KR20240074140A - Rotary compressor with flat muffler - Google Patents

Abstract

The rotary compressor includes a casing 10, a motor 20 installed inside the casing, a compression unit 40 installed below the motor, a lower flange 92 installed below the compression unit, and a lower flange ( It includes a flat muffler 72 installed on the lower surface of the muffler 92, and a sealing plate 100 installed between the flat muffler 72 and the lower flange 92.

Description

Rotary compressor with flat muffler}

The present disclosure relates to a rotary compressor, and more particularly to a rotary compressor having a flat muffler.

A compressor is a mechanical device that compresses gas to increase pressure. Depending on its operating principle, it can be divided into reciprocating compressors and rotary compressors.

Reciprocating compressors include the Recipro compressor, which sucks and compresses gas by converting the rotational motion of a motor into the linear reciprocating motion of a piston using a crankshaft and connecting rod.

Rotary compressors include rotary compressors and scroll compressors.

A rotary compressor is formed to suck in and compress refrigerant while a roller rotates within the cylinder of the compression unit due to the rotational movement of the motor.

The scroll compressor is formed so that the refrigerant is sucked in and compressed while the orbiting scroll rotates in a certain direction with respect to the fixed scroll by the rotational movement of the motor.

In a rotary compressor, compressed refrigerant is discharged inside the casing and discharged to the outside along with oil through the refrigerant discharge pipe.

A rotary compressor according to an embodiment of the present disclosure includes a casing (10); A motor (20) installed inside the casing; A compression unit 40 installed at the lower part of the motor; a lower flange (92) installed below the compression section; A flat muffler (72) installed on the lower surface of the lower flange (92); and a sealing plate 100 installed between the flat muffler 72 and the lower flange 92.

At this time, the top of the flat muffler 72 may not protrude above the lower surface of the lower flange 92.

Additionally, the flat muffler 72 may be formed in a dome shape. The side of the flat muffler 72 may include a plurality of concave portions 721 formed at regular intervals along the circumferential direction of the flat muffler 72. The sealing plate 100 may be formed in a ring shape. The inner peripheral surface of the sealing plate 100 may be formed to be concave and convex corresponding to the flat muffler 72.

Additionally, the lower flange 92 may include a plurality of lower refrigerant holes and a plurality of first bolt holes formed along the edge. The flat muffler 72 may include a plurality of second bolt holes formed to correspond to the plurality of first bolt holes of the lower flange 92 at positions corresponding to the plurality of recesses 721 along the edge. there is.

In addition, the sealing plate 100 protrudes toward the center from the inner peripheral surface of the sealing plate 100 and has a plurality of third bolt holes corresponding to the plurality of second bolt holes of the flat muffler 72. It may include a bolt location.

Additionally, the sealing plate 100 may be formed not to cover the plurality of lower refrigerant holes of the lower flange 92.

Additionally, the minimum distance between the inner peripheral surface of the sealing plate 100 and the plurality of lower refrigerant holes of the lower flange 92 may be 0.

Additionally, the thickness of the sealing plate 100 may have the following relationship with the thickness of the flat muffler 72.

0.5 ≤ Thickness of sealing plate 100 (Ts)/Thickness of flat muffler 72 (Tm) ≤ 2.0

Additionally, oil is accommodated in the lower part of the casing, and the flat muffler 72 can be submerged in the oil.

Additionally, the sealing plate 100 may be made of one of heat-resistant resin, steel, copper, and a material in which at least two of these are laminated.

In addition, the lower flange 92 includes a flange portion 925 formed in a disk shape; A boss 926 extending vertically from the flange portion 925 and including a through hole; and a bearing 927 installed in the through hole of the boss 926. The flat muffler 72 includes a fixing plate 723 that is fixed to the flange portion 925 of the lower flange 92 and is formed in a ring shape; A caulking portion 724 fixed to one end of the boss; and a muffler portion 725 provided between the fixing plate 723 and the caulking portion.

Additionally, the muffler portion 725 may include a plurality of concave portions 721 formed at regular intervals in the circumferential direction.

Additionally, the fixing plate 723 may include a plurality of protrusions 7231 corresponding to the plurality of concave parts 721 of the muffler part 725.

Additionally, the flange portion 925 of the lower flange 92 may include a plurality of lower refrigerant holes and a plurality of first bolt holes. The plurality of protrusions 7231 of the fixing plate 723 may include a plurality of second bolt holes corresponding to the plurality of first bolt holes.

In addition, the inner circumferential surface of the sealing plate 100 is formed so as not to cover the plurality of bolt seat portions formed to correspond to the plurality of protrusions 7231 of the fixing plate 723 and the plurality of lower refrigerant holes of the flange portion 925. It may include a plurality of refrigerant grooves 103 formed.

1 is a perspective view showing a rotary compressor according to an embodiment of the present disclosure.
FIG. 2 is a cross-sectional view of the rotary compressor of FIG. 1 cut along line AA.
FIG. 3 is a cross-sectional view of the rotary compressor of FIG. 1 taken along line BB.
Figure 4 is a perspective view showing a compression unit of a rotary compressor according to an embodiment of the present disclosure.
Figure 5 is a bottom view of the compression section of the rotary compressor of Figure 4.
Figure 6 is a cross-sectional view cut through the compression portion of the rotary compressor of Figure 4.
Figure 7 is an exploded perspective view of the compression section of the rotary compressor of Figure 4.
Figure 8 is a perspective view showing a flat muffler 72 used in a rotary compressor according to an embodiment of the present disclosure.
FIG. 9 is a perspective view of the flat muffler 72 of FIG. 8 viewed from above.
Figure 10 is a perspective view showing a sealing plate 100 used in a rotary compressor according to an embodiment of the present disclosure.
Figure 11 is a diagram showing a state in which the sealing plate 100 and the flat muffler 72 are installed on the lower flange.
Figure 12 is a bottom view of Figure 11.
FIG. 13 is a bottom view showing the flat muffler 72 in FIG. 11 removed.
Figure 14 is a diagram showing a state in which a portion of the flat muffler 72 is opened due to compressed refrigerant.
FIG. 15 is a graph showing changes in the deformation of the bearing and the opening of the flat muffler 72 according to the thickness of the sealing plate 100.
Figure 16 is a graph showing the rate of change of the energy efficiency of the rotary compressor 1 according to an embodiment of the present disclosure with respect to the energy efficiency of the rotary compressor according to the prior art using a skirt muffler.

Since these embodiments can be modified in various ways and have various embodiments, specific embodiments will be illustrated in the drawings and described in detail in the detailed description. However, this is not intended to limit the scope to specific embodiments, and should be understood to include various modifications, equivalents, and/or alternatives to the embodiments of the present disclosure. In connection with the description of the drawings, similar reference numbers may be used for similar components.

In describing the present disclosure, if it is determined that a detailed description of a related known function or configuration may unnecessarily obscure the gist of the present disclosure, the detailed description thereof will be omitted.

