JP3958459B2 - Rotary compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a rotary compressor used for cooling and air conditioning.
[0002]
[Prior art]
Conventionally, a rotary compressor including a rotary compression element that compresses refrigerant gas has been used. First, the structure and operation of a conventional rotary compressor will be described with reference to FIG. As shown in FIG. 10, the rotary compressor 1 includes a sealed casing 50, and the motor 67, the crankshaft 3, and the rotary compression element 49 are incorporated in the sealed casing 50.
[0003]
The crankshaft 3 is press-fitted into the rotor 6 of the motor 67 and drives the rotary compression element 49. The rotary compression element 49 includes a front head 11, a cylinder 5, a rear head 12, a rotary piston 16 and an eccentric part 15. A cylinder chamber 4 is provided inside the cylinder 5, and the refrigerant gas is compressed in the cylinder chamber 4.
[0004]
An oil sump 2 is provided at the lower part of the hermetic casing 50, and the lower end of the crankshaft 3 is introduced into the oil sump 2. Inside the crankshaft 3, an oil passage 3a extends upward from the lower end of the crankshaft 3, and oil passages 3b and 3c branch from predetermined positions of the oil passage 3a. At the top of the oil passage 3a, a gas vent hole 3d is provided for discharging the gas accumulated in the oil passage 3a.
[0005]
In the rotary compressor 1 having the above structure, the refrigerant gas is sent from the suction pipe 18 into the cylinder chamber 4 in the direction indicated by the arrow 300, and the refrigerant gas is compressed by the rotary piston 16 in the cylinder chamber 4. The compressed refrigerant gas passes through the discharge port 11 a provided in the front head 11 so as to face the cylinder chamber 4, and is sent into the muffler 17. The compressed refrigerant gas sent into the muffler 17 is discharged into the primary space 14 from a muffler opening 17 a provided in the muffler 17 in the direction indicated by the arrow 100.
[0006]
In the rotary compressor 1 described above, the oil is gradually sucked up from the oil reservoir 2 in the direction indicated by the arrow 20 by the rotation of the crankshaft 3. The sucked oil is supplied as lubricating oil from the oil passages 3b and 3c to the inside of the cylinder chamber 4 and the bearing portion, as indicated by the arrows 20b and 20c, and the rotation of the rotary sliding portion is made smooth. After being supplied as lubricating oil, the oil that has risen up to the top in the oil passage 3a is discharged as excess oil from the vent hole 3d to the primary space 14 and returns to the oil sump 2 as indicated by the direction of the arrow 20d. Is done.
[0007]
[Problems to be solved by the invention]
In the rotary compressor 1 as described above, while the refrigerant gas is being discharged from the muffler opening 17a to the primary space 14 in the direction indicated by the arrow 100, the region where the refrigerant gas flows is intersected. Excess oil may be discharged in the direction indicated by the arrow 20d from the vent hole 3d. In such a case, surplus oil discharged from the gas vent hole 3d is caught in the refrigerant gas discharged from the muffler opening 17a, passes through the air gap 8 together with the refrigerant gas in the direction indicated by the arrow 200, and 2 Ascending to the discharge pipe 10 through the next space 9. Thereby, the oil in the oil sump 2 is reduced, and the oil supply is hindered. Moreover, since the purity of the compressed refrigerant gas sent from the discharge pipe 10 to the condenser is lowered, the refrigerant supply capability of the rotary compressor is deteriorated.
[0008]
The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a rotary compressor that can suppress a fuel supply hindrance and discharge a high-purity refrigerant gas from a discharge pipe. .
[0012]
[Means for Solving the Problems]
Rotary compressor according to claim 1 of the present invention includes: a closed casing having an oil reservoir, a cylinder chamber for compressing a refrigerant gas introduced from the outside of the closed casing, a refrigerant gas compressed in the cylinder chamber closed casing A compressed refrigerant gas discharge portion that discharges to the space of the cylinder, a rotary drive shaft that passes through the cylinder chamber, an oil passage provided in the rotary drive shaft for supplying oil in the oil reservoir to the rotary slide portion, In order to discharge the gas in the passage, it is provided with a gas vent hole provided in the rotary drive shaft so as to communicate with the space in the closed casing from the oil passage, and when the rotary drive shaft is viewed in cross section, the compressed refrigerant During the discharge timing when the refrigerant gas is discharged from the gas discharge unit, an outlet of the gas vent hole is provided in the outer peripheral region of the rotational drive shaft other than the outer peripheral region of the rotary drive shaft facing the compressed refrigerant gas discharge unit.
