JP2011127438A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor reducing an agitating loss by a balancer, while reducing fluid density in a balance cover. <P>SOLUTION: This compressor 100 includes an oil drain pipe 30 installed in a balancer cover oil drain hole 12a and communicating a space in the balancer cover 12 with a motor lower space 22. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a scroll-type compressor used as a component of a refrigeration cycle apparatus such as an air conditioner, a heat pump water heater, a refrigerator, etc., and more particularly a compressor configured to reduce agitation loss of refrigeration oil by a balancer. It is about.

  Conventionally, there is a scroll compressor provided with a balancer and a balancer cover. The balancer is fixed to the crankshaft, rotates with the rotor, and has a function of correcting the deflection of the rotating shaft generated by the orbiting scroll. The balancer cover covers the balancer and has a function of suppressing agitation of the refrigerating machine oil discharged from the bearing portion by the balancer and suction of the refrigerating machine oil into the compression chamber. That is, the balancer cover suppresses scattering of the refrigerating machine oil in the shell.

  As such, “a compression unit comprising a fixed scroll and an orbiting scroll, each of which has a vortex and these vortices are combined together to form a compression chamber between the two vortices, A motor driven through a shaft, a balancer fixed to a rotating part such as the crankshaft, and having a static and dynamic balance, a shell for housing the compression part and the motor, and inside the shell, the compression part and a motor chamber A frame for partitioning into the upper part of the motor chamber, an intake pipe for supplying intake gas to the upper part of the motor chamber, and the crankshaft, provided in the frame in the vicinity of the inner wall surface of the shell that is symmetrical to the intake pipe, and the compression part and the motor A first suction port that communicates with the chamber, is supplied via the suction pipe, cools the motor, and then suctions the compression chamber via the first suction port. In the scroll fluid machine that forms the flow path of the intake gas guided to the part, the rotation locus part of the balancer is formed in an umbrella shape so as to cover from above, and the outer peripheral edge part is bent downward to provide a flange part. And a balancer cover formed so that the lower end of the flange portion is positioned below the upper end of the upper coil end has been proposed (see, for example, Patent Document 1).

Japanese Patent Laid-Open No. 07-1558569 (Example 7)

  However, in the technique described in Patent Document 1, when the amount of refrigeration oil discharged from the bearing portion increases, the balancer cover is filled with refrigeration oil. If it becomes so, the fluid density in a balancer cover will become large, and the stirring loss by stirring of a balancer will increase.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a compressor in which the agitation loss due to the balancer is reduced while the fluid density in the balancer cover is reduced.

  The compressor according to the present invention includes a shell, a motor stator fixedly supported in the shell, and is rotatably disposed on an inner peripheral surface side of the motor stator, and constitutes a motor together with the motor stator. A motor rotor, a crankshaft inserted into a central portion of the motor rotor and rotationally driven together with the motor rotor, a compression portion compressing fluid sucked into the shell by rotation of the crankshaft, A first balancer attached to the crankshaft and rotating together with the crankshaft; an outer peripheral edge portion bent downward to form a flange portion; and a balancer cover oil drain hole penetratingly formed in a part of the flange portion; The lower end of the part is below the upper end of the upper coil end of the winding wound around the motor / stator A balancer cover that is disposed so as to cover the rotation locus part of the first balancer from above, and is attached to the balancer cover oil drain hole, and a space in the balancer cover and a lower space of the motor, And a balancer cover drain pipe that communicates with each other.

  The compressor according to the present invention includes a shell, a motor stator fixedly supported in the shell, and is rotatably disposed on an inner peripheral surface side of the motor stator, and constitutes a motor together with the motor stator. A motor rotor, a crankshaft inserted into a central portion of the motor rotor and rotationally driven together with the motor rotor, a compression portion compressing fluid sucked into the shell by rotation of the crankshaft, A first balancer attached to the crankshaft and rotating together with the crankshaft; a second balancer attached to the bottom of the motor rotor and rotating together with the motor rotor; and a flange formed by bending the outer peripheral edge downward And the lower end of the flange is wound around the motor stator A balancer cover disposed so as to be positioned below the upper end of the upper coil end of the winding and covering the rotation locus of the first balancer from above, and the motor rotor has at least One motor / rotor oil drain hole is formed to penetrate in the axial direction, and at least one second balancer oil drain hole communicating with the motor / rotor oil drain hole is formed in the second balancer to penetrate in the axial direction. It is characterized by that.