In addition, the following examples may be modified into various other forms, and the scope of the technical idea of the present disclosure is not limited to the following examples. Rather, these embodiments are provided to make the present disclosure more faithful and complete and to completely convey the technical idea of the present disclosure to those skilled in the art.

The terms used in this disclosure are merely used to describe specific embodiments and are not intended to limit the scope of rights. Singular expressions include plural expressions unless the context clearly dictates otherwise.

In the present disclosure, expressions such as “have,” “may have,” “includes,” or “may include” refer to the presence of the corresponding feature (e.g., component such as numerical value, function, operation, or part). , and does not rule out the existence of additional features.

In the present disclosure, expressions such as “A or B,” “at least one of A or/and B,” or “one or more of A or/and B” may include all possible combinations of the items listed together. . For example, “A or B,” “at least one of A and B,” or “at least one of A or B” (1) includes at least one A, (2) includes at least one B, or (3) it may refer to all cases including both at least one A and at least one B.

Expressions such as “first,” “second,” “first,” or “second,” used in the present disclosure can modify various components regardless of order and/or importance, and can refer to one component. It is only used to distinguish from other components and does not limit the components.

In addition, terms such as 'front end', 'rear end', 'top', 'bottom', 'top', and 'bottom' used in the present disclosure are defined based on the drawings, and the shapes and shapes of each component are defined by these terms. Location is not limited.

Hereinafter, an embodiment of a rotary compressor according to the present disclosure will be described in detail with reference to the attached drawings.

Figure 1 is a perspective view showing a rotary compressor 1 according to an embodiment of the present disclosure.

Referring to FIG. 1, a rotary compressor 1 according to an embodiment of the present disclosure may include a casing 10.

The casing 10 forms the exterior of the rotary compressor 1. The casing 10 is formed as a sealed container. The casing 10 may include a refrigerant inlet 13 through which the refrigerant flows and a refrigerant discharge pipe 14 through which the refrigerant is discharged.

The rotary compressor 1 can form a refrigeration cycle with a condenser, expansion valve, and evaporator. In this case, the refrigerant inlet 13 may be connected to an evaporator, and the refrigerant discharge pipe 14 may be connected to a condenser.

An accumulator (3) may be installed on one side of the rotary compressor (1). In this case, the refrigerant inlet 13 may be connected to the accumulator 3. Since the inlet pipe of the accumulator (3) is connected to the evaporator, the refrigerant discharged from the evaporator can flow into the rotary compressor (1) through the accumulator (3).

Casing 10 may include an upper casing 11 and a lower casing 12. The upper casing 11 is coupled to the upper end of the lower casing 12 to form the casing 10.

The joint portion of the upper casing 11 and the lower casing 12 is sealed.

A refrigerant discharge pipe 14 is provided in the upper casing 11. The refrigerant discharge pipe 14 may be provided at the top of the upper casing 11.

A refrigerant inlet 13 is provided in the lower casing 12. The refrigerant inlet 13 communicates with the compression unit 40 installed inside the lower casing 12. Low-temperature/low-pressure refrigerant may flow into the refrigerant inlet 13. Accordingly, the refrigerant may flow into the compression unit 40 through the refrigerant inlet 13.

An accumulator 3 may be installed in the lower casing 12. In this case, the refrigerant inlet 13 may be connected to the discharge pipe of the accumulator 3.

A base 15 supporting the casing 10 may be provided at the bottom of the lower casing 12. The rotary compressor 1 can be installed perpendicular to the support surface by the base 15.

FIG. 2 is a cross-sectional view of the rotary compressor 1 of FIG. 1 taken along line A-A. FIG. 3 is a cross-sectional view of the rotary compressor 1 of FIG. 1 taken along line B-B.

Referring to FIGS. 2 and 3 , the rotary compressor 1 according to an embodiment of the present disclosure may include a casing 10, a motor 20, and a compression unit 40.

The casing 10 forms the exterior of the rotary compressor 1 and is a cylindrical sealed container. The casing 10 may include a lower casing 12 provided with a refrigerant inlet 13 and an upper casing 11 provided with a refrigerant discharge pipe 14.

The casing 10 is formed by combining the upper casing 11 and the lower casing 12, and the inside of the casing 10 except the refrigerant inlet 13 and the refrigerant discharge pipe 14 can be sealed. That is, the refrigerant can flow into or out of the casing 10 only through the refrigerant inlet 13 and the refrigerant discharge pipe 14.

High-pressure refrigerant discharged from the compression unit 40 is accommodated in the internal space of the casing 10, and is discharged to the outside through the refrigerant discharge pipe 14.

An oil reservoir 16 containing oil may be provided in the lower part of the casing 10.

An accumulator 3 may be installed on the outer peripheral surface of the casing 10. At this time, the refrigerant inlet 13 may be connected to the discharge pipe of the accumulator 3.

The motor 20 may be placed on the upper side inside the casing 10. The motor 20 includes a stator 21 and a rotor 22.

The stator 21 of the motor 20 is fixed to the inner peripheral surface of the casing 10. A plurality of oil recovery passages may be provided between the outer peripheral surface of the stator 21 and the inner peripheral surface of the casing 10. A plurality of oil recovery passages may be formed at regular intervals along the outer peripheral surface of the stator 21.

Oil from the upper side of the motor 20 can move to the lower part of the motor 20 through a plurality of oil return passages provided between the stator 21 and the casing 10. Oil moving to the lower part of the motor 20 may be collected in the oil reservoir 16 provided in the lower part of the casing 10.

The rotor 22 may be rotatably disposed at the center of the stator 21. The rotor 22 is installed to maintain a certain gap with the inner surface of the stator 21.

An axial hole 29 may be provided at the center of the rotor 22, penetrating the rotor 22 in the longitudinal direction. A plurality of refrigerant holes 27 may be provided around the shaft hole 29 of the rotor 22. The plurality of refrigerant holes 27 may be formed to penetrate the rotor 22 in the longitudinal direction, that is, in the vertical direction.

The refrigerant discharged from the compression unit 40 at the bottom of the motor 20 may move to the upper part of the motor 20 through the gap between the rotor 22 and the stator 21 and the plurality of refrigerant holes 27.

The drive shaft 30 is inserted and fixed into the shaft hole 29 penetrating the center of the rotor 22. Therefore, when power is applied to the motor 20, the rotor 22 can rotate due to the electromagnetic force acting between the stator 21 and the rotor 22, and the drive shaft 30 is integrated with the rotor 22. can be rotated.

When the drive shaft 30 rotates by the motor 20, the compression unit 40 operates to compress the refrigerant.

The drive shaft 30 may be formed to extend below the motor 20. The lower part of the drive shaft 30 extending below the motor 20 may be connected to the compression portion 40. The lower part of the drive shaft 30 may be formed as a crankshaft to operate the compression unit 40.

The crankshaft of the drive shaft 30 may include two eccentric portions, namely an upper eccentric portion 31 and a lower eccentric portion 32. Therefore, when the drive shaft 30 rotates, the upper eccentric part 31 and the lower eccentric part 32 of the crankshaft rotate integrally with the drive shaft 30.

