JP2016205186A - Motor compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce an amount of refrigeration oil flowing out to the outside of a closed container.SOLUTION: A motor compressor includes: an electric motor 2 comprising a stator 21 and a rotor 22; a compression mechanism part 3 rotatably driven by the electric motor; a closed container 4 housing the electric motor and the compression mechanism part thereinside; and a cover 71 arranged in the vicinity of one end in an axial direction of the stator. The cover includes an opposite part facing the one end of the stator. The opposite part is formed into a substantially circular shape with the rotational axis of the rotor as a center, and includes a large hole 72 larger than the outer diameter of the rotor.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an electric compressor used in a refrigeration and air conditioning apparatus such as a refrigerator-freezer or an air conditioner.

  The hermetic type electric compressor is compact and has a simple structure, and thus is often used in refrigeration and air conditioning equipment such as a refrigerator and an air conditioner. Here, description will be made assuming that the hermetic electric compressor is configured as a vertical rotary compressor.

  The electric compressor has an electric motor composed of a stator and a rotor, and a compression mechanism portion driven by the electric motor, inside the sealed container. The compression mechanism unit is a mechanism that compresses the working fluid and supplies it to the refrigeration cycle of the refrigeration air conditioner provided outside the sealed container.

  Inside the closed container, an upper space and a lower space are provided on the upper side and the lower side of the electric motor. An oil sump for storing refrigeration oil is provided at the bottom of the sealed container. The refrigerating machine oil is supplied to the compression mechanism unit, lubricates the sliding surface of the compression mechanism unit, and seals the gap in the compression mechanism unit. A part of the refrigerating machine oil is mixed into the working fluid by being supplied to the compression mechanism. The working fluid is compressed by the compression mechanism in a state including fine particles of the refrigeration oil (hereinafter simply referred to as “oil”), and is ejected to the lower space.

  The working fluid ejected to the lower space collides with the lower end surface of the rotor. After that, the flow of the working fluid becomes a strong swirling flow due to the influence of the rotational movement of the rotor. Part of the oil contained in the working fluid falls under its own weight while the working fluid stays in the lower space, or the inner wall of the sealed container or the like due to the centrifugal force associated with the swirling flow of the working fluid. When it adheres to the lower coil end or the like of the stator, it becomes oil droplets that fall along the inner wall of the sealed container, the wall surface of the stator, or the like due to its own weight. As a result, part of the oil separates from the working fluid and returns to the oil sump. However, at this time, oil remains in the working fluid. In particular, inside the sealed container, the working fluid is agitated by the swirling flow of the working fluid due to the rotational movement of the rotor, whereby the oil contained in the working fluid is refined to form a mist-like oil. Is likely to occur. A mist-like oil is light in weight per unit volume. Therefore, it is difficult for the electric compressor to completely separate the mist-like oil from the working fluid only by using the centrifugal force accompanying the swirling flow of the working fluid or the weight of the oil. As a result, oil (particularly, mist-like oil) remains in the working fluid. In this state, the working fluid is ejected from the lower space to the upper space.

  The phenomenon that mist-like oil is generated occurs when the working fluid passes near the end face of the rotor. Therefore, the phenomenon of mist-like oil occurs in all types of hermetic electric compressors, regardless of the type of vertical or horizontal type, or the compression method of a rotary compressor or scroll compressor. To do.

  The working fluid ejected into the upper space is directed to the discharge pipe provided in the upper part of the sealed container. At that time, the working fluid passes in the vicinity of the upper end surface of the rotor. At this time, a part of the flow of the working fluid becomes a swirling flow due to the influence of the rotational motion of the rotor. Part of the oil contained in the working fluid falls under its own weight while the working fluid stays in the upper space, or is fixed to the inner wall of the sealed container by the centrifugal force accompanying the swirling flow of the working fluid. When it adheres to the upper coil end or the like of the child, it becomes oil droplets and falls down by its own weight along the inner wall of the sealed container or the wall surface of the stator. As a result, part of the oil separates from the working fluid and returns to the oil sump. However, at this time, oil still remains in the working fluid. In this state, the working fluid is discharged from the sealed container to the refrigeration cycle via the discharge pipe.

  When the discharge amount of the refrigerating machine oil discharged into the refrigerating cycle (that is, the amount of refrigerating machine oil flowing out of the sealed container) is large, the oil level of the refrigerating machine oil stored in the oil sump decreases. As a result, the amount of refrigerating machine oil supplied to the compression mechanism portion becomes insufficient, and the compression mechanism portion becomes insufficiently lubricated or the gap in the compression mechanism portion is insufficiently sealed. Therefore, the operating efficiency of the electric compressor is reduced.

  In addition, when the discharge amount of refrigerating machine oil discharged into the refrigerating cycle (that is, the amount of refrigerating machine oil flowing out of the sealed container) is large, the refrigerating machine oil adheres to the inner wall of the heat transfer tube of the heat exchanger, The heat transfer coefficient between the working fluid and the wall surface in the heat transfer tube is reduced. Therefore, the operating efficiency of the refrigeration cycle is reduced.

  Therefore, some electric compressors have a configuration in which the main flow field of the working fluid is isolated from the end face of the rotor (see, for example, FIGS. 1, 4, and 5 of Patent Document 1). For example, the electric compressor described in FIG. 1 of Patent Document 1 has a configuration in which a shielding member is disposed on the lower end surface of the stator. Moreover, the electric compressor described in FIG. 4 of Patent Document 1 has a configuration in which a shielding member is disposed in the vicinity of the tip of the protruding portion of the main bearing. Moreover, the electric compressor described in FIG. 5 of Patent Document 1 has a configuration in which a shielding member is fixed to the inner wall of the hermetic container.

  The conventional electric compressor described in Patent Document 1 isolates the main flow field of the working fluid from the end face of the rotor, so that the working fluid is swirled by the working fluid due to the rotational motion of the rotor. It is suppressed that the working fluid is agitated by agitation or rotation of irregularities such as a balancer provided on the end face of the rotor. Such a conventional electric compressor suppresses the generation of mist oil by suppressing the working fluid from being agitated.

JP 2006-336463 A (FIGS. 1, 4, and 5)

  However, the conventional electric compressor described in Patent Document 1 can reduce the amount of refrigerating machine oil flowing out of the sealed container, but it is desired to realize the reduction more effectively. There was a problem.

  The conventional electric compressor described in Patent Document 1 can suppress the working fluid from being agitated by a swirling flow caused by unevenness such as a balancer. However, the conventional electric compressor described in Patent Document 1 suppresses that the working fluid is agitated by a strong jet of the working fluid that has been compressed by the compression mechanism and jetted into the lower space of the electric motor. I can't. Therefore, the conventional electric compressor may generate mist-like oil due to a strong working fluid jet.

