JPWO2018142466A1 - Compressor - Google Patents

Abstract

The compressor includes a hermetic container, a stator and a rotor disposed inside the stator, an electric mechanism portion provided in the hermetic container, and a drive shaft having one end connected to the electric mechanism portion. And a piston connected to the other end of the drive shaft, a cylinder that houses the piston, and a bearing that supports the other end of the drive shaft, the first discharge port discharging the refrigerant in the cylinder. And a silencer provided on the bearing and covering the first discharge port, and the first discharge port is provided between the end surface of the bearing and the silencer. A closed space to which the refrigerant discharged from is supplied is formed, and the silencer is configured to centrifuge the refrigerant in the closed space and the lubricating oil in the closed space.

Description

  The present invention relates to a compressor, and more particularly, to a compressor that is driven by an electric mechanism unit and includes a compression mechanism unit that compresses a refrigerant.

  The rotary compressor includes an airtight container, an electric mechanism, a compression mechanism, and a shaft that connects the electric mechanism and the compression mechanism (for example, see Patent Document 1). An electric mechanism part, a compression mechanism part, and a shaft are provided in the sealed container. As the rotor of the electric mechanism section rotates, the shaft rotates. Here, an oil flow path through which the lubricating oil flows is formed inside the shaft, and a pump for drawing the lubricating oil into the oil flow path is provided on the shaft. When the shaft rotates, the lubricating oil stored at the bottom of the sealed container is drawn into the oil passage of the shaft by the action of the pump. The lubricating oil drawn into the oil passage is supplied to the compression mechanism unit.

JP 2012-202215 A

  When the capacity of the compressor increases, the flow rate of the refrigerant discharged from the compressor increases accordingly. When the flow rate of the refrigerant discharged from the compressor increases, the lubricating oil in the sealed container easily flows out of the sealed container through the discharge pipe together with the refrigerant. The lubricating oil plays a role of suppressing wear between members constituting the compression mechanism. For this reason, if the lubricating oil flows out of the hermetic container, the compression mechanism is damaged, which causes a decrease in the reliability of the compressor and a decrease in the operating efficiency of the refrigeration cycle apparatus.

  The present invention has been made in order to solve the above-described problems. A compressor that suppresses the lubricating oil stored in the sealed container from flowing out of the sealed container. It is intended to provide.

  A compressor according to the present invention includes a hermetic container, a stator and a rotor disposed inside the stator, and an electric mechanism portion provided in the hermetic container, and one end side thereof is connected to the electric mechanism portion. A drive shaft, a piston connected to the other end of the drive shaft, a cylinder that houses the piston, and a first discharge port that discharges the refrigerant in the cylinder. A compression mechanism that compresses the refrigerant, and a silencer that is provided on the bearing and covers the first discharge port, and between the end surface of the bearing and the silencer, A closed space to which the refrigerant discharged from one discharge port is supplied is formed, and the silencer is configured to centrifuge the refrigerant in the closed space and the lubricating oil in the closed space.

  According to the compressor concerning the present invention, since it has the above-mentioned composition, it can control that lubricating oil stored in an airtight container flows out of the airtight container from the airtight container.

It is a longitudinal section showing the whole compressor 100 composition concerning an embodiment. It is an enlarged view of the compression mechanism part 3 shown in FIG. 1, and its periphery. It is an enlarged view of the bottom part of the compressor 100 shown in FIG. It is explanatory drawing of the spring which pushes a vane and a vane. It is the perspective view which has shown the upper silencer 50 of the compressor 100 which concerns on embodiment in the state decomposed | disassembled into the housing 51 and the ring 52. FIG. FIG. 5 is a perspective view of a housing 51. 4 is a top view of the housing 51. FIG. 4 is a bottom view of the housing 51. FIG. 3 is a side view of a housing 51. FIG. It is a longitudinal section of upper silencer 50 of compressor 100 concerning an embodiment. It is a schematic diagram for demonstrating the flow path currently formed in the upper silencer 50. FIG.

  Hereinafter, an embodiment of an indoor unit of an air conditioner according to the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments described below. Moreover, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

Embodiment.
FIG. 1 is a longitudinal sectional view showing an overall configuration of a compressor 100 according to an embodiment.
FIG. 2 is an enlarged view of the compression mechanism unit 3 shown in FIG. 1 and its surroundings.
FIG. 3 is an enlarged view of the bottom of the compressor 100 shown in FIG.
FIG. 4 is an explanatory diagram of vanes and springs that push the vanes.