The upper eccentric portion 31 is formed in a cylindrical shape with a diameter larger than that of the drive shaft 30, and may be provided so that its center line is eccentric with the center line of the drive shaft 30. An upper roller 33 may be installed on the outer peripheral surface of the upper eccentric portion 31.

The lower eccentric portion 32 is installed below the upper eccentric portion 31 and may be formed in the same manner as the upper eccentric portion 31. That is, the lower eccentric portion 32 is formed in a cylindrical shape with a diameter larger than the diameter of the drive shaft 30, and may be provided so that its center line is eccentric with the center line of the drive shaft 30. A lower roller 34 may be installed on the outer peripheral surface of the lower eccentric portion 32.

The lower eccentric portion 32 may be formed to be eccentric in a direction different from the upper eccentric portion 31 with respect to the center line of the drive shaft 30. For example, the lower eccentric portion 32 may be eccentric in a direction opposite to the upper eccentric portion 31 by 180 degrees with respect to the center line of the drive shaft 30.

The drive shaft 30 may be rotatably supported by the upper flange 91 and the lower flange 92. The upper flange 91 is installed to support the drive shaft 30 between the rotor 22 and the upper eccentric part 31, and the lower flange 92 is installed below the lower eccentric part 32 to support the drive shaft 30. It can be installed to support the lower part of the.

The compression unit 40 is installed below the motor 20. The compression unit 40 may be formed to compress the refrigerant according to the rotation of the drive shaft 30 and discharge the refrigerant to the upper side of the compression unit 40.

Hereinafter, the compression unit 40 of the rotary compressor 1 according to an embodiment of the present disclosure will be described in detail with reference to FIGS. 4 to 7.

Figure 4 is a perspective view showing the compression unit 40 of the rotary compressor 1 according to an embodiment of the present disclosure. FIG. 5 is a bottom view of the compression unit 40 of the rotary compressor 1 of FIG. 4. FIG. 6 is a cross-sectional view of the compression portion 40 of the rotary compressor 1 of FIG. 4. FIG. 7 is an exploded perspective view of the compression unit 40 of the rotary compressor 1 of FIG. 4.

The compression unit 40 is installed at the lower part of the casing 10 and is operated by a drive shaft 30 rotated by a motor 20 to suck in, compress, and discharge refrigerant.

Referring to FIGS. 4 to 7 , the compression portion 40 may be installed between the upper flange 91 and the lower flange 92 that rotatably support the drive shaft 30.

The compression unit 40 may include an upper compression unit 41, a lower compression unit 42, and an intermediate plate 70 provided between the upper compression unit 41 and the lower compression unit 42.

The upper compression unit 41 is formed to suck in and compress the refrigerant as the drive shaft 30 rotates. The lower compression unit 42 is provided below the upper compression unit 41 and is formed to suck in and compress the refrigerant as the drive shaft 30 rotates.

The upper compression unit 41 is installed on the upper surface of the middle plate 70 and may include a flat upper cylinder 50. The upper cylinder 50 may include a compression chamber. The compression chamber may be formed as a hollow 51 with a circular cross-section.

The upper roller 33 installed on the upper eccentric portion 31 of the drive shaft 30 may be accommodated in the hollow 51 of the upper cylinder 50 and rotate.

The upper compression unit 41 may include a refrigerant inlet passage 52 connected to the refrigerant inlet 13 provided in the casing 10. The refrigerant inflow passage 52 is formed in the upper cylinder 50.

The refrigerant inflow passage 52 may be formed as a through hole communicating with the hollow 51 of the upper cylinder 50 and the outer peripheral surface. Accordingly, the refrigerant may flow into the hollow 51 of the upper cylinder 50 through the refrigerant inlet 13 and the refrigerant inlet passage 52.

The upper compression unit 41 may include an upper discharge port 501 through which compressed refrigerant is discharged. The upper discharge port 501 may be provided on the upper surface of the upper cylinder 50.

When the upper roller 33 is rotated by the drive shaft 30, the refrigerant flows into the hollow 51 of the upper cylinder 50 through the refrigerant inflow passage 52, and is compressed by the upper roller 33. , can be discharged through the upper discharge port 501.

The lower compression unit 42 is installed on the lower surface of the middle plate 70 and may include a lower cylinder 60 that has a flat plate shape. The lower cylinder 60 may include a compression chamber. The compression chamber may be formed as a hollow 61 with a circular cross-section.

The lower roller 34 installed on the lower eccentric portion 32 of the drive shaft 30 may be installed to rotate while being accommodated in the hollow 61 of the lower cylinder 60.

The lower compression unit 42 may include a refrigerant inlet passage 62 connected to the refrigerant inlet 13 provided in the casing 10. The refrigerant inflow passage 62 is formed in the lower cylinder 60.

The refrigerant inflow passage 62 may be formed as a through hole communicating with the hollow 61 of the lower cylinder 60 and the outer peripheral surface. Accordingly, the refrigerant may flow into the hollow 61 of the lower cylinder 60 through the refrigerant inlet 13 and the refrigerant inlet passage 62.

The lower compression unit 42 may include a lower discharge port through which compressed refrigerant is discharged. The lower discharge port may be provided on the lower surface of the lower cylinder 60. Accordingly, the refrigerant compressed by the lower compression unit 42 may be discharged below the lower compression unit 42 through the lower discharge port.

When the lower roller 34 is rotated by the drive shaft 30, the refrigerant flows into the hollow 61 of the lower cylinder 60 through the refrigerant inflow passage 62 and is compressed by the lower roller 34. , can be discharged through the lower discharge port.

Low-pressure refrigerant can be supplied to the upper compression section 41 and the lower compression section 42 through the accumulator 3.

The middle plate 70 is installed between the upper cylinder 50 and the lower cylinder 60. The middle plate 70 may be formed in a flat shape. Accordingly, the lower cylinder 60, the middle plate 70, and the upper cylinder 50 can be stacked to form the compressed portion 40. The lower cylinder 60, the middle plate 70, and the upper cylinder 50 may be integrally coupled with a plurality of bolts 93.

An upper flange 91 may be installed on the upper surface of the upper cylinder 50. The upper flange 91 may be fixed to the inner peripheral surface of the casing 10. Accordingly, by fixing the upper cylinder 50 to the upper flange 91, the upper cylinder 50 can be fixed to the casing 10.

The upper flange 91 rotatably supports the drive shaft 30 and may be formed to block the upper end of the hollow 51 of the upper cylinder 50.

The upper flange 91 may be provided with an upper through hole communicating with the upper discharge port 501 of the upper cylinder 50. Accordingly, the refrigerant discharged through the upper discharge port 501 of the upper cylinder 50 may be discharged to the upper side of the upper flange 91 through the upper through hole of the upper flange 91.

The upper flange 91 may include an upper discharge valve 911 that opens and closes the upper through hole. Therefore, the upper through hole of the upper flange 91 can be opened and closed by the upper discharge valve 911. When the refrigerant introduced into the upper cylinder 50 is compressed, the upper discharge valve 911 is opened and the refrigerant can be discharged to the upper side of the upper flange 91.

