JP2021080906A - Rotary compressor - Google Patents

Abstract

To obtain a rotary compressor that can reduce noise generated from a discharge valve, reduce cost, and also reduce an oil rate.SOLUTION: A rotary compressor 1 comprises a closed container 2, a cylinder 8 provided in the closed container 2, an upper bearing 6 provided on an upper side of the cylinder 8, and a lower bearing 7 provided on a lower side of the cylinder 8. The rotary compressor also comprises: a discharge port 13 formed in the upper bearing 6, and for discharging gas compressed in the cylinder 8; a discharge valve 16 for opening/closing the discharge port 13, and provided in a valve housing space 17 formed inside the upper bearing 6; and a discharge flow passage 20 formed inside the upper bearing 6, formed in a radial direction from the valve housing space 17, and opened to an inner surface of the closed container.SELECTED DRAWING: Figure 1

Description

The present invention relates to a rotary compressor used in a refrigerating cycle such as an air conditioner or a refrigerator, and more particularly to a rotary compressor designed to reduce noise.

Noise reduction is a major issue for rotary compressors. A discharge valve is fixed to the upper bearing, lower bearing, or cylinder that constitutes the compression mechanism of the rotary compressor by a retainer. Noise is generated by the intermittent operation of this discharge valve, and reduction of the noise generated from this discharge valve is particularly required.

In order to reduce this noise, conventionally, as described in Japanese Patent Application Laid-Open No. 8-232877 (Patent Document 1), an iron discharge cover (bearing cover) is provided on the upper bearing and the lower bearing. The gas discharged from the compression chamber is allowed to flow through the discharge cover to attenuate the sound.

Japanese Unexamined Patent Publication No. 8-232877

In the above-mentioned Patent Document 1, a discharge cover is required to form a discharge flow path and reduce noise, which causes a problem that the cost of the compressor increases.

Further, in the above-mentioned Patent Document 1, the separation of the oil contained in the discharged gas is not described, and consideration is given to reducing the oil discharged from the compressor during the refrigeration cycle, that is, reducing the oil rate. Nor.

An object of the present invention is to obtain a rotary compressor capable of reducing noise generated from a discharge valve, reducing costs, and reducing an oil rate.

In order to achieve the above object, the present invention provides a closed container, a cylinder provided in the closed container, an upper bearing provided on the upper side of the cylinder, and a lower bearing provided on the lower side of the cylinder. The rotary compressor is provided in a discharge port formed in the upper bearing to discharge the compressed gas in the cylinder and a valve storage space formed inside the upper bearing while opening and closing the discharge port. It is characterized by including a discharge valve formed inside the upper bearing, and a discharge flow path formed in the radial direction from the valve storage space and opening to the inner surface of the closed container.

According to the present invention, there is an effect that it is possible to obtain a rotary compressor capable of reducing the noise generated from the discharge valve, reducing the cost, and reducing the oil rate.

The vertical sectional view which shows Example 1 of the rotary compressor of this invention. FIG. 1 is a cross-sectional view taken along the line II-II of FIG. FIG. 5 is an enlarged cross-sectional view of the upper bearing shown in FIG. 1 and shows a state in which the discharge valve is closed. FIG. 5 is an enlarged cross-sectional view of the upper bearing shown in FIG. 1 and shows a state in which the discharge valve is open. It is a figure which shows the modification 1 of Example 1, and is the figure which corresponds to FIG. FIG. 5 is a cross-sectional view showing a modified example 2 of the first embodiment, as viewed from the direction of the VI-VI line of FIG. The plan view of the rotary compressor shown in FIG. FIG. 6 is a cross-sectional view taken along the line VIII-VIII of FIG. The vertical sectional view which shows Example 2 of the rotary compressor of this invention. FIG. 9 is a cross-sectional view taken along the line XX of FIG.

Hereinafter, specific examples of the scroll compressor of the present invention will be described with reference to the drawings. In each figure, the parts with the same reference numerals are the same or corresponding parts.