[0013]
With the above-described structure, even when surplus oil is discharged from the gas vent hole while the refrigerant gas is being discharged from the compressed refrigerant gas discharge portion, the surplus oil remains in the region where the refrigerant gas is discharged. The risk of being discharged toward the head is reduced. Therefore, the oil discharged from the gas vent hole is restrained from being caught up and raised in the discharged refrigerant gas. As a result, the risk of oil supply hindrance that occurs because the oil does not flow back into the oil reservoir is reduced.
[0014]
Further, together with the refrigerant gas, the risk of surplus oil rising in the direction where there is a discharge pipe for discharging the refrigerant gas from the rotary compressor to the condenser is reduced. As a result, the purity of the refrigerant gas discharged from the discharge pipe is increased.
[0015]
The rotary compressor according to claim 2 is the rotary compressor according to claim 1 , wherein the rotary drive shaft outer periphery is separated from both ends of the rotary drive shaft outer peripheral region by a rotation angle of at least 15 degrees around the rotary drive shaft. In the region, a vent hole outlet is provided.
[0016]
By adopting the above-described structure, the possibility that the excess oil discharged from the vent hole is discharged toward the region where the refrigerant gas is discharged is further reduced. As a result, the risk of the oil discharged from the vent hole being caught up in the discharged refrigerant gas is further suppressed.
[0017]
The rotary compressor according to claim 3 is the rotary compressor according to claim 1 or 2 , wherein the refrigerant gas compressed in the cylinder chamber is discharged to the outside of the cylinder chamber, and discharged from the discharge port. A muffler that receives the refrigerant gas and guides the refrigerant gas from the muffler opening to a space in the casing, and the compressed refrigerant gas discharge part is the muffler opening.
[0018]
With the above-described structure, the relative positional relationship between the discharge port and the muffler opening can be appropriately selected by changing the position of the muffler opening. As a result, the refrigerant gas discharge part, that is, the exhaust gas is discharged from the refrigerant gas discharge part by changing the relative position of the muffler opening and the discharge port without changing the position of the gas vent hole provided in the rotation drive shaft. Interference between the compressed refrigerant gas and excess oil discharged from the vent hole can be suppressed.
[0019]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, a rotary compressor according to an embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 1, the rotary compressor 1 according to the present embodiment includes a motor 67 having a stator 7 and a rotor 6. Further, the rotary compressor 1 includes a rotary compression element 49 having a cylinder chamber 4 for compressing a refrigerant, which is formed by a front head 11, a rear head 12, and a cylinder 5 sandwiched between the front head 11 and the rear head 12. . When the motor 67 is driven, the crankshaft 3 fitted in the rotor 6 rotates as the rotor 6 rotates. In accordance with the rotation of the crankshaft 3, the eccentric portion 15 provided eccentrically with the crankshaft 3 rotates in the cylinder chamber 4.
[0020]
The rotation of the eccentric portion 15 causes the piston 16 to revolve while the inner peripheral surface is in contact with the outer peripheral surface of the eccentric portion 15. At this time, as shown in FIGS. 2 and 3, the rotation of the pair of semicircular bushes 20 embedded in the cylinder 5 and the bushing of the blade 16a partitioning the cylinder chamber 4 into the compression chamber 4a and the suction chamber 4b. The piston 16 revolves due to the reciprocating motion between the two. Further, due to the revolution of the piston 16, the refrigerant gas passing through the refrigerant gas suction pipe 18 through the suction port 18 a and sucked into the cylinder 5 and indicated by the arrow 300 is compressed in the cylinder chamber 4.
[0021]
When the refrigerant gas is compressed in the cylinder chamber 4, the compressed refrigerant gas, which indicates the direction indicated by the arrow 100 in FIG. 1, reaches a predetermined pressure and pushes up the discharge valve 21 provided on the front head 11 to discharge the refrigerant gas. The port 11a is opened and discharged into the space surrounded by the muffler 17 outside the cylinder chamber 4. Thereafter, the refrigerant gas indicating the direction of flow by the arrow 100 is discharged into the primary space 14 in the sealed casing 50 from the muffler opening 17a as the compressed refrigerant gas discharge portion of the present invention.