  Therefore, the conventional electric compressor still has a large amount of refrigerating machine oil discharged into the refrigerating cycle (that is, the amount of refrigerating machine oil flowing out of the sealed container). Therefore, in the conventional electric compressor, there is a possibility that the heat transfer coefficient between the working fluid and the wall surface in the heat transfer tube is lowered due to the refrigeration oil adhering to the inner wall of the heat transfer tube of the heat exchanger. Thereby, the operating efficiency of the refrigeration cycle may be reduced.

  The present invention has been made to solve the above-described problems, and has as its main object to provide an electric compressor that reduces the amount of refrigerating machine oil that flows out of the hermetic container.

In order to achieve the above object, the present invention provides an electric compressor comprising an electric motor including a stator and a rotor, a compression mechanism portion that is rotationally driven by the electric motor, and the electric motor and the compression mechanism portion. And a cover disposed in the vicinity of one end in the axial direction of the stator, and the cover includes a facing portion that faces one end of the stator, and the facing portion includes: The rotor is formed in a substantially circular shape around the rotation axis of the rotor, and has a hole larger than the outer diameter of the rotor.
Other means will be described later.

  The electric compressor suppresses the axial flow (jet flow) of the working fluid by the cover, and separates the working fluid that has flowed near the one end of the stator from the opposed portion through the hole from the one end of the stator. Flow in the direction. Thereby, this electric compressor can suppress that the oil contained in the working fluid is atomized by the flow (jet flow) of the working fluid in the axial direction and the oil contained in the working fluid. Therefore, this electric compressor can reduce the amount of refrigerating machine oil that flows out of the sealed container.

  According to the present invention, it is possible to reduce the amount of refrigerating machine oil that flows out of the sealed container.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view showing the overall configuration of an electric compressor according to a first embodiment. It is sectional drawing which shows the structure of the principal part of the electric compressor which concerns on Embodiment 1. FIG. It is sectional drawing which shows the structure of the principal part of the electric compressor which concerns on Embodiment 1. FIG. FIG. 3 is a perspective view illustrating a configuration of a cover used in the first embodiment. It is sectional drawing which shows the structure of the principal part of the electric compressor which concerns on Embodiment 2. FIG. It is explanatory drawing of the principal part of the electric compressor which concerns on Embodiment 2. FIG. It is sectional drawing which shows the structure of the principal part of the electric compressor which concerns on Embodiment 3. FIG. It is sectional drawing which shows the structure of the principal part of the electric compressor which concerns on Embodiment 4. FIG. 9 is a cross-sectional view illustrating a configuration of main parts of an electric compressor according to a fifth embodiment. FIG. 10 is a cross-sectional view illustrating a configuration of main parts of an electric compressor according to a sixth embodiment. FIG. 10 is a perspective view illustrating a configuration of a cover used in Embodiment 6. FIG. 10 is a cross-sectional view illustrating a configuration of main parts of an electric compressor according to a seventh embodiment. FIG. 10 is a perspective view illustrating a configuration of a cover used in Embodiment 7.

  Hereinafter, an embodiment of the present invention (hereinafter referred to as “the present embodiment”) will be described in detail with reference to the drawings. Each figure is only schematically shown so that the present invention can be fully understood. Therefore, the present invention is not limited to the illustrated example. Moreover, in each figure, the same code | symbol is attached | subjected about the common component and the same component, and those overlapping description is abbreviate | omitted.

  In addition, this invention can also solve the following subjects of the conventional electric compressor described in Patent Document 1.

  (1) The refrigerating machine oil is preferably returned to the oil sump by staying in the lower space as much as possible and separating it from the working fluid in the lower space. However, in the conventional electric compressor described in FIG. 1 and FIG. 4 of Patent Document 1, the working fluid is agitated by a strong jet of the working fluid compressed by the compression mechanism and ejected into the lower space. Can not be suppressed.

  Therefore, in the conventional electric compressor described in FIG. 1 and FIG. 4 of Patent Document 1, the working fluid containing a relatively large amount of oil is moved from the lower space to the upper space without much separation of the oil from the working fluid. There was a possibility of eruption. As a result, a relatively large amount of refrigerating machine oil may flow out from the lower space to the upper space.

  (2) Further, in the conventional electric compressor described in FIG. 1 and FIG. 4 of Patent Document 1, the fine oil adhering to the lower coil end of the stator is compressed by the compression mechanism section and is located in the lower space. When exposed to a flow field of a strong jet of working fluid ejected on the stator, there is a possibility of peeling from the lower coil end of the stator. Thereby, the mist-like oil may generate | occur | produce.

  (3) Moreover, the conventional electric compressor described in FIG. 5 of Patent Document 1 includes a strong jet of working fluid compressed by the compression mechanism and jetted into the lower space, a lower coil end of the stator, Can be isolated. However, in the conventional electric compressor described in FIG. 5 of Patent Document 1, the lower end surface of the rotor cannot be isolated from the lower coil end of the stator. Moreover, in the conventional electric compressor described in FIG. 5 of Patent Document 1, a strong swirl flow is generated in a small space formed by the lower end surface of the rotor and the shielding member. Therefore, the fine oil adhering to the lower coil end of the stator may be separated from the lower coil end of the stator by being exposed to a strong swirl flow field. Thereby, the mist-like oil may generate | occur | produce.

  (4) Moreover, in the conventional electric compressor described in FIG. 5 of Patent Document 1, a shielding member is provided over a wide range between the discharge port of the compression mechanism inside the sealed container and the lower coil end of the stator. Place. Therefore, the working fluid compressed by the compression mechanism and ejected to the lower space hits the shielding member. As a result, the flow of the working fluid may be stagnated or hindered. As a result, the pressure loss may increase.

(5) Moreover, the conventional electric compressor described in FIG. 1 and FIG. 5 of Patent Document 1 has a configuration in which it is difficult to dispose the rotor after disposing the shielding member. Therefore, the conventional electric compressor described in FIG. 1 and FIG. 5 of Patent Document 1 may increase cost, labor, and time during manufacturing.
The present invention can also solve the above problems.

[Embodiment 1]
<Configuration of electric compressor>
Hereinafter, the configuration of the electric compressor 1 according to the first embodiment will be described with reference to FIGS. Here, the case where the electric compressor 1 is a single cylinder vertical rotary compressor will be described.

