WO2024150854A1

WO2024150854A1 - Hermetic compressor

Info

Publication number: WO2024150854A1
Application number: PCT/KR2023/000580
Authority: WO
Inventors: 정택수; 이승목; 김철환
Original assignee: 엘지전자 주식회사
Priority date: 2023-01-12
Filing date: 2023-01-12
Publication date: 2024-07-18

Abstract

A hermetic compressor is disclosed. The hermetic compressor has a vibration-damping member provided inside or outside a casing, has a plurality of rigid parts arranged around a vibrating body by preset intervals in the circumferential direction and coupled to the vibrating body, and has a mass part that can be formed to be annular to connect the plurality of rigid parts to each other or formed as a circular arc to be independently connected to each of the plurality of rigid parts. Therefore, even if a driving motor, that is provided as a rotating motor, is provided, the vibration-damping member absorbs torsional vibration caused thereby such that the vibration noise of the compressor can be effectively lowered.

Description

Hermetic compressor

The present invention relates to compressors, and particularly to a sealed compressor equipped with a rotating motor.

Compressors can be divided into open compressors in which the driving part (or electric part) is provided outside the casing and only the compression part is provided inside the casing, and closed compressors in which the driving part (or electric part) and the compression part are provided together inside the casing. there is.

Compressors generate vibration in the driving part and the compression part, and a closed compressor in which the driving part and the compression part are provided together inside the casing may generate greater vibration than an open compressor.

Accordingly, conventionally, vibration-proof rubber is provided on the base that supports the compressor on the compressor installation surface to suppress vibration generated inside the casing from being transmitted to the refrigeration cycle through the casing. However, it does not effectively absorb vibrations generated inside the compressor, so there is a problem in that vibrations in the compressor and the refrigeration cycle to which the compressor is applied are not sufficiently attenuated.

Typically, a dynamic absorber (hereinafter used interchangeably with a vibration damping member) is known as a mechanism for damping the vibration of a vibrating body. Conventional dynamic absorber-related technology mainly places the anti-phase mode frequency of the dynamic absorber in the same band as the mode required for reduction of the target vibrating body (mainly shaft or pipe). For this purpose, emphasis is placed on controlling the stiffness between the vibrating body and the mass part of the dynamic absorber through various methods.

However, in a closed compressor equipped with a rotary motor, it is not only structurally difficult to install a dynamic absorber inside the casing, but also there is a problem in that the volume of the compressor increases when the dynamic absorber is installed inside the casing.

In addition, when the dynamic absorber is installed outside the casing, separate parts must be added, which increases the number of assembly steps and may increase manufacturing costs.

The purpose of the present invention is to provide a sealed compressor that has a rotating motor inside the casing and a dynamic absorber to reduce vibration noise.

Another object of the present invention is to provide a closed compressor in which a dynamic absorber can be installed inside the casing without excessively increasing the size of the casing.

Another object of the present invention is to provide a sealed compressor that can install a dynamic absorber outside the casing while minimizing the number of parts.

In order to achieve the purpose of the present invention, a closed compressor including a casing, a drive motor, a compression unit, a rotating shaft, and a vibration damping member may be disclosed. The drive motor may be provided in the inner space of the casing to generate rotational force. The compression unit is provided in the inner space of the casing and can compress the refrigerant while operating by rotational force generated by the drive motor. The rotation shaft may connect the drive motor and the compression unit to transmit the rotational force of the drive motor to the compression unit. The vibration damping member may be provided inside or outside the casing to dampen vibration. The vibration damping member may include a plurality of rigid parts and a plurality of mass parts. The plurality of rigid parts may be arranged at predetermined intervals along the circumferential direction around the vibrating body and coupled to the vibrating body. The mass portion may be formed in an annular shape to connect the plurality of rigid portions to each other, or may be formed in an arc shape to independently connect each of the plurality of rigid portions. Through this, even if the driving motor is a rotating motor, the vibration damping member absorbs the resulting torsional vibration, thereby effectively lowering the vibration noise of the compressor.

For example, the compression unit may include a main frame, a fixed scroll, and an orbiting scroll. The mainframe may be fixed to the inside of the casing. The fixed scroll may be coupled to the main frame on the opposite side of the drive motor. The orbiting scroll may be provided between the main frame and the fixed scroll to form a compression chamber between the main frame and the fixed scroll. The vibration damping member may be provided in the inner space of the casing. Through this, the torsional moment generated in the internal space of the casing is attenuated inside the casing, thereby preventing compressor vibration from being transmitted to the outside.

For example, the compression unit may be provided below the drive motor. The vibration damping member may be provided on a side opposite to the side facing the drive motor among both sides in the axial direction of the compression unit. Through this, it is possible to effectively utilize the internal space of the casing and suppress the increase in the volume of the casing while installing a vibration damping member in the internal space of the casing.

As another example, the compression unit may include a main frame, a fixed scroll, and an orbiting scroll. The mainframe may be fixed to the inside of the casing. The fixed scroll may be coupled to the main frame on the opposite side of the drive motor. The orbiting scroll may be provided between the main frame and the fixed scroll to form a compression chamber between the main frame and the fixed scroll. One end of the rigid portion of the vibration damping member may extend from the fixed scroll to the opposite side of the main frame. Through this, the length of the rigid part can be made as long as possible, thereby increasing the reliability of the rigid part and attenuating torsional vibrations of various frequencies.

For example, a plurality of fixing grooves may be formed on the lower surface of the fixed scroll by being recessed in the axial direction at preset intervals along the circumferential direction. The plurality of rigid parts may be coupled to each other by inserting one end of each into the plurality of fixing grooves. Through this, the reliability of the vibration damping member can be increased by stably fixing one end of the rigid portion to the vibrating body.

Specifically, the mass portion may be formed in an annular shape, and the plurality of rigid portions may extend as a single body from one side of the mass portion. Through this, the assembly efficiency of the vibration damping member can be improved by reducing the assembly man-hours for the rigid part and the mass part.

Specifically, the mass portion may be formed in an annular shape, and a plurality of fastening holes may be formed in the mass portion at predetermined intervals along the circumferential direction. The plurality of rigid parts may pass through each of the plurality of fastening holes and be fastened to the mass part. Through this, it is possible to appropriately form the shape of the rigid portion and/or the mass portion while increasing the assembly of the rigid portion and the mass portion.

More specifically, the plurality of rigid parts may be formed of a material having different stiffness from that of the mass part. Through this, it is possible to appropriately and actively respond to torsional vibration of various frequencies depending on the capacity of the compressor.

Additionally, a discharge cover that accommodates the refrigerant discharged from the compression chamber may be provided on one side of the fixed scroll forming the opposite side of the orbiting scroll. The mass portion may be located farther from the fixed scroll in the axial direction than the discharge cover. Through this, it is possible to secure a wide muffler space in the discharge cover, secure a long length of the rigid part, and at the same time form various shapes of the mass part.

