KR20240049729A - Scroll compressor - Google Patents

Abstract

A scroll compressor is disclosed. The scroll compressor includes a drive motor, a rotating shaft, an orbiting scroll, a non-orbiting scroll, a cylindrical shell, a base, a lower bearing, and a lower cap. The lower bearing is coupled through the bearing mounting hole of the base, and the lower cap is connected to the lower bearing. It may be coupled to the base by providing a bearing receiving portion to accommodate the. Through this, foreign substances generated during processing of the inner circumferential surface of the lower bearing can be discharged to the outside of the casing before the bottom of the casing is sealed, thereby preventing foreign substances from remaining in the oil storage space.

Description

Scroll compressor {SCROLL COMPRESSOR}

The present invention relates to scroll compressors.

Scroll compressors can be classified into an upper compression type or a lower compression type depending on the location of the driving motor and compression section that make up the driving or transmission section. The upper compression type is a type in which the compression part is located above the drive motor, and the bottom compression type is a type in which the compression part is located below the drive motor. This is a classification based on the case where the casing is installed vertically or vertically. If the casing is installed horizontally, the left side can be divided into the upper side and the right side can be divided into the lower side.

Additionally, scroll compressors can be divided into high-pressure and low-pressure types depending on the way the refrigerant is sucked. The high-pressure type is a type in which the refrigerant suction pipe communicates directly with the suction chamber and the inhaled refrigerant is sucked into the compression chamber (suction chamber) without passing through the inner space of the casing. The low-pressure type is a type in which the refrigerant suction pipe communicates directly with the inner space of the casing so that the inhaled refrigerant is sucked into the compression chamber (suction chamber). This method involves passing through the internal space of the casing and then being sucked into the compression chamber (suction chamber). Patent Document 1 (US Patent Publication US 2015/0345493 A) shows a scroll compressor that is a top compression type and a low pressure type. Patent Document 1 seals the internal space of the casing by welding a base to the bottom of the cylindrical shell that forms part of the casing. However, in Patent Document 1, the lower bearing is spaced apart from the base, and an oil pump with a trochoid gear is installed at the bottom of the rotating shaft to support the rotating shaft in the axial direction.

Patent Document 2 (US Patent US6,247,909 B1), like Patent Document 1, seals the internal space of the casing by welding a base to the bottom of the cylindrical shell that forms part of the casing. However, in Patent Document 2, the lower bearing is coupled to the upper surface of the base, and a cylindrical radial bearing and a disk-shaped axial bearing are respectively inserted inside the lower bearing.

However, in the conventional scroll compressor as described above, when the lower bearing is spaced apart from the base as in Patent Document 1, the axial support force for the compression part including the rotating shaft is limited, while when the lower bearing is in close contact with the base as in Patent Document 2. In this case, foreign matter generated during machining of the inner circumferential surface to form the radial bearing surface after assembling the lower bearing may remain in the oil storage space and flow into the bearing surface along with oil during refueling, causing wear of the bearing surface.

In addition, the conventional scroll compressor is connected by inserting a base into the cylindrical shell forming the casing, but this may limit the oil storage amount because the low oil volume of the casing is limited to the inner diameter of the cylindrical shell.

US published patent US 2012/0107163 A1 (publication date: 2012.05.03.) US Patent US6,247,909 B1 (Registration date: 2001.06.19.)

The purpose of the present invention is to provide a scroll compressor equipped with a lower bearing that can stably support a compression unit including a rotating shaft.

Another object of the present invention is to provide a scroll compressor that can stably support the compression unit including the rotating shaft and smoothly discharge foreign substances generated during processing of the inner peripheral surface of the lower bearing to the outside of the casing.

Another object of the present invention is to provide a scroll compressor that can increase the oil storage amount by expanding the oil storage volume of the casing.