  FIG. 1 is a longitudinal sectional view showing the overall configuration of the electric compressor 1. 2 and 3 are cross-sectional views showing the configuration of the main part of the electric compressor 1, respectively. FIG. 2 shows a configuration of the electric compressor 1 before a cover 71 described later is attached. FIG. 3 shows a configuration of the electric compressor 1 after a cover 71 described later is attached. FIG. 4 is a perspective view showing the configuration of the cover 71. FIG. 2A and FIG. 3A show the configuration of the longitudinal section of the electric compressor 1. 2 (b) and 3 (b) show the configuration of the cut surface obtained by cutting the electric compressor 1 along the line AA shown in FIG. 2 (a) or FIG. 3 (a). (The same applies to other drawings). Each drawing simplifies and shows only parts necessary for the description of the electric compressor 1 according to the first embodiment.

As shown in FIG. 1, the electric compressor 1 according to the first embodiment includes a sealed container 4 and an accumulator 5.
The sealed container 4 is a container that houses the electric motor 2 and the compression mechanism unit 3.
The accumulator 5 is a container that stores refrigerant gas that functions as a working fluid in a pressurized state.

  The sealed container 4 includes a cylinder body 41, a lid body 42, and a bottom body 43. The cylinder 41 is a cylindrical casing made of a steel plate and opened at the top and bottom. The sealed container 4 has a lid 42 fitted into the upper portion of the cylindrical body 41, a bottom body 43 fitted into the lower portion of the cylindrical body 41, and each fitting portion is welded so that the inside thereof is sealed. It has been configured.

  The electric motor 2 is a drive source that drives the compression mechanism unit 3. The electric motor 2 includes a stator 21 fixed to the sealed container 4 by shrink fitting or the like, and a rotor 22 fitted with a crankshaft 31 of the compression mechanism unit 3. The stator 21 includes an upper coil end protruding from the upper end surface and a lower coil end protruding from the lower end surface.

A gap 26 (see FIG. 2B) is provided between each tooth of the stator 21. Further, on the outer peripheral side of the stator 21, a space 46 (hereinafter referred to as “lower space”) provided on the lower side of the motor 2 and a space provided on the upper side of the motor 2 (hereinafter referred to as “upper space”). A plurality of outer peripheral grooves 27 (refer to FIG. 2B) are provided to communicate with each other. The gap 26 and the outer circumferential groove 27 function as a working fluid flow path.
The inner diameter of the core of the stator 21 is set to a value that is several millimeters larger than the outer diameter (diameter) of the rotor core. Therefore, a gap (not shown) of about several mm is provided between the stator 21 and the rotor 22.
The core of the rotor 22 is provided with a through hole (not shown) for expanding the communication area between the lower space 46 and the upper space 47.

  The compression mechanism unit 3 is a mechanism that compresses the working fluid with the rotational movement of the rotor 22 of the electric motor 2 and supplies the compressed working fluid to the refrigeration cycle of the refrigeration air-conditioning equipment. The compression mechanism unit 3 includes a main crankshaft 31, a main bearing 32, a cylinder 33, a sub bearing 34, a roller 35, and a vane 36.

  The crankshaft 31 is a member that drives the vane 36 inside the cylinder 33. The crankshaft 31 includes an eccentric portion 31a on the lower end side. The crankshaft 31 is rotatably supported inside the sealed container 4 by fitting the upper side of the eccentric part 31a into the main bearing 32 and fitting the lower side of the eccentric part 31a into the auxiliary bearing 34.

  The eccentric part 31 a of the crankshaft 31 is rotatably fitted inside the roller 35. The roller 35 is rotatably fitted in the vane 36 so that the outer periphery thereof abuts the vane 36. The vane 36 is fitted into the cylinder 33 so as to slide inside the cylinder 33.

  Inside the cylinder 33, a suction chamber (not shown) for sucking the working fluid and a compression chamber 44 for compressing the working fluid are formed. The compression chamber 44 is formed by the inner wall surface of the cylinder 33, the outer wall surface of the roller 35, the side surface of the vane 36, the inner wall surface of the main bearing 32, and the inner wall surface of the auxiliary bearing 34.

  The cylinder 33 is fastened to the main bearing 32 by bolts. The main bearing 32 closes the upper end surface of the cylinder 33 and holds the crankshaft 31. The main bearing 32 is provided with a digging portion. A discharge port 45 is provided inside the dug portion. The discharge port 45 is an opening for discharging the working fluid from the cylinder 33 to the lower space 46.

  The main bearing 32 includes a discharge valve 61 that selectively opens or closes the discharge port 45, and a retainer 62 that determines the opening degree of the discharge valve 61. The discharge valve 61 opens the discharge port 45 when the gas pressure Pd1 inside the lower space 46 and the gas pressure Pd2 inside the compression chamber 44 have a relationship of Pd2 ≧ Pd1. As a result, the discharge valve 61 ejects the high-pressure gas (working fluid) inside the compression chamber 44 into the lower space 46. Further, the discharge valve 61 closes the discharge port 45 at other times. Accordingly, the discharge valve 61 prevents the high-pressure gas (working fluid) inside the lower space 46 from flowing back into the compression chamber 44. The discharge valve 61 and the retainer 62 are covered with a cup muffler 63. The cup muffler 63 functions as a silencer. The cup muffler 63 is provided with a discharge port 63a (see FIG. 2A) for discharging the working fluid that has passed through the discharge port 45 to the lower space 46.

  The auxiliary bearing 34 is fastened to the cylinder 33 by bolts. The auxiliary bearing 34 closes the lower end surface of the cylinder 33 and holds the crankshaft 31. The compression mechanism 3 is fixed inside the sealed container 4 by fixing the main bearing 32 to the cylinder 41 by welding or the like.

  A discharge pipe 37 that discharges the working fluid from the sealed container 4 to the refrigeration cycle is provided on the top of the sealed container 4. Further, an accumulator 5 and a suction pipe 56 that guides the working fluid from the refrigeration cycle to the compression mechanism unit 3 through the accumulator 5 are provided on the side surface of the sealed container 4. An oil sump 43a for storing refrigerating machine oil is provided on the upper surface of the bottom body 43 that constitutes the bottom of the sealed container 4. The refrigerating machine oil is supplied to the compression mechanism unit 3 to lubricate the sliding surface of the compression mechanism unit 3 and seal the gap of the compression mechanism unit 3.

  A cover 71 is provided below the stator 21 inside the sealed container 4. The cover 71 suppresses the oil from being atomized by suppressing the flow of the working fluid toward the teeth of the stator 21. The principle will be described in the “Main Features of Electric Compressor” section below.