For example, an oil pickup may be provided on one side of the fixed scroll forming the opposite side of the orbiting scroll to communicate with the oil supply passage of the rotating shaft. The mass portion may be provided to surround the oil pickup. Through this, it is possible to suppress an increase in the volume of the casing due to the vibration damping member while installing the vibration damping member in the internal space of the casing.

As another example, the compression unit may include a main frame, a fixed scroll, and an orbiting scroll. The mainframe may be fixed to the inside of the casing. The fixed scroll may be coupled to the main frame on the opposite side of the drive motor. The orbiting scroll may be provided between the main frame and the fixed scroll to form a compression chamber between the main frame and the fixed scroll. The rotation shaft may pass through the main frame, the orbiting scroll, and the fixed scroll and be supported on the main frame and the fixed scroll. The vibration damping member may be coupled to the rotation shaft below the fixed scroll. Through this, the vibration damping effect can be further increased as the vibration damping member is provided at the vibration source of torsional vibration.

For example, the vibration damping member may further include a fixing part that is inserted and coupled to the outer peripheral surface of the rotating shaft. The plurality of rigid parts may each extend in a radial direction from the outer peripheral surface of the fixing part. Through this, it is possible to minimize the increase in the length of the casing while coupling the vibration damping member to the rotating shaft.

Specifically, the fixing part, the plurality of rigid parts, and the mass part may be formed as a single body. Through this, the manufacturing cost can be lowered by simplifying the assembly process of the vibration damping member.

As another example, the compression unit may include a main frame, a fixed scroll, and an orbiting scroll. The mainframe may be fixed to the inside of the casing. The fixed scroll may be coupled to the main frame on the opposite side of the drive motor. The orbiting scroll may be provided between the main frame and the fixed scroll to form a compression chamber between the main frame and the fixed scroll. The vibration damping member may be provided outside the casing. Through this, it is possible to easily install the vibration damping member and at the same time change the vibration damping member in various ways and appropriately.

For example, a base may be provided on the lower surface of the casing to support the casing on the compressor installation surface. The plurality of rigid parts may extend from the base in a direction opposite to the compressor installation surface. Through this, the vibration damping member can be installed simply and stably without providing a separate member for fixing the vibration damping member.

Specifically, the base includes: a first base portion in contact with the lower surface of the casing; And it may include a plurality of second base parts extending radially from the first base part and supported on the compressor installation surface. The plurality of rigid parts may each extend along the axial direction from the plurality of second base parts. Through this, the mass portion forming part of the vibration damping member can be installed to surround the casing while being spaced apart from the outer peripheral surface of the casing.

More specifically, fastening grooves or fastening holes may be formed in each of the plurality of second base portions. One end of the plurality of rigid parts may be inserted into the fastening groove or the fastening hole to be fastened. Through this, the rigid part forming part of the vibration damping member can be easily and stably formed.

Additionally, a refrigerant suction pipe communicating with the compression chamber may be passed through and coupled to the casing. The mass portion may be located lower than the refrigerant suction pipe. Through this, although the vibration damping member is installed outside the casing, the vibration damping member is formed to be located within the range of the refrigerant suction pipe that forms part of the compressor, thereby suppressing an increase in the volume of the compressor including the refrigerant suction pipe.

In the sealed compressor according to the present invention, a vibration damping member is provided inside or outside the casing, and a plurality of rigid parts are arranged at predetermined intervals in the circumferential direction around the vibrating body and coupled to the vibrating body, and the mass The portion may be formed in an annular shape to connect the plurality of rigid portions to each other, or may be formed in an arc shape to independently connect each of the plurality of rigid portions. Through this, even if the driving motor is a rotating motor, the vibration damping member absorbs the resulting torsional vibration, thereby effectively lowering the vibration noise of the compressor.

In the sealed compressor according to the present invention, a vibration damping member may be provided in the inner space of the casing. Through this, the torsional moment generated in the internal space of the casing is attenuated inside the casing, thereby preventing compressor vibration from being transmitted to the outside.

In the sealed compressor according to the present invention, one end of the rigid portion of the vibration damping member may extend from the fixed scroll to the opposite side of the main frame. Through this, the length of the rigid part can be made as long as possible, thereby increasing the reliability of the rigid part and attenuating torsional vibrations of various frequencies.

In the sealed compressor according to the present invention, the vibration damping member may be coupled to the rotating shaft below the fixed scroll. Through this, the vibration damping effect can be further increased as the vibration damping member is provided at the vibration source of torsional vibration.

In the sealed compressor according to the present invention, a vibration damping member may be provided on the outside of the casing. Through this, it is possible to easily install the vibration damping member and at the same time change the vibration damping member in various ways and appropriately.

1 is a perspective view showing the inside of a scroll compressor according to this embodiment.

Figure 2 is a longitudinal cross-sectional view of Figure 1.

Figure 3 is an exploded perspective view of the vibration damping member according to this embodiment.

Figure 4 is a front view showing the assembled vibration damping member according to this embodiment.

Figure 5 is a schematic diagram showing the effect of the vibration damping member according to this embodiment.

Figure 6 is an exploded perspective view of another embodiment of the vibration damping member in Figure 1.

Figure 7 is an assembled front view of Figure 6.

Figure 8 is an exploded perspective view of another embodiment of the vibration damping member in Figure 1.

Figure 9 is a schematic diagram showing the effect of the vibration damping member according to Figure 8.

Figure 10 is a perspective view showing another embodiment of the vibration damping member in Figure 1.

Figure 11 is a front view of Figure 10.

Figure 12 is an exploded perspective view of the vibration damping member according to Figure 10.

Figure 13 is a schematic diagram showing the effect of the vibration damping member according to Figure 10.

Hereinafter, the sealed compressor according to the present invention will be described in detail based on the accompanying drawings. In the following description, descriptions of some components may be omitted to clarify the characteristics of the present invention.

In addition, the "upper side" used in the following description refers to the direction away from the support surface supporting the scroll compressor according to the embodiment of the present invention, that is, when viewed centered on the drive unit (electric drive unit or drive motor) and the compression unit, the drive unit (electric drive unit or drive motor) is viewed from the center. The (drive motor) side refers to the upper side. “Lower side” refers to the direction approaching the support surface, that is, when looking at the driving part (electrical part or driving motor) and the compression part as the center, the compression part is the lower side.

Additionally, the term “axial direction” used in the following description refers to the longitudinal direction of the rotation axis. “Axis” can be understood as an upward and downward direction. “Radial” means the direction intersecting the axis of rotation.