In order to achieve the purpose of the present invention, the scroll compressor may include a drive motor, a rotating shaft, an orbiting scroll, a non-orbiting scroll, a cylindrical shell, a base, a lower bearing, and a lower cap. The rotation shaft transmits the rotational force of the drive motor. The orbiting scroll is coupled to the rotation shaft and performs a orbital movement. The non-orbiting scroll engages with the orbiting scroll to form a compression chamber. The cylindrical shell is fixed by inserting the drive motor, and has openings at both ends. The base is provided with a base insertion protrusion to be inserted into the lower end of the cylindrical shell to cover the lower end of the cylindrical shell, and a bearing mounting hole is formed through it in the axial direction. The lower bearing is coupled through a bearing mounting hole in the base and supports the rotating shaft. The lower cap may be coupled to the base by having a bearing receiving portion to accommodate the lower bearing. Through this, foreign substances generated during processing of the inner circumferential surface of the lower bearing can be discharged to the outside of the casing before the bottom of the casing is sealed, thereby preventing foreign substances from remaining in the oil storage space.

For example, the bearing mounting hole may be formed on the same axis as the base insertion protrusion. Through this, the lower bearing can be easily coupled on the same axis as the rotation axis.

For example, a bearing support protrusion for supporting the lower bearing in the radial direction is formed around the bearing mounting hole, and the bearing support protrusion may be formed in an annular shape. Through this, the lower bearing can be stably supported in the radial direction.

As another example, the lower bearing may include a fixing protrusion and a bearing protrusion. The fixing protrusion may be fixed to the base. The bearing protrusion extends axially from the fixing protrusion to penetrate the bearing mounting hole, and the rotation shaft can be rotatably inserted and supported in the radial direction. Through this, the lower bearing extends to the outside of the base, making it possible to easily discharge foreign substances generated during processing of the inner circumferential surface of the lower bearing to the outside of the base.

For example, the fixing protrusion may extend radially from one end of the bearing protrusion and be fixed to the outer surface of the base from the outside of the cylindrical shell. Through this, the lower bearing can be easily fixed while extending it to the outside of the base.

Specifically, a plurality of first fastening holes are formed between the bearing mounting hole and the base insertion protrusion at predetermined intervals along the circumferential direction, and the fixing protrusion corresponds to a portion of the first fastening hole in the axial direction. A second fastening hole may be formed to do so. Other portions of the plurality of first fastening holes may communicate with the bearing receiving portion of the lower cap outside the fixing protrusion. Through this, the lower bearing can be easily fastened to the base and the inner space of the cylindrical shell can be easily communicated with the bearing receiving portion.

More specifically, the fixing protrusion may have a plurality of extension parts extending in the radial direction to have an angular cross-sectional shape when projected in the axial direction, and the second fastening holes may be formed in each of the extension parts. Through this, while fastening the lower bearing to the base, a part of the first fastening hole provided in the base can be exposed to the outside of the lower bearing, allowing smooth communication between the internal space of the cylindrical shell and the bearing receiving portion.

For example, an axial bearing member that supports the rotating shaft in the axial direction may be provided on the inner peripheral surface of the bearing protrusion. Through this, the rotating shaft can be supported in the axial direction while both ends of the bearing protrusion are open.

Specifically, the inner peripheral surface of the bearing protrusion may be provided in an annular shape to form a stepped bearing support surface on which the axial bearing member is supported in the axial direction toward the rotation axis. Through this, the insertion position is limited when inserting the axial bearing member, so that the axial bearing member can be easily and accurately installed.

More specifically, the bearing support surface may have an inner diameter on a side facing the drive motor that is smaller than an inner diameter on a side facing the lower cap. A bearing support member may be provided on one axial side of the bearing support surface to support the axial bearing member in a direction opposite to the rotation axis. Through this, the axial bearing member can be easily mounted while supporting the axial bearing member in the axial direction.