[0022]
Further, by the rotation of the crankshaft 3, the oil is sucked up from the oil reservoir 2 provided at the lower part of the hermetic casing 50 into the oil passage 3 a provided inside the crankshaft 3 in the direction indicated by the arrow 20. Thereafter, the oil rises in the oil passage 3a and is supplied from the branched oil passages 3b and 3c to the inside of the cylinder chamber 4 and the rotating sliding portions such as the bearing portions in the directions indicated by the arrows 20b and 20c. Further, the oil rises from the oil passages 3b and 3c, and is discharged as surplus oil in the direction indicated by the arrow 20d from the gas vent hole 3d.
[0023]
Next, the structure inside the cylinder chamber 4 of the rotary compressor of the present embodiment will be described with reference to FIGS. FIG. 2 shows a state in which the blade 16a is most fed into the cylinder 5 in the cylinder chamber 4, that is, a state where the piston 16 is at the top dead center position. At this time, the clockwise rotation angle is set with the direction in which the center of the eccentric portion 15 inscribed in the piston 16 is displaced from the center of the crankshaft 3, that is, the eccentric direction indicated by the arrow 15a as the reference direction. FIG. 3 shows a state in which the eccentric direction indicated by the arrow 15 a of the eccentric portion 15 is rotated clockwise by the rotation angle θ from the reference direction indicated by the arrow 30.
[0024]
FIG. 4 shows a rotation angle with respect to the reference direction indicated by the arrow 30 in the direction in which the gas vent hole 3d faces in each of the suction process, the compression process, and the discharge process. Here, the discharge process means a state in which a valve for opening and closing the discharge port 11a is opened. The compression step refers to a state in which the discharge port 11a is closed in a state where the refrigerant gas is compressed after the refrigerant gas has been sucked. The suction process is a process in which only the refrigerant gas is sucked from the end of the discharge process to the start of the compression process.
[0025]
In the present embodiment, in the refrigerant gas discharge process, it is sufficient that the muffler opening 17a is not provided in the direction facing the gas vent hole 3d in plan view. That is, it is only necessary that the muffler opening 17a be provided at a timing when the refrigerant gas is not discharged, in other words, in the suction process or the compression process, that is, in the direction of 90 degrees to 270 degrees in FIG. By setting such a positional relationship, the surplus oil indicated by the arrow 20d discharged from the gas vent hole 3d is not caught in the refrigerant gas discharged from the muffler opening 17a.
[0026]
From another point of view, the following can be considered. As shown in FIG. 5, when the crankshaft 3 is viewed in a cross section, the crankshaft 3 is discharged during the discharge timing when the refrigerant gas is discharged from the compressed refrigerant gas discharge portion 17a, that is, when the refrigerant gas starts to be discharged. A point on the outer periphery of the crankshaft starting to face the refrigerant gas discharge portion 17a is set as a point a, and a point on the outer periphery of the crankshaft where the crankshaft 3 faces the refrigerant gas discharge portion 17a when the discharge of the refrigerant gas is finished. Let b. In this case, when the point b rotates in the direction indicated by the arrow c to the position of the point a, the crankshaft outer peripheral region A faces the compressed refrigerant gas discharge part 17a side. Therefore, the outlet of the gas vent hole 3d may be provided in the crankshaft outer peripheral region B other than the crankshaft outer peripheral region A.
[0027]
In order to more reliably prevent interference between the refrigerant gas indicated by the arrow 100 in FIG. 1 and the surplus oil indicated by the arrow 20d, both ends of the crankshaft outer peripheral region B, that is, the points a and b. It is only necessary to provide the gas vent 3d in the inner region by a rotation angle within x = 15 degrees from each of the above.
[0028]
Therefore, in the present embodiment, as shown in FIG. 6, the phase in the direction indicated by the arrow 20 d is advanced by 90 degrees with respect to the eccentric direction indicated by the arrow 15 a of the eccentric portion 15 that rotates inside the piston 16. The structure is provided with a gas vent hole 3d. Accordingly, surplus oil is discharged from the gas vent 3d in the direction indicated by the arrow 20d at a position advanced by 90 degrees with respect to the eccentric direction indicated by the arrow 15a.