An upper muffler 71 may be installed on the upper side of the upper flange 91. The upper muffler is formed to reduce noise generated by refrigerant discharged through the upper through hole of the upper flange (91).

The upper flange 91 may include a plurality of bolt holes 912 provided along the circumferential direction of the upper flange 91.

The upper flange 91 may include a plurality of upper refrigerant holes 913 provided along the circumferential direction. Refrigerant discharged from the lower cylinder 60 may flow to the upper side of the upper flange 91 through a plurality of upper refrigerant holes.

The upper muffler 71 may include a plurality of refrigerant openings 711 through which refrigerant can pass. The refrigerant that has passed through the upper flange 91 may be discharged into the space between the motor 20 and the compression unit 40 through the plurality of refrigerant openings 711 of the upper muffler 71.

The upper muffler 71 may be provided with a plurality of bolt holes 712 along the edge to correspond to the plurality of bolt holes 912 of the upper flange 91.

A plurality of openings 95 may be provided at the edge of the upper flange 91. A plurality of openings 95 may be formed around the upper muffler 71 installed on the upper flange 91. A plurality of openings 95 may be formed to penetrate the upper flange 91 vertically. Oil can move to the oil reservoir 16 in the lower part of the casing 10 through the plurality of openings 95.

The upper flange 91 may include an upper flange portion 915, an upper boss 916, and an upper bearing 917.

The upper flange portion 915 may be formed in a disk shape. The upper flange portion 915 is formed to cover the opening 51 of the upper cylinder 50. The upper flange portion 915 may be formed to have a diameter corresponding to the inner surface of the casing 10. Accordingly, the upper flange 91 can be fixed to the inner surface of the casing 10.

The upper flange portion 915 may include an upper through hole communicating with the upper discharge port 501 of the upper cylinder 50. Accordingly, the refrigerant discharged through the upper discharge port 501 of the upper cylinder 50 may be discharged to the upper side of the upper flange portion 915 through the upper through hole of the upper flange portion 915.

An upper discharge valve 911 may be provided in the upper through hole of the upper flange portion 915. Accordingly, the upper through hole of the upper flange portion 915 can be opened and closed by the upper discharge valve 911. When the refrigerant flowing into the upper cylinder 50 is compressed above a certain pressure, the upper discharge valve 911 is opened and the refrigerant can be discharged to the upper side of the upper flange portion 915.

The upper boss 916 may extend vertically from the center of the upper flange portion 915. The upper boss 916 may extend vertically upward from the upper flange portion 915. A through hole may be formed in the center of the upper boss 916.

The upper bearing 917 is installed in the through hole of the upper boss 916 and rotatably supports the drive shaft 30. The upper bearing 917 may be any type of bearing as long as it can rotatably support the drive shaft 30. In the present disclosure, a sliding bearing is used as the upper bearing 917.

A plurality of bolt holes 912 and a plurality of coolant holes 913 may be provided in the upper flange portion 915 around the upper boss 916. A plurality of openings 95 may be provided at the edge of the upper flange portion 915 outside the plurality of bolt holes 912.

The upper cylinder 50 may be provided with a plurality of tapped holes 502 corresponding to the plurality of bolt holes 912 of the upper flange portion 915. Additionally, the upper cylinder 50 may include a plurality of coolant holes 503 corresponding to the plurality of upper coolant holes 913 of the upper flange 91.

When the plurality of bolts 94 are fastened to the plurality of tapped holes 502 of the upper cylinder 50, the upper muffler 71 and the upper flange 91 are attached to the upper cylinder 50 by the plurality of bolts 94. It can be fixed.

The refrigerant discharged through the upper through hole of the upper flange 91 passes through the inside of the upper muffler 71, reduces noise, and then passes through the plurality of refrigerant openings 711 of the upper muffler 71. ), that is, it can be discharged into the space between the motor 20 and the compression unit 40.

A lower flange 92 may be installed on the lower surface of the lower cylinder 60. The lower flange 92 rotatably supports the lower end of the drive shaft 30 and may be formed to block the lower end of the hollow 61 of the lower cylinder 60.

The lower flange 92 may be provided with a lower through hole 924 that communicates with the lower discharge port of the lower cylinder 60. Accordingly, the refrigerant discharged through the lower discharge port of the lower cylinder 60 may be discharged to the lower side of the lower flange 92 through the lower through hole 924 of the lower flange 92.

The lower flange 92 may include a lower discharge valve 921 that opens and closes the lower through hole 924. Accordingly, the lower through hole 924 of the lower flange 92 can be opened and closed by the lower discharge valve 921. When the refrigerant flowing into the lower cylinder 60 is compressed above a certain pressure, the lower discharge valve 921 opens and the refrigerant can be discharged to the lower side of the lower flange 92.

A flat muffler 72 may be installed on the lower side of the lower flange 92. The flat muffler 72 is formed to reduce noise generated by refrigerant discharged through the lower through hole 924 of the lower flange 92.

Additionally, the lower flange 92 may be formed so that the refrigerant discharged through the lower through hole 924 is not discharged below the flat muffler 72.

The lower flange 92 may include a plurality of first bolt holes 922 provided along the circumferential direction of the lower flange 92.

The lower flange 92 may include a plurality of lower refrigerant holes 923 provided along the circumferential direction. Refrigerant discharged from the lower through hole 924 of the lower flange 92 may flow to the upper side of the lower flange 92 through the plurality of lower refrigerant holes 923.

Specifically, the plurality of lower refrigerant holes 923 of the lower flange 92 include the plurality of refrigerant holes 603 of the lower cylinder 60, the plurality of refrigerant holes 703 of the middle plate 70, and the upper cylinder 50. ) may be formed to match the plurality of refrigerant holes 503 and the plurality of upper refrigerant holes 913 of the upper flange 91.

Therefore, the refrigerant discharged from the lower through hole 924 of the lower flange 92 is the plurality of lower refrigerant holes 923 of the lower flange 92, the plurality of refrigerant holes 603 of the lower cylinder 60, and the middle plate. Through the plurality of refrigerant holes 703 of 70, the plurality of refrigerant holes 503 of the upper cylinder 50, and the plurality of upper refrigerant holes 913 of the upper flange 91, the upper flange 91 and the upper It can move into the space formed by the muffler 71.

The refrigerant in the space between the upper flange 91 and the upper muffler 71 may move to the upper side of the upper muffler 71 through the plurality of openings 711 of the upper muffler 71.

The flat muffler 72 does not include openings or holes through which refrigerant can be discharged. Accordingly, the refrigerant discharged through the lower through hole 924 of the lower flange 92 may not be discharged through the flat muffler 72 into the oil of the oil reservoir 16 in which the flat muffler 72 is immersed.

The lower flange 92 may include a flange portion 925, a boss 926, and a bearing 927.

The flange portion 925 may be formed in a disk shape. The flange portion 925 is formed to cover the opening 61 of the lower cylinder 60. The flange portion 925 may be formed in a size corresponding to the lower cylinder 60.