In addition, the axial bearing member may have a bearing body formed in an annular shape, and a guide protrusion extending radially from the outer peripheral surface of the bearing body may be formed. A guide groove into which the guide protrusion is slidably inserted in the axial direction may be formed on the inner peripheral surface of the bearing protrusion. Through this, the lower end of the rotating shaft can be stably supported by suppressing distortion of the axial bearing member when the axial bearing member is inserted.

As another example, the lower cap may have an inner diameter of the bearing receiving portion that is greater than or equal to an outer diameter of the lower bearing, so that the lower bearing can be fixed to the outer surface of the base. Through this, the bearing mounting hole of the base can be covered from the outside of the base while the lower cap accommodates the lower bearing.

For example, the inner diameter of the bearing receiving portion may be formed to be smaller than or equal to the outer diameter of the base insertion protrusion. Through this, an increase in manufacturing costs can be suppressed by optimizing the size of the lower cap.

Additionally, the inner diameter of the bearing receiving portion may be formed to be larger than or equal to the outer diameter of the base insertion protrusion. Through this, the volume of the lower cap can be increased and the oil storage space of the casing can be expanded.

The scroll compressor according to the present invention includes a drive motor, a rotating shaft, an orbiting scroll, a non-orbiting scroll, a cylindrical shell, a base, a lower bearing, and a lower cap. The lower bearing is coupled through the bearing mounting hole of the base, and the lower cap can be coupled to the base by providing a bearing receiving portion to accommodate the lower bearing. Through this, foreign substances generated during processing of the inner circumferential surface of the lower bearing can be discharged to the outside of the casing before the bottom of the casing is sealed, thereby preventing foreign substances from remaining in the oil storage space.

In the scroll compressor according to the present invention, the lower bearing includes a fixing protrusion and a bearing protrusion, the fixing protrusion is fixed to the base, and the bearing protrusion may extend in the axial direction from the fixing protrusion. Through this, the lower bearing extends to the outside of the base, making it possible to easily discharge foreign substances generated during processing of the inner circumferential surface of the lower bearing to the outside of the base.

In the scroll compressor according to the present invention, the lower cap is formed so that the inner diameter of the bearing receiving portion is greater than or equal to the outer diameter of the lower bearing, so that the lower bearing can be fixed to the outer surface of the base. Through this, the bearing mounting hole of the base can be covered from the outside of the base while the lower cap accommodates the lower bearing.

In the scroll compressor according to the present invention, the inner diameter of the bearing receiving portion may be formed to be smaller than or equal to the inner diameter of the base insertion protrusion. Through this, an increase in manufacturing costs can be suppressed by optimizing the size of the lower cap.

In the scroll compressor according to the present invention, the inner diameter of the bearing receiving portion may be formed to be larger than or equal to the inner diameter of the base insertion protrusion. Through this, the volume of the lower cap can be increased and the oil storage space of the casing can be expanded.

1 is a longitudinal cross-sectional view showing the inside of a scroll compressor according to this embodiment.
Figure 2 is a perspective view showing the periphery of the lower bearing in Figure 1 broken away.
Figure 3 is a perspective view of Figure 2 exploded from above.
Figure 4 is a perspective view of Figure 2 disassembled from the bottom.
Figure 5 is an exploded perspective view of the lower bearing in Figure 4.
Figure 6 is a cross-sectional view showing the assembled periphery of the lower bearing in Figure 2.
Figure 7 is a cross-sectional view taken along line "IX-IX" of Figure 6.
Figure 8 is a cross-sectional view showing the assembly position of the lower cap in Figure 2.
Figure 9 is a broken perspective view of another embodiment of the lower cap in Figure 1.
Figure 10 is a cross-sectional view showing the assembly position of the lower cap in Figure 9.

Hereinafter, a scroll compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings.