  The compressor 100 includes a sealed container 1, a suction muffler 5, an upper suction pipe 6, a lower suction pipe 7, a discharge pipe 8, and an oil supply pipe 44. The compressor 100 includes an electric mechanism unit 2, a compression mechanism unit 3, an upper silencer 50, and a lower silencer 41. The upper silencer 50 corresponds to the silencer in the present invention.

  As shown in FIG. 1, an electric mechanism portion 2 and a compression mechanism portion 3 are accommodated in the sealed container 1. A lubricating oil 4 that lubricates the compression mechanism 3 is stored at the bottom of the sealed container 1. The sealed container 1 includes a cylindrical central container 11, an upper container 12 fixed to the upper part of the central container 11, and a lower container 13 fixed to the lower part of the central container 11. The upper container 12 is fitted in the opening at the top of the central container 11. The electric mechanism unit 2 and the compression mechanism unit 3 are fixed to the inner peripheral surface of the central container 11. A lower container 13 is fitted in the opening at the bottom of the central container 11. An upper suction pipe 6 connected to the suction muffler 5 and a lower suction pipe 7 connected to the suction muffler 5 are connected to the central container 11. A discharge pipe 8 is connected to the upper container 12. The upper suction pipe 6 and the lower suction pipe 7 are pipes for supplying a gas refrigerant to the compression mechanism unit 3 through the suction muffler 5. The discharge pipe 8 is a pipe for discharging the gas refrigerant compressed by the compression mechanism unit 3 to, for example, a refrigerant pipe connected to the discharge pipe 8.

  The electric mechanism unit 2 includes a stator 21 fixed to the central container 11 and a rotor 22 provided inside the stator 21. The rotor 22 is connected to the drive shaft 23. The drive shaft 23 is provided, for example, parallel to the vertical direction. One end side of the drive shaft 23 is connected to the rotor 22 of the electric mechanism unit 2. The other end side of the drive shaft 23 is rotatably supported by the upper bearing 38 and the lower bearing 39. The upper bearing 38 corresponds to the bearing in the present invention.

  The drive shaft 23 is formed with an oil passage 23e, an oil suction hole 23a, an oil supply hole 23c, and an oil supply hole 23d. Lubricating oil flows through the oil passage 23e, the oil suction hole 23a, the oil supply hole 23c, and the oil supply hole 23d. The oil passage 23e is formed in the axial center part of the drive shaft 23, as shown in FIG. A spiral centrifugal pump 23b is provided in the oil passage 23e. The oil suction hole 23a is formed in the lower end part of the drive shaft 23, as shown in FIG. The oil suction hole 23a is an opening for taking lubricating oil into the oil passage 23e. The oil supply hole 23c and the oil supply hole 23d communicate with the oil passage 23e. The oil supply hole 23 c is a passage for lubricating oil supplied to the upper bearing 38. The oil supply hole 23 d is a passage for lubricating oil supplied to the lower bearing 39. The drive shaft 23 includes an eccentric part 23A1 and an eccentric part 23A2. An upper piston 33 is fixed to the eccentric portion 23A1. A lower piston 34 is fixed to the eccentric portion 23A2.

  The oil supply pipe 44 is a pipe that supplies the lubricating oil 4 stored at the bottom of the sealed container 1 to the drive shaft 23. The oil supply pipe 44 is disposed below the drive shaft 23. The oil supply pipe 44 is provided through the lower silencer 41 so as to extend from the drive shaft 23 side to the lower container 13 side. The oil supply pipe 44 includes a flat portion 44a as shown in FIG. The flat portion 44 a is provided at one end of the oil supply pipe 44. The flat portion 44 a is fixed between the lower bearing 39 and the lower silencer 41. Further, a gap Sp is formed between the flat portion 44 a of the oil supply pipe 44 and the lower end portion of the drive shaft 23. For this reason, even if the drive shaft 23 rotates, the oil supply pipe 44 does not rotate. The oil supply pipe 44 communicates with the oil suction hole 23a through the gap Sp. When the centrifugal pump 23 b rotates together with the drive shaft 23, the lubricating oil 4 is sucked into the oil supply pipe 44 as indicated by the arrow Z. The lubricating oil sucked into the oil supply pipe 44 is sucked into the oil passage 23e from the oil suction hole 23a. The diameter of the oil supply pipe 44 is determined so that optimum oil supply can be performed when the electric mechanism portion 2 rotates at high speed. That is, the diameter of the oil supply pipe 44 is smaller than the diameter of the oil suction hole 23 a of the drive shaft 23. Thereby, the lubricating oil is easily sucked from the oil supply pipe 44 to the drive shaft 23. That is, the lubricating oil 4 stored at the bottom of the sealed container 1 can be stably supplied to the compression mechanism unit 3.

