JP5948209B2 - Hermetic compressor and refrigeration cycle apparatus - Google Patents

Description

  Embodiments described herein relate generally to a hermetic compressor and a refrigeration cycle apparatus.

  Patent Document 1 discloses a two-cylinder hermetic compressor of a low pressure type in a case. This sucks and fills the low-pressure gas refrigerant into the sealed case, directs the refrigerant from the sealed case directly to the cylinder chamber of the compression mechanism section through the refrigerant guide tube, compresses it, and discharges it to the refrigerant tube.

  The pressure-resistant strength of the sealed case can be lowered, and the manufacturing unit price can be suppressed. Since the low-pressure gas refrigerant is low in temperature, the motor part can be cooled. Gas refrigerant can be gas-liquid separated in a sealed case, and a separate accumulator can be dispensed with.

  However, even in this type of compressor, the lubricating oil is discharged together with the gas refrigerant. Therefore, an oil separator is connected to the refrigerant pipe, the separated gas refrigerant is guided to the condenser, and the lubricating oil is returned to the compression mechanism through the oil return pipe. In the compression mechanism portion, the lubricating oil is once introduced into a through hole of the partition plate that is interposed between the two cylinders and that includes the upper partition plate and the lower partition plate.

JP2012-13052A

  The rotating shaft passes through the through-hole and faces a roller that moves eccentrically in the cylinder chamber, so that lubricating oil can be supplied to a sliding contact portion between the roller and the rotating shaft. Furthermore, a part of the lubricating oil is guided to the blade back chamber through an oil supply passage formed in a state where the upper and lower partition plates are combined. The blade back chamber is formed at the other end of the blade whose one end contacts the roller.

  However, the lubricating oil separated by the oil separator is increased in pressure and easily leaks into the sealed case in a low pressure atmosphere in the middle of the oil supply passage. The lack of lubricating oil for the blade back chamber hinders smooth operation of the blade and adversely affects the compression efficiency. If a seal member that prevents leakage of the lubricating oil is provided on the partition plate, the weight is increased by the seal member, leading to an increase in size of the partition plate and the compressor.

  For this reason, in the low-pressure type in the case, a sealed type that can guide the high-pressure lubricating oil returned from the oil separator to the compression mechanism part to the blade back chamber without leaking from the through hole of the partition plate. There has been a demand for a compressor and a refrigeration cycle apparatus using this hermetic compressor as a part of refrigeration cycle components.

  In the present embodiment, a compression mechanism unit and an electric motor unit that are connected via a rotating shaft are housed in the sealed case, and the pressure in the space in the sealed case is set to be the same as the suction pressure to the compression mechanism unit, The gas refrigerant compressed by the compression mechanism is discharged to a refrigerant pipe, and an oil separator is provided in the refrigerant pipe to separate the lubricating oil contained in the gas refrigerant, and the separated lubricating oil is compressed. In the hermetic compressor having an oil return passage returning to the mechanism portion, the compression mechanism portion is provided with two cylinder chambers via a partition plate, and a roller accommodated in each cylinder chamber so as to be eccentrically movable. A blade that reciprocates in contact with the roller and divides the cylinder chamber into a compression side and a suction side, and a sealed blade back chamber provided on the rear end side of the blade, and through the oil return passage In the compression mechanism Been lubricating oil, guided to the through hole in which the rotation shaft of the partition plate is penetrated, oil supply conduits for introducing directly into the blade back chamber is provided through the further the blade from the through hole.

The refrigeration cycle block diagram of the air conditioner as a refrigeration cycle apparatus based on 1st Embodiment. The longitudinal cross-sectional view of the hermetic compressor which connected the oil separator based on the embodiment. The top view of the 1st cylinder based on the embodiment. The top view of the upper partition plate and lower partition plate based on the embodiment. The longitudinal cross-sectional view and top view of a roller based on the embodiment. The top view and longitudinal cross-sectional view of a braid | blade based on the embodiment. The longitudinal cross-sectional view and top view of a roller based on 2nd Embodiment. The top view and longitudinal cross-sectional view of a braid | blade based on the embodiment.