Example 1 of the rotary compressor of the present invention will be described with reference to FIGS. 1 to 4. FIG. 1 is a vertical sectional view showing Example 1 of the rotary compressor of the present invention, FIG. 2 is a sectional view taken along line II-II of FIG. 1, and FIG. 3 is an enlarged sectional view showing the upper bearing shown in FIG. FIG. 4 is a cross-sectional view showing an enlarged upper bearing shown in FIG. 1, showing a state in which the discharge valve is closed, and is a view showing a state in which the discharge valve is open.
First, the overall configuration of the rotary compressor of the first embodiment will be described with reference to FIG. This rotary compressor is used in a refrigerating cycle of an air conditioner, a refrigerator, or the like.

The rotary compressor 1 is vertically configured, and a motor 3 is housed in the upper part of the closed container 2, and a rotary type compression mechanism 4 driven by the motor 3 is housed in the lower part of the closed container 2. There is. The electric motor 3 includes a stator 3a that is press-fitted into the closed container 2 and fixed, and a rotor 3b that is housed on the inner peripheral side of the stator 3a. A crankshaft 5 is integrally fixed to the center of the rotor 3b, and the crankshaft 5 is rotatably supported by an upper bearing 6 and a lower bearing 7 constituting the compression mechanism portion 4. The electric motor 3 is rotationally driven by connecting the power supply terminal 10 to a power source and energizing the electric motor 3.

The upper bearing 6 and the lower bearing 7 constituting the compression mechanism portion 4 are arranged so as to sandwich a cast cylinder (cylinder block) 8 from both sides, and the upper bearing 6 is provided with a fixture such as a tightening bolt 9. The bearing 6, the lower bearing 7, and the cylinder 8 are integrally assembled.

A cylinder chamber 11 is formed in the cylinder 8 of the compression mechanism unit 4, and a roller 12 is housed in the cylinder chamber 11. The roller 12 is arranged in the crank portion 5a of the crankshaft 5, and is eccentrically rotated while rolling in the cylinder chamber 11 as the crankshaft 5 is rotationally driven to perform a compression operation.

The cylinder 8 of the compression mechanism unit 4 is formed with a vane groove (not shown) extending in the outer diameter direction from the inner peripheral surface of the cylinder chamber 11, and the vane (not shown) is formed in the vane groove in the roller. It is accommodated by being urged by a valve spring so as to press the twelve. The inside of the cylinder chamber 11 is divided into a suction chamber and a compression chamber by this vane. A suction port (see the suction port 31 in FIG. 6) is formed in the cylinder 8 so as to communicate with the suction chamber, and a discharge port 13 is formed in the upper bearing 6 so as to communicate with the compression chamber.

The suction port described above is connected to the accumulator 15 via a suction pipe 14, and the gas refrigerant separated by the accumulator 15 is sucked into the suction chamber of the cylinder chamber 11.

The discharge port 13 is formed in the upper bearing 6 and discharges the compressed gas in the cylinder. The discharge port 13 is opened and closed by the discharge valve 16. That is, a valve storage space 17 is formed inside the upper bearing 6, and the discharge valve 16 is provided in the valve storage space 17 so as to open and close the discharge port 13.

Further, a valve retainer 19 that closes the valve storage space 17 opposite to the discharge port 13 and presses the discharge valve 16 via a spring member (spring) 18 is also provided. The spring member 18 is fixed to the convex portion formed in the center of the lower part of the valve retainer 19 by press fitting, and is not fixed by another member such as a screw or a rivet.

Further, in this embodiment, a discharge flow path 20 having a circular cross section, which is formed in the radial direction from the valve storage space 17 and opens to the inner surface of the closed container 2, is formed inside the upper bearing 6.

A refueling hole 22 provided with a refueling pump 21 is provided at the lower end of the crankshaft 5, and sucks up the oil stored in the oil sump 23 at the bottom of the closed container 2 so that the crank portion 5a and the roller 12 are brought into contact with each other. It is configured to lubricate the sliding parts. Reference numeral 24 denotes a discharge pipe that discharges the gas refrigerant compressed by the compression mechanism unit 4 and discharged into the closed container 2 into a refrigeration cycle of an air conditioner or the like.

