chamber 46. - Here, the present embodiment adopts a configuration as follows. The
thrust sliding portion 90 of therotary shaft 31 and theseal 82 of thebalancer cover 81 are brought into contact with each other to seal a portion in the axial direction between therotary shaft 31 and thebalancer cover 81. - According to this configuration, the portion in the axial direction between the
rotary shaft 31 and thebalancer cover 81 is sealed by theseal 82. Accordingly, it is possible to suppress a possibility that the lubricating oil J accommodated inside thecase 34 may enter the inside of thebalancer cover 81. The possibility that the lubricating oil J may enter the inside of thebalancer cover 81 is suppressed. Accordingly, even when thebalancer 91 is provided in theauxiliary shaft portion 89, it is possible to suppress a possibility that the eccentric rotation of thebalancer 91 may be hindered by the lubricating oil J when therotary shaft 31 is rotated. In this manner, rotational resistance acting on thebalancer 91 can be reduced when therotary shaft 31 is rotated. As a result, therotary shaft 31 can efficiently be rotated, and compression performance can be improved. - Incidentally, in the
rotary compressor 2, when therotary shaft 31 is displaced upward due to vibration caused by the eccentric rotation, thethrust sliding portion 90 and theseal 82 may be separated from each other in some cases. In this case, there is a possibility that the gas refrigerant discharged into thebalancer cover 81 through the auxiliarybearing discharge hole 73 may leak outward of thebalancer cover 81 through the through-hole 84. - Therefore, the present embodiment adopts a configuration as follows. The protruding
portion 87 protrudes downward from the lower end opening edge of the through-hole 84 of thebalancer cover 81 more than the predetermined distance which is the displacement amount of therotary shaft 31. According to this configuration, when the gas refrigerant discharged into thebalancer cover 81 leaks outward of thebalancer cover 81 through the through-hole 84, it is possible to suppress a possibility that the gas refrigerant may flow into the main flow path 95 after turning around the protrudingportion 87. In this manner, it is possible to suppress a possibility that the gas refrigerant may flow into thesupply channel 94 and the lubricating oil J may not spread to the sliding portion. That is, in therotary compressor 2 according to the present embodiment, the lubricating oil J can effectively be supplied to the sliding portion, and the desired lubrication performance can be obtained. - The refrigeration cycle apparatus 1 according to the present embodiment includes the above-described
rotary compressor 2. Accordingly, it is possible to provide the refrigeration cycle apparatus 1 capable of improving operation reliability and compression performance over a long period of time. -
Fig. 4 is a partial sectional view of arotary compressor 200 according to a second embodiment. In the following description, the same reference numerals will be assigned to configurations the same as those of the above-described embodiment, and description thereof will be omitted. - The
rotary compressor 200 according to the present embodiment is different from the above-described first embodiment in that a plurality of (for example, three) cylinders (upper cylinder 201,intermediate cylinder 202, and lower cylinder 203) are aligned in the axial direction. - In the
rotary compressor 200 shown inFig. 4 , theupper cylinder 201 and theintermediate cylinder 202 abut each other in the axial direction while anupper partitioning portion 210 is interposed therebetween. Theintermediate cylinder 202 and thelower cylinder 203 abut each other in the axial direction while alower partitioning portion 211 is interposed therebetween. A configuration of each of thecylinders 201 to 203 is the same as that of the above-described embodiment. Theupper cylinder 201, thelower cylinder 203, themain bearing 42, theauxiliary bearing 43, and thepartitioning portions compression mechanism 212 according to the present embodiment. - An upper end opening portion of the
upper cylinder 201 is closed by themain bearing 42. A space defined by theupper cylinder 201, themain bearing 42, and theupper partitioning portion 210 forms anupper cylinder chamber 221. - A space defined by the
intermediate cylinder 202 and thepartitioning portions intermediate cylinder chamber 222. - A lower end opening portion of the
lower cylinder 203 is closed by theauxiliary bearing 43. A space defined by thelower cylinder 203, theauxiliary bearing 43, and thelower partitioning portion 211 forms alower cylinder chamber 223. - The
rotary shaft 225 includes abase shaft portion 226 provided with thethrust sliding portion 90, and asupplementary shaft portion 228 fixed to thebase shaft portion 226 and forming a protrudingportion 227. - The
base shaft portion 226 includes a plurality ofeccentric portions 231 to 233 accommodated in therespective cylinder chambers 221 to 223. Specifically, the uppereccentric portion 231 is formed in a portion located inside theupper cylinder chamber 221 in thebase shaft portion 226. The intermediateeccentric portion 232 is formed in a portion located inside theintermediate cylinder chamber 222 in thebase shaft portion 226. The lowereccentric portion 233 is formed in a portion located inside thelower cylinder chamber 223 in thebase shaft portion 226. Each of theeccentric portions 231 to 233 has the same outer shape and the same size when viewed in the axial direction. Each of theeccentric portions 231 to 233 is eccentric with respect to the axis line O by the same amount in the radial direction while having a phase difference of 120° in the circumferential direction. That is, eccentric directions of the respectiveeccentric portions 231 to 233 are set to be equal to each other in the circumferential direction. Aroller 53 is fitted to each of theeccentric portions 231 to 233. The lower end surface of thebase shaft portion 226 serves as thethrust sliding portion 90. - A
