JPH09158869A - Closed rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To widen a gas discharge channel so as to improve performance efficiency and reduce a noise by forming holes on the side of a valve retainer by which the valve opening of an injection valve is regulated and at least one side of a pair of bearings in a cylinder in which a roller is eccentrically rotatively stored. SOLUTION: In a rotary compression mechanism 4 for which compressor action such as a refrigerant is executed by eccentrically rotating a roller piston 15 in a cylinder chamber 14 accompanying the rotational driving of a rotary shaft 7, for example, a pair of upper and lower widened holes 36, 37 such as circular shapes, are formed on both axial end walls of a cylinder 11 in the vicinity of the free end of a valve retainer 22b near a discharge opening 19. A part of the width of a gas discharge passage on the side of the valve retainer 22b is widened toward both axial, sides of the cylinder 11. Hereby, in the case that discharge gas is going to be led to flow from the side of the free end of the valve retainer 22b toward the root part thereof, its channel resistance is reduced so that performance efficiency can be improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hermetic rotary compressor that houses a rotary compression mechanism and an electric motor for driving the rotary compression mechanism in a hermetic case.

[0002]

2. Description of the Related Art In recent years, an example of this type of hermetic rotary compressor is described in the specification and drawings of Japanese Patent Application No. 7-42076. This hermetic rotary compressor is not publicly known, but a cylinder of a rotary compression mechanism housed in a hermetic case to eccentrically and rotatably accommodate a roller to compress a gas such as a refrigerant, and this cylinder. A discharge chamber that communicates with the chamber in the radial direction through the communication portion and discharges the gas compressed in the cylinder chamber is formed, and a discharge port that communicates the discharge chamber with the cylinder chamber is formed in the communication portion. A thin metal valve seat plate is fixed.

The valve seat plate is provided with a discharge valve that opens and closes the discharge port according to the pressure of the compressed gas, and a valve retainer that regulates the maximum opening of the discharge valve. Nickel (Ni) is contained at 3% by weight. It is made of a steel plate containing the above, or a plate made of a steel plate, the entire surface of which is nickel-plated. Also, the valve seat plate is integrally connected to the casting material and integrally fixed to the cylinder when the cylinder is cast.

[0004]

However, in such a conventional hermetic rotary compressor, the volume of the discharge chamber is limited by the axial thickness of the cylinder, which is thinned for downsizing. In addition, a part of the flow path of the discharge gas flowing into the discharge chamber from the discharge port of the valve seat plate is extremely narrowed by the discharge valve and the valve retainer, and the both axial end walls of the discharge chamber on both sides thereof. Therefore, the flow path resistance is high. For this reason, there is a problem that the flow velocity of the discharged gas increases, the coefficient of performance decreases, and the noise increases.

Therefore, the present invention has been made in consideration of such circumstances, and an object thereof is to improve the performance efficiency and noise by expanding the discharge valve in the discharge chamber and the discharge gas flow passage around the valve retainer. It is an object of the present invention to provide a hermetic rotary compressor that can reduce both of the above.

[0006]

In order to solve the above-mentioned problems, the invention according to a first aspect of the present invention comprises a hermetically sealed case and a housing which is housed in the hermetically sealed case and on which a roller is eccentrically rotatably housed to compress gas. A cylinder forming a cylinder chamber to be driven, and a discharge chamber communicating with the cylinder chamber in the radial direction through the communication portion to discharge the gas compressed in the cylinder chamber, and fixed to the communication portion of the cylinder. A valve seat plate that is formed with a discharge port that communicates the discharge chamber with the cylinder chamber, and that has a discharge valve that opens and closes the discharge port and a valve retainer that regulates the valve opening thereof.
In a hermetic rotary compressor having a pair of bearings that rotatably support a rotating shaft that drives the roller by sandwiching both ends of the cylinder in the axial direction, the cylinder includes a side portion of the valve retainer that is lateral to the valve retainer. A hole is formed on at least one side of the pair of bearings.

Therefore, according to the present invention, since the discharge gas flow passage on the side of the valve retainer can be widened by the amount of the hole of the cylinder, the flow passage resistance is reduced and the flow velocity of the discharge gas is reduced. You can Therefore, it is possible to improve the performance efficiency and reduce the noise.

The invention according to claim 2 is the invention according to claim 1, wherein the hole is a through hole penetrating at least one end side in the axial direction of the cylinder, and a recess communicating with the through hole is formed. It is formed on at least one of the pair of bearings.