  As shown in FIG. 4, the cover 71 includes a bottom surface portion 73 that faces the lower end of the stator 21. The “lower end of the stator 21” corresponds to “one end of the stator” recited in the claims. The “bottom surface portion 73” corresponds to a “facing portion” recited in the claims. The bottom portion 73 causes the working fluid that has flowed above the bottom portion 73 (that is, near one end of the stator 21) to flow downward (that is, in a direction away from one end of the stator 21) (FIG. 3 ( A flow hole 72 is formed for the purpose of the arrow fl3 shown in a).

  The flow hole 72 is formed in a substantially circular shape around the rotation axis of the rotor 22. The inner diameter of the flow hole 72 is set to a value larger than the outer diameter (diameter) of the rotor 22.

The cover 71 includes an inner wall surface portion 74 formed along the edge of the flow hole 72 so as to protrude from the bottom surface portion 73 toward the lower side of the stator 21.
In addition, the cover 71 includes an outer wall surface portion 75 formed along the outer peripheral edge of the bottom surface portion 73 so as to protrude from the bottom surface portion 73 toward the lower side of the stator 21.
In the first embodiment, the height of the outer wall surface portion 75 is set to a value higher than the height of the inner wall surface portion 74.

  The cover 71 can be separated between the discharge port 45 of the compression mechanism unit 3 and the lower coil end of the stator 21 and between the lower coil end of the stator 21 and the lower end surface of the rotor 22. Is arranged. Further, the cover 71 has a relatively small configuration from the viewpoint of productivity at the time of manufacturing, labor, time, and the like.

<Operation of electric compressor>
Hereinafter, the operation of the electric compressor 1 will be mainly described with reference to FIGS. 1 and 3. The arrows shown in FIGS. 1 and 3 indicate the flow path of the working fluid.

  The electric compressor 1 rotates the rotor 22 by energizing the stator 21 in the course of operation. Then, the roller 35 performs an eccentric rotational movement by the eccentric portion 31 a of the crankshaft 31, and accordingly, the vane 36 slides inside the cylinder 33. Thereby, the volume of the suction chamber (not shown) of the cylinder 33 and the compression chamber 44 changes.

  At this time, the working fluid is sucked into the suction chamber (not shown) from the accumulator 5 through the suction pipe 56 and compressed in the compression chamber 44. At this time, the oil supplied from the oil reservoir 43a to the compression mechanism unit 3 is mixed into the working fluid. The compressed working fluid is jetted into the lower space 46 through the discharge port 45 provided in the main bearing 32 in a state containing oil. The flow of the working fluid at this time is a substantially vertical strong jet fl1 (see FIGS. 2A and 3A) that goes from the discharge port 45 to the lower space 46. At this time, the cover 71 suppresses the flow of the working fluid jet fl1 toward the lower portion of the stator 21. Thereby, the electric compressor 1 can suppress that the oil contained in the working fluid is atomized.

  The working fluid ejected to the lower space 46 collides with the lower end surface of the rotor 22. Thereafter, the flow of the working fluid becomes a strong swirl flow fl2 (see FIGS. 2A and 3A) due to the influence of the rotational motion of the rotor 22. A part of the oil contained in the working fluid falls by its own weight while the working fluid stays in the lower space 46 or by the centrifugal force accompanying the swirling flow fl2 of the working fluid. The oil droplets are attached to the inner wall of the casing 21 and the lower coil end of the stator 21 and fall along the inner wall of the hermetic container 4 and the wall surface of the stator 21. As a result, part of the oil is separated from the working fluid and returned to the oil sump 43a.

  At this time, oil remains in the working fluid. However, since the oil is suppressed from being atomized by the cover 71, the oil is efficiently separated from the working fluid. As a result, the amount of oil contained in the working fluid is less than that of a conventional electric compressor. In this state, the working fluid has an outer circumferential groove 27 (see FIG. 2B) provided between the stator 21 and the hermetic container 4, and a gap provided between each tooth of the stator 21. 26 (see FIG. 2B), through a gap (not shown) provided between the stator 21 and the rotor 22, and a through hole (not shown) provided in the core of the rotor 22. , And ejected from the lower space 46 to the upper space 47.

  The working fluid ejected into the upper space 47 travels to the discharge pipe 37 provided at the upper part of the sealed container 4. At that time, the working fluid passes near the upper end surface of the rotor 22. At this time, a part of the flow of the working fluid becomes a swirling flow due to the influence of the rotational motion of the rotor 22. Part of the oil contained in the working fluid falls under its own weight while the working fluid stays in the upper space 47 or the inner wall of the sealed container 4 due to centrifugal force accompanying the swirling flow of the working fluid. Or oil droplets by adhering to the upper coil end or the like of the stator 21, and it drops by its own weight along the inner wall of the sealed container 4 or the wall surface of the stator 21. As a result, part of the oil is separated from the working fluid and returned to the oil sump 43a.

  At this time, oil may remain in the working fluid, but the amount thereof is smaller than that of the conventional electric compressor. In this state, the working fluid is discharged from the sealed container 4 to the refrigeration cycle via the discharge pipe 37.

<Main features of electric compressor>
The electric compressor 1 according to the first embodiment has the following characteristics.
(1) The electric compressor 1 has a cover 71 disposed in the vicinity of the lower portion of the stator 21 of the electric motor 2. The “lower part of the stator 21” corresponds to “one end of the stator 21 in the axial direction” recited in the claims. The cover 71 is a member that suppresses the flow of the working fluid toward the teeth of the stator 21. “The flow of the working fluid toward the teeth of the stator 21” corresponds to “the axial flow of the working fluid toward the one end of the stator” recited in the claims.

  The cover 71 suppresses the oil from being atomized by suppressing the flow of the working fluid toward the teeth of the stator 21. The principle is as follows. Here, the configuration in which the cover 71 shown in FIG. 2A is not attached is taken as a comparative example, and the comparative example and the configuration of the electric compressor 1 according to the first embodiment in which the cover 71 is attached (FIG. 3). The principle will be described in comparison with (a).

  In the electric compressor 1, only the working fluid is provided between an outer peripheral groove 27 (see FIG. 2B) provided between the stator 21 and the sealed container 4, and between each tooth of the stator 21. In the gap 26 (see FIG. 2B), a gap (not shown) provided between the stator 21 and the rotor 22, and a through hole (not shown) provided in the core of the rotor 22. It is ideal to reach the upper space 47 from the lower space 46 through.