  The compression mechanism unit 3 is, for example, a rotary type. The compression mechanism unit 3 is disposed below the electric mechanism unit 2. The compression mechanism unit 3 is fixed to the central container 11. An oil supply pipe 44 is provided below the compression mechanism unit 3. A space A formed between the electric mechanism portion 2 and the compression mechanism portion 3 is formed in the sealed container 1. The compression mechanism unit 3 includes an upper cylinder 31, a lower cylinder 32, an upper piston 33, a lower piston 34, an upper vane 35, a lower vane 36, a partition plate 37, an upper bearing 38, and a lower bearing 39. It has.

  The upper cylinder 31 and the lower cylinder 32 have a cylindrical shape, for example. The upper cylinder 31 and the lower cylinder 32 are eccentric with respect to the drive shaft 23. That is, the central axis of the upper cylinder 31 and the central axis of the upper cylinder 31 are deviated from the axis of the drive shaft 23. An upper piston 33 is accommodated in the upper cylinder 31. As shown in FIGS. 1 and 2, the upper cylinder 31 is formed with an upper compression chamber PR1 for compressing the refrigerant. The upper piston 33 is provided in the upper compression chamber PR1. The upper cylinder 31 has an upper suction port 42 formed therein. The upper suction pipe 6 is connected to the upper suction port 42. A lower piston 34 is accommodated in the lower cylinder 32. As shown in FIGS. 1 and 2, the lower cylinder 32 is formed with a lower compression chamber PR2 for compressing the refrigerant. The lower piston 34 is provided in the lower compression chamber PR2. A lower suction port 43 is formed in the lower cylinder 32. A lower suction pipe 7 is connected to the lower suction port 43.

  The upper compression chamber PR <b> 1 is a space surrounded by the inner peripheral surface of the upper cylinder 31, the lower end surface of the upper bearing 38, and the upper end surface of the partition plate 37. The lower compression chamber PR <b> 2 is a space surrounded by the inner peripheral surface of the lower cylinder 32, the upper end surface of the lower bearing 39, and the lower end surface of the partition plate 37.

  The upper bearing 38 is provided on the upper end surface of the upper cylinder 31. The upper bearing 38 and the upper end surface of the upper cylinder 31 are in contact with each other. The upper bearing 38 and the lower bearing 39 are cylindrical so that the drive shaft 23 can be inserted. The upper bearing 38 is formed with an upper gas hole (not shown) that communicates with the upper compression chamber PR1, and a discharge port O1 that discharges the refrigerant that has passed through the upper gas hole. The discharge port O1 corresponds to the first discharge port in the present invention. An upper silencer 50 is provided on the upper bearing 38. The lower bearing 39 is provided with a lower silencer 41. The upper bearing 38 has an end face 38 </ b> A facing the upper silencer 50. A discharge port O1 is provided in the end face 38A. Further, the lower bearing 39 is formed with a lower gas hole (not shown) communicating with the lower compression chamber PR2, and a discharge port O4 for discharging the refrigerant passing through the lower gas hole. The upper bearing 38 is provided in contact with the upper end surface of the upper cylinder 31, and the upper bearing 38 closes the upper opening of the upper cylinder 31. The lower bearing 39 is provided in contact with the lower end surface of the lower cylinder 32, and the lower bearing 39 closes the lower opening of the lower cylinder 32. The partition plate 37 is sandwiched between the lower end surface of the upper cylinder 31 and the upper end surface of the lower cylinder 32, and the partition plate 37 closes the lower opening of the upper cylinder 31 and opens the upper opening of the lower cylinder 32. Blocked.