When the rotary compressor 1 is driven, the refrigerant from the refrigeration cycle flows into the accumulator 15 to separate the gas and liquid, and the gas refrigerant is sucked into the cylinder chamber 11 of the compression mechanism unit 4 via the suction pipe 14. After being compressed by the roller 12, the discharge valve 16 is pushed up from the discharge port 13 and discharged to the valve storage space 17. The compressed refrigerant gas passes through the discharge flow path 20 formed in the radial direction from the valve storage space 17 and collides with the inner wall surface of the closed container 2. As a result, the refrigerant gas and the oil are separated, the separated oil is stored in the oil sump 23, and the compressed refrigerant gas from which the oil is separated is discharged into the closed container 2 and rises while cooling the electric motor 3. The oil is discharged into the refrigeration cycle from the discharge pipe 24 provided on the upper part of the closed container 2.

FIG. 2 is a cross-sectional view taken along the line II-II of FIG. 1, and the portion with the same reference numeral as that of FIG. 1 is the same portion. Further, FIG. 2 shows a plan sectional view cut at a portion of the discharge flow path 20 in the upper bearing 6.

The upper bearing 6 is fixed to the inner peripheral surface of the closed container 2 by means such as press fitting. As shown in FIG. 2, a valve storage space 17 for accommodating the discharge valve 16 is provided inside the upper bearing 6, and a discharge flow path communicating the valve storage space 17 with the inner peripheral surface side of the closed container 2. 20 is formed in the upper bearing 6 in the radial direction. A flow path expanding portion 25 is formed on the outer peripheral surface of the upper bearing 6 at the end of the discharge flow path 20 on the side of the closed container 2, and the refrigerant gas and oil flowing out of the discharge flow path 20 are collected from the flow path expanding portion 25. It collides with the inner wall surface of the closed container 2 and is turned downward. At this time, the oil is separated from the refrigerant gas, falls along the inner wall surface of the closed container 2, and collects in the oil sump 23 shown in FIG.

On the other hand, the refrigerant gas separated from the oil flows downward, flows to the motor 3 side through the passage 26 (see FIG. 1) formed in the cylinder 8 and the passage 27 formed in the upper bearing 6, and is discharged. It is discharged from the pipe 24. In addition, in FIG. 2, a plurality of the passages 27 are provided in the circumferential direction, and also serve to flow the oil accumulated in the upper bearing 6 to the oil reservoir 23 side. Further, 9 is a tightening bolt, and 28 is a leg portion provided on the outer periphery of the lower portion of the closed container 2 at equal intervals.

Next, the configuration in the vicinity of the discharge valve 16 and the discharge flow path 20 will be described in detail with reference to FIGS. 3 and 4, which are enlarged cross-sectional views of the upper bearing 6 shown in FIG. FIG. 3 is a diagram showing a state in which the discharge valve is closed, and FIG. 4 is a diagram showing a state in which the discharge valve is open.

As shown in FIGS. 3 and 4, the upper bearing 6 is formed with a valve hole 29 that penetrates the upper bearing 6 in the axial direction, and the cylinder chamber 11 (see FIG. 1) side of the valve hole 29 is said to have a valve hole 29. A valve seat 13a forming the discharge port 13 is provided. The discharge valve 16 is arranged in the portion of the valve seat 13a, and the discharge valve 16 is provided in a valve storage space 17 formed by the valve hole 29.

On the side of the valve storage space 17 opposite to the discharge port 13, a valve retainer 19 is provided by means such as press-fitting or screwing so as to close the valve hole 29, and the discharge valve 16 is provided in the valve retainer 19. The spring member 18 that presses against the valve seat 13a is provided. The spring member 18 is composed of a coil spring or the like, and is attached to the valve retainer 19 by means such as press fitting.