Therefore, according to the present invention, since the hole on the side of the valve retainer communicates with at least one hole of the pair of bearings, the discharge gas passage on the side of the valve retainer is further widened by the amount of the recess. Then, the flow path resistance can be further reduced.

Therefore, the flow velocity of the discharged gas can be further reduced, so that the performance efficiency can be further improved and the noise can be further reduced.

[0011] The invention according to claim 3 is the invention according to claim 1 or 2.
In the invention described above, the hole is formed so as to connect both the discharge valve side of the valve retainer and the space on the opposite side.

Therefore, according to the present invention, the discharge gas flowing from the discharge valve of the valve seat plate to the vicinity of the valve retainer of the discharge chamber passes through the hole of the cylinder or the concave portion of the bearing communicating with this hole, and the discharge of the valve retainer is suppressed. It can smoothly flow into the opposite side of the discharge valve.

Therefore, since the flow passage resistance of the discharge gas passage on the side of the valve retainer can be reduced, the flow velocity of the discharge gas flowing through this passage can be reduced. As a result, it is possible to improve both performance efficiency and noise.

The invention according to claim 4 is the invention according to any one of claims 1 to 3, further, the cylinders are laminated in a plurality of stages in the axial direction thereof, and between the cylinders. Through-holes are formed in the interposed partition plate so that the holes of adjacent cylinders communicate with each other.

Therefore, according to the present invention, the invention according to any one of claims 1 to 3 is applied to a twin rotary compressor having a plurality of rotary cylinders, and the same effects as those are obtained. Can play.

A fifth aspect of the invention is the invention according to the fourth aspect, further, the cylinders are arranged such that the positions of the discharge port and the discharge chamber are axially aligned with each other. The through hole of the partition plate and the hole of each cylinder that communicates with the through hole are formed as a communication hole that allows the discharge chambers of adjacent cylinders to communicate with each other.

Therefore, according to the present invention, in, for example, a twin rotary compressor having a plurality of cylinders, the holes of the cylinders on the side of the valve retainer are communicated with the through holes of the partition plate. The discharge gas flow passage on the side of each valve retainer can be further widened by the amount of the through hole.

The invention according to claim 6 is the invention according to claim 4 or 5.
In the invention described above, further, a pair of bearings for sandwiching a plurality of cylinders are each formed with a recess communicating with the hole of each cylinder.

Therefore, according to the present invention, the through holes of the partition plate and the recesses of the pair of bearings are made to communicate with the holes on the side of the valve retainers of the plurality of cylinders, respectively. The discharge gas flow passage on the side of the valve retainer can be widened by the amount corresponding to the hole and each recess of the pair of bearings to reduce the flow passage resistance.

For this reason, the flow velocity of the discharged gas can be further reduced, so that the performance efficiency can be further improved and the noise can be further reduced.

[0021]

FIG. 1 is a block diagram showing an embodiment of the present invention.
This will be described with reference to FIG. 1 to 6, the same or corresponding parts are designated by the same reference numerals.

FIG. 2 is a vertical sectional view of a hermetic rotary compressor according to an embodiment of the present invention, and FIG. 1 is an enlarged view of a main part thereof. In these drawings, the hermetic rotary compressor 1 is, for example, a vertical type. In the closed case 2, the electric motor 3 and the rotary compression mechanism 4 driven by the electric motor 3 are housed vertically.

The electric motor 3 has a stator 5 press-fitted and fixed in the hermetically sealed case 2 and a rotor 6 housed in the stator 5. The rotor 6 has a rotating shaft 7 as an output shaft fixed concentrically in its center hole. The electric motor 3 is electrically connected to a power supply terminal 8 and is rotated by connecting the power supply terminal 8 to a power supply and energizing it.

The rotary compression mechanism 4 rotatably supports the rotary shaft 7 of the electric motor 3 and a pair of upper and lower main bearings 9 and sub-bearings 10 in the figure, and a cast cylinder (which is sandwiched by these bearings 9 and 10 from above and below). The cylinder block 11 and the cylinder block 11 are integrally assembled with a fixing tool such as a tightening bolt 12. The cylinder 11 is fixedly supported by the closed case 2 via the support frame 13, while the support frame 13 is press-fitted into the closed case 2 and fixed by welding or the like.