  However, in the comparative example in which the cover 71 is not attached (see FIG. 2A), a strong jet fl1 from the discharge port 45 toward the lower space 46 is generated in the lower space 46, and the lower part of the rotor 22. A strong swirling flow fl2 is generated from the axial center to the outside due to unevenness such as a balancer provided on the end face. Therefore, in the comparative example, the working fluid is agitated in the lower space 46, and as a result, it is difficult to drop the oil. Further, in the comparative example, the oil adhering to the inner wall of the hermetic container 4 and the fine oil adhering to the lower coil end of the stator 21 are flowed by the strong jet flow fl1 and the strong swirling flow fl2, thereby forming a mist-like shape. Generate oil. The oil adhering to the inner wall of the hermetic container 4 and the lower coil end of the stator 21 is caused by the working fluid discharged from the compression chamber 44 and the working fluid flowing from the upper space 47 to the lower space 46. . In particular, when the outer diameter of the winding is relatively small, the mist-like oil is likely to be generated because the fine oil adhering to the lower coil end of the stator 21 becomes finer. A mist-like oil is generated on this principle.

  A mist-like oil is light in weight per unit volume. Therefore, in the comparative example, it is difficult to completely separate the mist-like oil from the working fluid only by using the centrifugal force accompanying the swirling flow of the working fluid or the weight of the oil. As a result, in the comparative example, the oil cannot be separated from the working fluid so much in the lower space 46, and the oil remains in the working fluid.

  The oil remaining in the working fluid mainly passes through the gaps 26 (see FIG. 2B) provided between the teeth of the stator 21 by the strong jet flow fl1 and the strong swirling flow fl2. Thus, the upper space 47 is reached.

  The oil that has reached the upper space 47 is further agitated by a swirling flow caused by unevenness such as a balancer provided on the upper end surface of the rotor 22 and a flow from the lower space 46 toward the upper space 47. There is no positive oil separation mechanism in the upper space 47.

  Therefore, in the comparative example, in order to perform oil separation, a relatively wide space is secured as the upper space 47, the distance from the rotor 22 to the discharge pipe 37 is set large, and the oil residence time in the upper space 47 It is necessary to drop the oil by its own weight and return the oil to the lower space 46 by extending the period of time. However, this causes the adverse effect that the comparative example increases the size of the apparatus.

Moreover, even if the comparative example is configured in this way, it is difficult to return the oil to the lower space 46 for the following reason.
That is, in the upper space 47, the swirling flow of the working fluid is generated by the rotation of the rotor 22, such that the unevenness such as the balancer provided on the upper end surface of the rotor 22 rotates. The working fluid flows from the lower space 46 into the upper space 47. Therefore, in the comparative example, the working fluid is agitated by the swirling flow of the working fluid and the flow of the working fluid from the lower space 46 toward the upper space 47, and the oil is agitated accordingly. As a result, in the upper space 47, it becomes difficult for oil to fall, or the oil becomes finer and mist-like oil is generated. Therefore, in the comparative example, it is difficult to return the oil to the lower space 46.

  In contrast, the electric compressor 1 according to the first embodiment includes a cover 71 that suppresses the flow of the working fluid toward the teeth of the stator 21 below the stator 21. Therefore, the electric compressor 1 suppresses the oil from flowing into the gaps 26 (see FIG. 2B) provided between the teeth of the stator 21 and the lower side of the stator 21. It can suppress that the oil adhering to a coil end peels and mist-like oil generate | occur | produces.

  Further, the electric compressor 1 shields the oil ejected from the discharge port 45 with the bottom surface portion 73 of the cover 71 and attaches it to the bottom surface portion 73, thereby making the oil into oil droplets, and the lower space 46 with its own weight. And the oil can be returned to the lower space 46.

  Further, the electric compressor 1 can cause the oil staying in the lower space 46 to flow to the outer peripheral side of the stator 21 along the bottom surface portion 73 of the cover 71. Therefore, the electric compressor 1 can prolong the residence time of oil in the lower space 46, and as a result, the oil can be efficiently dropped by its own weight and returned to the lower space 46. it can.

  Such an electric compressor 1 can separate oil from the working fluid with high efficiency in the lower space 46. Therefore, the electric compressor 1 can reduce the amount of oil contained in the working fluid flowing from the lower space 46 to the upper space 47. As a result, the discharge amount of the refrigerating machine oil discharged to the refrigeration cycle That is, the amount of refrigerating machine oil flowing out of the sealed container can be reduced.

  (2) In the first embodiment, the cover 71 includes an inner wall surface 74 and an outer wall surface 75. The inner wall surface 74 and the outer wall surface 75 can obtain the following effects.

First, the effect of the inner wall surface 74 will be described.
The discharge port 45 of the compression mechanism unit 3 is provided near the lower end surface of the rotor 22. Therefore, after the working fluid is discharged near the lower end surface of the rotor 22, the working fluid is affected by a strong swirling flow due to unevenness such as a balancer provided on the lower end surface of the rotor 22. As a result, the oil flows to the outer peripheral side of the stator 21. At this time, the inner wall surface 74 of the cover 71 suppresses the oil that has flowed to the outer peripheral side from flowing into the gaps 26 (see FIG. 2B) provided between the teeth of the stator 21. To do. Therefore, the cover 71 can reduce the amount of oil flowing into the gap 26 (see FIG. 2B).

  Note that the height of the inner wall surface 74 can be made higher than in the illustrated example. For example, the height of the inner wall surface portion 74 can be made high enough to completely shield the inner wall side of the stator 21 except for mounting holes (not shown).

  In this case, the electric compressor 1 more effectively increases the inflow amount of oil flowing into the gaps 26 (see FIG. 2B) provided between the teeth of the stator 21. Can be reduced. In addition, the electric compressor 1 significantly reduces the amount of oil flowing into the gap 26 (see FIG. 2B), thereby reducing the flow of the working fluid in the gap 26 from the flow toward the upper space 47. It is possible to positively change the flow toward the lower space 46. Therefore, the electric compressor 1 can return the oil staying in the upper space 47 to the lower space 46 with high efficiency. Also by this, the electric compressor 1 can reduce the discharge amount of the refrigerating machine oil discharged into the refrigerating cycle (that is, the amount of refrigerating machine oil flowing out of the sealed container).

Next, the effect of the outer wall surface 75 will be described.
The outer wall surface portion 75 can rectify the flow of the working fluid flowing into the outer circumferential groove 27 (see FIG. 2B). Thereby, the electric compressor 1 can reduce pressure loss. Therefore, the electric compressor 1 can improve the supply performance of the working fluid to the refrigeration cycle.

  (3) The cover 71 can function as a winding presser that presses down the lower end portion 25a of the winding of the stator 21 (see FIG. 3A). Thereby, the electric compressor 1 does not need to use a dedicated member for pressing the lower end portion 25a of the winding of the stator 21. Therefore, the electric compressor 1 can reduce the number of parts.

