JP2015206344A - compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a compressor capable of suppressing removal of refrigerator oil from the compressor as compared with a conventional compressor.SOLUTION: A high-pressure shell type compressor 100 includes: an electric mechanism 10 in which a counter bore 13 is formed under a rotor 12; a driving shaft 2 in which a passage 2a of refrigerator oil and a gas-vent hole 3 connected to the passage 2a and opened into the counter bore 13 are formed; a compression mechanism 1 arranged under the electric mechanism 10; and a closed vessel 20 which stores these units and forms an oil reservoir on a lower part. In plain view, a distance from a center axis of the driving shaft 2 up to an outer peripheral part of the counter bore 13 is shorter than a distance from the center axis of the driving shaft 2 up to a discharge port 6 of the compression mechanism 1, and an upper bearing 4 of the compression mechanism 1 is arranged so that its upper end part is inserted into the counter bore 13.

Description

  The present invention relates to a compressor, and relates to a compressor that suppresses carry-out of refrigeration oil in a sealed container.

  Conventionally, an electric mechanism, a compression mechanism disposed below the electric mechanism, and a drive shaft that transmits the driving force of the electric mechanism to the compression mechanism are housed in a sealed container, and the refrigerant compressed by the compression mechanism is sealed. A compressor that discharges into a container (a so-called high-pressure shell-type hermetic compressor) is known. In such a conventional compressor, a flow path for refrigerating machine oil stored in the lower part of the hermetic container and a gas vent hole communicating with the flow path and opening on the outer peripheral surface of the drive shaft are formed on the drive shaft. ing.

  When such a conventional compressor is driven (when the electric mechanism is rotated), the refrigerant gas is compressed by the compression mechanism, and the compressed gas passes through the discharge port of the compression mechanism (for example, the discharge port of the discharge muffler). It is discharged into a closed container. The refrigerant gas discharged into the sealed container passes through the gap between the sealed container and the stator of the electric mechanism, the gap between the rotor and the stator of the electric mechanism, and the through hole formed in the rotor. Then, it is discharged out of the compression chamber (refrigeration apparatus) from a discharge pipe provided in the upper part of the sealed container.

  On the other hand, when the drive shaft rotates together with the electric mechanism, the refrigerating machine oil stored in the lower part of the hermetic container moves up the flow path of the refrigerating machine oil formed inside the drive shaft, and is airtight in each sliding portion of the compression mechanism. Supplied as oil and lubricant. In addition, surplus refrigeration oil is discharged into the sealed container from the gas vent formed in the drive shaft, falls to the lower part of the sealed container, and is recirculated.

  In such a conventional compressor, the discharge port of the compression mechanism is located below the vent hole. For this reason, surplus refrigeration oil discharged from the gas vent hole is scattered in the sealed container by the rotation of the drive shaft, and is lifted together with the refrigerant gas discharged from the compression mechanism to the compressor upper space with the discharge pipe. It becomes easy to flow into the refrigeration apparatus.

  For this reason, in such a conventional compressor, when the refrigeration oil excessively flows into the refrigeration apparatus, the heat exchanger rate of the heat exchanger decreases due to the refrigeration oil adhering to the heat exchanger, and the performance of the refrigeration apparatus There was a problem of getting worse.

  Further, in such a conventional compressor, when the refrigerating machine oil sealed in the hermetic container is excessively reduced, the airtightness in the compression mechanism is lowered and the compression performance is lowered, or sufficient in each sliding portion. There was also a problem that the performance of the compressor could not be maintained, such as failure to ensure performance and cause failure.

  Therefore, in the conventional compressor, a counter bore is formed in the lower part of the rotor of the motor, and a gas vent hole formed in the drive shaft is opened in the counter bore. Has been proposed (see, for example, Patent Document 1). The compressor described in Patent Document 1 opens a gas vent hole in the counterbore, thereby causing an oil separation action on the inner wall surface of the counterbore to prevent the refrigerating machine oil from scattering and To prevent the refrigerating machine oil from flowing out of the discharge pipe.