Hereinafter, the first embodiment will be described with reference to FIGS.
FIG. 1 is a configuration diagram of a refrigeration cycle of an air conditioner 1 as a refrigeration cycle apparatus.
The air conditioner 1 is a hermetic compressor 2, an oil separator 3, a four-way valve 4, an outdoor heat exchanger 5 that is a heat source side heat exchanger, an expansion device 6, and a use side heat exchanger. A refrigeration cycle is configured by communicating the indoor heat exchanger 7 in a cycle through the refrigerant pipe P.

  In the air conditioner 1, during the cooling operation, the high-pressure gas refrigerant compressed by the hermetic compressor 2 and discharged to the refrigerant pipe P is guided as indicated by a solid arrow. That is, the refrigerant is guided to the outdoor heat exchanger 5 via the oil separator 3 and the four-way valve 4, and is condensed by exchanging heat with the outside air to be converted into liquid refrigerant. The liquid refrigerant is adiabatically expanded by the expansion device 6, guided to the indoor heat exchanger 7, and exchanges heat with room air to evaporate.

  In the indoor heat exchanger 7, the liquid refrigerant evaporates and changes to a gas refrigerant, so that heat is taken from the indoor air to cool it, and thus an indoor cooling action is performed. The evaporated gas refrigerant is sucked into the hermetic compressor 2 through the four-way valve 4, and further, the refrigerant circulates through the above-described path to continue the cooling operation.

  On the other hand, at the time of heating operation, the high-pressure gas refrigerant compressed by the hermetic compressor 2 and discharged to the refrigerant pipe P is guided as indicated by a broken line arrow. That is, the refrigerant is led to the indoor heat exchanger 7 via the oil separator 3 and the four-way valve 4, exchanges heat with room air, condenses, and changes into liquid refrigerant. At this time, the room air absorbs the heat of condensation, rises in temperature, and changes to warm air. Therefore, the indoor heating operation is performed.

  The liquid refrigerant is led to the expansion device 6 and adiabatically expands, and is led to the outdoor heat exchanger 5 to evaporate and change into a gas refrigerant. The gas refrigerant evaporated here is sucked into the hermetic compressor 2 through the four-way valve 4, and further, the refrigerant circulates through the above-described path and the heating operation is continued.

FIG. 2 is a longitudinal sectional view of the hermetic compressor 2.
The hermetic compressor 2 has a hermetic case 10 in which a compression mechanism unit 11 and an electric motor unit 12 are housed. The compression mechanism unit 11 is disposed on the lower side, and the electric motor unit 12 is disposed on the upper side, and is connected via a rotary shaft 13 having a vertical axis. When the electric motor unit 12 rotationally drives the rotating shaft 13, the compression mechanism unit 11 compresses the gas refrigerant.

  The gas refrigerant compressed by the compression mechanism unit 11 is discharged to the refrigerant pipe P connected to the outside of the sealed case 10. The refrigerant pipe P is provided with the oil separator 3 described above, and the oil separator 3 separates the lubricating oil contained in the gas refrigerant from the gas refrigerant discharged from the compression mechanism unit 11.

  The lubricating oil separated by the oil separator 3 is returned to the compression mechanism unit 11 via an oil return pipe (oil return passage) 15. The compression mechanism section 11 is provided with an oil introduction path 16 as will be described later, and guides the lubricating oil from the oil return pipe 15 to each sliding contact section of the compression mechanism 11.

  The electric motor unit 12 includes a rotor 18 and a stator 19. The stator 19 is fixed to the inner peripheral portion of the hermetic case 10, and the rotor 18 is rotatably disposed inside the stator 19. A rotary shaft 13 is fitted along the axis of the rotor 18, and the rotary shaft 13 is pivotally supported by a main bearing 20 and a sub bearing 21 that constitute the compression mechanism 11. A pair of eccentric portions a and b are formed on the rotary shaft 13 with a predetermined interval in the axial direction and facing the radial direction by 180 °.

  The compression mechanism unit 11 includes a partition plate 22 configured by bringing an upper partition plate 22a and a lower partition plate 22b into contact with each other, a first cylinder 23A and a second cylinder 23A located on both upper and lower surfaces with the partition plate 22 interposed therebetween. A cylinder 23B, a discharge chamber 24 formed in each of the upper and lower partition plates 22a and 22b, and a discharge valve 25 attached to the discharge chamber 24 are provided.