  According to the compressor of the present invention, the fluid density in the balancer cover can be reduced, and the stirring loss of the fluid due to the rotation of the balancer can be reduced.

It is a longitudinal section showing an example of section composition of a compressor concerning Embodiment 1 of the present invention. It is a schematic diagram which shows a balancer cover and a balancer cover oil drain pipe typically. It is a longitudinal cross-sectional view which shows the cross-sectional structural example of the compressor which concerns on Embodiment 2 of this invention. It is a top view which shows the state which looked at the motor from the top.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view showing an example of a sectional configuration of a compressor 100 according to Embodiment 1 of the present invention. FIG. 2 is a schematic diagram schematically showing the balancer cover 12 and the balancer cover oil drain pipe 30. Based on FIG.1 and FIG.2, the structure and operation | movement of the compressor 100 are demonstrated. The compressor 100 is widely used in various industrial machines such as a refrigerator, a freezer, a vending machine, an air conditioner, a refrigeration apparatus, and a water heater. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

  FIG. 1 shows an example in which the compressor 100 is a vertical scroll compressor. The compressor 100 has a function of sucking fluid (for example, refrigerant, air, and other working fluid), compressing it, and discharging it in a high temperature / high pressure state. The compressor 100 is configured such that a compression unit 60, a drive unit 70, and other components are housed in a shell 14 constituting an outer shell. As shown in FIG. 1, in the shell 14, the compression part 60 is arrange | positioned at the upper side, and the drive part 70 is arrange | positioned at the lower side, respectively. That is, the compressor 100 can be broadly classified into the compression unit 60 and the drive unit 70.

  The compression unit 60 has a function of compressing the fluid sucked from the suction pipe 15 and discharging it to the high-pressure space 53 formed above the shell 14. The high-pressure fluid is discharged from the discharge pipe 16 to the outside of the compressor 100. The drive unit 70 serves to drive the orbiting scroll 50 constituting the compression unit 60 in order to compress the fluid by the compression unit 60. That is, when the drive unit 70 drives the orbiting scroll 50 via the crankshaft 3, the fluid is compressed by the compression unit 60.

  The compression unit 60 includes at least a fixed scroll 40, an orbiting scroll 50, and a frame 5. As shown in FIG. 1, the orbiting scroll 50 is arranged on the lower side, and the fixed scroll 40 is arranged on the upper side. The fixed scroll 40 includes an end plate 41 and a wrap 42 that is a spiral projection erected on one surface of the end plate 41. The orbiting scroll 50 includes an end plate 51 and a wrap 52 that is a spiral projection standing on one surface of the end plate 51. The fixed scroll 40 and the swing scroll 50 are mounted in the shell 14 with the wrap 42 and the wrap 52 meshing with each other.

  A compression chamber 4 having a relatively variable volume is formed between the wrap 52 and the wrap 42. Further, an Oldham joint 6 is provided on the end surface on the side opposite to the lap of the swing scroll 50 (hereinafter referred to as a thrust surface). That is, the Oldham joint 6 is provided between the swing scroll 50 and the frame 5.

  The fixed scroll 40 is fixed in the shell 14 via the frame 5. A discharge port 43 that discharges the compressed and high pressure fluid is formed at the center of the fixed scroll 40. That is, the fluid compressed by the compression unit 60 is discharged from the discharge port 43 into the high-pressure space 53 and discharged to the outside of the compressor 100 through the discharge pipe 16. The fixed scroll 40 is coupled to the frame 5 with a bolt or the like (not shown).