base flow path 235 is formed in thebase shaft portion 226. Thebase flow path 235 extends coaxially with the axis line O. A lower end portion of thebase flow path 235 is open on a lower end surface (thrust sliding portion 90) of thebase shaft portion 226. Thebase flow path 235 communicates with each of thesub-flow paths base shaft portion 226, the sub-flow path may be provided at a position corresponding to each of thepartitioning portions - The protruding
portion 227 including thesupplementary shaft portion 228 is formed in a cylindrical shape extending coaxially with the axis line O. That is, the inside of the protrudingportion 227 forms a protrudingportion flow path 236 that penetrates the protrudingportion 227 in the axial direction. An upper end portion of the protrudingportion 227 is fixed inside thebase flow path 235 by means of press-fitting. That is, the protrudingportion 227 is fixed to thebase shaft portion 226 in a state where the protrudingportion 227 protrudes downward from thethrust sliding portion 90, and thebase flow path 235 and the protrudingportion flow path 236 communicate with each other. Thebase flow path 235 and the protrudingportion flow path 236 form amain flow path 237 according to the present embodiment. A method of fixing thebase shaft portion 226 of the protrudingportion 227 may be any desired method other than the press-fitting. - A
balancer cover 240 according to the present embodiment includes acover body 241 that covers theauxiliary bearing 43 from below, and athrust plate 242 attached to thecover body 241. Even in the present embodiment, the inside of thebalancer cover 240 communicates with the inside of themuffler 65 through a communication hole (not shown). - The
cover body 241 is formed in a bottomed cylindrical shape. An upper end portion of thecover body 241 is attached to theflange portion 72 of theauxiliary bearing 43. Anaccommodation hole 243 is formed in a bottom portion of thecover body 241. Theaccommodation hole 243 penetrates the bottom portion of thecover body 241 in the axial direction. A lower end portion of thebase shaft portion 226 is accommodated inside theaccommodation hole 243. In the illustrated example, it is preferable that thethrust sliding portion 90 and the bottom portion (lower surface) of thecover body 241 are disposed flush with each other. - The
thrust plate 242 is formed in a disk shape having a diameter larger than that of the above-describedaccommodation hole 243. Thethrust plate 242 closes theaccommodation hole 243 from below in a state where an outer peripheral portion is fixed to the bottom portion of thecover body 241 by ascrew 244. In thethrust plate 242, a through-hole 245 is formed in a portion that overlaps themain flow path 237 of therotary shaft 225 when viewed in the axial direction. The inner diameter of the through-hole 245 is smaller than the inner diameter of theaccommodation hole 243 and is larger than the outer diameter of the protrudingportion 227. The above-describedprotruding portion 227 penetrates into the through-hole 245. In this manner, a lower end opening portion of the main flow path 95 communicates with the inside of thecase 34 below the balancer cover 81 (lower surface of the thrust plate 242). - The above-described
thrust sliding portion 90 is in contact with a portion (seal 242a) located around the through-hole 245 in the axial direction, on the upper surface of thethrust plate 242. In this manner, communication between the inside of thebalancer cover 81 and the inside of thecase 34 is blocked. - In the present embodiment, a gap S1 in the radial direction between the inner peripheral surface of the
accommodation hole 243 and the outer peripheral surface of thebase shaft portion 226 is larger than a gap S2 in the radial direction between the inner peripheral surface of the through-hole 245 and the outer peripheral surface of the protrudingportion 227. The gaps S1 and S2 do may not be uniform in the entire circumferential direction due to dimensional variations. The gap S1 may be equal to or smaller than the gap S2. - Next, a method for manufacturing the
rotary compressor 200 according to the present embodiment will be described. In the following description, an assembly process of assembling thethrust plate 242 to thecover body 241 in a state where therotary shaft 225 and thecover body 241 are assembled will be described. -
Fig. 5 is a process drawing for describing the assembly process. - As shown in
Fig. 5 , the assembly process of thethrust plate 242 according to the present embodiment includes a positioning process and a fixing process. - In the positioning process, a
jig 250 is used to position thethrust plate 242 with respect to the protrudingportion 227. Specifically, thejig 250 is formed in a cylindrical shape disposed coaxially with the axis line O. Thejig 250 has anoperation portion 251 located in a lower portion and aplate holding portion 252 located in an upper portion. - The outer diameter of the
operation portion 251 is larger than the inner diameter of the through-hole 245. - The
plate holding portion 252 is connected to an upper side of theoperation portion 251. Theplate holding portion 252 is formed in a tapered shape whose outer diameter gradually decreases upward. A minimum outer diameter of theplate holding portion 252 is smaller than the inner diameter of the through-hole 245. - The inside of the