JP 2002-89476 A (summary, FIG. 1)

  The compressor described in Patent Document 1 has a large gap (that is, the outlet of the counter bore) formed between the inner wall surface (outer peripheral portion) of the counter bore and the drive shaft. For this reason, when the refrigeration oil discharged from the vent hole into the rotor counterbore and separated from the refrigerant by the centrifugal action of the drive shaft flows out of the counterbore, the rotation of the drive shaft and the rotor causes the counterbore to rotate. It flows out so that it may diffuse to the space below, that is, above the discharge port of the compression mechanism. For this reason, in the compressor described in Patent Document 1, the refrigeration oil is still lifted together with the refrigerant gas discharged from the discharge port of the compression mechanism into the compressor upper space where the discharge pipe is located, and is discharged from the discharge pipe to the outside of the compression chamber ( There is a problem that it is not possible to sufficiently prevent the refrigerating machine oil from being discharged to the refrigerating apparatus) and taking out the refrigerating machine oil from the compressor.

  The present invention has been made in order to solve the above-described problems, and an object of the present invention is to obtain a compressor capable of suppressing refrigerating machine oil from being taken out from a compressor as compared with the conventional art.

  A compressor according to the present invention includes a rotor and a stator, an electric mechanism having a counter bore formed in a lower portion of the rotor, a drive shaft connected to the rotor, and a drive shaft connected to the drive shaft. A compression mechanism that is disposed below the electric mechanism, compresses the refrigerant by the driving force of the electric mechanism transmitted through the drive shaft, and discharges the compressed refrigerant from at least one outlet, and the electric A mechanism, the drive shaft and the compression mechanism, and a sealed container having an oil sump formed in a lower part thereof, wherein the compression mechanism discharges the compressed refrigerant from the discharge port into the sealed container, A compressor having a refrigerating machine oil flow passage formed in the axial direction on the drive shaft and a gas vent hole communicating with the flow passage and opening into the counterbore, in plan view, The outer periphery of the counter bore from the central axis of the drive shaft Is smaller than the distance from the central axis of the drive shaft to the discharge port, and the compression mechanism includes a bearing that rotatably supports the drive shaft at an upper portion thereof. An upper end portion is inserted and arranged in the counter bore.

  In the present invention, since the tip end of the bearing is inserted into the counter bore, the counter bore outlet with respect to the volume in the counter bore (the gap formed between the bearing and the inner wall surface (outer peripheral portion) of the counter bore) However, it will be smaller than before. For this reason, the refrigerating machine oil separated from the refrigerant in the counterbore becomes a directional flow when flowing out of the counterbore, and diffuses in a space below the counterbore, that is, above the discharge port of the compression mechanism. difficult. In the present invention, the distance from the central axis of the drive shaft to the counterbore is smaller than the distance from the central axis of the drive shaft to the discharge port of the compression mechanism. For this reason, in the present invention, the refrigerating machine oil flowing out from the counterbore flows toward the center axis side of the drive shaft from the discharge port of the compression mechanism. Therefore, according to the present invention, the refrigerating machine oil can be prevented from being lifted together with the refrigerant gas discharged from the discharge port of the compression mechanism into the compressor upper space having the discharge pipe, and the refrigerating machine oil is taken out from the compressor. Can be suppressed more than before.

It is a longitudinal cross-sectional view which shows the structure of the compressor which concerns on Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows the structure of the compressor which concerns on Embodiment 2 of this invention. It is a perspective view (main part enlarged view) which shows the upper part of the compression mechanism in the compressor which concerns on Embodiment 2 of this invention. It is a perspective view (main part enlarged view) which shows the upper part of another example of the compression mechanism which concerns on Embodiment 2 of this invention. It is a plane sectional view showing the compression mechanism neighborhood of the compressor concerning Embodiment 3 of the present invention. It is a perspective view (main part enlarged view) which shows the upper part of the compression mechanism in the compressor which concerns on Embodiment 4 of this invention.

  DESCRIPTION OF EMBODIMENTS Hereinafter, preferred embodiments of a compressor according to the present invention will be described in detail with reference to the accompanying drawings.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view showing the structure of a compressor according to Embodiment 1 of the present invention.
The compressor 100 according to the first embodiment is a high-pressure shell-type hermetic compressor, and is housed in a hermetic container 20 in which an oil sump 20a for storing refrigeration oil is formed in the lower part, and in the hermetic container 20. An electric mechanism 10, a drive shaft 2, and a compression mechanism 1 are provided. In addition, a discharge pipe 21 for discharging the refrigerant gas in the sealed container 20 to the outside of the sealed container 20 (a refrigeration apparatus) is provided, for example, at the upper part of the sealed container 20.