As shown in FIGS. 1 to 3, the rotary compression mechanism 4 forms a cylinder chamber 14 defined by a cylinder bore in a cylinder 11, and a roller piston 15 is housed in the cylinder chamber 14. ing. The roller piston 15 is fitted onto the outer periphery of the crank portion 7a of the rotary shaft 7, and is eccentrically rotated while rolling in the cylinder chamber 14 as the rotary shaft 7 is driven to perform a compressor action of gas such as refrigerant. It is like this.

As shown in FIG. 3, the rotary compression mechanism 4 is provided with a blade groove 16 extending radially outward from the inner peripheral surface of the cylinder chamber 14. A blade 17 is housed in the blade groove 16 by spring-biasing so that the inner end of the blade 17 slidably presses the outer peripheral surface of the roller piston 15. The blade 17 compresses the inside of the cylinder chamber 14 with the suction side. It is partitioned into the chambers 14a and 14b on the side. A suction port 18 and a discharge port 19 are formed on both sides of the cylinder 11 with the blade groove 16 interposed therebetween.

As shown in FIG. 2, the suction port 18 is connected to an accumulator 21 via a suction pipe 20, and the gas refrigerant separated into gas and liquid in the accumulator 21 is sucked into the suction side chamber 14a of the cylinder chamber 14. It is like this.

The discharge port 19 is communicated with the discharge chamber 23 via a discharge valve mechanism 22 having a discharge valve 22a composed of a reed valve and a valve retainer 22b for controlling the maximum valve opening degree, and the cylinder chamber 14 is compressed. The refrigerant compressed in the side chamber 14b is discharged into the discharge chamber 23. The discharge chamber 23 is shown in FIG.
The cylinder 11 is formed so as to communicate with the cylinder chamber 14 via the communication portion 24 as shown in FIG. Discharge chamber 2
Although the outer peripheral side of 3 is open, this opening is hermetically sealed by the discharge chamber cover 25. The discharge chamber cover 25 is mounted from the outer peripheral side of the cylinder 11 by one-touch by elastic pressing means 26 such as a plate spring made of a plate or a coil spring,
It is hooked on the locking claw of the cylinder 11.

As shown in FIG. 3, the cylinder 11 has an arc-shaped discharge flow passage hole 27 communicating with the discharge chamber 23, and the sub-muffler chamber shown in FIGS. A discharge chamber outlet hole 29 communicating with 28 is formed in the cylinder 11, and a communicating hole 10 communicating with the outlet hole 29 is formed.
The sub-bearing 10 is provided with a.

As shown in FIG. 1, the sub muffler chamber 28 communicates with the main muffler chamber 31 via a communication hole 30 formed in the cylinder 11. The discharge chamber outlet hole 29 and the communication hole 30 are bored in the cylinder 11 so as to be substantially parallel to the cylinder axis, while the main muffler chamber 31 and the sub muffler chamber 28 are attached to the main bearing 9 and the sub bearing 10, respectively, from the outside. Formed by the bearing covers 32 and 33. The bearing covers 32 and 33 are fixed to the main bearing 9 and the sub-bearing 10 by tightening together with tightening bolts 13 and the like.

A discharge port 34 is formed in the main bearing cover 32 so that the compressed gas is discharged into the closed case 2 and further discharged from the discharge pipe 2a to the outside.

Then, as shown in FIG. 3, the cylinder 11
A valve seat plate 35 is fixed to the communication portion 24 of the. Valve seat plate 3
5 is preformed by a thin metal plate, and when the cylinder 11 is molded by casting, the casting material is incorporated into the mold so that the valve seat plate 35 is integrally connected to the casting material, and casting is performed. The plates 35 are joined together. As a result, the valve seat plate 35 is firmly fixed so as to form a part of the inner peripheral surface of the communicating portion 24 of the cylinder 11 (the inner peripheral surface of the cylinder bore) as shown in FIG. The cylinder 11 is manufactured.

The valve seat plate 35 is formed of a thin steel plate having a thickness of, for example, about 0.5 mm to 3 mm. A discharge port 19 is formed in the valve seat plate 35. A discharge valve 22a that opens and closes the discharge port 19 and a valve retainer 22b that controls the maximum valve opening degree are fixed to the valve seat plate 35 by co-fastening or the like. Valve seat plate 3
Reference numeral 5 is a steel plate or a steel plate containing a nickel (Ni) component in an amount of 3 wt% (wt%) or more. The valve seat plate 35 may have a steel plate surface plated with nickel.