jig 250 forms aninsertion hole 253 into which the protrudingportion 227 can be inserted. Thejig 250 is not limited to a cylindrical shape as long as a configuration has a plate holding portion for holding the inner peripheral surface of the through-hole 245 and an accommodation portion capable of accommodating theprotruding portion 227. - In the positioning process, the
plate holding portion 252 is inserted into the through-hole 245 of thethrust plate 242. Then, a lower end opening edge of the through-hole 245 is held by the outer peripheral surface of theplate holding portion 252. It is preferable that theplate holding portion 252 holds thethrust plate 242 in a state where theplate holding portion 252 does not protrude upward from the through-hole 245. - Subsequently, the
jig 250 is disposed coaxially with the axis line O below the rotary shaft 225 (cover body 241), and thethrust plate 242 and thejig 250 are raised. Then, thethrust plate 242 moves close to thecover body 241 while the protrudingportion 227 is inserted into theinsertion hole 253 of thejig 250. Thethrust plate 242 is raised until thethrust plate 242 abuts the lower surface of thecover body 241. In this manner, the size of the gap between the through-hole 245 of thethrust plate 242 and the outer peripheral surface of the protrudingportion 227 becomes substantially uniform in the circumferential direction, and thethrust plate 242 is positioned in the radial direction with respect to the protrudingportion 227. Thethrust plate 242 may be rotated in the circumferential direction with respect to thecover body 241 to align a fixing portion between thethrust plate 242 and thecover body 241. - Next, in the fixing process, the
thrust plate 242 is fixed to thecover body 241 by a screw 244 (refer toFig. 4 ). Thereafter, thejig 250 is retreated to complete the assembly process of thethrust plate 242. - In the present embodiment, in addition to achieving operational effects the same as those of the above-described first embodiment, the following operational effects are achieved.
- That is, in the present embodiment, the
base shaft portion 226 and the protruding portion 227 (supplementary shaft portion 228) are separately formed. In this manner, the rotary shaft does not need to be processed into a stepped shape as in a case where the base shaft portion and the protruding portion are integrally formed. Therefore, the accuratethrust sliding portion 90 can easily be manufactured, and it is possible to provide the lowcost rotary compressor 200 having excellent manufacturing efficiency. Since thebase shaft portion 226 and the protrudingportion 227 are separately formed, an optimum material can be selected for each component. Therefore, design can more freely be selected. - Since the
base shaft portion 226 and the protrudingportion 227 are separate from each other, a shaft length of each component can be shortened, and each component can accurately and easily be formed. - The present embodiment adopts a configuration as follows. The gap S1 in the radial direction between the inner peripheral surface of the
accommodation hole 243 and the outer peripheral surface of thebase shaft portion 226 is larger than the gap S2 in the radial direction between the inner peripheral surface of the through-hole 245 and the outer peripheral surface of the protrudingportion 227. According to this configuration, since the gap S1 is enlarged, the lubricating oil J existing inside thebalancer cover 240 can easily be accommodated inside the gap S1. - In this manner, the lubricating oil J is likely to be interposed between the outer peripheral surface of the
base shaft portion 226 and the inner peripheral surface of theaccommodation hole 243, and between thethrust sliding portion 90 and theseal 242a. Therefore, it is possible to improve lubrication performance. - On the other hand, since the gap S2 is reduced, a contact area (seal area) is likely to increase between the
thrust sliding portion 90 and theseal 242a. In this manner, sealing performance can be improved, and a surface pressure acting between thethrust sliding portion 90 and theseal 242a can be reduced. - Therefore, it is possible to provide the power-saving and high-
quality rotary compressor 200 excellent in operation reliability over a long period of time. When the position of therotary shaft 225 is displaced upward, it is possible to suppress a leakage amount when the gas refrigerant discharged into thebalancer cover 240 leaks outward of thebalancer cover 240 through the through-hole 245. - The present embodiment adopts a configuration as follows. The
jig 250 having theplate holding portion 252 for holding the inner peripheral surface of the through-hole 245 and theinsertion hole 253 into which the protrudingportion 227 is inserted is used so that thethrust plate 242 is positioned with respect to the protrudingportion 227. - According to this configuration, it is possible to suppress contact between the protruding
portion 227 and thethrust plate 242. Therefore, it is possible to suppress friction during the operation. - The gap S1 is enlarged as described above. In this manner, it is easy to avoid contact between the
base shaft portion 226 having a large turning radius in therotary shaft 225 and thecover body 241. In this manner, it is also possible to suppress the friction during the operation. - As a result, it is possible to provide the power-saving and high-
quality rotary compressor 200 excellent in operation reliability over a long period of time. - In the second embodiment, a configuration having three cylinders has been described. However, a configuration having a plurality of cylinders other than three may be adopted.