FIG. 3 is a plan view of the first cylinder 23A.
As shown in FIGS. 2 and 3, a first cylinder chamber 27 a is formed in the inner diameter portion of the first cylinder 23 </ b> A with the upper surface closed by the main bearing 20 and the lower surface closed by the upper partition plate 22 a. The eccentric part a of the rotating shaft 13 is disposed in the first cylinder chamber 27a, and the first roller 28a is fitted into the eccentric part a.

  A second cylinder chamber 27b whose upper surface is closed by the lower partition plate 22b and whose lower surface is closed by the auxiliary bearing 21 is formed in the inner diameter portion of the second cylinder 23B shown in FIG. The eccentric part b of the rotating shaft 13 is disposed in the second cylinder chamber 27b, and the second roller 28b is fitted into the eccentric part b.

  When the rotary shaft 13 rotates, the eccentric portions a and b and the first and second rollers 28a and 28b move eccentrically at an angle of 180 ° in the first and second cylinder chambers 27a and 27b. At this time, part of the outer peripheral wall of the first and second rollers 28a, 28b moves while making line contact with part of the inner peripheral wall of the first and second cylinder chambers 27a, 27b.

  As shown in FIG. 3, the first cylinder 23A is provided with a blade groove 30 whose one end opens into the first cylinder chamber 27a. The other end portion of the blade groove 30 communicates with the first blade back chamber 31 a that is a hole portion having a diameter larger than the width dimension of the blade groove 30.

  A first blade 32 is slidably fitted in the blade groove 30. As will be described later, the front end portion of the first blade 32 is engaged with the outer peripheral wall of the first roller 28a, and the rear end portion can protrude and retract into the first blade back chamber 31a. The axial length of the first blade 32 matches the plate thickness which is the axial length of the first cylinder 23A.

  Similar to the first cylinder chamber 27a, the blade groove 30 and the first blade back chamber 31a are closed at the upper surface by the main bearing 20 and at the lower surface by the upper partition plate 22a to form a sealed structure. As will be described later, high-pressure lubricating oil is guided to the first blade back chamber 31a, and a high pressure is applied to the rear end portion of the first blade 32, and the front end portion is urged toward the first roller 28a. To do.

  A suction port 34 communicating from the outer diameter surface of the first cylinder 23A to the first cylinder chamber 27a is provided. A discharge port 35 and an oil introduction port 36 are provided at positions different from the suction port 34 with a gap from the outer surface of the first cylinder chamber 27a. Holes d and e penetrating the upper and lower surfaces of the first cylinder 23A are provided at the end portions of the discharge port 35 and the oil introduction port 36.

  As shown in FIG. 2, a refrigerant pipe P for introducing the refrigerant that has circulated through the refrigeration cycle is connected to the upper end surface of the sealed case 10. The upper end portion of the sealed case 10 is connected to one end portion of the first refrigerant guide tube Pa and the second refrigerant guide tube Pb for once leading the refrigerant filling the sealed case 10 to the outside of the sealed case 10. Is done.

  The first refrigerant guide tube Pa is bent along the lower direction of the sealed case 10, and further passes through the sealed case 10 and is inserted into a suction port 34 provided in the first cylinder 23A. That is, the first cylinder chamber 27a sucks the low-pressure gas refrigerant filling the sealed case 10 through the first refrigerant guide pipe Pa.

  As described above, the high-pressure gas refrigerant compressed in the compression mechanism section 11 is discharged to the refrigerant pipe P. The end of the refrigerant pipe P is the first cylinder shown in FIG. It is connected to the discharge port 35 provided in 23A. One end of the oil return pipe 15 that guides the lubricating oil separated by the oil separator 3 is connected to the oil inlet 36.

  On the other hand, although not shown, the blade groove 30 is provided in the second cylinder 23B, and the blade 32 is slidably fitted. The leading end of the blade engages with the outer peripheral wall of the second roller 28b, as will be described later, and the rear end can project and retract into the second blade back chamber 31b communicating with the other end of the blade groove.