The flange portion 925 may include a lower through hole 924 that communicates with the lower discharge port of the lower cylinder 60. Accordingly, the refrigerant discharged through the lower discharge port of the lower cylinder 60 may be discharged below the flange portion 925 through the lower through hole 924 of the flange portion 925.

A lower discharge valve 921 may be provided in the lower through hole 924 of the flange portion 925. Accordingly, the lower through hole 924 of the flange portion 925 can be opened and closed by the lower discharge valve 921. When the refrigerant flowing into the lower cylinder 60 is compressed above a certain pressure, the lower discharge valve 921 is opened and the refrigerant can be discharged to the lower side of the flange portion 925.

Boss 926 may extend vertically from the center of flange portion 925. The boss 926 may extend vertically upward from the flange portion 925. A through hole may be formed in the center of the boss 926.

The bearing 927 is installed in the through hole of the boss 926 and rotatably supports the drive shaft 30. Accordingly, the drive shaft 30 can be rotatably supported by the bearing 927 and the upper bearing 917. The bearing 927 may be any type of bearing as long as it can rotatably support the drive shaft 30. In the case of the present disclosure, a sliding bearing is used as the bearing 927.

A plurality of first bolt holes 922 and a plurality of lower refrigerant holes 923 may be provided in the flange portion 925 around the boss 926.

The lower cylinder 60 may be provided with a plurality of bolt holes 602 corresponding to the plurality of first bolt holes 922 of the flange portion 925. Additionally, the lower cylinder 60 may include a plurality of refrigerant holes 603 corresponding to the plurality of lower refrigerant holes 923 of the lower flange 92.

A flat muffler 72 may be installed on the lower surface of the flange portion 925 of the lower flange 92. Hereinafter, with reference to FIGS. 8 and 9, the flat muffler 72 will be described in detail.

Figure 8 is a perspective view showing a flat muffler 72 used in the rotary compressor 1 according to an embodiment of the present disclosure. FIG. 9 is a perspective view of the flat muffler 72 of FIG. 8 viewed from above.

Referring to Figures 8 and 9, the flat muffler 72 is formed in an approximately dome shape, and a plurality of concave portions 721 are formed on the side of the flat muffler 72 at regular intervals along the circumferential direction of the flat muffler 72. ) may include. Specifically, the flat muffler 72 may be formed in a shape where the central portion of the disc protrudes downward in a substantially dome shape.

Additionally, the flat muffler 72 may include a plurality of second bolt holes 722 formed at positions corresponding to the plurality of concave portions 721 along the edge. The plurality of second bolt holes 722 may be formed to correspond to the plurality of first bolt holes 922 of the lower flange 92.

For example, the flat muffler 72 may include a fixing plate 723, a caulking portion 724, and a muffler portion 725.

The fixing plate 723 may be formed in a substantially ring shape. The fixing plate 723 may include an outer peripheral surface formed in a circular shape and an inner peripheral surface that is concentric with the outer peripheral surface and has a small diameter. The inner peripheral surface of the fixing plate 723 may include a plurality of protrusions 7231. A plurality of protrusions 7231 on the inner peripheral surface may be formed to protrude toward the center of the fixing plate 723. The plurality of protrusions 7231 may be formed to correspond to the plurality of concave parts 721 of the muffler portion 725. Each of the plurality of protrusions 7231 may be formed as a curve corresponding to the plurality of concave parts 721 of the muffler portion 725.

The space between the two adjacent protrusions 7231 is concave to form a recess 7232. That is, the plurality of protrusions 7231 may form a plurality of recessed parts 7232. Since each of the plurality of protrusions 7231 forms a convex part, a plurality of recessed parts 7232 and a plurality of convex parts may be alternately provided on the inner peripheral surface of the fixing plate 723. Accordingly, the inner peripheral surface of the fixing plate 723 may be formed to be concave and convex by the plurality of protrusions 7231.

The fixing plate 723 may be fixed to the flange portion 925 of the lower flange 92. The fixing plate 723 may include a plurality of second bolt holes 722. A plurality of second bolt holes 722 may be formed on a plurality of protrusions 7231 of the fixing plate 723, respectively. The plurality of second bolt holes 722 may be formed to correspond to the plurality of first bolt holes 922 of the lower flange 92.

The muffler portion 725 may be formed to extend downward from the inner peripheral surface of the fixing plate 723. The muffler portion 725 may be formed to protrude from the lower surface of the fixing plate 723 in a substantially dome shape. A plurality of concave portions 721 may be formed on the side of the muffler portion 725 at regular intervals in the circumferential direction. The plurality of concave portions 721 may be formed as curved surfaces that protrude into the interior of the muffler portion 725.

As shown in FIG. 9 , a plurality of concave portions 721 may protrude into the internal space of the muffler portion 725. Accordingly, the internal space of the muffler portion 725 may be formed to be concave and convex.

A through hole 726 may be provided at the bottom of the muffler portion 725. The oil pump installed at the lower end of the drive shaft 30 may be immersed in the oil storage tank 16 through the through hole 726 of the muffler portion 725.

A caulking portion 724 may be provided at the bottom of the muffler portion 725. The caulking portion 724 may be provided at the edge of the through hole 726. The caulking portion 724 is formed to be fixed to one end of the boss 926 of the lower flange 92. When the caulking part 724 of the muffler part 725 is coupled to one end of the boss 926 of the lower flange 92, one end of the boss 926 of the lower flange 92 and the through hole of the muffler part 725 ( 726) It is possible to prevent refrigerant from leaking through the gap.

The caulking portion 724 can be formed by caulking along the entire circumference of the through hole 726 of the muffler portion 725.

The muffler portion 725 may be provided between the fixing plate 723 and the caulking portion 724.

The top of the flat muffler 72 may be formed so as not to protrude above the lower surface of the lower flange 92. Specifically, the fixing plate 723 of the flat muffler 72 may not protrude above the lower surface of the flange portion 925 of the lower flange 92, but may be located below. That is, the upper surface of the fixing plate 723 of the flat muffler 72 may contact the lower surface of the flange portion 925 of the lower flange 92.

The upper surface of the fixing plate 723 of the flat muffler 72 may be formed so as not to contact the side of the flange portion 925 of the lower flange 92. If the fixing plate 723 of the flat muffler 72 does not contact the side of the flange portion 925 of the lower flange 92, pressure by the flat muffler 72 is applied to the bearing 927 installed on the lower flange 92. You may not lose.

A sealing plate 100 may be installed between the lower flange 92 and the flat muffler 72. The sealing plate 100 may be formed to prevent or minimize the leakage of refrigerant between the lower flange 92 and the flat muffler 72.

The sealing plate 100 may be positioned between the lower surface of the flange portion 925 of the lower flange 92 and the upper surface of the fixing plate 723 of the flat muffler 72.

Figure 10 is a perspective view showing the sealing plate 100 used in the rotary compressor 1 according to an embodiment of the present disclosure.