  The upper piston 33 and the lower piston 34 are fitted on the drive shaft 23. The upper piston 33 and the lower piston 34 are provided eccentric to the axis of the drive shaft 23. As the drive shaft 23 rotates, the upper piston 33 and the lower piston 34 also rotate. As shown in FIG. 4, an upper vane 35 is in contact with the upper piston 33, and a lower vane 36 is in contact with the lower piston 34. The upper vane 35 is pressed against the upper piston 33 by the action of the upper elastic body 35A. The lower vane 36 is pressed against the lower piston 34 by the action of the lower elastic body 36A.

FIG. 5A is a perspective view showing the upper silencer 50 of the compressor 100 according to the embodiment in a state where the upper silencer 50 is disassembled into a housing 51 and a ring 52.
FIG. 5B is a perspective view of the housing 51. In FIG. 5B, the arrow AR indicates the flow of the gas refrigerant containing the lubricating oil, the arrow AR1 indicates the flow of the lubricating oil centrifuged from the gas refrigerant, and the arrow AR2 indicates the gas refrigerant of which the lubricating oil has been centrifuged. The flow is shown.

  The upper silencer 50 has a silencer function for suppressing noise generated when refrigerant is discharged from the discharge port O3 of the upper bearing 38, and a function of centrifuging the refrigerant and the lubricating oil. The upper silencer 50 is formed with a discharge port O2 that discharges the gas refrigerant and a discharge port O3 that discharges the lubricating oil centrifuged from the gas refrigerant. The discharge port O2 corresponds to the second discharge port in the present invention. The discharge port O3 corresponds to the third discharge port in the present invention.

  The upper silencer 50 is provided on the upper bearing 38. The upper silencer 50 covers the discharge port O1 of the upper bearing 38. In a state where the upper silencer 50 is attached to the upper bearing 38, a closed space B is formed between the upper silencer 50 and the end surface 38 </ b> A of the upper bearing 38. The refrigerant discharged from the discharge port O1 and the lubricating oil discharged from the discharge port O1 are supplied to the closed space B. Further, the refrigerant discharged from the discharge port O4 and the lubricating oil discharged from the discharge port O4 are supplied to the closed space B through gas holes that penetrate the lower bearing 39 and the like. The closed space B is a space surrounded by the upper silencer 50 and the end surface 38A of the upper bearing 38. More specifically, the closed space B is a space surrounded by the facing surface 51F of the housing 51, the inner peripheral surface 52S1 of the ring 52, and the end surface 38A of the upper bearing 38.

  The upper silencer 50 is, for example, a cylindrical member. The upper silencer 50 includes a housing 51 and a ring 52. The housing 51 is a cylindrical member in which an opening 51A is formed. Housing 51 includes an opening 51A, a flange 51B1, and a body 51B2. A spiral groove 51C is formed in both the flange 51B1 and the body portion 51B2. Since the upper silencer 50 includes the spiral groove 51C, the upper silencer 50 can centrifuge the lubricating oil from the refrigerant.

  The upper bearing 38 and the drive shaft 23 are inserted into the opening 51A. The inner peripheral surface of the housing 51 and the upper bearing 38 may be brought into contact with each other so that no gap is generated between the inner peripheral surface of the housing 51 and the upper bearing 38. Thereby, it can suppress that the refrigerant | coolant and lubricating oil of closed space B leak to the space A from 51 A of opening parts.

  The flange 51B1 is provided at the upper end portion of the body portion 51B2. The flange 51B1 and the body portion 51B2 are cylindrical members. As for flange 51B1, 1st surface 51B11, 2nd surface 51B12 (refer FIG. 7A), and flow-path formation part 51B13 are formed. In a state where the upper silencer 50 is attached to the upper bearing 38, the first surface 51B11 is parallel to the horizontal plane or inclined downward in the direction from the central axis of the upper silencer 50 toward the outer peripheral surface 51S2. is doing. When the lubricating oil flows from the groove 51C of the body portion 51B2 to the groove 51C of the flange 51B1, it reaches the first surface 51B11. When the lubricating oil reaches the first surface 51B11, the flow direction of the lubricating oil becomes the horizontal direction. Thus, the first surface 51B11 has a function of changing the flow direction of the lubricating oil. That is, the first surface 51B11 suppresses the lubricant from being discharged upward from the discharge port O3.