  The high-pressure lubricating oil is guided to the second blade back chamber, and the tip of the blade is urged toward the second roller 28b. One end of the second refrigerant guide tube Pb penetrates the sealed case 10 and is connected to a suction port 34 provided in the second cylinder 23B. Accordingly, the pressure in the space of the sealed case 10 and the suction pressure into the compression mechanism unit 11 are set to be the same.

  Note that the discharge port 35 and the oil introduction port 36 provided in the first cylinder 23A are not provided in the second cylinder 23B. The gas refrigerant compressed in the second cylinder chamber 27b is guided to the discharge port 35 of the first cylinder 23A via the partition plate 22 as will be described later.

  Further, the lubricating oil introduced from the oil separator 3 through the oil return pipe 15 to the oil introduction port 36 of the first cylinder 23A is also introduced into the second cylinder 23B through the partition plate 22 as will be described later. It is burned. Therefore, the second cylinder 23B does not need the discharge port 35 and the oil introduction port 36 as in the first cylinder 23A.

4A is a plan view of the upper partition plate 22a, and FIG. 4B is a plan view of the lower partition plate 22b.
As described above, the partition plate 22 is formed by joining the upper partition plate 22a and the lower partition plate 22b having the same outer diameter.

  The upper partition plate 22 a is provided with a through hole 38 through which the rotary shaft 13 penetrates in the shaft core portion, and a recess 39 a is provided around the through hole 38. A through hole 38 through which the rotary shaft 13 passes is also provided in the shaft core portion of the lower partition plate 22b, and a recess 39a is also provided around the through hole 38.

  The diameters of the through holes 38 of the upper partition plate 22a and the through holes 38 of the lower partition plate 22b are the same. In a state where the first and second rollers 28a and 28b are eccentrically moved in the first and second cylinder chambers 27a and 27b, the through holes 38 protrude from the outer peripheral walls of the first and second rollers 28a and 28b. The diameter is not set.

  That is, regardless of the position of the first and second rollers 28a and 28b, the through hole 38 does not communicate with the first and second cylinder chambers 27a and 27b, and the first and second rollers are always connected. It faces 28a, 28b or eccentric part a, b.

  The recesses 39a and 39b of the upper partition plate 22a and the lower partition plate 22b have the same shape. The upper and lower partition plates 22a and 22b are opposed to each other and joined to form the discharge chamber 24 described above. . The discharge valves 25 and 25 described above are provided in a part of the respective recesses 39a and 39b.

  The discharge valve 25 located in the recess 39a of the upper partition plate 22a is provided to face the first cylinder chamber 27a, and the discharge valve 25 located in the recess 39b of the lower partition plate 22b faces the second cylinder chamber 27b. Provided.

  For this reason, when the inside of the first cylinder chamber 27 a reaches a predetermined high pressure state, the discharge valve 25 provided in the upper partition plate 22 a is opened to guide the high pressure gas to the discharge chamber 24. When the inside of the second cylinder chamber 27 b reaches a predetermined high pressure state, the discharge valve 25 provided in the lower partition plate 22 b is opened to guide the high pressure gas to the same discharge chamber 24.

  A discharge guide port 40 is provided in part of the recesses 39a and 39b of the upper and lower partition plates 22a and 22b so as to penetrate the upper and lower surfaces of the upper and lower partition plates 22a and 22b. When assembled as the compression mechanism 11, the discharge guide port 40 of the upper partition plate 22a is in a position communicating with the hole d of the discharge port 35 provided in the first cylinder 23A.

  That is, the high-pressure gas refrigerant compressed in the first and second cylinder chambers 27 a and 27 b and discharged to the discharge chamber 24 of the upper and lower partition plates 22 a and 22 b through the discharge valve 25 is discharged from the discharge guide port 40. It is guided to the discharge port 35 through the hole d, and can be guided to the refrigerant pipe P connected thereto.

  The joining surfaces of the upper partition plate 22a and the lower partition plate 22b are provided with oil supply grooves 41a and 41b at the same position and having one end communicating with the through hole 38, and the upper and lower partition plates 22a and 22b are combined. It becomes the oil supply hole 41 in a state. Holes f and g are provided at the other end portions of the oil supply grooves 41a and 41b, respectively, and communicate with the oil introduction port 36 of the first cylinder 23A.