- In the second embodiment, a configuration in which each of the
rotary shaft 225 and thebalancer cover 240 is separately formed has been described. However, any one of therotary shaft 225 and thebalancer cover 240 may separately be formed. - In the second embodiment, a configuration in which the
thrust plate 242 is assembled in a state where therotary shaft 225 and thecover body 241 are assembled has been described. However, the present invention is not limited only to this configuration. For example, thecover body 241 may be assembled to theauxiliary bearing 43 in a state where thecover body 241 and thethrust plate 242 are assembled in advance. - In the above-described embodiment, a configuration in which the
roller 53 and theblade 55 are separate from each other has been described. However, the present invention is not limited only to this configuration. For example, a type in which the blade and the roller are integrated with each other may be adopted. - According to at least one of the above-described embodiments, desired lubrication performance can be obtained.
- Some embodiments of the present invention have been described. However, the embodiments have been described as examples, and do not intend to limit the scope of the invention. The embodiments can be implemented in various other forms, and various omissions, substitutions, and modifications can be made within the scope not departing from the concept of the invention. The embodiments or modifications thereof are included in the scope and the concept of the invention, and are also included in the scope of the invention described in the appended claims and an equivalent scope thereof.
-
- 1:
- Refrigeration cycle apparatus
- 2:
- Rotary compressor
- 3:
- Condenser
- 4:
- Expansion device
- 5:
- Evaporator
- 33:
- Compression mechanism
- 31:
- Rotary shaft
- 33:
- Compression mechanism
- 34:
- Case
- 41:
- Cylinder
- 42:
- Main bearing
- 43:
- Auxiliary bearing
- 51:
- Eccentric portion
- 81:
- Balancer cover
- 82:
- Seal
- 84:
- Through-hole
- 87:
- Protruding portion
- 90:
- Thrust sliding portion
- 91:
- Balancer
- 94:
- Supply channel
- 200:
- Rotary compressor
- 201:
- Upper cylinder (Cylinder)
- 202:
- Intermediate cylinder (Cylinder)
- 203:
- Lower cylinder (Cylinder)
- 225:
- Rotary shaft
- 226:
- Base shaft portion
- 227:
- Protruding portion
- 228:
- Supplementary shaft portion
- 230:
- Balancer cover
- 231:
- Upper eccentric portion (Eccentric portion)
- 232:
- Intermediate eccentric portion (Eccentric portion)
- 233:
- Lower eccentric portion (Eccentric portion)
- 240:
- Balancer cover
- 241:
- Cover body
- 242:
- Thrust plate
- 242a:
- Seal
- 243:
- Accommodation hole
- 245:
- Through-hole
- 250:
- Jig
Claims (6)
- A rotary compressor comprising:a case configured to store a lubricating oil;a rotary shaft disposed inside the case, and having an eccentric portion;a compression mechanism havinga cylinder accommodating the eccentric portion,a main bearing configured to rotatably support the rotary shaft from above the cylinder, andan auxiliary bearing configured to rotatably support the rotary shaft from below the cylinder;a balancer attached to the rotary shaft at a position below the auxiliary bearing; anda balancer cover configured to cover the balancer from below,wherein a through-hole is formed at a position of the balancer cover facing the rotary shaft in an axial direction, andthe rotary shaft includesa thrust sliding portion configured to come into contact with a seal located around the through-hole of the balancer cover, in the axial direction,a protruding portion located on an inner peripheral side of the thrust sliding portion, and protruding downward from a lower end of the through-hole through the through-hole, anda supply channel open on a lower end surface of the protruding portion to guide the lubricating oil.