In addition, the following description will take a scroll compressor as an example, and the scroll compressor will be described by taking a closed scroll compressor in which a driving part (electrical drive part or driving motor) and a compression part are provided in a casing. However, it can be applied in the same or similar manner to compressors in which a rotary motor is applied as a driving part, such as a rotary compressor and a reciprocating compressor.

In addition, the following description will take as an example a vertical scroll compressor in which the transmission unit and the compression unit are arranged in the vertical axial direction, and a lower compression type scroll compressor in which the compression unit is located lower than the drive unit (electric unit or drive motor). However, the same can be applied to a horizontal scroll compressor in which the driving part (electrical part or drive motor) and the compression part are arranged left and right, as well as a top compression type scroll compressor in which the compression part is located above the driving part (electrical part or driving motor).

In addition, in the following description, a high-pressure scroll compressor is taken as an example, which is a lower compression type, in which the refrigerant suction pipe forming the suction passage is directly connected to the compression unit, and the refrigerant discharge pipe communicates with the inner space of the casing, so that the inner space of the casing creates the discharge pressure. Listen and explain. However, the same can be applied to a low-pressure scroll compressor where the internal space of the casing creates suction pressure.

Figure 1 is a perspective view showing the inside of a scroll compressor according to this embodiment, and Figure 2 is a longitudinal cross-sectional view of Figure 1.

Referring to FIGS. 1 and 2, the high-pressure, bottom-compression type scroll compressor (hereinafter abbreviated as scroll compressor) according to this embodiment includes a drive motor 120 forming a transmission portion in the upper half of the casing 110. is installed, and the main frame 130, fixed scroll 140, orbiting scroll 150, discharge cover 160, and vibration damping member 170 are sequentially installed on the lower side of the drive motor 120. Typically, the drive motor 120 forms a transmission part as described above, and the main frame 130, fixed scroll 140, orbiting scroll 150, discharge cover 160, and vibration damping member 170 are the compression part (C). ) is achieved.

The drive motor 120 forming the transmission unit is coupled to the upper end of the rotation shaft 125, which will be described later, and the compression unit C is coupled to the lower end of the rotation shaft 125. Accordingly, the compressor 10 has the lower compression structure described above, and the compression unit C is connected to the drive motor 120 by the rotation shaft 125 and operates by the rotational force of the drive motor 120. Accordingly, the drive motor 120 can be understood as a driving unit that drives the compression unit (C), so hereinafter, the driving motor can be described interchangeably with the electric motor or driving unit.

Referring to Figures 1 and 2, the casing 110 according to this embodiment may include a cylindrical shell 111, an upper shell 112, a lower shell 113, and a base 114.

The cylindrical shell 111 is formed in a cylindrical shape with openings at both upper and lower ends, the upper shell 112 is coupled to cover the open top of the cylindrical shell 111, and the lower shell 113 is a part of the cylindrical shell 111. It is combined to cover the opened bottom. Accordingly, the internal space 110a of the casing 110 is sealed, and the sealed internal space 110a of the casing 110 is divided into a lower space (S1) and an upper space (S2) based on the driving motor 120. do.

The lower space (S1) is a space formed on the lower side of the drive motor 120. The lower space (S1) can be divided into a storage space (S11) and a discharge space (S12) based on the compression section (C). .

The oil storage space (S11) is a space formed on the lower side of the compression section (C), and forms a space where mixed oil (hereinafter referred to as oil), which is a mixture of oil or liquid refrigerant, is stored. The discharge space (S12) is a space formed between the upper surface of the compression unit (C) and the lower surface of the drive motor 120, and forms a space where the refrigerant compressed in the compression unit (C) or a mixed refrigerant mixed with oil is discharged. .

The upper space (S2) is a space formed on the upper side of the drive motor 120, and forms an oil separation space where oil is separated from the refrigerant discharged from the compression unit (C). A refrigerant discharge pipe communicates with the upper space (S2).

The above-described drive motor 120 and main frame 130 are inserted and fixed inside the cylindrical shell 111. An oil return passage (unmarked) may be formed on the outer peripheral surface of the drive motor 120 and the outer peripheral surface of the main frame 130, spaced apart from the inner peripheral surface of the cylindrical shell 111 by a preset distance.

A refrigerant suction pipe 115 penetrates and is coupled to the side of the cylindrical shell 111. Accordingly, the refrigerant suction pipe 115 penetrates the cylindrical shell 111 forming the casing 110 in the radial direction and is coupled thereto. The refrigerant suction pipe 115 is formed in an L shape, and one end penetrates the cylindrical shell 111 and directly communicates with the suction port 1421 of the fixed scroll 140, which will be described later, forming the compression portion C. Accordingly, the refrigerant may flow into the compression chamber (V) through the refrigerant suction pipe 115.

The upper shell 112 is penetrated so that the inner end of the refrigerant discharge pipe 116 communicates with the inner space 110a of the casing 110, specifically the upper space S2 formed on the upper side of the drive motor 120. are combined. An oil separation device (unmarked) is installed in the refrigerant discharge pipe 116 to separate oil from the refrigerant discharged from the casing 110, or to block the refrigerant discharged from the casing 110 from flowing back into the casing 110. A check valve (not marked) may be installed.

The lower shell 113 forms a storage space S11 together with the lower half of the cylindrical shell 111. One end of an oil circulation pipe (not shown) may be coupled to the lower half of the lower shell 113 in the radial direction.

The base 114 may be formed in a ring shape and coupled to the lower surface of the lower shell 113, or may be formed in a plate shape and coupled to cover the open lower end of the cylindrical shell 111. The description will focus on the example in which the base 114 of this embodiment is formed in a ring shape and is coupled to the lower surface of the lower shell 113.

In addition, the base 114 extends radially from the first base portion 1141 and the outer peripheral surface of the first base portion 1141, which are in contact with the lower surface of the lower shell 113, and is supported on the compressor installation surface 1. It may include two second base portions 1142. The second base portion 1142 is provided with an anti-vibration rubber 1143 to attenuate compressor vibration and at the same time suppress the compressor vibration from being transmitted to the compressor installation surface 1. The base 114 will be described again in another embodiment later.

Referring to Figures 1 and 2, the drive motor 120 according to this embodiment includes a stator 121 and a rotor 122. The stator 121 is inserted and fixed to the inner peripheral surface of the cylindrical shell 111, and the rotor 122 is rotatably provided inside the stator 121.

The stator core 1211 is formed in a cylindrical shape and is fixed to the inner peripheral surface of the cylindrical shell 111 by hot pressing. The stator coil 1212 is wound around the stator core 1211 and is electrically connected to an external power source through a terminal (not shown) that is penetrated and coupled to the casing 110.

The rotor 122 includes a rotor core 1221 and a permanent magnet 1222.