Further, inside the upper bearing 6, a discharge flow path 20 formed in the radial direction from the valve storage space 17 and opening to the inner surface of the closed container 2 is provided. The end portion of the discharge flow path 20 on the closed container 2 side is a flow path expansion portion 25 having an enlarged flow path cross-sectional area, and is configured so that the oil contained in the refrigerant gas can be easily separated. Further, the flow path expanding portion 25 opens in the direction of the lower oil sump 23.

Reference numeral 27 is a passage through which the refrigerant gas or oil passes, 30 is a notch for reducing one-sided contact with the upper bearing 6 of the crankshaft 5 (see FIG. 1), and 38 is the upper bearing 6 in the closed container 2. It is a plug welding for fixing.

The discharge port 13 is formed so as to open into a compression chamber near the vane in the cylinder chamber 11. When the crankshaft 5 rotates and the refrigerant gas in the compression chamber is compressed by the roller 12 (see FIG. 1), the pressure in the compression chamber gradually increases. When the differential pressure between the pressure in the compression chamber and the pressure in the valve storage space 17 is smaller than the pressing force of the spring member 18, the discharge valve 16 is seated on the valve seat 13a as shown in FIG. The pressure in the compression chamber continues to rise as the crankshaft 5 rotates.

When the force pushing up the discharge valve 16 due to the differential pressure between the pressure in the compression chamber and the pressure in the valve storage space 17 becomes larger than the pushing pressure of the spring member 18, as shown in FIG. 4, the discharge valve 16 It is pushed up against the pushing pressure of the spring member 18. As a result, the refrigerant gas in the compression chamber and the oil contained in the refrigerant gas are discharged from the discharge port 13 into the valve storage space 17 as shown by the broken line arrow in FIG. 4, from which the discharge flow path 20 is radially oriented. It flows, flows into the flow path expanding portion 25, and collides with the inner wall surface of the closed container 2.

When the refrigerant gas and the oil collide with the inner wall surface of the closed container 2 at the flow path expanding portion 25, the refrigerant gas is turned downward and decelerated, and the oil has a higher density than the gas, so that the closed container 2 After colliding with the inner wall surface, it flows downward along the inner wall surface of the closed container. By this action, the oil is separated from the refrigerant gas. The refrigerant gas from which the oil is separated and flows downward passes through the passage 26 (see FIG. 1) of the cylinder 8, passes through the lower bearing 7 and the outer peripheral side of the cylinder 8, and then the motor 3 from the passage 27 formed in the upper bearing 6. It flows to the side and is discharged from the discharge pipe 24 (see FIG. 1) into the refrigeration cycle.

As described above, the rotary compressor 1 of the present embodiment opens and closes a discharge port 13 formed in the upper bearing 6 and discharges the compressed gas in the cylinder 8, and opens and closes the discharge port 13 and also opens and closes the upper bearing 6. A discharge valve 16 provided in the valve storage space 17 formed inside the valve, and a discharge flow formed inside the upper bearing 6 and formed in the radial direction from the valve storage space 17 and opening to the inner surface of the closed container 2. Since the road 20 is provided, the following effects can be obtained.
(1) Since the refrigerant gas containing oil passes through the discharge flow path 20 and then collides with the inner wall surface of the closed container 2 of the rotary compressor 1, the direction is changed downward. After colliding with the closed container 2, the contained oil flows down along the inner wall surface thereof, and the effect of separating the oil from the redirected refrigerant gas can be obtained. Therefore, the ratio of the oil discharged from the discharge pipe 24 to the refrigeration cycle, that is, the oil rate can be reduced, and the oil required for the oil sump 23 can be stored, so that the reliability of the compressor can be improved. Further, since the amount of oil released into the refrigeration cycle can be reduced, it is possible to prevent the oil from adhering to the heat exchanger or the like and lowering the heat exchange efficiency.
(2) Since the discharge valve 16 is arranged inside the upper bearing 6, the sound of hitting the valve seat 13a due to the opening and closing of the discharge valve 16 is blocked by the valve retainer 19 and is less likely to leak to the outside. Further, the noise when the compressed refrigerant gas discharged from the cylinder chamber 11 passes through the discharge flow path 20 can also be reduced because the discharge flow path is formed inside the upper bearing 6. Therefore, it is possible to realize a rotary compressor that can reduce noise.
(3) In the conventional rotary compressor as shown in Patent Document 1, a discharge cover is provided so as to form a discharge flow path and project from the outer peripheral surface of the upper bearing or the lower bearing in order to reduce noise. In this embodiment, since this discharge cover can be abolished, the effect that the rotary compressor can be manufactured at low cost can be obtained.