The electric mechanism 10 includes a substantially cylindrical stator 11 in which a through-hole penetrating in the vertical direction is formed in an inner peripheral portion, and a substantially cylindrical shape disposed on the inner peripheral side of the stator 11 with a predetermined interval. Rotor 12. The stator 11 is configured by laminating steel plates, and is attached to the inner peripheral surface of the sealed container 20 by press fitting, welding, or the like. The rotor 12 is configured by laminating steel plates. The rotor 12 is formed with at least one through hole 14 serving as a flow path for the refrigerator oil so as to penetrate the rotor 12 in the vertical direction. In addition, a counter bore 13 that is, for example, a cylindrical recess having an opening at the bottom is formed in the lower portion of the rotor 12 according to the first embodiment.
The number of through holes 14 is arbitrary.

  The drive shaft 2 has an upper end connected to the rotor 12 of the electric mechanism 10 and a lower end connected to the compression mechanism 1. That is, the drive shaft 2 transmits the driving force of the electric mechanism 10 to the compression mechanism 1. The drive shaft 2 is rotatably supported by the upper bearing 4 and the lower bearing 7 of the electric mechanism 10. The drive shaft 2 is formed with a refrigerating machine oil flow path 2a along the axial direction thereof. An oil supply hole 2b for supplying refrigerating machine oil to each sliding portion of the compression mechanism 1 communicates with the flow path 2a. Further, the drive shaft 2 is also formed with a gas vent hole 3 communicating with the vicinity of the upper end portion of the flow path 2a (above the upper bearing 4). The vent hole 3 is opened in the counter bore 13.

  The compression mechanism 1 is disposed below the electric mechanism 10 and compresses the refrigerant by the driving force of the electric mechanism 10 transmitted via the drive shaft 2. In the first embodiment, a rotary compression mechanism is employed as the compression mechanism 1. The compression mechanism 1 includes a cylinder 8, a piston 9, a discharge muffler 5, an upper bearing 4, a lower bearing 7, and the like.

  The cylinder 8 has a through hole penetrating in the vertical direction, and the upper and lower openings of the through hole are closed by the upper bearing 4 and the lower bearing 7. And the said through hole of the cylinder 8 becomes the cylinder chamber 8a. The piston 9 is disposed in the cylinder chamber 8a. The piston 9 has a substantially cylindrical shape, and is slidably attached to the outer periphery of an eccentric shaft portion 2 c provided eccentric to the drive shaft 2. That is, in the compression mechanism 1 according to the first embodiment, the eccentric shaft portion 2c rotates as the drive shaft 2 rotates, and the piston 9 rotates in the cylinder chamber 8a together with the eccentric shaft portion 2c. The refrigerant gas sucked from 22 is compressed inside the cylinder chamber 8a. When the compressed refrigerant gas reaches a predetermined pressure, it passes through a discharge port (not shown) formed in the upper bearing 4, for example, and is discharged from the cylinder chamber 8 a to the internal space of the discharge muffler 5. It is discharged from the discharge port 6 into the sealed container 20.

  Here, the discharge port 6 corresponds to the discharge port of the compression mechanism in the present invention, and at least one discharge port 6 is formed in the discharge muffler 5. In the first embodiment, the distance from the central axis of the drive shaft 2 to the outer peripheral portion of the counterbore 13 is smaller than the distance from the central axis of the drive shaft 2 to the discharge port 6. Furthermore, in the first embodiment, the upper bearing 4 disposed at the upper portion of the compression mechanism 1 is disposed such that the upper end portion is inserted into the counter bore 13.

  In the present invention, the configuration of the compression mechanism is not limited to the rotary type. As long as the compression mechanism is provided below the electric mechanism 10 and the upper bearing 4 is provided on the upper part, various types of compression mechanisms such as a vane type can be used.