The rotor core 1221 is formed in a cylindrical shape and is rotatably inserted into the stator core 1211 at intervals equal to a predetermined gap. The permanent magnets 1222 are embedded inside the rotor core 1222 at preset intervals along the circumferential direction.

Additionally, the rotating shaft 125 is press-fitted and coupled to the center of the rotor core 1221. An orbiting scroll 150, which will be described later, is eccentrically coupled to the upper end of the rotation shaft 125. Accordingly, the rotational force of the drive motor 120 can be transmitted to the orbiting scroll 150 through the rotation shaft 125.

An oil supply passage 126 is formed in a hollow shape inside the rotating shaft 125, and an oil pickup 127 for pumping the oil filled in the oil reservoir space S11 may be coupled to the lower end of the rotating shaft 125. Accordingly, the oil filled in the oil storage space (S11) is sucked to the top of the rotating shaft 125 through the oil pickup 127 and the oil supply passage 126 when the rotating shaft 125 rotates and lubricates the sliding portion.

As described above, the compression unit (C) according to this embodiment includes a main frame 130, a fixed scroll 140, an orbiting scroll 150, a discharge cover 160, and a vibration damping member 170.

Referring to Figures 1 and 2, the main frame 130 according to this embodiment is installed below the drive motor 120, and is fixed to the inner wall of the cylindrical shell 111 by hot pressing or welding. The main frame 130 includes a frame head plate portion 131, a frame side wall portion 132, and a main bearing portion 133.

The frame plate portion 131 is formed in an annular shape and is installed below the drive motor 120. The frame side wall portion 132 extends in a cylindrical shape from the lower edge of the frame end plate portion 131, and the outer peripheral surface of the frame side wall portion 132 is fixed to the inner peripheral surface of the cylindrical shell 111 by hot pressing or welding. . Accordingly, the storage space (S11) and the discharge space (S12) forming the lower space (S1) of the casing (110) are separated by the frame head plate portion (131) and the frame side wall portion (132).

The main bearing portion 133 protrudes upward toward the drive motor 120 from the central upper surface of the frame plate portion 131. The main bearing portion 133 is formed by penetrating a cylindrical main bearing hole 1331 in the axial direction, and a rotating shaft 125 is inserted into the main bearing hole 1331 and supported in the radial direction.

Referring to FIGS. 1 and 2, the fixed scroll 140 according to this embodiment may include a fixed head plate portion 141, a fixed side wall portion 142, a sub-bearing portion 143, and a fixed wrap 144. there is.

The fixed head plate portion 141 is formed in a disk shape with a plurality of concave portions formed on the outer peripheral surface, and a sub-bearing hole 1431 forming a sub-bearing portion 143, which will be described later, may be formed through the center in the vertical direction. Discharge holes 1411 and 1412 may be formed around the sub-axle hole 1431, which communicate with the compression chamber V and discharge the compressed refrigerant into the muffler space 160a of the discharge cover 160, which will be described later.

Although not shown in the drawing, only one discharge port may be formed so as to communicate with both the first compression chamber (V1) and the second compression chamber (V2), which will be described later. However, as in the present embodiment, the first discharge port (not coded) may communicate with the first compression chamber (V1), and the second discharge port (not coded) may communicate with the second compression chamber (V2). Accordingly, the refrigerant compressed in the first compression chamber (V1) and the second compression chamber (V2) can be independently discharged through different discharge ports.

In addition, a plurality of fixing grooves 141a are formed on the lower surface of the fixed head plate portion 141 at preset intervals along the circumferential direction, and these fixing grooves 141a include the rigid portion 171 of the vibration damping member 170, which will be described later. ) can be inserted and combined, respectively. These fixing grooves 141a and the vibration damping member 170 will be described later.

The fixed side wall portion 142 may extend in the vertical direction from the upper surface edge of the fixed head plate portion 141 to form a ring shape. The fixed side wall portion 142 may be coupled to the frame side wall portion 132 of the main frame 130 so as to face in the vertical direction.

A suction port 1421 is formed in the fixed side wall portion 142 and penetrates the fixed side wall portion 142 in the radial direction. The end of the refrigerant suction pipe 115 penetrating the cylindrical shell 111 is inserted and coupled to the suction port 1421 as described above. Accordingly, the refrigerant can be sucked directly into the compression chamber (V) through the refrigerant suction pipe 115.

The sub-bearing portion 143 extends axially from the center of the fixed head plate portion 141 toward the discharge cover 160. At the center of the sub-bearing unit 143, a cylindrical sub-bearing hole 1431 is formed penetrating in the axial direction, and the lower end of the rotating shaft 125 is inserted into the sub-bearing hole 1431 to be supported in the radial direction. .

The fixing wrap 144 may be formed to extend axially from the upper surface of the fixing head plate portion 141 toward the orbiting scroll 150. The fixed wrap 144 engages with the orbiting wrap 152, which will be described later, to form a compression chamber (V). The fixed wrap 144 will be described later along with the swing wrap 152.

Referring to FIGS. 1 and 2 , the orbiting scroll 150 according to this embodiment includes a pivoting plate portion 151, a pivoting wrap 152, and a rotating shaft engaging portion 153.

The pivoting plate portion 151 is formed in a disk shape and is accommodated in the main frame 130. The upper surface of the pivot plate portion 151 may be supported in the axial direction on the main frame 130 with a back pressure sealing member (not indicated) interposed therebetween.

The swing wrap 152 may be formed to extend from the lower surface of the pivot plate portion 151 toward the fixed scroll 140. The orbiting wrap 152 engages with the fixed wrap 144 to form a compression chamber (V).

The orbiting wrap 152 may be formed in an involute shape together with the fixed wrap 144. However, the orbiting wrap 152 and the fixed wrap 144 may be formed in various shapes other than the involute.

For example, the orbital wrap 152 has a shape in which a plurality of circular arcs with different diameters and origins are connected, and the outermost curve may be formed in an approximately elliptical shape with a long axis and a short axis. The fixing wrap 144 may also be formed in the same way.

The inner end of the pivoting wrap 152 is formed in the central portion of the pivoting disk portion 151, and a rotating shaft engaging portion 153 may be formed through the central portion of the pivoting disk portion 151 in the axial direction.

The eccentric portion (not marked) of the rotation shaft 125 is rotatably inserted and coupled to the rotation shaft coupling portion 153. Accordingly, the outer peripheral portion of the rotating shaft coupling portion 153 is connected to the orbital wrap 152 and serves to form a compression chamber (V) together with the fixed wrap 144 during the compression process.

The rotation axis coupling portion 153 may be formed at a height that overlaps the orbital wrap 152 on the same plane. That is, the rotation shaft coupling portion 153 may be disposed at a height where the eccentric portion (not marked) of the rotation shaft 125 overlaps the pivot wrap 152 on the same plane. Accordingly, the repulsion force and the compression force of the refrigerant are applied to the same plane based on the orbital plate portion 151 and cancel each other out, and through this, the tilt of the orbiting scroll 150 due to the action of the compression force and the repulsion force can be suppressed.