(4) The flow hole 72 is formed in a substantially circular shape around the rotation axis of the rotor 22. The inner diameter of the flow hole 72 is set to a value larger than the outer diameter (diameter) of the rotor 22. Therefore, the electric compressor 1 can easily arrange the rotor 22 inside the stator 21 through the flow holes 72 of the cover 71 after attaching the stator 21 and the cover 71 to the sealed container 4. it can. Such an electric compressor 1 can be easily manufactured.
Further, the flow hole 72 can cause the working fluid that has flowed upward from the bottom surface portion 73 to flow downward (see the arrow fl3 shown in FIG. 3A).

  Such an electric compressor 1 can suppress generation of mist-like oil inside the sealed container 4. Moreover, the electric compressor 1 can promote the separation of the oil from the working fluid, and can reduce the refrigeration oil flowing out of the sealed container 4 with high efficiency. In addition, the electric compressor 1 can improve the heat exchange efficiency of the refrigeration cycle, reduce pressure loss, or hold a necessary amount of refrigeration oil inside the sealed container 4. As a result, the electric compressor 1 can improve performance and reliability.

  As described above, according to the electric compressor 1 according to the first embodiment, the amount of refrigerating machine oil flowing out of the sealed container 4 can be reduced.

[Embodiment 2]
Hereinafter, the configuration of the electric compressor 1 </ b> A according to the second embodiment will be described with reference to FIGS. 5 and 6. FIG. 5 is a cross-sectional view showing a configuration of a main part of the electric compressor 1A. FIG. 6 is an explanatory diagram of a main part of the electric compressor 1A. FIG. 6A shows an enlarged region B shown in FIG. FIG. 6B shows the relationship between the inner wall surface 74a of the cover 71A used in the second embodiment and its surroundings.

  As shown in FIGS. 5 and 6, the electric compressor 1 </ b> A according to the second embodiment uses a cover 71 </ b> A instead of the cover 71 as compared with the electric compressor 1 according to the first embodiment (see FIG. 3). It is different in point.

The cover 71A is a member having a shape in which the upper end of the inner wall surface portion 74a is notched.
The electric compressor 1A has the following configuration.
As shown in FIG. 6A, the stator 21 has an auxiliary portion 21b around which no winding is wound. The auxiliary portion 21 b includes an inner wall facing the flow hole 72. An opening 21c is formed between the inner wall surface 74a of the cover 71A and the auxiliary portion 21b.

  The opening amount of the opening 21c is set to a smaller value than the opening between the inner wall surface 74 and the auxiliary portion 21b of the electric compressor 1 according to the first embodiment. The opening amount of the opening portion 21c can be adjusted by using the cover 71A having a different height of the inner wall surface portion 74a according to the operation.

  FIG. 6B shows a configuration in which the inner wall surface 74a of the cover 71A and the inner wall of the auxiliary portion 21b are expanded in plan view in a range of 360 degrees from the axial center. As shown in FIG. 6B, the area S21c of the opening 21c is 20% or less of the total area of the area S74a of the inner wall surface 74a of the cover 71A and the area S21b of the inner wall of the auxiliary portion 21b. That is, the area S21c of the opening 21c, the area S74a of the inner wall surface 74a of the cover 71A, and the area S21b of the inner wall of the auxiliary portion 21b are in a relationship of “S21c ≦ (S74a + S21b) × 20/100”.

  Since the electric compressor 1A uses the cover 71A, the gap 26 (provided between each tooth of the stator 21 from the inner peripheral side of the stator 21 than the electric compressor 1 according to the first embodiment ( The outflow amount of the working fluid flowing in FIG. 2 (b) can be greatly reduced. Therefore, the electric compressor 1 </ b> A can reduce the amount of oil that reaches the upper space 47 from the lower space 46. As a result, the electric compressor 1A is more efficient than the electric compressor 1 according to the first embodiment. The discharge amount of the refrigerating machine oil discharged into the refrigerating cycle (that is, the refrigerating machine oil flowing out of the sealed container 4 is reduced). Amount) can be reduced.

  In addition, the electric compressor 1A can ensure a clearance with a winding auxiliary member (not shown) when the cover 71A is attached. Therefore, the electric compressor 1A can improve productivity.

  The bottom surface 73 of the cover 71A has one or more bottom surface holes 77 (see FIG. 5B) penetrating from the upper surface to the lower surface. The electric compressor 1 </ b> A can return oil existing above the bottom surface portion 73 to the lower space 46 through the bottom surface hole 77. Therefore, depending on the design, the electric compressor 1A is more efficiently discharged than the electric compressor 1 according to the first embodiment. The amount of refrigerating machine oil) can be reduced.

As described above, according to the electric compressor 1A according to the second embodiment, the amount of refrigerating machine oil flowing out of the sealed container 4 can be reduced more efficiently than the electric compressor 1 according to the first embodiment. Can do.
Moreover, according to the electric compressor 1B, productivity can be improved.

[Embodiment 3]
Hereinafter, the configuration of the electric compressor 1B according to the third embodiment will be described with reference to FIG. FIG. 7 is a cross-sectional view showing a configuration of a main part of the electric compressor 1B.

  As illustrated in FIG. 7, the electric compressor 1 </ b> B according to the third embodiment uses a cover 71 </ b> B instead of the cover 71 as compared with the electric compressor 1 according to the first embodiment (see FIG. 3B). It is different in point.

  The cover 71 </ b> B is a member in which one or more bottom surface holes 78 penetrating from the upper surface to the lower surface are formed in the bottom surface portion 73. The diameter of the bottom surface hole 78 is set to a value smaller than the diameter of the bottom surface hole 77 of the second embodiment. And the total area of the area of the bottom face part hole 78 is set to the value of 20% or less of the area of the bottom face part 73 of the cover 71B.

  Since the electric compressor 1B uses the cover 71B, the gap 26 provided between each tooth of the stator 21 from the inner peripheral side of the stator 21 is the same as the electric compressor 1 according to the first embodiment. The amount of oil flowing in can be reduced. Therefore, the electric compressor 1 </ b> B can reduce the amount of oil that reaches the upper space 47 from the lower space 46. As a result, the electric compressor 1B can reduce the discharge amount of the refrigerating machine oil discharged into the refrigerating cycle (that is, the amount of refrigerating machine oil flowing out of the sealed container 4).