In the above-described embodiment, all the refrigerant gas that flows out from the discharge flow path 20 and collides with the inner wall surface of the closed container 2 at the flow path expansion portion 25 is configured to change direction downward and flow. The enlarged portion 25 may be configured not only to open downward but also to open upward. In this way, a part of the refrigerant gas from the discharge flow path 20 can be turned upward by the flow path expanding portion 25 and flowed to the motor chamber 39 side where the motor 3 is provided.
(Modification example 1)
Next, a modification 1 in the first embodiment of the rotary compressor of the present invention will be described with reference to FIG. FIG. 5 is a diagram corresponding to FIG. 2, and the portions having the same reference numerals as those in FIGS. 1 to 4 indicate the same or corresponding portions, and mainly the portions different from those in the first embodiment shown in FIGS. 1 to 4. The description will be omitted for the same parts.

In the first embodiment shown in FIGS. 1 to 4 described above, the discharge valve 16 arranged in the valve storage space 17 is formed in a circular shape as shown in FIG. 2, but in the present modification 1, the discharge valve 16 is formed in a circular shape. As shown in 5, the discharge valve 16a is configured to be non-circular. In the first modification, the non-circular discharge valve 16a has a substantially triangular shape, and each side of the triangle has an arc shape bulging in the outer diameter direction.

In the present modification 1, the specific shape of the non-circular discharge valve 16a is shown to be a substantially triangular shape, but the shape is not limited to a triangle, and may be a polygon such as a quadrangle or a pentagon. Further, although an example is shown in which each side of the polygon has an arc shape bulging in the outer diameter direction, each side may be a straight line. Further, the shape of the non-circular discharge valve 16a is not limited to a polygon, and may be configured to be another non-circular shape, for example, an elliptical shape or an oval shape.
Other configurations are the same as those shown in FIGS. 1 to 4.
(Modification 2)
Modification 2 of the rotary compressor of the present invention in Example 1 will be described with reference to FIGS. 6 to 8. 6 is a view seen from the direction of line VI-VI of FIG. 7, FIG. 7 is a plan view of the rotary compressor shown in FIG. 6, and FIG. 8 is a cross-sectional view taken along the line VIII-VIII of FIG. Further, in FIGS. 6 to 8, the parts having the same reference numerals as those in FIGS. 1 to 4 indicate the same or corresponding parts, and the parts different from those in the first embodiment shown in FIGS. 1 to 4 will be mainly described. The description of the same part will be omitted.

In the first embodiment shown in FIGS. 1 to 4 described above, the cross-sectional shape of the discharge flow path 20 is formed in a circular shape, but in the present modification 2, as shown in FIG. 6, the cross-sectional shape of the discharge flow path 20a is , The width (dimension in the compressor circumferential direction) in the discharge flow path 20a is larger than the height (dimension in the compressor axial direction), for example, an elliptical shape. That is, as is clear from a comparison between FIGS. 2 and 8, in the present modification 2, the width of the discharge flow path 20a is larger than that of the discharge flow path 20 of the first embodiment shown in FIG.

Therefore, if the cross-sectional area (flow path area) of the discharge flow path 20 is the same, the axial dimension of the compressor can be made smaller in the present modification 2 as shown in FIG. The effect of reducing the height can be obtained.