  The orbiting scroll 50 performs a revolving motion without rotating with respect to the fixed scroll 40. Further, a hollow cylindrical swing scroll / bearing sliding portion 2a for receiving a driving force is formed at a substantially central portion of the thrust surface of the swing scroll 50. An eccentric pin portion 3d provided at the upper end of a crankshaft 3 to be described later is fitted (engaged) and connected to the swing scroll / bearing sliding portion 2a. The thrust surface of the orbiting scroll 50 functions as the orbiting scroll / thrust sliding portion 2b.

  The Oldham coupling 6 provided on the thrust surface of the orbiting scroll 50 functions to prevent the rotating motion of the orbiting scroll 50 and to enable a revolving motion. That is, the Oldham joint 6 functions as a rotation prevention mechanism for the swing scroll 50. Although FIG. 1 shows an example in which the Oldham coupling 6 is provided on the thrust surface of the orbiting scroll 50, the Oldham coupling 6 is provided between the fixed scroll 40 and the orbiting scroll 50. Also good.

  The frame 5 is fixed to the inner peripheral surface of the shell 14 by press fitting or the like, and a through hole is formed at the center for supporting the crankshaft 3. The frame 5 supports the orbiting scroll 50 and supports the crankshaft 3 rotatably by a crankshaft / frame bearing sliding portion 3b. Further, the frame 5 is formed with a suction port 5 a for taking a fluid into the compression chamber 4 so as to penetrate from the drive unit 70 side to the compression unit 60. Further, the frame 5 has an oil drain hole 5b for returning the refrigerating machine oil 17a having lubricated the sliding portions (the swing scroll / bearing slide portion 2a, the swing scroll / thrust slide portion 2b) to the oil sump 17. It is formed so as to penetrate from the compression unit 60 side to the drive unit 70 side. The frame 5 may be fixed to the inner peripheral surface of the shell 14 by shrink fitting, welding, or the like.

  The drive unit 70 is fixedly held in the shell 14, and a motor stator (stator) 13, and a motor rotor fixed to the crankshaft 3 and rotatably disposed on the inner peripheral surface side of the motor stator 13. (Rotor) 9 and at least a crankshaft 3 which is a rotating shaft accommodated in the shell 14 in the vertical direction. The motor / rotor 9 and the motor / stator 13 constitute an electric motor.

  The motor stator 13 has a function of rotating the motor rotor 9 when energized. Further, the outer surface of the motor / stator 13 is fixedly supported on the shell 14 by shrink fitting or the like. In FIG. 1, coil ends (upper coil end 13 a and lower coil end 13 b) wound around the motor stator 13 are illustrated at the upper end and the lower end of the motor stator 13, respectively. The motor rotor 9 has a function of rotating and driving the crankshaft 3 by energizing the motor stator 13. This motor rotor 9 uses high-frequency heating, is partially heated to expand its inner diameter, is shrink-fitted on the outer periphery of the crankshaft 3, has a permanent magnet inside, and has a slight clearance from the motor-stator 13 Are held apart.

  The crankshaft 3 rotates with the rotation of the motor / rotor 9 to drive the swing scroll 50 to rotate. The crankshaft 3 is a crankshaft / frame bearing sliding portion 3b positioned on the upper side of the center of the frame 5 and has a lower side of a bearing positioned on the center of the second frame 19 fixedly disposed below the shell 14. 20 is rotatably supported. At the upper end portion of the crankshaft 3, an eccentric pin portion 3 d that is fitted to the swing scroll / bearing sliding portion 2 a of the swing scroll 50 and rotates together with the swing scroll 50 is formed. An eccentric hole 3a is formed in the crankshaft 3 so as to penetrate in the axial direction. An oil pump 18 is provided at the lower end portion of the crankshaft 3 to supply the refrigerating machine oil 17a to the sliding portion through the eccentric hole 3a.

  A second balancer 11 is attached to the lower surface of the motor rotor 9 with screws or the like. A first balancer 10 is mounted on the outer periphery of the crankshaft 3 above the motor rotor 9 by shrink fitting or the like. The first balancer 10 and the second balancer 11 have a function of rotating together with the motor rotor 9 and correcting the deflection of the crankshaft 3 generated by the swing scroll 50.