When the cylinder 11 with a built-in valve seat plate is molded, a cylinder casting is cast at a molten metal temperature of, for example, about 1450 ° C. The Ni component of the seat plate 35 is melted and fused with the cylinder casting, so that an integral connection with the cylinder casting becomes possible. Therefore, the joint portion of the cylinder casting and the valve seat plate 35 is integrated into a high-strength connection, and the mechanical and physical strengths can be improved, and the valve seat plate built-in cylinder 11 suitable for mass production can be manufactured. It becomes possible to manufacture.

Since the hermetic rotary compressor is constructed as described above, the compression chamber 14 of the cylinder chamber 14 is
When the compressed gas such as the refrigerant compressed in b flows into the discharge chamber 23 from the discharge port 19 as shown in FIG. 3, the arc-shaped gas flow path hole 27 is formed in the discharge chamber 23 as shown by a broken line A in the figure. Since it tries to flow in the circumferential direction toward the outlet 29 of the discharge chamber, as shown in FIG.
(Along the axial direction of the cylinder 11) in the longitudinal direction, but since the axial thickness of the cylinder 11 is thin for downsizing, the discharge gas flow path on the side of the valve retainer 22b. Is very narrow.

Therefore, there is the above-mentioned problem that the flow resistance of the discharge gas flow path on the side of the valve retainer 22b is high and the flow velocity is increased.

Therefore, in this embodiment, as shown in FIGS. 1 and 3, in the vicinity of the free tip portion of the valve retainer 22b in the vicinity of the discharge port 19, for example, a pair of upper and lower circular widened holes 36 in FIG. , 37 are formed on both axial end walls of the cylinder 11, and a part of the width of the discharge gas flow passage on the side of the valve retainer 22b is widened toward both axial sides of the cylinder 11.

The widening holes 36 and 37 are not limited to circular shapes but may be rectangular shapes. However, in the free tip portion of the valve retainer 22b, the space on the discharge valve 22a side and the opposite side (the discharge chamber cover 25).
1) is formed at a position and a size that allow the space of the cylinder 11 to communicate with the space in the radial direction.
Is formed so as to penetrate through a pair of upper and lower end walls.

In FIG. 1, a pair of upper and lower main and sub-bearings 9 and 10 are formed on the inner bottom surfaces of the respective widening holes 3
Circular communication recesses 38 and 39, which communicate with 6 and 37, are formed, and the width of the discharge gas flow path on the side of the free end of the valve retainer 22b is further expanded to both sides in the axial direction of the cylinder 11. By appropriately setting the volumes of the communication recesses 38 and 39, it is possible to provide the effect of a muffler (silence room).

Therefore, according to the embodiment configured as described above, the roller piston 15 of the rotary compression mechanism 4 is eccentrically rotated while rolling in the cylinder chamber 14 by the rotation of the rotary shaft 7 of the electric motor 3. As a result, a gas such as a refrigerant is sucked into the suction chamber 14a of the cylinder chamber 14 from the suction port 18, while a gas such as a refrigerant is compressed in the compression chamber 14b in the cylinder chamber 14.

When the pressure of the compressed gas rises above a predetermined pressure, the pressure pushes the discharge valve 22a against the elastic force to open the discharge port 19, and the discharge port 22 opens into the discharge chamber 23. To do.

Further, as shown in FIG. 4, this discharge gas tends to flow in the longitudinal direction from the side of the free front end of the valve retainer 22b near the discharge port 19 toward its root.
Since the discharge gas flow passage on the side of the free tip portion of the valve retainer 22b is widened by the widening holes 36, 37 and the communication recesses 38, 39, the flow passage resistance is reduced and the flow velocity of the discharge gas is reduced. It Therefore, the performance efficiency is improved and the noise is reduced. Further, in the cylinder 11, since the widened holes 36 and 37 are only locally formed at the free front end portion of the valve retainer 22b, the thickness of both axial end walls of the cylinder 11 is sufficiently secured and mechanically secured. The strength can be secured.

After that, the discharge gas is an arc-shaped gas passage 27.
1 through the discharge chamber outlet hole 29 on the bottom surface thereof, and then into the sub muffler chamber 28 shown in FIG. 1, and then through the communication hole 30 and the main muffler chamber 31 sequentially and then discharged from the discharge port 34 into the closed case 2 once. Further, it is discharged from the discharge pipe 2a to the outside.