[0029]
When the rotary compressor is operated in the positional relationship between the eccentric portion 15 and the crankshaft 3 as described above, the state in the cylinder chamber 4 from the start to the end of the refrigerant gas discharge process is shown in FIGS. Will be described. 7 to 9 schematically show the state in the cylinder chamber 4 at the start of the discharge process, during the discharge process, and at the end of the discharge process, respectively. 7 to 9, the crankshaft 3 rotates and the piston 16 revolves in the direction indicated by the arrow 15c while being in contact with the inner periphery of the cylinder chamber 4 so that the refrigerant gas is compressed. Due to the pressure of the compressed refrigerant gas, the discharge port 11a is opened from the start to the end of the discharge process shown in FIGS. At this time, simultaneously with the opening of the discharge port 11a, the refrigerant gas is discharged from the muffler opening 17a located on the back side of the crankshaft 3 with respect to the discharge port 11a.
[0030]
Next, the state in each process will be specifically described. In the state of FIG. 7 immediately after the start of the discharge process when the compression process is finished and the discharge port 11a starts to open, the eccentric direction indicated by the arrow 15a is a direction rotated by approximately 180 degrees from the reference direction indicated by the arrow 30; The direction in which excess oil is discharged from the gas vent hole 3d is a direction rotated by 270 degrees from the reference direction, as indicated by the arrow 20d.
[0031]
In the state of FIG. 8 in the middle of the discharge process, the eccentric direction indicated by the arrow 15a is in a direction rotated by approximately 270 degrees from the reference direction indicated by the arrow 30, and the direction in which excess oil is discharged from the gas vent hole 3d is As indicated by the arrow 20d, the direction coincides with the reference direction.
[0032]
In the state of FIG. 9 immediately after the end of the discharge process, the eccentric direction indicated by the arrow 15a coincides with the reference direction, and the direction in which excess oil is discharged from the vent hole 3d is the reference direction as indicated by the arrow 20d. It is in the direction rotated 90 degrees from.
[0033]
In the discharge process shown in FIGS. 7 to 9, the crankshaft outer peripheral region B provided with the gas vent holes 3d other than the crankshaft outer peripheral region A facing the muffler opening 17a in plan view is the muffler opening. Do not face 17a. Therefore, in a plan view, the direction indicated by the arrow 20d in which the excess oil in the oil passage 3a is discharged from the gas vent hole 3d does not intersect the position of the muffler opening 17a. Thereby, the surplus oil discharged in the direction indicated by the arrow 20 is not easily caught in the refrigerant gas discharged from the muffler opening 17a. Therefore, in FIG. 1, the surplus oil whose direction is indicated by the arrow 20d discharged from the gas vent hole 3d passes through the air gap 8 together with the refrigerant gas whose direction is indicated by the arrow 100, and rises in the discharge pipe direction. Is suppressed. As a result, the possibility of the occurrence of oil supply inhibition due to the decrease in the oil in the oil reservoir 2 and the decrease in the purity of the compressed refrigerant gas discharged from the discharge pipe due to the oil mixed into the refrigerant gas are reduced.
[0034]
Note that the structures described in the above embodiments are merely examples, and the present invention is not limited to these structures. For example, in the present embodiment, the compressed refrigerant gas discharge part in the present invention is the muffler opening 17a. However, if the compressed refrigerant gas discharge part is an opening through which the refrigerant compressed in the cylinder chamber 4 flows out, the discharge port 17a itself is the compressed refrigerant. It may be a gas discharge part.
[0035]
【The invention's effect】
According to the rotary compressor of the first aspect of the present invention, there is a reduced risk of oil supply interruption caused by the fact that oil does not recirculate in the oil sump, and the purity of the refrigerant gas discharged from the discharge pipe is increased.
[0036]
According to the rotary compressor of the second aspect , the risk of the oil discharged from the gas vent hole being caught in the discharged refrigerant gas and further rising is further suppressed.