Next, the operation of the compressor 100 configured as described above will be described.
When the electric mechanism 10 is rotated, the rotor 12 is rotated, and the drive shaft 2 connected to the rotor 12 is rotated accordingly. When the drive shaft 2 rotates, the eccentric shaft portion 2c rotates accordingly, and the piston 9 rotates in the cylinder chamber 8a together with the eccentric shaft portion 2c, so that the refrigerant gas sucked from the suction pipe 22 is in the cylinder chamber 8a. Compressed internally. When the compressed refrigerant gas reaches a predetermined pressure, it passes through, for example, a discharge port (not shown) formed in the upper bearing 4 and is discharged from the cylinder chamber 8a to the internal space of the discharge muffler 5.

  The refrigerant gas discharged into the internal space of the discharge muffler 5 is discharged from the discharge port 6 of the discharge muffler 5 into the space below the electric mechanism 10. The refrigerant gas discharged into the space below the electric mechanism 10 is a gap between the sealed container 20 and the stator 11, a gap between the rotor 12 and the stator 11, a through hole 14 formed in the rotor 12, and the like. And flows into the space above the electric mechanism 10. The refrigerant gas that has flowed into the space above the electric mechanism 10 is discharged out of the compression chamber (a refrigeration apparatus) from a discharge pipe 21 provided in the upper part of the sealed container 20.

  On the other hand, the refrigerating machine oil stored in the lower portion of the hermetic container 20 rises in the flow path 2 a formed inside the drive shaft 2 when the drive shaft 2 rotates. A part of the refrigerating machine oil flowing into the flow path 2a is slid between the upper bearing 4 and the drive shaft 2 and the lower bearing 7 and the drive shaft 2 through the oil supply hole 2b communicating with the flow path 2a. And the sliding portion of the compression mechanism 1 such as the sliding portion between the eccentric shaft portion 2 c and the piston 9. Of the refrigerating machine oil that has flowed into the flow path 2a, the surplus refrigerating machine oil that has not been supplied to the sliding portions of the compression mechanism 1 flows into the counter bore 13 from the vent hole 3 that communicates with the flow path 2a. To do.

  The refrigeration oil that has flowed into the counterbore 13 is separated from the refrigerant by the centrifugal separation action obtained by the rotation of the drive shaft 2, and flows out below the counterbore 13. At this time, in the conventional compressor in which the upper end portion of the upper bearing is not inserted into the counter bore, the outlet of the counter bore becomes a gap between the drive shaft and the outer peripheral portion of the counter bore. For this reason, in the conventional compressor, the outlet of the counter bore is larger than the volume in the counter bore. Therefore, the refrigerating machine oil flowing out from the counter bore spreads and flows out so as to diffuse above the compression mechanism. For this reason, in the conventional compressor, the refrigeration oil is lifted to the upper space of the compressor having the discharge pipe together with the refrigerant gas discharged from the discharge port of the compression mechanism, and discharged from the discharge pipe to the outside of the compression chamber (refrigeration apparatus). It was not possible to sufficiently prevent the refrigerating machine oil from being taken out of the compressor.

  In contrast, in the compressor 100 according to the first embodiment, since the upper end portion of the upper bearing 4 is inserted into the counter bore 13, the outlet of the counter bore 13 is connected to the upper end portion of the upper bearing 4 and the counter bore 13. It becomes a clearance gap between the outer peripheral parts. For this reason, in the compressor 100 according to the first embodiment, the outlet of the counter bore 13 is smaller than the conventional one with respect to the volume in the counter bore 13. Therefore, in the compressor 100 according to the first embodiment, the refrigeration oil flowing out from the counterbore 13 has a flow having a directivity that is blown out in a certain direction from the outlet of the counterbore 13. Furthermore, in the compressor 100 according to the first embodiment, the distance from the central axis of the drive shaft 2 to the outer peripheral portion of the counter bore 13 is smaller than the distance from the central axis of the drive shaft 2 to the discharge port 6. ing. For this reason, the refrigerating machine oil flowing out from the counter bore 13 as a directional flow flows toward the central axis of the drive shaft 2 from the discharge port 6 of the compression mechanism 1. Therefore, in the compressor 100 according to the first embodiment, the refrigeration oil is lifted to the upper space of the compressor 100 having the discharge pipe 21 together with the refrigerant gas discharged from the discharge port 6 of the compression mechanism 1. From the compressor 100 to the outside of the compressor 100 (refrigeration apparatus) can be suppressed, and the refrigerator oil can be sufficiently suppressed from being taken out of the compressor 100.