FIG. 5 is a longitudinal sectional view of a second embodiment in which the present invention is applied to a twin rotary type hermetic compressor 1A,
FIG. 6 is a front view of the main part thereof. The compressor 1A has a pair of upper and lower rotary cylinders 11 of substantially the same shape and size.
A and 11B are laminated concentrically in the axial direction, a partition plate 40 is interposed between both cylinders 11A and 11B, and the two cylinders 11A and 11B are partitioned from each other and applied to a twin rotary type compressor. Other than that, the configuration is almost the same as that of the compression mechanism 4 of the hermetic rotary compressor 1 according to the first embodiment shown in FIGS. Are attached with the same symbols, and the upper and lower cylinders 11
The same symbol A or B as A and 11B is added to indicate the affiliation, while the duplicate description is omitted or simplified.

This hermetic rotary compressor 1A
As shown in FIG. 6, a partition plate 40 is formed with a widening communication hole 41 that communicates with the widening holes 37 and 36 of the pair of upper and lower cylinders 11A and 11B, respectively, so as to penetrate in the plate thickness direction. It is characterized in that the discharge chambers 23A and 23B are communicated with each other in the axial direction.

Further, as shown in FIG.
Discharge chamber communicating hole 42 for communicating the discharge chamber outlet hole 29A of the upper cylinder 11A with the discharge chamber 23B of the lower cylinder 11B.
And a pair of upper and lower crank portions 7aA, 7 of the rotary shaft 7.
An insertion hole 43 for rotatably inserting the connecting portion 7b connecting the aBs and a communication hole 44 for connecting the communication holes 30A, 30B of the upper and lower cylinders 11A, 11B are provided.

Therefore, according to this embodiment, although two compression mechanisms 4A and 4B are provided, the operation is almost the same except that the compression operation by the compression mechanism 4 according to the first embodiment is performed in two stages. The description is omitted because it is the same. However, in the present embodiment, as shown in FIG. 6, the width of the discharge gas passage on the side of the free front end of the pair of upper and lower valve retainers 22bA and 22bB in the drawing is set to the depth of the widening communication hole 41 of the partition plate 40. Since the volume of the muffler chamber is increased by the amount corresponding to the volume of the widened communication hole 41, the efficiency of performance and the reduction of discharge noise can be further improved.

In this embodiment, the twin type in which the two rotary compression mechanisms 4A and 4B are provided in two stages in the vertical direction has been described, but the present invention may also be applied to one having three or more compression mechanisms. Can be applied.

The rotary compressor having three rotary type compression mechanisms may have a multi-stage compression structure. For example, the rotary type compression mechanism at the center in the axial direction
It is also possible to configure a stage compressor and to configure the second stage compressor by rotary type compression mechanisms on the upper and lower sides thereof.
In this case, the discharge refrigerant compressed by the central rotary compression mechanism and discharged to the discharge chamber may be guided to the suction side of the rotary compression mechanism on the upper and lower sides.

In each of the embodiments of the present invention, the example of the vertical rotary compressor has been described, but the present invention is not limited to this, and the rotary compressor may be a horizontal compressor.

[0051]

As described above, according to the rotary compressor of the first aspect of the present invention, the discharge gas passage on the side of the valve retainer can be widened by the amount corresponding to the hole of the cylinder. The flow path resistance can be reduced and the flow velocity of the discharge gas can be reduced. For this reason, it is possible to improve the performance efficiency and reduce the noise.

According to the second aspect of the present invention, since the hole on the side of the valve retainer is communicated with at least one hole of the pair of bearings, the discharge gas flow passage on the side of the valve retainer by the recessed portion. Can be further widened to further reduce the flow path resistance.

Therefore, the flow velocity of the discharged gas can be further reduced, so that the performance efficiency can be further improved and the noise can be further reduced.

According to the third aspect of the present invention, the discharge gas flowing from the discharge valve of the valve seat plate into the vicinity of the valve retainer of the discharge chamber passes through the hole of the cylinder or the recess of the bearing communicating with this hole, It is possible to smoothly flow into the side opposite to the discharge valve of the valve retainer.

Therefore, since the flow passage resistance of the discharge gas passage on the side of the valve retainer can be reduced, the flow velocity of the discharge gas flowing through this passage can be reduced. As a result, it is possible to improve both performance efficiency and noise.

According to the invention described in claim 4, the invention described in any one of claims 1 to 3 is applied to a twin rotary compressor having a plurality of rotary cylinders, and the same as those described above. It is possible to obtain the action and effect.