Referring to FIG. 10, the sealing plate 100 may be formed as a substantially ring-shaped flat plate. The sealing plate 100 may be formed to correspond to the fixing plate 723 of the flat muffler 72. The sealing plate 100 may be formed to seal the flat portion between the flat muffler 72 and the lower flange 92.

The sealing plate 100 may include an outer peripheral surface formed in a circular shape and an inner peripheral surface that is concentric with the outer peripheral surface and has a small diameter.

The inner peripheral surface of the sealing plate 100 may include a plurality of bolt seat portions 101 and a plurality of refrigerant grooves 103.

The plurality of bolt seat parts 101 may be formed to protrude from the inner peripheral surface of the sealing plate 100 toward the center of the sealing plate 100. The plurality of bolt seat portions 101 may be formed to correspond to the plurality of protrusions 7231 of the fixing plate 723. Accordingly, the plurality of bolt seat portions 101 may correspond to the plurality of recessed portions 721 of the muffler portion 725. Each of the plurality of bolt seat portions 101 may be formed as a curve corresponding to the plurality of concave portions 721 of the flat muffler 72.

A plurality of third bolt holes 102 corresponding to the plurality of second bolt holes 722 of the flat muffler 72 may be formed in each of the plurality of bolt seats 101. Additionally, the plurality of third bolt holes 102 of the sealing plate 100 may be formed to correspond to the plurality of first bolt holes 922 of the lower flange 92.

The plurality of refrigerant grooves 103 may be formed not to cover the plurality of lower refrigerant holes 923 of the lower flange 92. Therefore, when the sealing plate 100 is installed on the lower surface of the lower flange 92, the sealing plate 100 may not cover the plurality of lower refrigerant holes 923.

A plurality of refrigerant grooves 103 may be formed between the plurality of bolt seats 101. That is, a plurality of refrigerant grooves 103 and a plurality of bolt seat portions 101 may be formed alternately in the circumferential direction of the sealing plate 100.

Each of the plurality of bolt seats 101 may form a convex part, and each of the plurality of refrigerant grooves 103 may form a recessed part. Accordingly, the inner peripheral surface of the sealing plate 100 may include a plurality of convex portions and a plurality of recessed portions. That is, the inner peripheral surface of the sealing plate 100 may be formed to be concave and convex. Accordingly, the inner peripheral surface of the sealing plate 100 may be formed to be concave and convex corresponding to the flat muffler 72.

The sealing plate 100 may be made of a material that can prevent refrigerant from leaking between the flat muffler 72 and the lower flange 92. For example, the sealing plate 100 may be formed of heat-resistant resin, steel, copper, etc. Alternatively, the sealing plate 100 may be formed of a material in which at least two of heat-resistant resin, steel, and copper are stacked in a plate shape.

The flat muffler 72, sealing plate 100, and lower flange 92 may be fixed to the upper cylinder 50 by a plurality of bolts 93. Specifically, the plurality of bolts 93 are connected to the plurality of second bolt holes 722 of the flat muffler 72, the plurality of third bolt holes 102 of the sealing plate 100, and the plurality of plurality of bolt holes 722 of the lower flange 92. A plurality of tapped holes 502 of the upper cylinder 50 through the first bolt hole 922, a plurality of bolt holes 602 of the lower cylinder 60, and a plurality of bolt holes 702 of the middle plate 70. can be concluded. Then, the flat muffler 72, the sealing plate 100, the lower flange 92, the lower cylinder 60, and the middle plate 70 can be integrally fixed to the upper cylinder 50.

The refrigerant discharged downward through the lower through hole 924 of the lower flange 92 passes through the inside of the flat muffler 72, reduces noise, and then passes through the plurality of lower refrigerant holes 923 of the lower flange 92. may flow into.

The refrigerant flowing into the plurality of lower refrigerant holes 923 of the lower flange 92 is the plurality of refrigerant holes 603 of the lower cylinder 60, the plurality of refrigerant holes 703 of the middle plate 70, and the upper cylinder ( It can be discharged to the upper side of the upper flange 91 through the plurality of refrigerant holes 503 of 50 and the plurality of upper refrigerant holes 913 of the upper flange 91.

The refrigerant discharged to the upper side of the upper flange 91 is discharged to the upper side of the upper muffler 71, that is, to the space between the motor 20 and the compression unit 40, through the plurality of openings 711 of the upper muffler 71. It can be.

The refrigerant that has moved into the space between the motor 20 and the compression unit 40 may move to the upper part of the motor 20 through the motor 20. For example, the refrigerant in the space between the motor 20 and the compression unit 40 is transferred to the motor 20 through the gap between the rotor 22 and the stator 21 and the plurality of refrigerant holes 27 provided in the rotor 22. ) can be moved to the top.

The refrigerant moving to the top of the motor 20 may be discharged to the outside of the casing 10 through the refrigerant discharge pipe 14 installed in the upper casing 11.

Hereinafter, with reference to FIGS. 11 to 13, the positional relationship between the lower flange 92, the flat muffler 72, and the sealing plate 100 will be described in detail.

Figure 11 is a diagram showing a state in which the sealing plate 100 and the flat muffler 72 are installed on the lower flange 92. Figure 12 is a bottom view of Figure 11. FIG. 13 is a bottom view showing the flat muffler 72 in FIG. 11 removed.

11 to 13, a flat muffler 72 is installed on the lower surface of the lower flange 92. A sealing plate 100 is installed between the lower flange 92 and the flat muffler 72.

The sealing plate 100 may be installed on the lower surface of the lower flange 92 so that the plurality of third bolt holes 102 correspond to the plurality of first bolt holes 922 of the lower flange 92.

When the plurality of third bolt holes 102 of the sealing plate 100 are aligned with the plurality of first bolt holes 922 of the lower flange 92, the plurality of refrigerant grooves 103 of the sealing plate 100 are formed in the lower part. It may be located at the edge of the plurality of lower refrigerant holes 923 of the flange 92.

At this time, the minimum distance between the inner peripheral surface of the sealing plate 100 and the plurality of lower refrigerant holes 923 of the lower flange 92 may be 0. For example, as shown in FIG. 13, when the inner peripheral surface of the lower refrigerant hole 923 and the bottom surface of the refrigerant groove 103 of the sealing plate 100 are in contact, the lower refrigerant hole 923 and the sealing plate 100 ) is O.

Additionally, the inner peripheral surface of the sealing plate 100 may be formed so that the bottom surface of the refrigerant groove 103 of the sealing plate 100 is spaced apart from the inner peripheral surface of the lower refrigerant hole 923. In this case, the distance between the lower refrigerant hole 923 and the inner peripheral surface of the sealing plate 100 may be greater than 0. At this time, the distance between the lower coolant hole 923 and the inner peripheral surface of the sealing plate 100 may be set to be smaller than the minimum distance between the outer peripheral surface of the lower flange 92 and the lower coolant hole 923. If the distance between the lower refrigerant hole 923 and the inner peripheral surface of the sealing plate 100 is greater than the minimum distance between the lower refrigerant hole 923 and the outer peripheral surface of the lower flange 92, refrigerant may leak.