  In a state where the upper silencer 50 is attached to the upper bearing 38, the second surface 51 </ b> B <b> 12 is parallel to the drive shaft 23 and parallel to the radial direction of the housing 51. When the lubricating oil reaches the flow path forming portion 51B13, the lubricating oil flows along the circumferential direction of the housing 51. Thereafter, when the lubricating oil reaches the second surface 51B12, the flow direction of the lubricating oil changes from the circumferential direction of the housing 51 to the radial direction. As described above, the second surface 51B12 has a function of changing the flow direction of the lubricating oil. Since the upper silencer 50 is formed with the second surface 51 </ b> B <b> 12, it is possible to prevent the lubricating oil from turning inside the sealed container 1.

  The flow path forming portion 51B13 is formed so as to face the first surface 51B11 and the second surface 51B12.

  An upper end surface 51S1 is formed on the body portion 51B2. A discharge port O2 is formed in the upper end surface 51S1. The number of discharge ports O2 formed is the same as the number of grooves 51C. In the embodiment, two discharge ports O2 are formed on the upper end surface 51S1. The direction of the discharge port O2 is directed to the central container 11 (see FIG. 1) of the sealed container 1. As shown in FIG. 5A, the direction of the discharge port O2 matches the direction vector Dr. When the direction vector Dr is extended to the inner peripheral surface of the central container 11, the direction vector Dr and the inner peripheral surface of the central container 11 may form an acute angle. As a result, the gas refrigerant flows along the inner peripheral surface of the central container 11 even after being discharged from the upper silencer 50, and forms a swirl flow in the sealed container 1. Therefore, even if lubricating oil is contained in the gas refrigerant discharged from the discharge port O2, the lubricating oil can be centrifuged from the gas refrigerant.

  An outer peripheral surface 51S2 is formed on the body portion 51B2. A spiral groove 51C is formed on the outer peripheral surface 51S2. The groove 51C is formed so as to extend in the circumferential direction of the outer peripheral surface 51S2 and in the upward direction. Two grooves 51C are formed in the body portion 51B2. In addition, the groove | channel 51C may be formed in the trunk | drum 51B2 only 1 line, and may be formed 3 or more.

  An opposing surface 51F is formed on the body portion 51B2. In a state where the upper silencer 50 is attached to the upper bearing 38, the facing surface 51 </ b> F faces the end surface 38 </ b> A of the upper bearing 38.

  The ring 52 is a cylindrical member. The ring 52 accommodates the body portion 51B2 of the housing 51. On the end of the ring 52, a flange 51B1 of the housing 51 is provided. Specifically, in a state where the upper silencer 50 is attached to the upper bearing 38, the upper end portion of the ring 52 and the lower end surface of the flange 51B1 of the housing 51 are in contact with each other. The ring 52 has an inner peripheral surface 52S1 and an outer peripheral surface 52S2. The inner peripheral surface 52S1 is in contact with the outer peripheral surface 51S2 of the housing 51. That is, the ring 52 is put on the outer peripheral surface 51S2 of the housing 51, whereby the release portion of the groove 51C is closed. As a result, a flow path through which the refrigerant and the lubricating oil flow is formed along the groove 51C. This flow path will be described later with reference to FIG. 7B.

FIG. 6A is a top view of the housing 51.
FIG. 6B is a bottom view of the housing 51.

  As shown in FIG. 6A, one discharge port O2 and the other discharge port O2 are arranged at a position of 180 degrees with the central axis of the housing 51 as the center. As shown in FIG. 6B, one discharge port O3 and the other discharge port are arranged at a position of 180 degrees with the central axis of the housing 51 as the center.

  As shown in FIG. 6B, the housing 51 is formed with a suction port O5. The suction port O5 is located at the lower end of the groove 51C. The refrigerant in the closed space B and the lubricating oil in the closed space B flow into the groove 51C from the suction port O5. The number of suction ports O5 formed is equal to the number of grooves 51C. The suction port O5 is formed in the facing surface 51F.