In FIG. 6, the member visible inside the discharge flow path 20a is the spring member 18 that presses the discharge valve 16 (see FIG. 3). Further, 31 is connected to a suction pipe 14 (see FIG. 7) by a suction port formed in the cylinder 8. Further, reference numeral 32 denotes a vane that separates the cylinder chamber 11 (see FIG. 1) into a suction chamber and a compression chamber, and the vane 32 is pressed against the roller 12 (see FIG. 1) by the valve spring 33.
Other configurations are the same as those shown in FIGS. 1 to 4.

Example 2 of the rotary compressor of the present invention will be described with reference to FIGS. 9 and 10. In FIGS. 9 and 10, the parts having the same reference numerals as those in FIGS. 1 to 4 indicate the same or corresponding parts. Further, in the description of the second embodiment, the parts different from the first embodiment will be mainly described, and the description of the same parts as the first embodiment will be omitted.

In the first embodiment described above, the discharge valve 16 has no fixed portion, and the discharge port 13 is opened and closed by reciprocating in the axial direction while being pressed by the spring member 18. On the other hand, in the second embodiment, as shown in FIGS. 9 and 10, the discharge valve 34 provided in the valve storage space 17 is composed of a reed valve, and one end side thereof is the operating range of the reed valve. Is fixed by the rivet 36 together with the valve retainer (retainer) 35 provided in the valve storage space. The discharge valve 34 is made of an elastic thin steel plate made of spring steel or the like, and is configured to press the discharge port 13 with the spring force.

Further, in the second embodiment, the cover member 37 is provided so as to close the valve hole 29 on the side of the valve storage space 17 opposite to the discharge port 13. The cover member 37 suppresses the sound of the discharge valve 34 hitting the valve seat 13a and the sound of the refrigerant gas flowing through the valve storage space 17 and the discharge flow path 20 from leaking, as in the first embodiment.
Other configurations are the same as those of Example 1 shown in FIGS. 1 to 4.

The operation of the discharge valve 34 in the second embodiment will be described.
When the crankshaft 5 rotates and the refrigerant gas in the compression chamber is compressed by the roller 12 (see FIG. 1), the pressure in the compression chamber gradually increases. When the differential pressure between the pressure in the compression chamber and the pressure in the valve storage space 17 is smaller than the pressing force of the discharge valve 34, the discharge valve 34 is kept seated on the valve seat 13a. The pressure in the compression chamber continues to rise with the rotation of the crankshaft 5.

When the force pushing up the discharge valve 34 due to the differential pressure between the pressure in the compression chamber and the pressure in the valve storage space 17 becomes larger than the pushing pressure of the discharge valve 34, the discharge valve 34 pushes up against the spring force. Be done. Here, the rise of the discharge valve 34 is limited by the valve retainer 35. As a result, the refrigerant gas in the compression chamber and the oil contained in the refrigerant gas are discharged from the discharge port 13 into the valve storage space 17 in the same manner as described with reference to FIG. It flows and flows into the flow path expanding portion 25, and collides with the inner wall surface of the closed container 2.

When the refrigerant gas and the oil collide with the inner wall surface of the closed container 2 at the flow path expanding portion 25, the refrigerant gas is turned downward and decelerated, and the oil has a higher density than the gas, so that the closed container 2 After colliding with the inner wall surface, it flows downward along the inner wall surface of the closed container. By this action, the oil is separated from the refrigerant gas. The refrigerant gas passes through the passage 26 of the cylinder 8, passes through the lower bearing 7 and the outer peripheral side of the cylinder 8, then flows from the passage 27 formed in the upper bearing 6 to the motor 3 side, and is discharged from the discharge pipe 24 into the refrigeration cycle. Cylinder.
In this way, the second embodiment also operates in the same manner as in the first embodiment, and the same effect as that of the first embodiment can be obtained.

The present invention is not limited to the above-described examples, and includes various modifications. Further, it is possible to replace a part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment.
Furthermore, the above-described examples have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the described configurations.