  As described above, by configuring the compressor 100 as in the first embodiment, it is possible to sufficiently prevent the refrigerating machine oil from being taken out of the compressor 100. Therefore, the compressor 100 according to the first embodiment can prevent the performance of the refrigeration apparatus from being lowered due to the oil rising, and can suppress the performance degradation of the compressor 100 itself.

1. Actual form
By forming the following relief portion at the upper end portion of the upper bearing 4, it is possible to further suppress the refrigerating machine oil from being taken out from the compressor 100. In the second embodiment, the same reference numerals are given to the same parts as those in the first embodiment, and only the parts different from the first embodiment will be described.

FIG. 2 is a longitudinal sectional view showing the structure of the compressor according to Embodiment 2 of the present invention. FIG. 3 is a perspective view (main part enlarged view) showing the upper part of the compression mechanism in the compressor.
As shown in FIGS. 2 and 3, the compressor 100 according to the second embodiment is provided at the upper end portion of the upper bearing 4 (more specifically, from the portion inserted into the counter bore 13 to the portion not inserted. ), A relief portion 4a having a circular arc shape in a plan view (in other words, a half donut shape) is formed.

  Also in the compressor 100 according to the second embodiment, as in the first embodiment, the refrigerating machine oil flowing out from the counterbore 13 has a flow having a directionality that is blown out from the outlet of the counterbore 13 in a certain direction. Become. Further, in the compressor according to the second embodiment, by forming the relief portion 4a at the upper end portion of the upper bearing 4, the shape of the outlet of the counter bore 13 can be made non-uniform. Specifically, the width of the outlet of the counter bore 13 (the gap between the upper end portion of the upper bearing 4 and the outer peripheral portion of the counter bore 13) is not formed in the range where the relief portion 4a is formed. Be bigger than the range. For this reason, most of the refrigerating machine oil flowing out from the counterbore 13 flows out from the range where the escape portion 4a is formed. Therefore, the refrigerating machine oil flowing out from the counterbore 13 is blown out in a more fixed direction than in the first embodiment, and further flows with directionality. For this reason, the compressor 100 according to the second embodiment can further suppress the refrigeration oil flowing out from the counter bore 13 from diffusing above the compression mechanism 1 as compared with the first embodiment. It is further suppressed that the refrigerant gas discharged from the discharge port 6 of the mechanism 1 is lifted to the upper space of the compressor 100 having the discharge pipe 21 and discharged from the discharge pipe to the outside of the compressor 100 (refrigeration apparatus). It is possible to further suppress the refrigerating machine oil from being taken out of the compressor 100.

  As described above, by configuring the compressor 100 as in the second embodiment, it is possible to further suppress the refrigerating machine oil from being taken out from the compressor 100 as compared with the first embodiment. Therefore, the compressor 100 according to the second embodiment can further prevent the performance of the refrigeration apparatus from being deteriorated due to oil rising, and can further suppress the performance degradation of the compressor 100 itself, as compared with the first embodiment.

  In addition, the shape of the relief part formed in the upper end part of the upper bearing 4 is not limited to the shape (arc shape) of said relief part 4a.

FIG. 4 is a perspective view (main part enlarged view) showing the upper part of another example of the compression mechanism according to Embodiment 2 of the present invention.
For example, as shown in FIG. 4, a crescent-shaped relief portion 4b in a plan view is formed at the upper end portion of the upper bearing 4 (more specifically, from the portion inserted into the counter bore 13 to the portion not inserted). Also good. Thus, even if the relief portion 4b is formed at the upper end portion of the upper bearing 4, the effect shown in the second embodiment can be obtained.