  The distance from the discharge port O2 to the drive shaft 23 is shorter than the distance from the discharge port O3 to the drive shaft 23. As shown in FIG. 6A, the distance from the discharge port O2 to the axis of the drive shaft 23 can be represented by a distance Dst1. Further, as shown in FIG. 6B, the distance from the discharge port O3 to the axis of the drive shaft 23 can be represented by a distance Dst2. Here, in the upper silencer 50, the distance Dst1 is shorter than the distance Dst2. That is, the discharge port O3 is located outside the discharge port O2. Thereby, the effect which centrifuges lubricating oil from a gas refrigerant increases.

FIG. 7A is a side view of the housing 51.
FIG. 7B is a longitudinal sectional view of the upper silencer 50 of the compressor 100 according to the embodiment. FIG. 7B is a cross-sectional view taken along line AA shown in FIG. 7A.
FIG. 7C is a schematic diagram for explaining a flow path formed in the upper silencer 50. FIG. 7C shows the same longitudinal section as FIG. 7B, but for convenience of explanation, the housing 51 is not hatched.

  The upper silencer 50 includes a spiral main flow path FP, a first branch flow path FP1 branched from the main flow path FP, and a discharge port O2 connected to the first branch flow path FP1 and discharging a refrigerant. . The upper silencer 50 also includes a second branch channel FP2 that branches from the main channel FP, and a discharge port O3 that is connected to the second branch channel FP2 and that discharges the lubricating oil centrifuged from the refrigerant. .

  The main flow path FP is formed between the groove 51C and the inner peripheral surface 52S1 of the ring 52. One of the main flow paths FP is connected to the closed space B. The other of the main flow paths FP is connected to the first branch flow path FP1 and the second branch flow path FP2.

  The first branch flow path FP <b> 1 is a through hole formed in the housing 51. The first branch channel FP1 has a configuration different from that of the groove 51C. The first branch flow path FP1 is a flow path that penetrates the outer peripheral surface 51S2 of the housing 51 and the upper end surface 51S1 of the housing 51. That is, one of the first branch flow paths FP1 is connected to the groove 51C of the outer peripheral surface 51S2. The other end of the first branch flow path FP1 is connected to the discharge port O2 of the upper end surface 51S1. That is, the first branch channel FP1 is a channel formed closer to the center axis of the housing 51 than the second branch channel FP2.

  A portion that branches from the main flow path FP to the first branch flow path FP1 and the second branch flow path FP2 is referred to as a branch portion Br. The second branch channel FP2 is formed above the branch part Br. The second branch channel FP2 is formed by a part of the groove 51C. That is, the groove 51C forms both the main flow path FP and the second branch flow path FP2. The second branch flow path FP2 is formed in both the flange 51B1 and the body portion 51B2.

  The first surface 51B11 is arranged such that the flow direction of the lubricating oil at the end of the second branch flow path FP2 is horizontal, or the lubricating oil at the end of the second branch flow path FP2 is on the lower side. It is formed to head. Thereby, the compressor 100 can suppress that lubricating oil is discharged | emitted upwards from the discharge outlet O3, and can return lubricating oil to the bottom part of the airtight container 1 efficiently.

  The second surface 51B12 is formed at the end of the second branch flow path FP2. The second surface 51B12 is connected to the first surface 51B11. The second surface 51B12 is parallel to the drive shaft 23 and parallel to the radial direction of the housing 51. Thereby, the compressor 100 can suppress that lubricating oil turns in the airtight container 1, and can return lubricating oil to the bottom part of the airtight container 1 efficiently.

  The refrigerant discharged from the discharge port O1 flows into the main flow path FP after the refrigerant compressed by the compression mechanism unit 3 is supplied to the closed space B. Here, since the main flow path FP is narrower than the closed space B, the fluid resistance increases accordingly. For this reason, the upper silencer 50 can obtain an effect of suppressing sound when the refrigerant is discharged from the discharge port O1.

Next, the operation of the compressor 100 according to the embodiment will be described.
The lubricating oil 4 stored at the bottom of the sealed container 1 is drawn into the oil suction hole 23 a through the oil supply pipe 44 by the action of the centrifugal pump 23 b that rotates together with the drive shaft 23. The lubricating oil drawn into the oil suction hole 23 a is supplied between the upper bearing 38 and the drive shaft 23 from the oil supply hole 23 c. In addition, the lubricating oil drawn into the oil suction hole 23 a is supplied between the upper bearing 38 and the upper surface of the upper piston 33. The lubricating oil drawn into the oil suction hole 23 a is supplied between the lower bearing 39 and the drive shaft 23 through the oil supply hole 23 d. Further, the lubricating oil drawn into the oil suction hole 23 a is supplied between the lower bearing 39 and the lower surface of the lower piston 34. By supplying the lubricating oil, the drive shaft 23 rotates smoothly. Although not shown, the lubricating oil is also supplied from the drive shaft 23 to the upper vane 35 and the lower vane 36.