Referring to Figures 1 and 2, the discharge cover 160 according to this embodiment is coupled to the lower surface of the fixed scroll 140, and a muffler is installed inside the discharge cover 160 to accommodate the discharge port of the fixed scroll 140. A space 160a is formed. The muffler space is separated from the reservoir space (S11) of the casing and is a discharge space between the main frame 130 and the drive motor 120 through a discharge passage (unmarked) penetrating the fixed scroll 140 and the main frame 130. It connects to (S12).

The outer diameter of the discharge cover 160, specifically the outer diameter of the portion forming the muffler space, may be formed to be smaller than or equal to the outer diameter of the fixed scroll 140. For example, when the outer diameter of the discharge cover 160 is smaller than the outer diameter of the fixed scroll 140, the rigid portion 171 of the subsequent vibration damping member 170 moves from the outer peripheral surface of the discharge cover 160 to the fixed scroll. It can be coupled to (140). On the other hand, when the outer diameter of the discharge cover 160 is formed to be the same as the outer diameter of the fixed scroll 140, the rigid portion receiving groove (171) of the vibration damping member 170 is accommodated on the outer peripheral surface of the discharge cover 160 ( (not marked) may be formed to be depressed. In this embodiment, the outer diameter of the discharge cover 160 is smaller than the outer diameter of the fixed scroll 140, for example, a virtual connection is made between the inside of the fixing groove 141a to which the rigid part 171 of the vibration damping member 170 is fastened. An example formed smaller than the diameter of a circle is shown.

Meanwhile, referring to FIGS. 1 and 2, the vibration damping member 170 according to this embodiment includes a plurality of stiffness portions 171 and mass portions 172.

The plurality of rigid parts 171 may be formed in a thin rod shape and spaced apart at predetermined intervals along the circumferential direction, and may be formed in an annular shape to connect the plurality of rigid parts 171 to each other. Accordingly, the rigid part 171 forming the upper end of the vibration damping member 170 is fixed to the fixed scroll 140, while the mass part 172 forming the lower end of the vibration damping member 170 is attached to the lower side of the discharge cover 160. It is provided to attenuate torsional vibration transmitted along the rotation axis 125. The vibration damping member 170 according to this embodiment will be described later.

In the drawing, reference numeral 117 is a gas-liquid separation pipe, 1271 is an oil supply pipe, 1272 is an oil supply filter, 180 is an Oldham ring, and 190 is a flow guide that separates the discharged refrigerant from the recovered oil.

The scroll compressor according to this embodiment as described above operates as follows.

That is, when power is applied to the drive motor 120, a rotational force is generated in the rotor 122 and the rotation shaft 125 to rotate, and the orbiting scroll 150 eccentrically coupled to the rotation shaft 125 rotates the Oldham ring 180. A turning movement is performed with respect to the fixed scroll 140.

Then, the volume of the compression chamber (V) gradually decreases from the outside to the inside. Then, the refrigerant is sucked into the compression chamber (V) through the refrigerant suction pipe 115, compressed, and then discharged into the muffler space 160a of the discharge cover 160 through the discharge ports 1411 and 1412.

Then, this refrigerant passes through the muffler space (160a) of the discharge cover (160) and through the discharge hole (unmarked) of the fixed scroll (140) into the discharge space (S12) between the main frame (130) and the drive motor (120). moves to . Then, this refrigerant passes through the drive motor 120 and moves to the upper space (S2) of the casing 110 formed on the upper side of the drive motor 120.

The refrigerant that has moved to the upper space (S2) is separated into refrigerant and oil in the upper space (S2), and the refrigerant separated in the upper space is discharged to the outside of the casing (110) through the refrigerant discharge pipe (116). The oil separated from the refrigerant in space S2 is recovered into the storage space S11 of the casing 110.

This oil is supplied to each bearing surface (not marked) and the compression chamber (V) through the oil supply passage 126 of the rotating shaft 125. The oil supplied to the bearing surface and the compression chamber (V) is discharged to the discharge cover 160 together with the refrigerant and a series of recovery processes are repeated.

Meanwhile, as described above, during operation of the compressor, torsional vibration is generated as the rotational shaft 125 transmits the rotational force of the drive motor 120, which is a rotary motor, to the compression section, and this torsional vibration is transmitted to the casing through the compression section C. It can be transmitted to (110) to excite the compressor vibration.

Accordingly, in this embodiment, by providing a vibration damping member 170 forming a dynamic absorber in the internal space 110a of the casing 110, torsional vibration transmitted through the rotation shaft 125 can be attenuated.

Figure 3 is a perspective view showing the vibration damping member according to the present embodiment disassembled, Figure 4 is a front view showing the vibration damping member according to the present embodiment assembled, and Figure 5 is the operational effect of the vibration damping member according to the present embodiment. This is a schematic diagram showing.

Referring to Figures 3 and 4, the vibration damping member 170 according to the present embodiment includes a plurality of rigid parts 171 and a mass part 172 as described above, and the plurality of rigid parts 171 are fixed scroll They can be respectively inserted and coupled to the fixing grooves 141a provided on the lower surface of (140). For example, one end of the plurality of rigid parts 171 may be press-fitted into the fixing groove 141a of the fixed scroll 140 and coupled thereto. Accordingly, the plurality of rigid parts 171 may each extend long in the axial direction from the lower surface of the fixed scroll 140 toward the lower surface of the lower shell 113.

Specifically, the plurality of rigid parts 171 are formed in a thin rod shape, and may be formed in a circular cross-section shape. In this case, the plurality of rigid parts 171 may each have a length larger than their respective diameters. Accordingly, the plurality of rigid parts 171 have sufficient elasticity and can effectively attenuate torsional vibration.

Although not shown in the drawings, each of the plurality of rigid parts 171 may be formed in a non-circular cross-sectional shape. For example, the plurality of rigid parts 171 may each be formed in an arc-shaped cross-section. In this case, the plurality of rigid parts 171 may be formed so that each axial length is smaller than or equal to each circumferential diameter. Accordingly, the plurality of rigid parts 171 have sufficient rigidity, so that the number of rigid parts 171 can be reduced.

In addition, the lower end of the plurality of rigid parts 171 extends to the lower side of the discharge cover 160, and may extend to a position higher than the lower end of the oil pickup 127. In other words, the plurality of rigid parts 171 are arranged to surround the oil supply filter 1272 forming the oil pickup 127, and the lower ends of each may extend only to a position where they overlap the oil pickup 127 in the radial direction. Accordingly, it is possible to prevent the volume of the compressor from increasing by suppressing the plurality of rigid parts 171 from being excessively long.