[0037]
According to the rotary compressor of the third aspect , it is possible to change the relative position between the refrigerant gas discharge portion and the gas vent hole without changing the position of the gas vent hole provided in the crankshaft.
[Brief description of the drawings]
FIG. 1 is an enlarged sectional view showing a rotary compression element portion of a rotary compressor according to an embodiment of the present invention.
FIG. 2 shows eccentricity provided eccentrically to a cylinder, a rotary piston, a crankshaft, and a crankshaft when the rotary piston is in a top dead center state among the rotary compression elements of the rotary compressor of the present embodiment. It is an AA line sectional view of Drawing 10 showing a portion.
3 shows a cylinder, a rotary piston, a crankshaft, and an eccentric portion provided eccentrically with respect to the crankshaft in the middle of a discharge process among the rotary compression elements of the rotary compressor of the present embodiment. FIG. FIG.
FIG. 4 shows the rotation angle of the vent hole and the suction, compression, and discharge processes when the eccentric direction with the rotary piston at the top dead center is used as a reference in the rotary compressor of the present embodiment. It is a figure which shows a relationship typically.
FIG. 5 is a schematic diagram for illustrating a crankshaft outer peripheral region facing a muffler opening of the rotary compressor according to the embodiment of the present invention.
FIG. 6 is a view showing a state of a gas outlet hole of a rotary piston, an eccentric part and a crankshaft of a rotary compressor in an embodiment of the present invention.
FIG. 7 is a diagram schematically showing a relationship between a muffler opening and a discharge direction of surplus oil immediately after the start of a discharge process in a cylinder of a rotary compressor according to an embodiment of the present invention.
FIG. 8 is a diagram schematically showing a relationship between a muffler opening and a discharge direction of surplus oil in the middle of a discharge process in a cylinder of a rotary compressor according to an embodiment of the present invention.
FIG. 9 is a diagram schematically showing the relationship between the muffler opening and the discharge direction of excess oil in the cylinder of the rotary compressor according to the embodiment of the present invention immediately after the discharge process is completed.
FIG. 10 is a cross-sectional view showing the overall structure of a conventional rotary compressor.
[Explanation of symbols]
3 Crankshafts 3a, 3b, 3c Oil passage 3d Gas vent hole 4 Cylinder chamber 14 Primary space 17a Muffler opening 20d Direction in which excess oil is discharged 100 Direction in which refrigerant gas is discharged

Claims (3)

A sealed casing (50) having an oil sump (2);
A cylinder chamber (4) for compressing refrigerant gas taken from the outside of the hermetic casing (50);
A compressed refrigerant gas discharge section (17a) for discharging the refrigerant gas compressed in the cylinder chamber (4) to the space (14) in the sealed casing;
A rotary drive shaft (3) passing through the cylinder chamber (4);
An oil passage (3a, 3b, 3c) provided in the rotary drive shaft (3) for supplying the oil in the oil reservoir (2) to the rotary sliding portion;
In order to discharge the gas in the oil passage (3a, 3b, 3c), the rotary drive shaft (3) is communicated from the oil passage (3a, 3b, 3c) to the space (14) in the sealed casing. 3) with a vent hole (3d) provided in
Rotation toward the compressed refrigerant gas discharge part (17a) during the discharge timing when the refrigerant gas is discharged from the compressed refrigerant gas discharge part (17a) when the rotary drive shaft (3) is viewed in a cross section. A rotary compressor in which an outlet of the gas vent hole (3d) is provided in a rotational drive shaft outer peripheral region (B) other than the drive shaft outer peripheral region (A). The rotary drive shaft outer peripheral region (at least 15 degrees or more around the rotary drive shaft (3) from both ends of the rotary drive shaft outer peripheral region (A) facing the compressed refrigerant gas discharge part (17a). in B), the outlet of the vent holes (3d) is provided, the rotary compressor according to claim 1. A discharge port (11a) for discharging the refrigerant gas compressed in the cylinder chamber (4) to the outside of the cylinder chamber (4);
A muffler (17) that receives the refrigerant gas (100) discharged from the discharge port (11a) and guides the refrigerant gas (100) from the muffler opening (17a) to the space (14) in the casing;
The rotary compressor according to claim 1 or 2 , wherein the compressed refrigerant gas discharge section (17a) is the muffler opening.

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