  The lubricating oil separated by the oil separator 3 is guided from the oil return pipe 15 to the compression mechanism section 11, and further, the oil introduction port 36 of the first cylinder 23A and the oil supply holes 41 of the upper and lower partition plates 22a and 22b. It is led between the through hole 38 and the peripheral wall of the rotary shaft 13 via the, and is filled here.

  Next, the first roller 28a and the first blade 32 will be described in detail, but the second roller 28b and the second blade 32 (not shown) have exactly the same configuration, and these are shown and described. Is omitted.

  FIG. 5A is a longitudinal sectional view of the first roller 28a, and FIG. 5B is a plan view of the first roller 28a. FIG. 6A is a plan view of the first blade 32, and FIG. 6B is a longitudinal sectional view of the first blade 32.

  The first roller 28a and the first blade 32 are set so that their axial lengths coincide with each other. An oil sump groove 43 formed of a concave portion is provided in the axial direction on the inner diameter surface of the first roller 28a. Oil grooves 44 are provided on both upper and lower end surfaces of the first roller 28a, which are both ends of the oil sump groove 43, and engagement grooves 45 having an arcuate cross section along the axial direction are provided on the outer diameter surface.

  One end portion of the first blade 32 is a tip portion K having an arcuate cross section that fits into the engaging groove 45 of the first roller 28a, and has a flat plate shape except for this end portion. An oil introduction groove 46 that communicates the engagement groove 45 and the first blade back chamber 31a is provided on both upper and lower end surfaces of the first blade 32 including the tip K.

  As the first roller 28a performs an eccentric motion in the first cylinder chamber 27a, the first blade 32 with which the tip K is engaged with the engagement groove 45 of the first roller 28a follows. However, since the first blade 32 is fitted in the blade groove 30, its movement is restricted and reciprocates along the blade groove 30.

  From the oil reservoir groove 43 provided on the inner diameter surface of the first roller 28a to the oil groove 44 provided on the upper and lower end faces and the oil introduction groove 46 provided on the upper and lower end faces of the first blade 32, an oil supply conduction path 47 is provided. Is formed.

  As described above, the first roller 28a and the first blade 32 are in sliding contact with the main bearing 20 on the upper surface and in sliding contact with the upper partition plate 22a on the lower surface. Further, since the inner diameter surface of the first roller 28a is in sliding contact with the eccentric portion a of the rotating shaft 13, the oil reservoir groove 43 is provided on the sliding contact surface with the eccentric portion a of the first roller 28a.

  The oil grooves 44 on the upper and lower end faces of the first roller 28a and the oil introduction grooves 46 on the upper and lower end faces of the first blade 32 are formed by the first roller 28a and the first blade 32, the main bearing 20 and the upper partition. It will be provided on the sliding contact surface with the plate 22a.

  Note that the second roller 28b and the second blade have the same structure as the first roller 28a and the first blade 32, and therefore the first roller 28a and the first blade 32 are here. Adapting the structure description, the new description is omitted.

  In such a configuration, when the air conditioner 1 is operated, the electric motor unit 12 rotationally drives the rotary shaft 13, and the first and second rollers 28 a and 28 b fitted to the eccentric parts a and b are the first ones. Then, it rolls into the second cylinder chambers 27a and 27b. Along with this, the first and second blades 32 reciprocate to divide the first and second cylinder chambers 27a and 27b into the compression side and the suction side.

  The low-pressure gas refrigerant is guided and filled in the sealed case 10, and further, the first cylinder chamber 27a and the first cylinder are respectively connected from the sealed case 10 through the first refrigerant guide pipe Pa and the second refrigerant guide pipe Pb. 2 is sucked into the cylinder chamber 27b and compressed.

  The gas refrigerant compressed in the first and second cylinder chambers 27 a and 27 b is discharged into the discharge chamber 24 by opening the discharge valve 25 provided in the partition plate 22. Further, it is led from the discharge chamber 24 to the discharge port 35 provided in the first cylinder 23A, and is led to the oil separator 3 from the refrigerant pipe P connected thereto.