  When the drive shaft 23 rotates, the upper piston 33 and the lower piston 34 also rotate. Since the upper piston 33 is in contact with the upper vane 35, the upper piston 33 performs an eccentric motion. Further, since the lower piston 34 is in contact with the lower vane 36, the lower piston 34 performs an eccentric motion. At this time, the upper vane 35 and the lower vane 36 perform piston operation. The gas refrigerant is supplied to the upper compression chamber PR1 and the lower compression chamber PR2 in the compression mechanism section 3 through the upper suction pipe 6 and the lower suction pipe 7. The gas refrigerant in the upper compression chamber PR1 is compressed as the upper piston 33 rotates. The gas refrigerant in the lower compression chamber PR2 is compressed as the lower piston 34 rotates. At this time, the refrigerant in the upper compression chamber PR1 is mixed with lubricating oil. Lubricating oil is also mixed in the refrigerant in the lower compression chamber PR2. For this reason, in the compression mechanism part 3, lubricating oil is also compressed with a refrigerant | coolant, and a refrigerant | coolant and lubricating oil become a mixed gas.

  This mixed gas is discharged from the discharge port O1 and the discharge port O4. The mixed gas discharged from the discharge port O1 is supplied to the closed space B of the upper silencer 50. The mixed gas discharged from the discharge port O4 is supplied to the closed space in the lower silencer 41. The mixed gas discharged into the closed space of the lower silencer 41 passes through a gas hole (not shown) penetrating the lower bearing 39, the lower cylinder 32, the partition plate 37, the upper cylinder 31 and the upper bearing 38, and then the upper silencer. 50 closed spaces B are supplied.

  As the mixed gas discharged into the closed space B flows through the upper silencer 50, the lubricating oil is centrifuged from the gas refrigerant. The gas refrigerant is discharged into the space A from the discharge port O2. The gas refrigerant forms a swirling flow in the space A of the sealed container 1. Lubricating oil is discharged from the discharge port O3 into the space inside the sealed container 1 and returns to the bottom of the sealed container 1.

  The gas refrigerant swirling in the space A reaches the upper part in the hermetic container 1 through the gas hole 22 a provided in the rotor 22 and the air gap 2 a between the stator 21 and the rotor 22. The gas refrigerant that has reached the upper part in the sealed container 1 is discharged from the discharge pipe 8 to the outside of the sealed container 1.

  DESCRIPTION OF SYMBOLS 1 Airtight container, 2 Electric mechanism part, 2a Air gap, 3 Compression mechanism part, 4 Lubricating oil, 5 Suction muffler, 6 Upper suction pipe, 7 Lower suction pipe, 8 Discharge pipe, 11 Central container, 12 Upper container, 13 Lower Container, 21 Stator, 22 Rotor, 22a Gas hole, 23 Drive shaft, 23A1 Eccentric part, 23A2 Eccentric part, 23a Oil suction hole, 23b Centrifugal pump, 23c Oil supply hole, 23d Oil supply hole, 23e Oil passage, 31 Upper cylinder, 32 Lower cylinder, 33 Upper piston, 34 Lower piston, 35 Upper vane, 35A Upper elastic body, 36 Lower vane, 36A Lower elastic body, 37 Partition plate, 38 Upper bearing, 38A End face, 39 Lower bearing, 41 Lower Silencer, 42 Upper suction port, 43 Lower suction port, 44 Refueling pipe, 44a Plane portion, 50 Upper silencer, 51 housing, 51A opening, 51B1 flange, 51B11 first surface, 51B12 second surface, 51B13 flow path forming portion, 51B2 trunk, 51C groove, 51F facing surface, 51S1 upper end surface, 51S2 outer peripheral surface, 52 ring, 52S1 inner surface, 52S2 outer surface, 100 compressor, A space, B closed space, Br branching section, Dr direction vector, Dst1 distance, Dst2 distance, FP main channel, FP1 first branch channel, FP2 second Branch flow path, O1 discharge port, O2 discharge port, O3 discharge port, O4 discharge port, O5 suction port, PR1 upper compression chamber, PR2 lower compression chamber, Sp gap.