1: Rotary compressor 2: Closed container 3: Electric motor, 3a: stator, 3b: rotor,
4: Compression mechanism, 5: Crankshaft, 6: Upper bearing, 7: Lower bearing, 8: Cylinder,
9: Tightening bolt, 10: Power supply terminal,
11: Cylinder chamber, 12: Roller, 13: Discharge port, 14: Suction pipe,
15: Accumulator, 16, 16a: Discharge valve, 17: Valve storage space,
18: Spring member, 19: Valve retainer,
20, 20a: Discharge flow path, 21: Refueling pump, 22: Refueling hole, 23: Oil sump,
24: Discharge pipe, 25: Flow path expansion part,
26, 27: passage, 28: leg, 29: valve hole, 30: notch,
31: Suction port, 32: Vane, 33: Valve spring,
34: Discharge valve (reed valve), 35: Valve retainer (retainer), 36: Rivets,
37: Cover member, 38: Plug welding, 39: Motor room.

Claims (15)

A rotary compressor including a closed container, a cylinder provided in the closed container, an upper bearing provided on the upper side of the cylinder, and a lower bearing provided on the lower side of the cylinder.
A discharge port formed on the upper bearing and discharging the compressed gas in the cylinder, and a discharge port.
A discharge valve that opens and closes the discharge port and is provided in a valve storage space formed inside the upper bearing.
A discharge flow path formed inside the upper bearing, formed in the radial direction from the valve storage space, and opened to the inner surface of the closed container.
A rotary compressor characterized by being equipped with. In the rotary compressor according to claim 1,
A rotary compressor characterized in that the pressure in the closed container is configured in a high pressure chamber system having substantially a discharge pressure. In the rotary compressor according to claim 1,
A rotary compressor characterized in that the discharge flow path has a cross-sectional shape having a width larger than a height. In the rotary compressor according to claim 1,
A rotary compressor characterized in that a flow path expansion portion having an enlarged flow path cross-sectional area is provided at the end portion of the discharge flow path on the closed container side. In the rotary compressor according to claim 4,
A rotary compressor characterized in that the flow path expansion portion is configured to open downward. In the rotary compressor according to claim 5,
The flow path expanding portion is configured to open upward, and a part of the refrigerant gas from the discharge flow path is configured to be turned upward by the flow path expanding portion and flowed to the motor chamber side. Rotary compressor. In the rotary compressor according to claim 1,
A rotary compressor comprising a valve retainer that closes the side of the valve storage space opposite to the discharge port and presses the discharge valve via a spring member. In the rotary compressor according to claim 7.
A valve hole that penetrates the upper bearing in the axial direction is formed in the upper bearing, and the valve storage space is formed by the valve hole, and the valve is formed on the side of the valve storage space opposite to the discharge port. A rotary compressor characterized in that the valve retainer is fixed by press fitting or screwing so as to close a hole. In the rotary compressor according to claim 7.
A rotary compressor characterized in that the discharge valve has no fixed portion, and the discharge port is opened and closed by the discharge valve by reciprocating in the axial direction while being pressed by the spring member. In the rotary compressor according to claim 9,
A rotary compressor characterized in that the discharge valve is formed in a circular shape. In the rotary compressor according to claim 9,
A rotary compressor characterized in that the discharge valve is formed in a non-circular shape. In the rotary compressor according to claim 11,
A rotary compressor characterized in that the discharge valve is formed in a polygon and each side of the polygon is arcuate. In the rotary compressor according to claim 7.
A rotary compressor characterized in that the spring member is fixed to the valve retainer by press fitting. In the rotary compressor according to claim 1,
The discharge valve is composed of a reed valve, and one end of the reed valve is fixed by rivets together with a valve retainer provided in the valve storage space while limiting the operating range of the reed valve. A rotary compressor featuring. In the rotary compressor according to claim 14,
A rotary compressor including a cover member that closes the valve storage space on the side opposite to the discharge port.

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