Embodiment 3 FIG.
In the second embodiment, no particular mention was made of the formation positions of the relief portions 4a and 4b in plan view. By setting the formation positions of the relief portions 4a and 4b in plan view to the following positions, it is possible to further suppress the refrigerating machine oil from being taken out from the compressor 100. In the third embodiment, the same reference numerals are given to the same parts as those in the above embodiment, and only the parts different from the above embodiment will be described. In the third embodiment, the case where the relief portion 4a is formed at the upper end portion of the upper bearing 4 will be described as an example.

FIG. 5 is a plan sectional view showing the vicinity of the compression mechanism of the compressor according to Embodiment 3 of the present invention.
As shown in FIG. 5, the angle range in which the discharge port 6 of the compression mechanism 1 is formed and the angle in which the discharge port 6 of the compression mechanism 1 is not formed centered on the central axis of the drive shaft 2 in plan view. When divided into the range 4c, the relief portion 4a according to the third embodiment is formed in the angular range 4c where the discharge port 6 of the compression mechanism 1 is not formed.

  Thus, by forming the relief portion 4a in the angle range 4c where the discharge port 6 of the compression mechanism 1 is not formed, most of the refrigerating machine oil flowing out of the counter bore 13 is formed in the discharge port 6 of the compression mechanism 1. It will flow out to the angle range 4c which is not done. That is, the refrigerating machine oil flowing out in the vicinity of the discharge port 6 of the compression mechanism 1 is reduced. For this reason, the compressor 100 according to the third embodiment is different from the second embodiment in that the compressor 100 having the discharge pipe 21 together with the refrigerant gas in which the refrigeration oil is discharged from the discharge port 6 of the compression mechanism 1. It can further be suppressed that it is lifted to the upper space and discharged from the discharge pipe to the outside of the compressor 100 (refrigeration apparatus), and the refrigerating machine oil can be further prevented from being taken out of the compressor 100.

  As described above, by configuring the compressor 100 as in the third embodiment, it is possible to further suppress the refrigerating machine oil from being taken out from the compressor 100 as compared with the second embodiment. Therefore, the compressor 100 according to the third embodiment can further prevent the performance degradation of the refrigeration apparatus due to the oil rise, and can further suppress the performance degradation of the compressor 100 itself, as compared with the second embodiment.

  When the compressor 100 is configured as in the third embodiment, when the relief portion 4a (arc shape) is adopted as the shape of the relief portion formed at the upper end portion of the upper bearing 4, the shape of the relief portion is used. Control of the width of the outlet of the counterbore 13 in the range where the escape portion is formed is easier than in the case where the escape portion 4b (crescent shape) is adopted. This is because the distance between the outer peripheral portion of the counter bore 13 and the relief portion 4a is uniform. For this reason, when the relief portion 4a (arc shape) is adopted as the shape of the relief portion formed at the upper end portion of the upper bearing 4, compared to the case where the relief portion 4b (crescent shape) is adopted as the shape of the relief portion, It becomes easier to control the directionality of the refrigerating machine oil flowing out from the counterbore 13. Therefore, when emphasizing prevention of performance deterioration of the refrigeration apparatus and the compressor 100 itself, it is preferable to adopt the escape portion 4a (arc shape) as the shape of the escape portion. On the other hand, the relief part 4b is easier to process the upper bearing 4 than the relief part 4a. For this reason, when importance is attached to the workability of the upper bearing 4, that is, the suppression of the cost increase of the compressor 100, it is preferable to adopt the relief portion 4 b (crescent shape) as the shape of the relief portion.

Actual form 4.
Instead of the escape portions 4a and 4b shown in the second embodiment and the third embodiment, the following notch may be formed in the upper end portion of the upper bearing 4. In the fourth embodiment, the same reference numerals are given to the same parts as those in the above embodiment, and only the parts different from those in the above embodiment will be described.

FIG. 6 is a perspective view (main part enlarged view) showing an upper part of a compression mechanism in a compressor according to Embodiment 4 of the present invention.
As shown in FIG. 6, the compressor 100 according to the fourth embodiment includes at least an upper end portion of the upper bearing 4 (more specifically, from a portion inserted into the counter bore 13 to a portion not inserted). One notch 4d is formed.