Typically, scroll compressors can be divided into a vertical scroll compressor whose rotation axis is arranged perpendicular to the ground and a horizontal scroll compressor whose rotation axis is arranged parallel to the ground. For example, in a vertical scroll compressor, the upper side may be defined as facing away from the ground, and the lower side may be defined as facing toward the ground. Hereinafter, a vertical scroll compressor will be described as an example. However, it can be applied equally or similarly to a horizontal scroll compressor. Therefore, hereinafter, the axial direction is understood as the axial direction of the rotation axis, and the radial direction is understood as the radial direction of the rotation axis. The axial direction is understood as the up and down direction, the radial direction as the left and right sides, the inner peripheral surface as the top surface, and the axial radial direction as the side surfaces, respectively. It can be understood.

1 is a longitudinal cross-sectional view showing the inside of a scroll compressor according to this embodiment.

Referring to Figure 1, in the scroll compressor according to this embodiment, a drive motor 120 forming a transmission part is installed in the lower half of the casing 110, and a main frame 130 forming a compression part is installed on the upper side of the drive motor 120, An orbiting scroll 140, a non-orbiting scroll 150, and a back pressure chamber assembly 160 are installed. The transmission part is coupled to one end of the rotation shaft 125, and the compression part is coupled to the other end of the rotation shaft 125. Accordingly, the compression unit is connected to the transmission unit by the rotation shaft 125 and operates by the rotational force of the transmission unit.

The casing 110 includes a cylindrical shell 111, a cover 112, and a base 113.

The cylindrical shell 111 has a cylindrical shape with openings at both upper and lower ends, and the above-described drive motor 120 and main frame 130 are inserted and fixed to the inner peripheral surface. A terminal bracket (not shown) is coupled to the upper half of the cylindrical shell 111. A terminal (not shown) for transmitting external power to the drive motor 120 is coupled through the terminal bracket. In addition, a refrigerant suction pipe 117, which will be described later, penetrates and is coupled to the upper half of the cylindrical shell 111, for example, the upper side of the drive motor 120.

The cover 112 is coupled to cover the open top of the cylindrical shell 111. Between the cylindrical shell 111 and the cover 112, the edge of a high-low pressure separator plate 115, which will be described later, is inserted and welded to the cylindrical shell 111 and the cover 112. Accordingly, the upper space of the casing 110 is sealed.

The base 113 is coupled to cover the opened lower end of the cylindrical shell 111. For example, a base insertion protrusion 113c, which will be described later, is formed on the base 113 and can be welded and coupled to the bottom of the cylindrical shell 111 in a press-fitted state. However, the base 113 according to this embodiment is formed with a bearing mounting hole 113a so that the lower bearing 180, which will be described later, passes through and is coupled to it, and this bearing mounting hole 113a is formed by the lower cap 114, which will be described later. It is covered. Accordingly, the lower space of the casing 110 is sealed.

In addition, the base 113 forms an oil storage space 110c together with the lower half of the cylindrical shell 111 and the lower cap 114, which will be described later. The oil storage space 110c will be described again later along with the base 113 and lower cap 114.

Referring to FIG. 1, the drive motor 120 according to this embodiment is installed in the lower half of the low-pressure part 110a and includes a stator 121 and a rotor 122. The stator 121 is fixed to the inner wall of the cylindrical shell 111 by hot pressing, and the rotor 122 is rotatably provided inside the stator 121.

The stator 121 includes a stator core 1211 and a stator coil 1212.

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 within 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 140, 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 140 through the rotation shaft 125.

An eccentric portion 1251 is formed at the top of the rotation shaft 125, which is eccentrically coupled to the orbiting scroll 140, which will be described later. An oil pickup 126 may be installed at the bottom of the rotating shaft 125 to absorb oil stored in the lower part of the casing 110. The rotation shaft 125 is formed with an oil passage 1252 penetrating therein in the axial direction.

Referring to FIG. 1, the main frame 130 according to this embodiment is installed on the upper side of 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 according to this embodiment includes a main flange portion 131, a main bearing portion 132, a pivoting space portion 133, a scroll support portion 134, an Oldham ring support portion 135, and a frame fixing portion 136. ) includes.