  The gas refrigerant discharged from the hermetic compressor 2 to the refrigerant pipe P contains a lubricating oil component, and the oil separator 3 separates the gas refrigerant and the lubricating oil component. The gas refrigerant is guided to the outdoor heat exchanger 5 or the indoor heat exchanger 7 via the four-way valve 4 and then sucked into the hermetic compressor 2 again and circulates in the above-described path.

  The lubricating oil separated by the oil separator 3 is returned to the hermetic compressor 2 through the oil return pipe 15 and guided to the oil introduction path 16 provided in the compression mechanism section 11. Furthermore, it fills between the through-hole 38 and the rotating shaft 13 surrounding wall through the oil supply hole 41 provided in the partition plate 22 from the oil inlet 36 provided in the 1st cylinder 23A.

  Since the through-hole 38 faces the sliding contact surface between the first and second rollers 28a and 28b and the eccentric portions a and b in the first and second cylinder chambers 27a and 27b, the sliding contact therebetween. Refueled on the surface. Further, the lubricating oil in the through hole 38 is also supplied to the engaging portion between the engaging groove 45 of the first and second rollers 28 a and 28 b and the tip K of the first and second blades 32.

  The lubricating oil in the through hole 38 is also supplied to the oil sump groove 43 provided on the inner diameter surfaces of the first and second rollers 28a and 28b. The oil sump groove 43 communicates with oil grooves 44 on both end faces of the first and second rollers 28a, 28b and oil introduction grooves 46 on both end faces of the first and second blades 32. The first and second blade back chambers 31a and 31b are open.

  Therefore, the high-pressure lubricating oil in the oil sump groove 43 is guided along the oil supply passage 47 including the oil groove 44 and the oil introduction groove 46, and fills the first and second blade back chambers 31a and 31b. The high-pressure lubricating oil filled here applies pressure to the first and second blades 32 in the direction of the first and second rollers 28a and 28b, and ensures their smooth reciprocation.

  As described above, the lubricating oil guided to the through hole 38 of the partition plate 22 is directly supplied to the first and second blades via the first and second rollers 28 a and 28 b and the first and second blades 32. An oil supply conduction path 47 leading to the back chambers 31a and 31b was provided.

  On the other hand, conventionally, an oil supply passage from the oil supply groove provided on the mating surface of the upper and lower partition plates 22a and 22b to the first and second blade back chambers 31a and 31b bypassing the recesses 39a and 39b is provided. However, in this embodiment, this oil supply passage is unnecessary.

  The lubricating oil separated by the oil separator 3 and returning to the compression mechanism 11 is high pressure, and in the conventional structure in which high pressure lubricating oil is conducted to the oil supply passage provided on the mating surface of the upper and lower partition plates, the low pressure is supplied from the oil supply passage. Lubricating oil was likely to leak into the sealed case. Further, an elastic body for energizing the blade is necessary for the blade back chamber.

  With the above-described configuration, the high-pressure lubricating oil is guided directly from the through hole 38 to the first and second blade back chambers 31a and 31b through the blade 32. Therefore, it is possible to prevent the high-pressure lubricating oil from leaking into the low-pressure sealed case 10.

  Further, a hooking groove 45 having an arcuate cross section is provided along the axial direction on the outer diameter surfaces of the first and second rollers 28a and 28b, and the first and second blades 32 are cross-sectional circles that fit into the hooking groove 45. Since the arcuate tip K is used, the first and second blades 32 smoothly follow the movements of the first and second rollers 28a and 28b without an elastic body. Therefore, the conventionally used elastic body becomes unnecessary.

Next, a second embodiment according to the oil supply conducting path will be described.
FIG. 7A is a longitudinal sectional view of the first roller 28a, and FIG. 7B is a plan view of the first roller 28a. FIG. 8A is a plan view of the first blade 32, and FIG. 8B is a longitudinal sectional view of the first blade 32.

  An oil reservoir groove 43 is provided along the axial direction on the inner diameter surface of the first roller 28a. An engaging groove 45 having an arcuate cross section is provided along the outer diameter surface of the first roller 28a facing the oil sump groove 43. Here, two oil holes 48 are provided in the radial direction of the first roller 28 a across the oil sump groove 43 and the engaging groove 45 with a predetermined interval.