  Moreover, the electric compressor 1B can return the oil which exists above the bottom face part 73 to the lower space 46 through the bottom face hole 78 similarly to the electric compressor 1A according to the second embodiment. Therefore, depending on the design, the electric compressor 1B flows out of the closed container 4 out of the discharge amount of the refrigeration oil discharged into the refrigeration cycle with higher efficiency than the electric compressor 1 according to the first embodiment. The amount of refrigerating machine oil) can be reduced.

As described above, according to the electric compressor 1 </ b> B according to the third embodiment, the amount of refrigerating machine oil flowing out of the sealed container 4 can be reduced in the same manner as the electric compressor 1 according to the first embodiment.
Moreover, according to the electric compressor 1B, the amount of refrigerating machine oil that flows out of the sealed container 4 can be reduced with higher efficiency than the electric compressor 1 according to the first embodiment, depending on the design.

[Embodiment 4]
Hereinafter, the configuration of the electric compressor 1 </ b> C according to the fourth embodiment will be described with reference to FIG. 8. FIG. 8 is a cross-sectional view showing a configuration of a main part of the electric compressor 1C.

  As shown in FIG. 8, the electric compressor 1 </ b> C according to the fourth embodiment includes a cover 81 in addition to the cover 71 as compared with the electric compressor 1 according to the first embodiment (see FIG. 3A). Is different.

  The cover 81 is a member disposed above the stator 21. The cover 81 has the same configuration as the cover 71 (see FIG. 4).

  Since the electric compressor 1C includes the cover 81 in addition to the cover 71, the working fluid is agitated in the upper space 47 due to the rotational movement of the rotor 22, and as a result, the oil is agitated or refined. Can be suppressed. Therefore, the electric compressor 1 </ b> C is more efficient than the electric compressor 1 according to the first embodiment, and the amount of refrigerating machine oil discharged into the refrigerating cycle (that is, the amount of refrigerating machine oil flowing out of the sealed container 4). ) Can be reduced.

  The cover 81 can function as a winding presser that presses the upper end 25b of the stator 21 winding. As a result, the electric compressor 1 </ b> C does not need to use a dedicated member for pressing the upper end 25 b of the winding of the stator 21. Therefore, the electric compressor 1C can reduce the number of parts.

  As described above, according to the electric compressor 1 </ b> C according to the fourth embodiment, the amount of refrigerating machine oil flowing out of the sealed container 4 can be reduced more efficiently than the electric compressor 1 according to the first embodiment. Can do.

[Embodiment 5]
Hereinafter, the configuration of the electric compressor 1D according to the fifth embodiment will be described with reference to FIG. FIG. 9 is a cross-sectional view illustrating a configuration of a main part of the electric compressor 1D.

  As shown in FIG. 9, the electric compressor 1D according to the fifth embodiment is different from the electric compressor 1 according to the first embodiment (see FIG. 3) in that a cover 71D is used instead of the cover 71. doing.

  The cover 71D is different from the cover 71 of the first embodiment in that a gap 76 between the outer periphery of the bottom surface portion 73 and the inner wall of the sealed container 4 is large. The area of the gap 76 is larger than the total area of the outer peripheral grooves 27.

  Similarly to the electric compressor 1 according to the first embodiment, the electric compressor 1D has a gap 26 (see FIG. 5) provided between each tooth of the stator 21 from the inner peripheral side of the stator 21 by the cover 71D. 2 (b)), the outflow amount of the working fluid flowing can be reduced. Therefore, the electric compressor 1 </ b> D can reduce the amount of oil that reaches the upper space 47 from the lower space 46. As a result, the electric compressor 1D can reduce the discharge amount of the refrigerating machine oil discharged into the refrigerating cycle (that is, the amount of refrigerating machine oil flowing out of the sealed container 4).

  Moreover, since the electric compressor 1D uses the cover 71D in which the area of the gap 76 is larger than the total area of the outer peripheral grooves 27, the outer peripheral groove provided between the stator 21 and the sealed container 4 is used. 27 does not impede the flow of working fluid through 27. Therefore, the electric compressor 1D can reduce pressure loss. Therefore, the electric compressor 1D can improve the supply performance of the working fluid to the refrigeration cycle.

As described above, according to the electric compressor 1D according to the fifth embodiment, similarly to the electric compressor 1 according to the first embodiment, the amount of refrigerating machine oil flowing out of the sealed container 4 can be reduced.
Moreover, according to the electric compressor 1 </ b> D, the pressure loss can be reduced also by the electric compressor 1 according to the first embodiment.

[Embodiment 6]
Hereinafter, the configuration of the electric compressor 1E according to the sixth embodiment will be described with reference to FIGS. FIG. 10 is a cross-sectional view illustrating a configuration of a main part of the electric compressor 1E. FIG. 11 is a perspective view showing a configuration of a cover 71E used in the sixth embodiment.

  As shown in FIGS. 10 and 11, the electric compressor 1 </ b> E according to the sixth embodiment uses a cover 71 </ b> E instead of the cover 71 as compared with the electric compressor 1 according to the first embodiment (see FIG. 3). It is different in point.

  The cover 71E is different from the cover 71 of the first embodiment in that the outer wall surface portion 75 is removed.

  Since the electric compressor 1E uses the cover 71E from which the outer wall surface 75 is removed, the oil returning from the upper side to the lower side of the hermetic container 4 than the electric compressor 1 according to the first embodiment is supplied to the outer peripheral side of the stator 21. The oil that has returned to the lower side of the sealed container 4 can be prevented from rotating and being re-stirred by the swirling flow due to 22 and the jet flow accompanying the discharge from the compression mechanism unit 3. Furthermore, since the electric compressor 1E can manufacture the cover 71E at a lower cost than the cover 71 of the first embodiment, the electric compressor 1E can be manufactured at a lower cost than the electric compressor 1 according to the first embodiment. The oil discharge amount can be reduced.

  The rotor 22 of the electric compressor 1E is formed with a plurality of openings 66 and 67 (see FIG. 10A) provided inside and outside. The electric compressor 1 </ b> E returns oil from the upper space 47 to the lower space 46 through the openings 66 and 67. Hereinafter, the opening 66 is referred to as “inner opening 66”, and the opening 67 is referred to as “outer opening 67”. The inner diameter of the outer opening 67 is set to a value larger than the inner diameter of the inner opening 66 so that the working fluid can flow smoothly.

  As described above, according to the electric compressor 1E according to the sixth embodiment, the oil returning from the upper side to the lower side of the sealed container 4 is transferred to the outer peripheral side of the stator 21 as compared with the electric compressor 1 according to the first embodiment. It is possible to prevent the oil returned to the lower side of the sealed container 4 from rotating and re-stirring by the swirling flow due to 22 and the jet flow accompanying the discharge from the compression mechanism unit 3. The amount of refrigerating machine oil flowing out of the sealed container 4 can be reduced at a lower cost than the electric compressor 1.