Additionally, in order to prevent refrigerant leakage, the distance between the bottom surface of the refrigerant groove 103 of the sealing plate 100 and the outer peripheral surface of the sealing plate 100 may be at least 1 mm. That is, the distance between the concave portion of the inner peripheral surface of the sealing plate 100 and the outer peripheral surface of the sealing plate 100 may be at least 1 mm.

When the sealing plate 100 is formed in the structure described above, the plurality of lower refrigerant holes 923 of the lower flange 92 may be exposed through the plurality of refrigerant grooves 103 of the sealing plate 100. That is, the plurality of lower refrigerant holes 923 of the lower flange 92 are not covered by the sealing plate 100.

Accordingly, the refrigerant in the space between the lower flange 92 and the flat muffler 72 can flow into the lower refrigerant hole 923 of the lower flange 92 without interference from the sealing plate 100.

When the flat muffler 72 is installed on the lower surface of the lower flange 92, when the space between the lower flange 92 and the flat muffler 72 is filled with compressed refrigerant, the flat muffler ( Part of 72) may open and refrigerant may leak.

Figure 14 is a diagram showing a state in which a portion of the flat muffler 72 is opened due to compressed refrigerant. For reference, in Figure 14, the opened portion of the flat muffler 72 is exaggerated to show the opened state.

Referring to FIG. 14, reference number G indicates the opening of the flat muffler 72. That is, the opening of the flat muffler 72 refers to the vertical distance between the protrusion 7231 and the recessed portion of the fixing plate 723 of the flat muffler 72.

When the rotary compressor (1) operates and refrigerant is discharged into the space between the lower flange (92) and the flat muffler (72), a plurality of units that secure the flat muffler (72) to the lower flange (92) by the pressure of the compressed refrigerant The portion of the fixing plate 723 between the plurality of protrusions 7231 of the fixing plate 723 where the bolts 93 are installed is deformed. That is, the main portion of the fixing plate 723 may be deformed in a downward direction compared to the protruding portion 7231 due to the pressure of the refrigerant.

If there is no compressed refrigerant between the lower flange 92 and the flat muffler 72, the plurality of recesses of the fixing plate 723 of the flat muffler 72 are restored to their original state and form a plane with the plurality of protrusions 7231. That is, the opening (G) of the flat muffler 72 can be 0.

In order to minimize deformation of the bearing 927 of the lower flange 92 and minimize the amount of refrigerant leaking between the lower flange 92 and the flat muffler 72, the sealing plate 100 may be formed to have a constant thickness Ts. . For example, the thickness Ts of the sealing plate 100 may be formed to have a constant thickness ratio with the thickness Tm of the flat muffler 72.

The thickness Ts of the sealing plate 100 may be formed to have the following relationship with the thickness Tm of the flat muffler 72.

0.5 ≤ Thickness of sealing plate 100 (Ts)/Thickness of flat muffler 72 (Tm) ≤ 2.0

Figure 15 is a graph showing changes in the deformation of the bearing 927 and the opening of the flat muffler 72 according to the thickness of the sealing plate 100.

Figure 15 shows the lower flange ( Shows the results of calculating the deformation amount of the bearing 927 installed in 92) and the opening (G) of the flat muffler 72 through computer simulation. Here, the opening (G) of the flat muffler 72 refers to the vertical distance between the protrusion 7231 and the recessed portion of the fixing plate 723 of the flat muffler 72.

Referring to FIG. 15, when the thickness Ts of the sealing plate 100 increases, the recessed portion between the plurality of protrusions 7231 of the fixing plate 723 of the flat muffler 72 is deformed, that is, the flat muffler 72 is deformed. The gaping (G) may be reduced. Accordingly, when the thickness Ts of the sealing plate 100 increases, refrigerant leakage between the flat muffler 72 and the lower flange 92 can be minimized or prevented.

Additionally, as the thickness Ts of the sealing plate 100 increases, deformation of the bearing 927 installed on the lower flange 92 may increase. Specifically, when the thickness Ts of the sealing plate 100 increases, the moving distance of the bolt 93 increases, thereby increasing the stress generated in the boss 926 of the lower flange 92. If the stress of the boss 926 increases, the deformation of the bearing 927 installed on the boss 926 may increase.

If the deformation of the bearing 927 of the lower flange 92 increases, the input of the rotary compressor 1 may increase. When the input of the rotary compressor (1) increases, the energy efficiency (EER: Energy Efficiency Ratio) of the rotary compressor (1) may decrease.

When the deformation of the bearing 927 is reduced, there is room for maintaining the oil film thickness, allowing a design to reduce the bearing diameter, and improving the reliability of the rotary compressor 1.

When using a skirt type muffler, the bearing deformation is 10.5㎛, and when using the flat muffler 72 according to an embodiment of the present disclosure and the sealing plate 100 with a thickness of 1mm, the bearing deformation is 6.7 It can be reduced to ㎛.

Therefore, it is necessary to determine the thickness Ts of the sealing plate 100 so as to minimize bearing deformation and minimize the opening G of the flat muffler 72.

Referring again to FIG. 15, when the thickness (Tm) of the flat muffler (72) is 1 mm and the thickness (Ts) of the sealing plate (100) is 0.5 mm or less, the bearing deformation is 6.7 μm, which is the rotary compressor (1). The input may not be increased, but the opening of the flat muffler 72 becomes 18.0㎛, so the leakage of refrigerant is too large.

When the thickness (Ts) of the sealing plate (100) is 2.5 mm or more, the opening (G) of the flat muffler (72) becomes 12.0 ㎛, so refrigerant leakage is adequate, but the bearing deformation is 7.3 ㎛, which causes rotary compressor (1) input can be increased. Therefore, the thickness Ts of the sealing plate 100 can be greater than 0.5 mm and less than 2.5 mm.

For example, considering the ratio of the thickness (Ts) of the sealing plate 100 to the thickness (Tm) of the flat muffler 72, when the thickness (Tm) of the flat muffler 72 is 1.2 mm, the sealing plate The thickness (Ts) of (100) can be 0.6 mm to 2.4 mm.

The performance of the rotary compressor 1 according to an embodiment of the present disclosure having the above structure was compared with the rotary compressor according to the prior art using a skirt muffler.

Table 1 below is a performance comparison table between the rotary compressor 1 according to an embodiment of the present disclosure and a rotary compressor according to the prior art using a skirt muffler. Figure 16 is a graph showing the rate of change of the energy efficiency of the rotary compressor 1 according to an embodiment of the present disclosure with respect to the energy efficiency of the rotary compressor according to the prior art using a skirt muffler.

The comparative test below was conducted under ASHRAE-T conditions. ASHRAE-T conditions include condensing temperature of 54.4℃, liquid temperature of 46.1℃, evaporating temperature of 7.2℃, suction temperature of 35℃, and ambient temperature. ) is 35℃.