  The compressor 100 is connected to a suction pipe 15 for sucking fluid and a discharge pipe 16 for discharging fluid. Further, a second frame 19 is fixed to the inside lower part of the shell 14 of the compressor 100 by press fitting or the like. The second frame 19 is fixed to the inner peripheral surface of the shell 14, and a through hole is formed at the center for supporting the crankshaft 3. The second frame 19 rotatably supports the crankshaft 3 with a bearing 20. The frame 5 is fixed on the upper side, and the second frame 19 is fixed on the lower side. An oil sump 17 for storing the refrigerating machine oil 17a is formed below the crankshaft 3, that is, at the bottom of the shell 14.

  A motor upper space 21 is formed above the motor stator 13 in the shell 14, and a motor lower space 22 is formed above the motor stator 13 in the shell 14. Further, in the shell 14, there is a frame oil drain pipe 7 that communicates the oil drain hole 5 b formed in the frame 5 with the motor lower space 22 and guides the refrigeration oil 17 a flowing out from the oil drain hole 5 b to the oil sump 17. It is provided along the inner wall. The frame oil drain pipe 7 is fixed to a drain oil pipe fixing plate 8 provided on the lower surface side of the frame 5 by brazing or welding means.

  Further, the compressor 100 is provided with a balancer cover 12 on the lower surface side of the frame 5 that covers the rotation locus portion of the first balancer 10 from above. The drain pipe fixing plate 8 and the balancer cover 12 are fixed to the frame 5 with bolts or the like. The outer peripheral edge portion of the balancer cover 12 is formed in a flange shape (hereinafter referred to as a flange portion 12b) bent downward (see FIG. 2). The balancer cover 12 is configured such that the lower end portion of the flange portion 12b of the balancer cover 12 is positioned below the upper end of the upper coil end 13a.

  Further, as clearly shown in FIG. 2, the balancer cover oil drain hole 12 a is formed through the side surface (flange portion 12 b) of the balancer cover 12. A balancer cover drain pipe 30 is attached to the balancer cover drain hole 12a by brazing or welding means. That is, the balancer cover oil exhaust pipe 30 allows the space in the balancer cover 12 and the motor lower space 22 to communicate with each other.

The operation of the compressor 100 will be described together with the flow of fluid (dotted arrow shown in FIG. 1).
When the motor stator 13 is energized, rotational torque is generated in the motor rotor 9, and the crankshaft 3 rotates together with the motor rotor 9. Then, the orbiting scroll 50 engaged with the eccentric pin portion 3d of the crankshaft 3 also starts to rotate. At this time, the rotational motion of the orbiting scroll 50 is hindered by the Oldham joint 6 and converted into a revolving motion. As a result, the orbiting scroll 50 is oscillated to start revolving and compress the fluid by a known compression principle. Here, when the motor rotor 9 rotates, the eccentric revolving motion of the orbiting scroll 50 starts. The static balance and the dynamic balance are performed by the first balancer 10 and the second balancer 11.

When the compressor 100 is operated, fluid gas is sucked into the shell 14 from the suction pipe 15.
The fluid gas sucked into the shell 14 is formed by the wrap 42 of the fixed scroll 40 and the wrap 52 of the orbiting scroll 50 through the suction port 5a after the motor is cooled by the rotational drive of the crankshaft 3. Into the compression chamber 4 and compression starts. That is, the fluid gas sucked into the compression chamber 4 is increased in pressure by the volume of the compression chamber 4 being reduced by the compression action of the fixed scroll 40 and the swing scroll 50.