[Embodiment 7]
Hereinafter, the configuration of the electric compressor 1 </ b> F according to the seventh embodiment will be described with reference to FIGS. 12 and 13. FIG. 12 is a cross-sectional view illustrating a configuration of a main part of the electric compressor 1F. FIG. 13 is a perspective view showing a configuration of a cover 71F used in the seventh embodiment.

  As shown in FIGS. 12 and 13, the electric compressor 1 </ b> F according to the seventh embodiment uses a cover 71 </ b> F instead of the cover 71 as compared with the electric compressor 1 according to the first embodiment (see FIG. 3). It is different in point.

  The cover 71F is a member in which the bottom surface portion 73f is inclined so that the height on the outer peripheral side is lower than the height on the inner peripheral side.

  Similarly to the electric compressor 1 according to the first embodiment, the electric compressor 1F includes a gap 26 (see FIG. 5) provided between each tooth of the stator 21 from the inner peripheral side of the stator 21 by the cover 71F. 2 (b)), the outflow amount of the working fluid flowing can be reduced. Therefore, the electric compressor 1 </ b> F can reduce the amount of oil that reaches the upper space 47 from the lower space 46. As a result, the electric compressor 1F can reduce the discharge amount of the refrigerating machine oil discharged into the refrigerating cycle (that is, the amount of refrigerating machine oil flowing out of the sealed container 4).

Moreover, since the electric compressor 1F uses the cover 71F having a configuration in which the bottom surface portion 73f is inclined, the oil that has become oil droplets by adhering to the cover 71F or the upper space 47 returns to the lower space 46. The oil drop position can be adjusted.
Moreover, the electric compressor 1F can adjust the direction of the oil flowing to the outer peripheral side of the stator 21 along the bottom surface portion 73f of the cover 71F.

As described above, according to the electric compressor 1F according to the seventh embodiment, similarly to the electric compressor 1 according to the first embodiment, the amount of refrigerating machine oil flowing out of the sealed container 4 can be reduced.
Moreover, according to the electric compressor 1F, the oil dropping position can be adjusted as compared with the electric compressor 1 according to the first embodiment, and the outer peripheral side of the stator 21 along the bottom surface portion 73f of the cover 71F. The direction of the oil flowing through can be adjusted.

  The present invention is not limited to the above-described embodiment, and includes various modifications. For example, the above-described embodiment has been described in detail for easy understanding of the present invention, and is not necessarily limited to one having all the configurations described. Further, a part of the configuration of an embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of an embodiment. In addition, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

  Further, for example, in the above-described embodiment, the description has been given by taking the hermetic vertical rotary compressor as an example. However, the present invention is not limited to this, and can be applied to, for example, a non-hermetic rotary compressor, a scroll compressor, and the like.

1, 1A, 1B, 1C, 1D, 1E, 1F Electric compressor 2 Electric motor 3 Compression mechanism part 4 Sealed container 5 Accumulator 21 Stator 21b Auxiliary part 21c Opening part 22 Rotor 25a Winding lower end part 25b Winding Upper end portion 26 clearance 27 outer peripheral groove 31 crankshaft 31a eccentric portion 32 main bearing 33 cylinder 34 auxiliary bearing 35 roller 36 vane 37 discharge pipe 41 cylindrical body 42 lid body 43 bottom body 43a oil reservoir 44 compression chamber 45 discharge port 46 lower Side space 47 Upper space 56 Suction pipe 61 Discharge valve 62 Retainer 63 Cup muffler 63a Discharge hole 66 Inner opening 67 Outer opening 71 Cover 72 Flow hole 73, 73f Bottom surface (opposite part)
74, 74a, 74e Inner wall surface portion 75 Outer wall surface portion 76 Clearance 77, 78 Bottom surface portion hole (opposing portion hole)
81 Top cover

Claims (11)

An electric motor composed of a stator and a rotor;
A compression mechanism that is rotationally driven by the electric motor;
A sealed container that houses the electric motor and the compression mechanism, and
A cover disposed in the vicinity of one axial end of the stator,
The cover includes a facing portion facing one end of the stator,
The electric compressor according to claim 1, wherein the facing portion is formed in a substantially circular shape centering on a rotation axis of the rotor and has a hole larger than an outer diameter of the rotor. The electric compressor according to claim 1,
The electric compressor according to claim 1, wherein the cover includes an inner wall surface portion formed along an edge of the hole so as to protrude from the facing portion toward one end of the stator. The electric compressor according to claim 2,
Furthermore, the said cover is provided with the outer wall surface part formed along the edge of the outer periphery of the said opposing part so that it may protrude in the one end side of the said stator from the said opposing part, The electric compressor characterized by the above-mentioned. The electric compressor according to claim 3,
The electric compressor according to claim 1, wherein a height of the outer wall surface portion is higher than a height of the inner wall surface portion. The electric compressor according to any one of claims 1 to 4,
The opposing portion is formed with one or more opposing portion holes penetrating from one surface to the other surface,
The electric compressor according to claim 1, wherein a total area of the opposed portion holes is 20% or less of an area of the opposed portion. The electric compressor according to claim 2,
The stator has an auxiliary portion around which no winding is wound,
The auxiliary portion includes an inner wall facing the hole,
An opening is formed between the inner wall surface portion and the auxiliary portion,
The area of the opening is 20% or less of the total area of the inner wall surface portion and the inner wall of the auxiliary portion. The electric compressor according to any one of claims 1 to 6,
The electric compressor according to claim 1, wherein the cover presses one end of the winding of the stator in the axial direction. The electric compressor according to any one of claims 1 to 7,
The electric compressor further includes another cover disposed in the vicinity of the other axial end of the stator. The electric compressor according to claim 8,
The electric compressor according to claim 1, wherein the other cover presses the other end in the axial direction of the winding of the stator. The electric compressor according to any one of claims 1 to 9,
A gap is formed between the outer peripheral portion of the facing portion of the cover and the inner wall of the sealed container,
Between the stator core and the inner wall of the closed container, a plurality of outer peripheral grooves functioning as working fluid flow paths are formed,
The electric compressor is characterized in that an area of the gap is wider than a total area of the plurality of outer peripheral grooves. The electric compressor according to any one of claims 1 to 10,
The electric compressor is characterized in that the facing portion is formed so as to be inclined such that the height on the outer peripheral side is lower than the height on the inner peripheral side.

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