Additionally, the plurality of rigid portions 171 may be formed to have the same stiffness. For example, the plurality of rigid parts 171 may be formed of the same material and the same standard. Accordingly, the torsional vibration is equally absorbed through the plurality of rigid parts 171, and the torsional vibration transmitted through the rotation shaft 125 can be stably attenuated.

Meanwhile, the mass portion 172 according to this embodiment is formed in an annular shape as described above, and the lower ends of the plurality of rigid portions 171 may be connected to the upper side facing the fixed scroll 140. For example, the mass portion 172 may be formed in an annular shape to surround the oil pickup 127 below the lower surface of the discharge cover 160.

In other words, the mass portion 172 is formed to be larger than the outer diameter of the discharge cover 160 and/or the outer diameter of the oil pickup 127 when projected in the axial direction, so that the mass portion 172 is formed to be larger than the outer diameter of the oil pickup 127 at the lower side of the discharge cover 160 in the radial direction with the oil pickup 127. It can be arranged to overlap. Accordingly, the vibration damping member 170 can be installed in the internal space 110a of the casing 110 while maintaining the axial length of the casing 110.

Although not shown in the drawing, the mass portion 172 may be formed at a position that overlaps the discharge cover 160 in the radial direction. In this case, the vibration damping member 170 may be placed higher than the oil level of the oil contained in the oil storage space. Accordingly, even if the vibration damping member 170 vibrates at the same frequency as the vibrating body, it does not affect the oil contained in the reservoir space, thereby suppressing the generation of bubbles due to the vibration of the vibration damping member 170.

Additionally, the mass portion 172 may be formed to have the same cross-sectional area along the circumferential direction, or may be formed to have a plurality of cross-sectional areas along the circumferential direction. This embodiment shows an example in which the mass portion 172 is formed to have the same cross-sectional area along the circumferential direction.

For example, the mass portion 172 may be formed in an annular shape in which the circumferential cross-sectional area is greater than or equal to the longitudinal cross-sectional area of each rigid portion 171. Accordingly, the vibration damping member 170 can absorb and attenuate torsional vibration transmitted along the rotation axis 125.

Additionally, the mass portion 172 may be formed of the same material as the rigid portion 171, but in some cases, it may be formed of a different material from the rigid portion 171. This embodiment shows an example in which the mass portion 172 is formed of the same material as the rigid portion 171. Accordingly, the mass portion 172 can be easily connected to the rigid portion 171.

For example, the mass portion 172 and the rigid portion 171 may be formed of the same iron-based material, but may be extended as a single body. In other words, a plurality of rigid parts 171 may each extend as a single body along the axial direction on one side (upper surface) of the mass part 172. In this case, there is no need to separately couple the mass portion 172 to the rigid portion 171, thereby improving the assembly efficiency between the rigid portion 171 and the mass portion 172.

As the vibration damping member 170 forming a dynamic absorber is provided in the internal space 110a of the casing 110 as described above, the driving motor 120, which is a rotating motor, is installed in the internal space 110a of the casing 110. Even if it is provided, the vibration damping member 170 absorbs the resulting torsional vibration, thereby effectively reducing the vibration noise of the compressor. (see Figure 5)

In addition, the vibration damping member 170, which forms a dynamic absorber, is provided on the lower side of the discharge cover 160, which is the lower space, and is installed to surround the oil pickup 127 that communicates with the oil supply passage 126 of the rotating shaft 125. It can be. Accordingly, the vibration damping member 170 is installed in the internal space 110a of the casing 110 without excessively increasing the size of the casing 110, thereby increasing the volume of the compressor due to the installation of the vibration damping member 170. It can be suppressed from doing so.

In addition, the vibration damping member 170 forming the dynamic absorber is composed of a plurality of rod-shaped rigid parts 171 and an annular mass part 172, and the plurality of rigid parts 171 and the mass part 172 are formed as a single body. By forming, the assembly of the vibration damping member 170 can be simplified.

Although not shown in the drawing, the mass portion 172 may be formed in a plurality of circular arc shapes. In this case, the plurality of mass parts 172 may be formed in one-to-one matching with the plurality of rigid parts 171. In this case, it is possible to improve the assembling of the vibration damping member 170 and at the same time attenuate vibrations in various frequency bands.

Meanwhile, other examples of vibration damping members are as follows.

That is, in the above-described embodiment, a plurality of rigid parts and a mass part are formed as a single body, but in some cases, a plurality of rigid parts may be post-assembled into the mass part.

Figure 6 is an exploded perspective view of another embodiment of the vibration damping member in Figure 1, and Figure 7 is an assembled front view of Figure 6.

Referring to Figures 6 and 7, the basic configuration and resulting effects of the scroll compressor according to this embodiment are the same as the above-described embodiment. For example, the scroll compressor according to this embodiment includes a casing 110, a driving motor 120 that forms a rotating motor and a rotating motor, a fixed scroll 140, a turning scroll 150, a discharge cover 160, and a vibration damping member. It is provided with a compression unit (C) including (170), and the basic configuration and effect of the casing 110, the drive motor 120, and the compression unit (C) are the same as the above-described embodiment.

However, in this embodiment, the rigid portion 171 and the mass portion 172 forming the vibration damping member 170 may be post-assembled differently from the embodiment of FIG. 3 described above. For example, the mass portion 172 is formed in an annular shape, and a plurality of fastening holes and/or fastening grooves (hereinafter, fastening holes will be described as an example) 172a) may be formed along the circumferential direction and spaced apart by a preset distance. there is. In other words, a plurality of fastening holes 172a are formed in the mass portion 172, and these fastening holes 172a may be formed on the same axis as the fixing groove 141a of the fixed scroll 140.

The rigid portion 171 is formed in the shape of a thin circular rod as in the above-described embodiment of FIG. 3, but the outer diameter of the rigid portion 171 may be formed to be larger than the inner diameter of the fastening hole 172a. In this case, a fastening protrusion 171a that is inserted into or penetrates the fastening hole 172a and fastened to the lower end of the rigid portion 171 fastened to the mass portion 172 may be formed to be stepped. For example, the length of the fastening protrusion 171a may be longer than the length of the fastening hole 172a and may be fastened with the fastening nut 175 on the other side (lower surface) of the mass portion 172.

Additionally, the upper end of the rigid portion 171 may be press-fitted into or fastened to the fixing groove 141a of the fixed scroll 140 as in the above-described embodiment. This embodiment shows an example in which screw threads are formed at the top of the rigid portion 171 and the fixing groove 141a of the fixed scroll 140 and are fastened to each other.