  That is, in the compression unit 60, when the orbiting scroll 50 revolves, the fluid gas is taken in from the suction port 5 a and is gradually compressed with the rotation of the orbiting scroll 50 toward the center. The sucked fluid is compressed until the compression chamber 4 communicates with the discharge space (high pressure space 53), and the pressure is increased. The compressed high-pressure fluid gas passes through the discharge port 43 of the fixed scroll 40, passes through the high-pressure space 53, and then is discharged to the outside of the compressor 100 through the discharge pipe 16. When the motor / stator 13 is de-energized, the compressor 100 stops operating.

Next, the flow of the refrigerating machine oil 17a in the shell 14 (solid line arrow shown in FIG. 1) will be described.
When the crankshaft 3 rotates, the refrigeration oil 17a is sucked by the oil pump 18, and passes through the eccentric hole 3a provided in the crankshaft 3 by the centrifugal force from the bottom to the top. The swing scroll / bearing sliding portion 2a, After being supplied to the sliding parts such as the crankshaft / frame bearing sliding part 3b, the swinging scroll / thrust sliding part 2b and the bearing 20, the oil returns to the oil sump 17 provided at the inner bottom part of the shell 14 by gravity. Further, the excessive refrigerating machine oil 17 a supplied to the swing scroll / thrust sliding portion 2 b passes through the oil drain hole 7 through the oil drain hole 5 b and returns to the oil reservoir 17 through the motor lower space 22.

  The refrigerating machine oil 17 a discharged from the crankshaft / frame bearing sliding portion 3 b is agitated by the first balancer 10 in the balancer cover 12. Therefore, the balancer cover 12 is a flange portion 12b whose outer peripheral edge portion is bent downward in order to prevent the stirred refrigerating machine oil 17a from being sucked into the compression chamber 4 together with the suction gas, and a lower end portion of the flange portion 12b. Is formed below the upper end of the upper coil end 13a. Therefore, scattering of the refrigerating machine oil 17a can be suppressed.

  The refrigerating machine oil 17a agitated by the first balancer 10 becomes mist, is mixed in the suction gas, hits the inner wall surface of the balancer cover 12, and moves downward by its own weight. On the other hand, the mist-like refrigerating machine oil 17a scattered outward when falling from the lower end surface of the balancer cover 12 hits the inner wall surface of the upper coil end 13a, and is prevented from being scattered upward and moved downward by its own weight. Then, it returns to the oil sump 17 through the motor lower space 22.

  By the way, in the motor upper space 21, the first balancer 10 rotates with the rotation of the crankshaft 3, so that a swirling gas flow is generated in the space in the balancer cover 12. As described above, the mist refrigerating machine oil 17a is mixed in the suction gas flowing in the shell 14, but heavy oil particles are separated to the outside around the crankshaft 3 by the centrifugal force action of the swirling flow. As a result, a gas having a high oil concentration is generated in the vicinity of the inner wall surface of the balancer cover 12.

  As a result, in the conventional balancer cover, the crankshaft rotates in a gas having a high oil concentration, so that a fluid agitation loss is caused by the first balancer. Therefore, in the compressor 100 according to Embodiment 1, the balancer cover 12 is provided with the balancer cover drain hole 12a and the balancer cover drain pipe 30 so as to reduce the fluid density in the balancer cover 12. That is, in the compressor 100, the refrigeration machine oil 17a existing in the space in the balancer cover 12 is returned to the oil sump 17 through the balancer cover drain hole 12a and the balancer cover drain pipe 30 so that the fluid density in the balancer cover 12 is restored. We are trying to reduce it.

  As described above, according to the compressor 100 according to the first embodiment, the oil discharge passage (balancer cover exhaust oil) that discharges the refrigerating machine oil 17a that has been blocked by hitting the inner wall surface of the balancer cover 12 to the oil sump 17. Since the hole 12a and the balancer cover oil drain pipe 30) are provided, the fluid density in the balancer cover 12 can be efficiently reduced. Therefore, the stirring loss of the fluid due to the rotation of the balancer (particularly the first balancer 10) can be reduced. Therefore, a high-performance compressor 100 can be provided. In addition, the installation number of the balancer cover oil discharge hole 12a and the balancer cover oil discharge pipe 30 is not particularly limited.