- The rotary compressor according to Claim 1,wherein the rotary shaft is displaceable by a predetermined distance in the axial direction with respect to the compression mechanism, andthe protruding portion protrudes from the lower end of the through-hole to be longer than the predetermined distance.
- The rotary compressor according to Claim 1 or 2,
wherein the rotary shaft includes a base shaft portion provided with the thrust sliding portion, and a supplementary shaft portion fixed to the base shaft portion and forming the protruding portion. - The rotary compressor according to any one of Claims 1 to 3,wherein the rotary shaft has a base shaft portion provided with the thrust sliding portion,the balancer cover includesa cover body attached to the auxiliary bearing, and having an accommodation hole for accommodating the base shaft portion, anda thrust plate having the through-hole, and with which the thrust sliding portion comes into contact, anda gap in a radial direction of the rotary shaft between an outer peripheral surface of the base shaft portion and an inner peripheral surface of the accommodation hole is wider than a gap in the radial direction between an outer peripheral surface of the protruding portion and an inner peripheral surface of the through-hole.
- A method for manufacturing the rotary compressor according to Claim 4, comprising:an assembly process of assembling the thrust plate to the cover body in a state where the base shaft portion is accommodated inside the accommodation hole of the cover body fixed to the auxiliary bearing,wherein the assembly process hasa positioning process of positioning the thrust plate with respect to the protruding portion, anda fixing process of fixing the positioned thrust plate to the cover body.
- A refrigeration cycle apparatus comprising:the rotary compressor according to any one of claims 1 to 4;a radiator connected to the rotary compressor;an expansion device connected to the radiator; andan evaporator connected between the expansion device and the rotary compressor.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2019020870 | 2019-02-07 | ||
PCT/JP2019/041020 WO2020161965A1 (en) | 2019-02-07 | 2019-10-18 | Rotary compressor, method for manufacturing rotary compressor, and refrigeration cycle device |
Publications (2)
Publication Number | Publication Date |
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EP3922854A1 true EP3922854A1 (en) | 2021-12-15 |
EP3922854A4 EP3922854A4 (en) | 2022-11-02 |
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Application Number | Title | Priority Date | Filing Date |
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EP19914314.0A Pending EP3922854A4 (en) | 2019-02-07 | 2019-10-18 | Rotary compressor, method for manufacturing rotary compressor, and refrigeration cycle device |
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EP (1) | EP3922854A4 (en) |
JP (1) | JP7113091B2 (en) |
CN (1) | CN113396285B (en) |
WO (1) | WO2020161965A1 (en) |
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WO2022080179A1 (en) * | 2020-10-14 | 2022-04-21 | 東芝キヤリア株式会社 | Compressor and refrigeration cycle apparatus |
JPWO2022085443A1 (en) * | 2020-10-22 | 2022-04-28 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS618491A (en) * | 1984-06-20 | 1986-01-16 | Matsushita Electric Ind Co Ltd | Lubricating device for rotary compressor |
JPS61171890A (en) * | 1985-01-28 | 1986-08-02 | Sanyo Electric Co Ltd | Oil return device of enclosure type compressor |
TW411382B (en) * | 1997-10-23 | 2000-11-11 | Toshiba Corp | Helical compressor and method of assembling the same |
KR101718014B1 (en) * | 2010-02-26 | 2017-03-20 | 엘지전자 주식회사 | Compressor with oil level controlling means |
US9695825B2 (en) * | 2012-07-09 | 2017-07-04 | Panasonic Intellectual Property Management Co., Ltd. | Rotary compressor |
JP2015197044A (en) | 2014-03-31 | 2015-11-09 | ダイキン工業株式会社 | rotary compressor |
JP2017002814A (en) * | 2015-06-10 | 2017-01-05 | ダイキン工業株式会社 | Rotary type compressor |
KR102483241B1 (en) * | 2016-04-26 | 2022-12-30 | 엘지전자 주식회사 | Scroll compressor |
JP6762253B2 (en) | 2017-03-28 | 2020-09-30 | 東芝キヤリア株式会社 | Revolver and refrigeration cycle equipment |
JP6861591B2 (en) | 2017-07-13 | 2021-04-21 | 日立Astemo株式会社 | Vehicle control unit |
-
2019
- 2019-10-18 CN CN201980091316.7A patent/CN113396285B/en active Active
- 2019-10-18 JP JP2020570364A patent/JP7113091B2/en active Active
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CN113396285A (en) | 2021-09-14 |
JP7113091B2 (en) | 2022-08-04 |
EP3922854A4 (en) | 2022-11-02 |
JPWO2020161965A1 (en) | 2021-10-14 |
WO2020161965A1 (en) | 2020-08-13 |
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