When the rigid portion 171 and the mass portion 172 are post-assembled as described above, the rigid portion 171 and the mass portion 172 may be formed of the same material, but in some cases, the rigid portion 171 and the mass portion ( 172) can be formed from different materials. For example, the rigid portion 171 may be formed of a material with greater rigidity per unit area than the mass portion 172, and the mass portion 172 may be formed of a material with a greater mass per unit area than the rigid portion 171. You can. On the other hand, in some cases, it can be formed in the opposite way. Through this, torsional vibration in various frequency bands can be effectively attenuated and can be appropriately changed and applied depending on the compressor capacity.

Although not shown in the drawing, a plurality of rigid parts 171 forming part of the vibration damping member 170 extend as a single body from the fixed scroll 140, and a mass part 172 forming another part of the vibration damping member 170 may be fastened to the bottom of the plurality of rigid parts 171. In this case as well, the structure in which the plurality of rigid parts 171 and the mass part 172 are fastened may be the same as the embodiment of FIG. 3 described above.

Meanwhile, another example of the vibration damping member is as follows.

That is, in the above-described embodiments, the vibration damping member is assembled to the fixed scroll, but in some cases, the vibration damping member may be coupled to the rotating shaft.

Figure 8 is an exploded perspective view of another embodiment of the vibration damping member in Figure 1, and Figure 9 is a schematic diagram showing the effect of the vibration damping member according to Figure 8.

Referring again to FIG. 2, the basic configuration and resulting effects of the scroll compressor according to this embodiment are the same as the above-described embodiment. For example, the scroll compressor according to this embodiment includes a casing 110, a driving motor 120 that forms a rotating motor and a rotating motor, a fixed scroll 140, a turning scroll 150, a discharge cover 160, and a vibration damping member. It is provided with a compression unit (C) including (170), and the basic configuration and effect of the casing 110, the drive motor 120, and the compression unit (C) are the same as the above-described embodiment.

However, as shown in FIGS. 8 and 9, in this embodiment, the vibration damping member 170 may be directly coupled to the rotation shaft 125, differently from the above-described embodiments. For example, the lower end of the rotating shaft 125 may extend long enough to protrude from the lower end of the sub-bearing unit 143, and the vibration damping member 170 may be fastened to the lower end of the rotating shaft 125. In this case, the vibration damping member 170 is located between the fixed scroll 140 and the oil pickup 127, for example, between the sub-bearing portion 143 and the oil supply pipe 1271 forming the oil pickup 127. 125).

Specifically, the vibration damping member 170 may include a plurality of rigid parts 171, mass parts 172, and fixing parts 173. Unlike the above-described embodiments, the plurality of rigid parts 171 may extend in the radial direction and be formed as a single body on the inner peripheral surface of the mass portion 172 and the outer peripheral surface of the fixing portion 173. The mass portion 172 is formed in an annular shape so that its inner circumferential surface is connected to the outer ends of the plurality of rigid portions 171, and the fixing portion 173 is formed in an annular shape so that its outer peripheral surface is connected to the inner ends of the plurality of rigid portions 171. Each can be connected. The fixing part 173 may be press-fitted to the outer peripheral surface of the rotating shaft 125 or may be post-assembled. This embodiment shows an example in which the fixing part 173 is press-fitted to the outer peripheral surface of the rotating shaft 125.

In this case as well, the cross-sectional area of each rigid portion 171 may be smaller than or equal to the cross-sectional area of the mass portion 172. Accordingly, torsional vibration transmitted through the rotation shaft 125 can be effectively attenuated.

Additionally, the cross-sectional area of the fixing part 173 may be smaller than or equal to the cross-sectional area of the mass part 172. Accordingly, the weight of the part of the vibration damping member 170 that is not involved in vibration damping is minimized and the weight of the vibration damping member 170, which forms part of the rotating body, is prevented from increasing excessively, thereby reducing the weight of the vibration damping member 170. Deterioration in compressor efficiency can be minimized.

When the vibration damping member 170 is coupled to the rotating shaft 125 as described above, the torsional vibration can be attenuated more effectively because the vibration damping member 170 is directly coupled to the rotating shaft 125, which is the source of the torsional vibration. This can further reduce compressor vibration. (see Figure 9)

Meanwhile, another example of the vibration damping member is as follows.

That is, in the above-described embodiments, the vibration damping member is provided inside the casing, but in some cases, the vibration damping member may be provided outside the casing.

Figure 10 is a perspective view showing another embodiment of the vibration damping member in Figure 1, Figure 11 is a front view of Figure 10, Figure 12 is an exploded perspective view of the vibration damping member according to Figure 10, and Figure 13 is a perspective view of Figure 10. This is a schematic diagram showing the effect of the vibration damping member according to .

Referring again to FIG. 2, the basic configuration and resulting effects of the scroll compressor according to this embodiment are the same as the above-described embodiment. For example, the scroll compressor according to this embodiment includes a casing 110, a driving motor 120 that forms a rotating motor and is a rotating motor, a fixed scroll 140, a turning scroll 150, and a discharge cover 160. It is provided with a unit (C), and the basic configuration and effect of the casing (110), the drive motor (120), and the compression unit (C) are the same as the above-described embodiment.

However, as shown in FIGS. 10 to 12, in this embodiment, the vibration damping member 170 may be installed outside the casing 110, unlike the above-described embodiments. For example, the vibration damping member 170 may be installed on the base 114 that forms part of the casing 110.

Specifically, the vibration damping member 170 includes a plurality of rigid parts 171 and a mass part 172, and the plurality of rigid parts 171 are each of the second base parts 1142 that form part of the base 114. It may extend upward along the axial direction. Accordingly, the mass portion 172 may be formed in an annular shape and arranged to surround the outer peripheral surface of the cylindrical shell 111 forming part of the casing 110 at a predetermined distance.

For example, the refrigerant suction pipe 115 is connected to one side of the cylindrical shell 111, and the mass portion 172 is formed in an annular shape to surround the cylindrical shell 111, but may be placed lower than the refrigerant suction pipe 115. . In other words, when projected in the axial direction, the outer peripheral surface of the mass portion 172 may be formed to be located within the range of the refrigerant suction pipe 115. Accordingly, the outer diameter of the vibration damping member 170 may be formed to be excessively large, thereby preventing an increase in the volume of the compressor including the vibration damping member 170.

Additionally, the plurality of rigid portions 171 and mass portions 172 may be formed as a single body as in the above-described embodiment of FIG. 3 or may be post-assembled as in the embodiment of FIG. 6 . This embodiment shows an example in which a plurality of rigid parts 171 and mass parts 172 are post-assembled.

Additionally, the plurality of rigid parts 171 may be press-fitted into the second base part 1142, or may be fastened to each other using fastening nuts 175. This embodiment shows an example in which each rigid part 171 is fastened to the second base part 1142 using a fastening nut 175.