Embodiment 2. FIG.
FIG. 3 is a longitudinal sectional view showing a sectional configuration example of the compressor 100a according to Embodiment 2 of the present invention. FIG. 4 is a plan view showing the motor viewed from above. Based on FIG.3 and FIG.4, a structure and operation | movement of the compressor 100a are demonstrated. Similar to the compressor 100, the compressor 100a is widely used in various industrial machines such as a refrigerator, a freezer, a vending machine, an air conditioner, a refrigeration apparatus, and a water heater. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.

  In the compressor 100a according to the second embodiment, the motor / rotor 9 and the second balancer 11 are formed with a motor / rotor oil drain hole 9a and a second balancer oil drain hole 11a that communicate with the upper end and the lower end, respectively. . That is, the space in the balancer cover 12 and the motor lower space 22 are communicated with each other by the motor / rotor oil drain hole 9a and the second balancer oil drain hole 11a. The number of formed motor / rotor oil drain holes 9a and second balancer oil drain holes 11a and the cross-sectional shape of the flow path will be described below. The other points are basically the same as those of the compressor 100 according to the first embodiment.

Features of the compressor 100a according to the second embodiment will be described.
In the conventional motor / rotor and the second balancer, the refrigerating machine oil 17a accumulated on the top surface of the motor / rotor falls by its own weight, and at the same time, is scattered again by centrifugal force. For this reason, a fluid stirring loss has occurred due to the first balancer. Therefore, in the compressor 100a according to the second embodiment, the motor / rotor oil drain hole 9a and the second balancer oil drain hole 11a are provided to reduce the fluid density in the balancer cover 12. That is, in the compressor 100a, the refrigerating machine oil 17a existing in the space in the balancer cover 12 is returned to the oil sump 17 via the motor / rotor oil discharge hole 9a and the second balancer oil discharge hole 11a, so that the balancer cover 12 The fluid density is reduced.

  Also, as shown in FIG. 4, a plurality of motor / rotor oil drain holes 9a are provided in the circumferential direction on the inner side (crankshaft 3 side) than the inner wall surface (the inner wall surface closest to the crankshaft 3) of the balancer cover 12. It is preferable. If it carries out like this, the flow-path resistance of waste oil can be reduced and the fluid density in the balancer cover 12 can be reduced more efficiently. Although not shown, the number and positions of the second balancer drain holes 11a are also determined according to the number and positions of the motor / rotor drain holes 9a.

  Furthermore, as shown in FIG. 4, when the motor / rotor oil drainage hole 9a is disposed so that the cross-sectional shape of the motor / rotor oil drainage hole 9a is a long hole and the longitudinal part is orthogonal to the crankshaft 3. Good. In this way, the refrigerating machine oil 17a accumulated on the top surface of the motor / rotor 9 is scattered by centrifugal force, but the oil / drainage efficiency can be increased by the motor / rotor oil drain hole 9a, and the balancer cover 12 The fluid density can be further reduced. Although not shown, the cross-sectional shape and arrangement position of the second balancer oil drain hole 11a are also determined according to the cross-sectional shape and arrangement position of the motor / rotor oil drain hole 9a.

  As described above, according to the compressor 100 a according to the second embodiment, the refrigerating machine oil 17 a that has fallen due to its own weight hitting the inner wall surface of the balancer cover 12 and accumulated on the top surface of the motor rotor 9 is stored in the oil reservoir 17. Since the oil discharge path (the motor / rotor oil discharge hole 9a and the second balancer oil discharge hole 11a) is provided, the fluid density in the balancer cover 12 can be efficiently reduced. Therefore, the stirring loss of the fluid due to the rotation of the balancer (particularly the first balancer 10) can be reduced. Therefore, a high-performance compressor 100a can be provided.