According to the fifth aspect of the present invention, in, for example, a twin rotary compressor having a plurality of cylinders, the holes of the cylinders on the side of the valve retainer communicate with the through holes of the partition plate. The discharge gas flow passage on the side of each valve retainer can be further widened by the amount of the through hole of the partition plate.

According to the sixth aspect of the present invention, the through holes of the partition plate and the recesses of the pair of bearings communicate with the holes on the side of the valve retainers of the plurality of cylinders. The flow passage resistance can be reduced by widening the discharge gas flow passage on the side of the valve retainer by the amount corresponding to the through hole of the plate and the concave portions of the pair of bearings.

For this reason, the flow velocity of the discharged gas can be further reduced, so that the performance efficiency can be further improved and the noise can be further reduced.

[Brief description of the drawings]

1 is a sectional view of a rotary type compression mechanism incorporated in the rotary compressor of FIG.

FIG. 2 is a vertical cross-sectional view showing the entire first embodiment of the rotary compressor according to the present invention.

FIG. 3 is a plan view of a valve seat plate built-in cylinder of the rotary compression mechanism in FIGS.

FIG. 4 is a view taken in the direction of arrow IV in FIG. 3;

FIG. 5 is a sectional view of a twin rotary type compression mechanism of a second embodiment of the rotary compressor according to the present invention.

FIG. 6 is a front view of a pair of upper and lower valve retainers shown in FIG. 5 and its peripheral portion.

[Explanation of symbols]

1, 1A Hermetic rotary compressor 2 Hermetic case 3 Electric motor 4, 4A, 4B Rotary compression mechanism 5 Stator 6 Rotor 7 Rotating shaft 7a, 7b Crank part 9 Main bearing 10 Sub-bearing 11, 11A, 11B Cylinder (valve seat plate) Built-in cylinder) 14 Cylinder chamber (compression chamber) 15 Roller piston 16 Blade groove 17 Blade 18 Suction port 19 Discharge port 21 Accumulator 22 Discharge valve mechanism 22a, 22aA, 22aB Discharge valve 22b, 22bA, 22bB Valve retainer 23, 23A, 23B Discharge chamber 28 Sub muffler chamber 29, 29A, 29B Discharge chamber outlet hole 31 Main muffler chamber 33, 34 Bearing cover 35, 35A, 35B Valve seat plate 36, 37 Pair of widening holes 38, 39 Pair of communicating recesses 40 Partition plate 41 widening Communication hole

Claims (6)

[Claims] 1. A hermetically sealed case, a cylinder chamber which is housed in the hermetically sealed case and eccentrically rotatably accommodates a roller to compress gas, and is communicated with the cylinder chamber in a radial direction via a communicating portion. A cylinder forming a discharge chamber for discharging compressed gas in the lever chamber, and a discharge port fixed to the communication portion of the cylinder for connecting the discharge chamber to the cylinder chamber, A valve seat plate having a discharge valve for opening and closing the discharge port and a valve retainer for regulating the valve opening degree, and a rotary shaft for rotatably supporting the roller by sandwiching both axial ends of the cylinder. In a hermetic rotary compressor having a pair of bearings, which are located at a side of the valve retainer and at least one of the pair of bearings. At hermetic rotary compressor, characterized in that the formation of the hole. 2. The hermetic rotary compressor according to claim 1, wherein the hole is a through hole penetrating at least one end side in the axial direction of the cylinder, and a recess communicating with the through hole is formed in at least one of the pair of bearings. A hermetic rotary compressor characterized by being formed into a. 3. The hermetic rotary compressor according to claim 1, wherein the hole is formed so as to connect the discharge valve side of the valve retainer and the space opposite to the discharge valve side. Type rotary compressor. 4. The hermetic rotary compressor according to any one of claims 1 to 3, wherein the cylinders are stacked in a plurality of stages in the axial direction, and the partition plates interposed between the cylinders are stacked. The hermetic rotary compressor is characterized in that a through hole that connects the holes of adjacent cylinders to each other is formed. 5. The hermetic rotary compressor according to claim 4, wherein the cylinders are arranged such that the positions of their discharge ports and discharge chambers are axially aligned with each other, and the cylinders have through-holes. A hermetic rotary compressor characterized in that a hole of each cylinder communicating with the through hole is formed as a communication hole for communicating the discharge chambers of the adjacent cylinders. 6. The hermetic rotary compressor according to claim 4 or 5, wherein a pair of bearings holding a plurality of cylinders are formed with recesses communicating with the holes of each cylinder. Type rotary compressor.