In this case, a fastening protrusion 171a similar to the embodiment of FIG. 6 is formed at the bottom of each rigid part 171 to be stepped, and is inserted into the fastening hole 1142a provided in the second base portion 1142. 2 It can be fastened to the bottom of the base portion 1142 with a fastening nut 175.

Also, in this case, the plurality of rigid portions 171 and mass portions 172 may be formed of the same material or may be formed of different materials. In other words, the rigid portion 171 may be formed of a material with greater or lesser rigidity than the mass portion 172, and the mass portion 172 may be formed of a material heavier or lighter than the rigid portion 171.

When the vibration damping member 170 is installed outside the casing 110 as described above, the vibration damping member 170 absorbs and attenuates torsional vibration transmitted to the casing 110. (see Figure 13)

In this case, as the vibration damping member 170 is installed outside the casing 110, the specifications and/or shapes of the vibration damping member 170 can be applied in various ways. Furthermore, when the vibration damping member 170 is installed on the base 114, separate parts for fixing the vibration damping member 170 can be excluded, thereby minimizing the number of parts and forming the vibration damping member 170 ) can be installed on the outside of the casing 110.

Although not shown in the drawing, the vibration damping member 170 may be installed on the outer peripheral surface of the casing 110, for example, the outer peripheral surface of the cylindrical shell 111 and/or upper shell 112 and/or lower shell 113. . In this case, a plurality of rigid parts 171 may be directly connected to the outer peripheral surface of the casing 110 and extend in the radial direction, and as in the embodiment of FIG. 8, a separate fixing part 173 is coupled to the casing 110. In this state, a plurality of rigid parts 171 on the outer peripheral surface of the fixing part 173 may extend in the radial direction.

Meanwhile, in the above-described embodiments, a scroll compressor has been described as an example, but the same can be applied to a compressor having a transmission unit made of a rotary motor.

Claims

casing;

A drive motor provided in the inner space of the casing to generate rotational force;

A compression unit provided in the inner space of the casing and compressing the refrigerant while operating by rotational force generated by the drive motor;

a rotation shaft that connects the drive motor and the compression unit to transmit the rotational force of the drive motor to the compression unit; and

It includes a vibration damping member provided inside or outside the casing to dampen vibration,

The vibration damping member is,

A plurality of rigid parts arranged at preset intervals along the circumferential direction around the vibrating body and coupled to the vibrating body; and

A hermetic compressor including a mass portion formed in an annular shape to connect the plurality of rigid portions to each other, or an arc-shaped mass portion to be independently connected to each of the plurality of rigid portions.
According to paragraph 1,

The compression unit,

A main frame fixed to the inner space of the casing;

a fixed scroll coupled to the main frame on the opposite side of the drive motor; and

An orbiting scroll is provided between the main frame and the fixed scroll to form a compression chamber between the main frame and the fixed scroll,

The vibration damping member is,

A sealed compressor provided in the inner space of the casing.
According to paragraph 2,

The compression unit is provided on the lower side of the drive motor,

The vibration damping member is,

A sealed compressor provided on a side opposite to the side facing the drive motor among both axial sides of the compression section.
According to paragraph 1,

The compression unit,

A main frame fixed to the inner space of the casing;

a fixed scroll coupled to the main frame on the opposite side of the drive motor; and

An orbiting scroll is provided between the main frame and the fixed scroll to form a compression chamber between the main frame and the fixed scroll,

The vibration damping member is,

A closed compressor wherein one end of the rigid portion extends from the fixed scroll to the opposite side of the main frame.
According to paragraph 4,

A plurality of fixing grooves are formed on the lower surface of the fixed scroll by being depressed in the axial direction at preset intervals along the circumferential direction,

The plurality of rigid parts,

A closed compressor in which each end is inserted and coupled to the plurality of fixing grooves.
According to clause 5,

The mass portion is formed in a ring shape,

The plurality of rigid parts,

A closed compressor extending as a single body from one side of the mass portion.
According to clause 5,

The mass portion is formed in an annular shape, and a plurality of fastening holes are formed in the mass portion at predetermined intervals along the circumferential direction,

The plurality of rigid parts,

A closed compressor that is fastened to the mass portion by passing through each of the plurality of fastening holes.
In clause 7,

A closed compressor wherein the plurality of rigid parts are formed of a material having different stiffness from that of the mass part.
According to paragraph 4,

A discharge cover for accommodating refrigerant discharged from the compression chamber is provided on one side of the fixed scroll, which forms a side opposite to the orbiting scroll,

The mass part is,

A closed compressor located axially farther from the fixed scroll than the discharge cover.
According to paragraph 4,

An oil pickup is provided on one side of the fixed scroll, which forms a side opposite to the orbiting scroll, to communicate with the oil supply passage of the rotating shaft,

The mass part is,

A sealed compressor provided to surround the oil pickup.
According to paragraph 1,

The compression unit,

A main frame fixed to the inner space of the casing;

a fixed scroll coupled to the main frame on the opposite side of the drive motor; and

An orbiting scroll is provided between the main frame and the fixed scroll to form a compression chamber between the main frame and the fixed scroll,

The rotation axis passes through the main frame, the orbiting scroll, and the fixed scroll and is supported on the main frame and the fixed scroll,

The vibration damping member is,

A closed compressor coupled to the rotating shaft below the fixed scroll.
According to clause 11,

The vibration damping member further includes a fixing part inserted and coupled to the outer peripheral surface of the rotating shaft,

The plurality of rigid parts,

A sealed compressor extending radially from the outer peripheral surface of the fixing part.
According to clause 12,

A closed compressor in which the fixing part, the plurality of rigid parts, and the mass part are formed as a single body.
According to paragraph 1,

The compression unit,

A main frame fixed to the inner space of the casing;

a fixed scroll coupled to the main frame on the opposite side of the drive motor; and

An orbiting scroll is provided between the main frame and the fixed scroll to form a compression chamber between the main frame and the fixed scroll,

The vibration damping member is,

A sealed compressor provided outside the casing.
According to clause 14,

A base is provided on the lower surface of the casing to support the casing on the compressor installation surface,

The plurality of rigid parts,

A closed compressor extending from the base in a direction opposite to the compressor installation surface.
According to clause 15,

The base is,

a first base portion in contact with the lower surface of the casing; and

It includes a plurality of second base parts extending radially from the first base part and supported on the compressor installation surface,

The plurality of rigid parts,

A closed compressor extending along an axial direction from each of the plurality of second base parts.
According to clause 16,

A fastening groove or fastening hole is formed in each of the plurality of second base parts,

The plurality of rigid parts,

A closed compressor whose end is inserted into the fastening groove or the fastening hole and fastened.
According to clause 14,

A refrigerant suction pipe communicating with the compression chamber is penetrated and coupled to the casing,

The mass part is,

A closed compressor located below the refrigerant intake pipe.