The main flange portion 131 is formed in an annular shape and is accommodated in the low pressure portion 110a of the casing 110. The outer diameter of the main flange portion 131 is smaller than the inner diameter of the cylindrical shell 111, so that the outer peripheral surface of the main flange portion 131 is spaced apart from the inner peripheral surface of the cylindrical shell 111. However, a frame fixing part 136, which will be described later, protrudes in the radial direction from the outer peripheral surface of the main flange part 131. The outer peripheral surface of the frame fixing part 136 is fixed in close contact with the inner peripheral surface of the casing 110. Accordingly, the frame 130 is fixedly coupled to the casing 110.

The main bearing portion 132 protrudes downward from the central lower surface of the main flange portion 131 toward the drive motor 120. The main bearing portion 132 has a cylindrical bearing hole 132a penetrating in the axial direction. A rotating shaft 125 is inserted into the inner peripheral surface of the bearing hole 132a and supported in the radial direction.

The pivoting space portion 133 is depressed from the center of the main flange portion 131 toward the main bearing portion 132 to a preset depth and outer diameter. The orbiting space portion 133 is formed to be larger than the outer diameter of the rotation shaft coupling portion 143 provided in the orbiting scroll 140, which will be described later. Accordingly, the rotation shaft coupling portion 143 can be rotatably accommodated within the pivot space portion 133.

The scroll support portion 134 is formed in an annular shape along the periphery of the pivot space portion 133 on the upper surface of the main flange portion 131. Accordingly, the scroll support part 134 can support the bottom surface of the turning plate part 141, which will be described later, in the axial direction.

The Oldham ring support portion 135 is formed in an annular shape along the outer peripheral surface of the scroll support portion 134 on the upper surface of the main flange portion 131. Accordingly, the Oldham ring 170 can be inserted into the Oldham ring support portion 135 and pivotably accommodated.

The frame fixing portion 136 extends radially from the outside of the Oldham ring support portion 135. The frame fixing portion 136 extends in an annular shape or with a plurality of protrusions spaced apart from each other by a predetermined distance along the circumferential direction. This embodiment shows an example in which the frame fixing portion 136 is formed of a plurality of protrusions along the circumferential direction.

Referring to FIG. 1, the orbiting scroll 140 according to this embodiment is coupled to the rotation shaft 125 and is provided between the main frame 130 and the non-orbiting scroll 150. An Oldham ring 170, an anti-rotation mechanism, is provided between the main frame 130 and the orbiting scroll 140. Accordingly, the rotating movement of the orbiting scroll 140 is restrained and the orbiting scroll 140 performs a rotating movement with respect to the non-orbiting scroll 150.

Specifically, the orbiting scroll 140 includes a pivoting plate portion 141, a pivoting wrap 142, and a rotating shaft engaging portion 143.

The pivot plate portion 141 is formed in a substantially disk shape. The outer diameter of the pivot plate portion 141 is supported in the axial direction by being placed on the scroll support portion 134 of the frame 130. Accordingly, the pivot plate portion 141 and the scroll support portion 134 facing it form an axial bearing surface (not denoted).

The orbiting wrap 142 is formed in a spiral shape by protruding at a preset height from the upper surface of the orbiting mirror plate portion 141 facing the non-orbiting scroll 150. The orbiting wrap 142 is formed to correspond to the non-orbiting wrap 152 of the non-orbiting scroll 150, which will be described later, so as to engage with the non-orbiting wrap 152 and perform a rotating movement. Accordingly, the orbiting wrap 142 forms a compression chamber (V) together with the non-swivel wrap 152.