Claims (12)

A sealed container;
An electric mechanism portion including a stator and a rotor disposed inside the stator, and provided in the sealed container;
A drive shaft having one end connected to the electric mechanism,
A piston connected to the other end side of the drive shaft, a cylinder accommodating the piston, and a first discharge port for discharging the refrigerant in the cylinder are formed to support the other end side of the drive shaft. A compression mechanism that includes a bearing and compresses the refrigerant;
A silencer provided on the bearing and covering the first outlet;
With
Between the end surface of the bearing and the silencer, a closed space is formed to which the refrigerant discharged from the first discharge port is supplied,
The silencer is configured to centrifuge the refrigerant in the closed space and the lubricating oil in the closed space. The silencer includes a spiral main flow path, a first branch flow path branched from the main flow path, a second discharge port connected to the first branch flow path and discharging refrigerant, and the main flow A second branch flow path that branches from the path, and a third discharge port that is connected to the second branch flow path and discharges the lubricating oil centrifuged from the refrigerant,
One of the main flow paths is connected to the closed space;
The compressor according to claim 1, wherein the other of the main flow paths is connected to the first branch flow path and the second branch flow path. The compressor according to claim 2, wherein a distance from the second discharge port to the drive shaft is shorter than a distance from the third discharge port to the drive shaft. The silencer includes an inner peripheral surface extending from the compression mechanism portion side to the electric mechanism portion side, and an opposing surface facing the bearing,
The closed space is formed by an end surface of the bearing, the inner peripheral surface, and the facing surface,
The compressor according to claim 2 or 3, wherein a suction port to which one of the main flow paths is connected is formed on the facing surface. The silencer includes a flange provided on an upper portion,
The flange is formed with the second branch channel, the third discharge port, and a first surface formed at an end of the second branch channel,
The first surface is arranged so that the flow direction of the lubricating oil at the end of the second branch flow path is horizontal, or the lubricating oil at the end of the second branch flow path is on the lower side. The compressor according to any one of claims 2 to 4, wherein the compressor is formed so as to face. The flange includes a second surface formed at an end of the second branch flow path and connected to the first surface,
The compressor according to claim 5, wherein the second surface is parallel to the drive shaft and parallel to a radial direction of the silencer. The silencer
A cylindrical housing including an outer peripheral surface in which a spiral groove is formed;
An inner peripheral surface that contacts the outer peripheral surface of the housing, and a cylindrical ring that houses the housing,
The compressor according to claim 2 or 3, wherein the main flow path is interposed between the outer peripheral surface of the housing and the inner peripheral surface of the ring, and is formed along the spiral groove. The housing includes a facing surface facing the bearing;
The closed space is formed by an end surface of the bearing, the inner peripheral surface of the ring, and the facing surface,
The compressor according to claim 7, wherein a suction port to which one of the main flow paths is connected is formed on the facing surface. The housing includes a flange provided on an end of the ring;
The flange is formed with the second branch channel, the third discharge port, and a first surface formed at an end of the second branch channel,
The first surface is arranged so that the flow direction of the lubricating oil at the end of the second branch flow path is horizontal, or the lubricating oil at the end of the second branch flow path is on the lower side. The compressor according to claim 7 or 8, wherein the compressor is formed so as to face. The flange includes a second surface formed at an end of the second branch flow path and connected to the first surface,
The compressor according to claim 9, wherein the second surface is parallel to the drive shaft and parallel to a radial direction of the housing. The sealed container includes a cylindrical central container to which the stator is fixed,
The compressor according to any one of claims 2 to 10, wherein the second discharge port is directed to the central container. The silencer
A cylindrical housing including an outer peripheral surface in which a spiral groove is formed;
A cylindrical ring that includes an inner peripheral surface that contacts the outer peripheral surface of the housing and houses the housing;
The compressor according to claim 1, further comprising: a spiral main channel that is interposed between the outer peripheral surface of the housing and the inner peripheral surface of the ring and is formed along the spiral groove.

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