Driving speed Cooling power (Btu/h) Input (W) EER prior art This disclosure prior art This disclosure prior art This disclosure 30 23,906 +0.5% 2,058 -1.2% 11.61 +1.7% 45 36,598 +0.4% 3,079 -0.6% 11.88 +1.1% 60 49,947 +0.4% 4,246 -0.5% 11.76 +0.8%

In Table 1, the prior art refers to a rotary compressor in which a skirt muffler is installed on the lower flange 92. The present disclosure refers to a rotary compressor (1) in which a flat muffler (72) and a sealing plate (100) are installed on the lower flange (92). Here, the skirt muffler is formed to include a skirt surrounding the side of the flange portion 925 of the lower flange 92. That is, the skirt muffler includes a skirt extending upward from the outer peripheral surface of the fixing plate 723 of the flat muffler 72 according to an embodiment of the present disclosure. The unit of driving speed is revolutions per second (rps). EER stands for energy efficiency.

Referring to Table 1, it can be seen that the rotary compressor 1 using the flat muffler 72 and the sealing plate 100 according to an embodiment of the present disclosure has increased cooling power compared to the rotary compressor according to the prior art. That is, the cooling power of the rotary compressor 1 using the flat muffler 72 and the sealing plate 100 according to an embodiment of the present disclosure increases by 0.4% to 0.5% compared to the cooling power of the rotary compressor according to the prior art. Accordingly, it can be seen that refrigerant leakage between the flat muffler 72 and the lower flange 92 is minimized by the sealing plate 100.

In addition, it can be seen that the input of the rotary compressor 1 using the flat muffler 72 and the sealing plate 100 according to an embodiment of the present disclosure is reduced compared to the rotary compressor according to the prior art. That is, the input of the rotary compressor 1 using the flat muffler 72 and the sealing plate 100 according to an embodiment of the present disclosure is reduced by 0.5% to 1.2% compared to the input of the rotary compressor according to the prior art. Accordingly, it can be seen that the bearing deformation of the lower flange 92 due to the sealing plate 100 and the flat muffler 72 is minimized.

In addition, it can be seen that the rotary compressor 1 using the flat muffler 72 and the sealing plate 100 according to an embodiment of the present disclosure has increased energy efficiency compared to the rotary compressor according to the prior art. That is, the EER of the rotary compressor 1 using the flat muffler 72 and the sealing plate 100 according to an embodiment of the present disclosure increases by 0.8% to 1.7% compared to the EER of the rotary compressor according to the prior art. Therefore, the rotary compressor 1 using the flat muffler 72 and the sealing plate 100 according to an embodiment of the present disclosure operates at 30 to 60 rps compared to the rotary compressor according to the prior art. EER may increase by an average of 1.2% in the area.

As described above, the rotary compressor 1 according to an embodiment of the present disclosure installs the flat muffler 72 and the sealing plate 100 on the lower flange 92, thereby minimizing bearing deformation of the lower flange 92. And, since refrigerant leakage due to the flat muffler 72 can be minimized, energy efficiency can be improved.

Although the present disclosure has been shown and described above with reference to various embodiments, it is understood that various changes in form and detail may be made in the present technology without departing from the scope of the present disclosure as defined by the appended claims and their equivalents. It will be understood by those skilled in the art.

One; rotary compressor 3; accumulator
10; housing 20; motor
21; stater 22; rotor
30; drive shaft 40; Compression part
50; upper cylinder 60; lower cylinder
70; middle plate 71; upper muffler
72; flat muffler 91; upper flange
92; lower flange 100; Ceiling board
101; Bolt position 103; Refrigerant Home

Claims (15)

Casing (10);
A motor (20) installed inside the casing (10);
A compression unit 40 installed at the lower part of the motor 20;
A lower flange (92) installed below the compression unit (40);
A flat muffler (72) installed on the lower surface of the lower flange (92); and
A rotary compressor including a sealing plate (100) installed between the flat muffler (72) and the lower flange (92). According to claim 1,
A rotary compressor wherein the top of the flat muffler (72) does not protrude above the lower surface of the lower flange (92). According to claim 1,
The flat muffler 72 is formed in a dome shape and includes a plurality of concave portions 721 formed on a side of the flat muffler 72 at regular intervals along the circumferential direction of the flat muffler 72,
The sealing plate 100 is formed in a ring shape,
A rotary compressor, wherein the inner peripheral surface of the sealing plate (100) is formed to be concave and convex corresponding to the flat muffler (72). According to claim 3,
The lower flange 92 includes a plurality of lower refrigerant holes and a plurality of first bolt holes formed along the edge,
The flat muffler 72 includes a plurality of second bolt holes formed to correspond to the plurality of first bolt holes of the lower flange 92 at positions corresponding to the plurality of recesses 721 along the edge, rotary compressor. According to claim 4,
The sealing plate 100 protrudes toward the center from the inner peripheral surface of the sealing plate 100 and has a plurality of bolt positions where a plurality of third bolt holes corresponding to the plurality of second bolt holes of the flat muffler 72 are formed. rotary compressor, comprising: According to claim 5,
The sealing plate (100) is formed not to cover the plurality of lower refrigerant holes of the lower flange (92). According to claim 6,
A rotary compressor, wherein the distance between the concave portion of the sealing plate (100) and the outer peripheral surface of the sealing plate (100) is at least 1 mm. According to claim 1,
A rotary compressor wherein the thickness of the sealing plate (100) has the following relationship with the thickness of the flat muffler (72).
0.5 ≤ Thickness of sealing plate 100 (Ts)/Thickness of flat muffler 72 (Tm) ≤ 2.0 According to claim 1,
A rotary compressor wherein oil is accommodated in the lower part of the casing, and the flat muffler (72) is immersed in the oil. According to claim 1,
The sealing plate 100 is a rotary compressor made of one of heat-resistant resin, steel, copper, and a material in which at least two of these are laminated. According to claim 1,
The lower flange 92 is,
A flange portion 925 formed in a disk shape;
A boss 926 extending vertically from the flange portion 925 and including a through hole; and
It includes a bearing 927 installed in the through hole of the boss 926,
The flat muffler 72 is,
A fixing plate 723 fixed to the flange portion 925 of the lower flange 92 and formed in a ring shape;
A caulking portion 724 fixed to one end of the boss; and
A rotary compressor including a muffler portion 725 provided between the fixing plate 723 and the caulking portion. According to claim 11,
The muffler portion 725 includes a plurality of concave portions 721 formed at regular intervals in the circumferential direction. According to claim 12,
The fixing plate 723 includes a plurality of protrusions 7231 corresponding to the plurality of recesses 721 of the muffler portion 725. According to claim 13,
The flange portion 925 of the lower flange 92 includes a plurality of lower refrigerant holes and a plurality of first bolt holes,
The plurality of protrusions 7231 of the fixing plate 723 include a plurality of second bolt holes corresponding to the plurality of first bolt holes. According to claim 14,
The inner peripheral surface of the sealing plate 100 is formed not to cover the plurality of bolt seat portions formed to correspond to the plurality of protrusions 7231 of the fixing plate 723 and the plurality of lower refrigerant holes of the flange portion 925. A rotary compressor comprising a plurality of refrigerant grooves (103).

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