  In addition, by providing a plurality of motor / rotor oil drain holes 9a and second balancer oil drain holes 11a, it is possible to reduce flow path resistance when the refrigerating machine oil 17a collected on the top surface of the motor / rotor 9 is drained. The loss of stirring of the fluid due to the rotation of the balancer can be further reduced. Further, by making the cross-sectional shape of the motor / rotor oil drain hole 9a and the second balancer oil drain hole 11a into a long hole shape, the refrigerating machine oil 17a accumulated on the top surface of the motor / rotor 9 is scattered by the centrifugal force. As a result, the oil drainage efficiency can be increased, and the agitation loss of the fluid due to the rotation of the balancer can be further reduced.

  You may make it combine the characteristic matter of the compressor 100 which concerns on Embodiment 1 with the characteristic matter of the compressor 100a which concerns on Embodiment 2. FIG.

  2a oscillating scroll / bearing sliding part, 2b oscillating scroll / thrust sliding part, 3 crankshaft, 3a eccentric hole, 3b crankshaft / frame bearing sliding part, 3d eccentric pin part, 4 compression chamber, 5 frame, 5a Suction port, 5b Oil drain hole, 6 Oldham coupling, 7 Frame oil drain pipe, 8 Oil drain pipe fixing plate, 9 Motor rotor, 9a Motor rotor oil drain hole, 10 1st balancer, 11 2nd balancer, 11a 2nd Balancer oil drain hole, 12 Balancer cover, 12a Balancer cover oil drain hole, 12b Flange part, 13 Motor stator, 13a Upper coil end, 13b Lower coil end, 14 Shell, 15 Suction pipe, 16 Discharge pipe, 17 Oil sump, 17a Refrigeration machine oil, 18 Oil pump, 19 Second frame, 20 Bearing, 2 1 motor upper space, 22 motor lower space, 30 balancer cover oil drain pipe, 40 fixed scroll, 41 end plate, 42 wrap, 43 discharge port, 50 swing scroll, 51 end plate, 52 wrap, 53 high pressure space, 60 compression unit, 70 Drive unit, 100 compressor, 100a compressor.

Claims (3)

Shell,
A motor stator fixedly supported in the shell;
A motor rotor which is rotatably arranged on the inner peripheral surface side of the motor stator and constitutes a motor together with the motor stator;
A crankshaft inserted into the center of the motor rotor and driven to rotate together with the motor rotor;
A compression unit that compresses the fluid sucked into the shell by rotation of the crankshaft;
A first balancer attached to the crankshaft and rotating together with the crankshaft;
The outer peripheral edge portion is bent downward to form a flange portion, a balancer cover oil drain hole is formed through a part of the flange portion, and the lower end of the flange portion is an upper portion of the winding wound around the motor / stator A balancer cover arranged to be positioned below the upper end of the coil end so as to cover the rotation locus of the first balancer from above;
A compressor comprising: a balancer cover oil exhaust pipe that is attached to the balancer cover oil exhaust hole and communicates a space in the balancer cover with a lower space of the motor. Shell,
A motor stator fixedly supported in the shell;
A motor rotor which is rotatably arranged on the inner peripheral surface side of the motor stator and constitutes a motor together with the motor stator;
A crankshaft inserted into the center of the motor rotor and driven to rotate together with the motor rotor;
A compression unit that compresses the fluid sucked into the shell by rotation of the crankshaft;
A first balancer attached to the crankshaft and rotating together with the crankshaft;
A second balancer attached to the bottom of the motor rotor and rotating with the motor rotor;
The outer peripheral edge portion is bent downward to form a flange portion, and the lower end of the flange portion is disposed so as to be located below the upper end of the upper coil end of the winding wound around the motor stator, A balancer cover configured to cover the rotation locus part of the balancer from above,
The motor rotor is formed with at least one motor rotor oil drain hole penetrating in the axial direction,
The compressor characterized in that at least one second balancer oil drain hole communicating with the motor / rotor oil drain hole is formed through the second balancer in the axial direction. A balancer cover oil drainage hole is formed through a part of the flange portion of the balancer cover, and is attached to the balancer cover oil drainage hole so as to communicate the space in the balancer cover and the lower space of the motor. The compressor according to claim 2, wherein an oil pipe is provided.

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