  Also in the compressor 100 according to the fourth embodiment, by forming the notch 4d in the upper end portion of the upper bearing 4, the shape of the outlet of the counter bore 13 can be made non-uniform. For this reason, most of the refrigerating machine oil flowing out from the counterbore 13 flows out from the range where the notches 4d are formed. Therefore, the refrigerating machine oil flowing out of the counterbore 13 is blown out in a more constant direction, as in the second embodiment, and has a more directional flow than in the first embodiment. For this reason, the compressor 100 according to the fourth embodiment can further suppress the refrigerating machine oil flowing out from the counter bore 13 from diffusing above the compression mechanism 1 as compared with the first embodiment, so that the refrigerating machine oil is compressed. It is further suppressed that the refrigerant gas discharged from the discharge port 6 of the mechanism 1 is lifted to the upper space of the compressor 100 having the discharge pipe 21 and discharged from the discharge pipe to the outside of the compressor 100 (refrigeration apparatus). It is possible to further suppress the refrigerating machine oil from being taken out of the compressor 100.

  Thus, even if the compressor 100 is configured as in the fourth embodiment, it is possible to further suppress the refrigerating machine oil from being taken out of the compressor 100 as in the second embodiment. Therefore, the compressor 100 according to the fourth embodiment can further prevent the performance deterioration of the refrigeration apparatus due to the oil rising and further suppress the performance deterioration of the compressor 100 itself as compared with the first embodiment.

  In the fourth embodiment, similarly to the third embodiment, the notch 4d may be formed in the angular range 4c where the discharge port 6 of the compression mechanism 1 is not formed. By forming the notch 4d in the angular range 4c where the discharge port 6 of the compression mechanism 1 is not formed, the same effect as in the third embodiment can be obtained.

  DESCRIPTION OF SYMBOLS 1 Compression mechanism, 2 Drive shaft, 2a Flow path, 2b Oil supply hole, 2c Eccentric shaft part, 3 Gas vent hole, 4 Upper bearing, 4a, 4b Relief part, 4c Angular range, 4d Notch, 5 Discharge muffler, 6 Discharge Outlet, 7 Lower bearing, 8 Cylinder, 8a Cylinder chamber, 9 Piston, 10 Electric mechanism, 11 Stator, 12 Rotor, 13 Counter bore, 14 Through hole, 20 Airtight container, 20a Oil sump, 21 Discharge pipe, 22 Suction Tube, 100 compressor.

Claims (5)

An electric mechanism having a rotor and a stator and having a counter bore formed in a lower portion of the rotor;
A drive shaft connected to the rotor;
The refrigerant is compressed by the driving force of the electric mechanism connected to the driving shaft and disposed below the electric mechanism and transmitted through the driving shaft, and the compressed refrigerant is discharged from at least one discharge port. A compression mechanism;
A sealed container that houses the electric mechanism, the drive shaft, and the compression mechanism, and in which an oil sump is formed at the bottom;
With
The compression mechanism discharges the compressed refrigerant from the discharge port into the sealed container,
A compressor having a refrigerating machine oil flow passage formed in the axial direction on the drive shaft and a gas vent hole communicating with the flow passage and opening into the counterbore;
In plan view, the distance from the central axis of the drive shaft to the outer peripheral portion of the counter bore is smaller than the distance from the central axis of the drive shaft to the discharge port,
The compression mechanism includes a bearing that rotatably supports the drive shaft at an upper portion thereof.
The compressor is characterized in that an upper end portion of the bearing is inserted into the counter bore.   The compressor according to claim 1, wherein an escape portion having a circular arc shape or a crescent shape in plan view is formed at an upper end portion of the bearing. In plan view, when divided into an angular range in which the discharge port of the compression mechanism is formed and an angular range in which the discharge port of the compression mechanism is not formed around the central axis of the drive shaft,
The compressor according to claim 2, wherein the escape portion is formed in an angle range in which the discharge port of the compression mechanism is not formed.   The compressor according to claim 1, wherein at least one notch is formed in an upper end portion of the bearing. In plan view, when divided into an angular range in which the discharge port of the compression mechanism is formed and an angular range in which the discharge port of the compression mechanism is not formed around the central axis of the drive shaft,
The compressor according to claim 4, wherein the notch is formed in an angular range where the discharge port of the compression mechanism is not formed.

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