  One end of the first blade 32 is formed at a tip K having an arcuate cross section, and engages with the engaging groove 45 of the first roller 28a. Two oil introduction holes 49 that penetrate from the end face K end face of the first blade 32 to the other end face facing each other and communicate with the engaging groove 45 and the first blade back chamber 31a are provided at a predetermined interval. It is done.

  Two oil holes 48 provided in the first roller 28a and 2 provided in the first blade 32 in a state where the leading end K of the first blade 32 is engaged with the engaging groove 45 of the first roller 28a. The individual oil introduction holes 49 communicate with each other.

Therefore, the oil supply passage 50 is formed by the oil hole 48 provided in the first roller 28 a from the oil reservoir groove 43 and the oil introduction hole 49 provided in the first blade 32.
The second roller 28b and the second blade 32 have exactly the same structure, and a new description is omitted by applying the structure of the first roller 28a and the first blade 32.

  The high-pressure lubricating oil collected in the oil sump groove 43 from the through hole 38 of the partition plate 22 is the oil hole 48 of the first and second rollers 28 a and 28 b and the oil introduction hole 49 of the first and second blades 32. The first and second blade back chambers 31a and 31b are led through an oil supply conduction path 50 made of

  The first and second blade back chambers 31a and 31b are filled with high-pressure lubricant, and pressure is applied to the first and second blades 32 in the direction of the first and second rollers 28a and 28b. Lubricating oil does not leak in the middle of being led from the through hole 38 to the first and second blade back chambers 31a and 31b via the oil supply conduction path 50, and a sufficient effect can be obtained.

  As mentioned above, although this embodiment was described, the above-mentioned embodiment is shown as an example and does not intend limiting the range of embodiment. The novel embodiment can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

  DESCRIPTION OF SYMBOLS 10 ... Sealing case, 13 ... Rotating shaft, 11 ... Compression mechanism part, 12 ... Electric motor part, P ... Refrigerant pipe, 3 ... Oil separator, 15 ... Oil return pipe (oil return path), 22 ... Partition plate, 27a ... 1st cylinder chamber, 27b ... 2nd cylinder chamber, 28a ... 1st roller, 28b ... 2nd roller, 32 ... Blade, 31a ... 1st blade back chamber, 31b ... 2nd blade back chamber, 38 ... through hole, 47, 50 ... oil supply passage, 45 ... engagement groove, K ... spherical tip, 5 ... outdoor heat exchanger (heat source side heat exchanger), 7 ... indoor heat exchanger (use side heat exchanger) ).

Claims (3)

A compression mechanism portion and an electric motor portion connected via a rotating shaft are housed in the sealed case, and the pressure in the space inside the sealed case is set to be the same as the suction pressure into the compression mechanism portion. Oil return that discharges the compressed gas refrigerant to the refrigerant pipe, provides an oil separator in the refrigerant pipe to separate the lubricating oil contained in the gas refrigerant, and returns the separated lubricating oil to the compression mechanism section In a hermetic compressor with a passage,
The compression mechanism section is provided with two cylinder chambers via a partition plate. Each cylinder chamber has a roller accommodated therein so as to be able to move eccentrically, and reciprocates in contact with the roller. A blade partitioned on the suction side, and a sealed blade back chamber provided on the rear end side of the blade,
The lubricating oil returned to the compression mechanism through the oil return passage is guided to a through hole through which the rotary shaft of the partition plate passes, and is further introduced from the through hole into the blade back chamber through the blade. A hermetic compressor provided with an oil supply passage. The outer peripheral wall of the roller is provided with a hooking groove having an arc-shaped cross section along the axial direction,
The blade is provided with a tip having an arcuate cross section that is rotatably fitted in the engaging groove of the roller.
2. The hermetic compressor according to claim 1, wherein the oil supply conduction path is provided in the blade so as to communicate the engagement groove of the roller and the blade back chamber.   A refrigeration cycle apparatus comprising the hermetic compressor according to any one of claims 1 and 2, a heat source side heat exchanger, an expansion device, and a use side heat exchanger.

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