The compression chamber (V) consists of a first compression chamber (V1) and a second compression chamber (V2) based on the turning wrap (142). The first compression chamber (V1) and the second compression chamber (V2) are formed sequentially as a suction pressure chamber (not symbol), an intermediate pressure chamber (not symbol), and a discharge pressure chamber (not symbol), respectively. Hereinafter, the compression chamber formed between the outer surface of the orbital wrap 142 and the inner surface of the non-swivel wrap 152 facing it is referred to as the first compression chamber V1, and the inner surface of the orbital wrap 142 and the inner surface of the non-swivel wrap 152 facing it are referred to as the first compression chamber V1. The description will be made by defining the compression chamber formed between the outer surfaces of the non-swivel wrap 152 as the second compression chamber V2.

The rotation shaft coupling portion 143 is formed to protrude from the lower surface of the pivot plate portion 141 toward the main frame 130. The rotation shaft coupling portion 143 is formed in a cylindrical shape so that a slew bearing (not shown) made of a bush bearing can be press-fitted.

Referring to FIG. 1, the non-orbiting scroll 150 according to this embodiment is disposed on the upper part of the main frame 130 with the orbiting scroll 140 interposed therebetween. The non-orbiting scroll 150 may be fixedly coupled to the main frame 130 or movably coupled to the main frame 130. This embodiment shows an example in which the non-orbiting scroll 150 is movably coupled to the main frame 130 in the axial direction.

The non-orbiting scroll 150 according to this embodiment includes a non-orbiting head plate portion 151, a non-orbiting wrap 152, a non-orbiting side wall portion 153, and a guide protrusion 154.

The non-swivel plate portion 151 is formed in a disk shape and is disposed laterally in the low pressure portion 110a of the casing 110. A discharge port 1511, a bypass hole 1512, and a scroll side pressure hole 1513 are each penetrated in the central portion of the non-swivel mirror plate portion 151 in the axial direction.

The discharge port 1511 is formed at a position where the discharge pressure chambers (not marked) of both compression chambers V1 and V2 formed inside and outside the non-circulating wrap 152 communicate with each other. The bypass hole 1512 is formed to communicate with both compression chambers V1 and V2, respectively. The scroll side back pressure hole (hereinafter referred to as the first back pressure hole) 1513 is spaced apart from the discharge port 1511 and the bypass hole 1512.

The non-swivel wrap 152 extends in the axial direction from the lower surface of the non-swivel head plate 151 facing the orbital scroll 140 to a preset height, and extends from the non-swivel side wall portion 153 around the discharge port 1511. It extends to be wound several times in a spiral direction. The non-swivel wrap 152 is formed to correspond to the swirl wrap 142 and can form a pair of compression chambers (V) between the non-swivel wrap 142 and the swirl wrap 142 .

The non-swivel side wall portion 153 extends in the axial direction from the lower edge of the non-swivel hard plate portion 151 to surround the non-swivel wrap 152 and is formed in an annular shape. An intake port 1531 penetrating in the radial direction is formed on one side of the outer peripheral surface of the non-circulating side wall portion 153.

The guide protrusion 154 may extend in the radial direction from the lower outer peripheral surface of the non-circulating side wall portion 153. The guide protrusion 154 may be formed in a single annular shape, or may be formed in plural pieces at predetermined intervals along the circumferential direction. This embodiment shows an example in which a plurality of guide protrusions 154 are formed at preset intervals along the circumferential direction.

Referring to FIG. 1, the back pressure chamber assembly 160 according to this embodiment is provided above the non-orbiting scroll 150. Accordingly, the back pressure of the back pressure chamber 160a (more precisely, the force that the back pressure exerts on the back pressure chamber) acts on the non-orbiting scroll 150. In other words, the non-orbiting scroll 150 is pressed in the direction toward the orbiting scroll 140 by back pressure to seal both compression chambers (V1) (V2).

Specifically, the back pressure chamber assembly 160 includes a back pressure plate 161 and a floating plate 165. The back pressure plate 161 is coupled to the upper surface of the non-swivel plate portion 151. The floating plate 165 is slidably coupled to the back pressure plate 161 to form a back pressure chamber 160a together with the back pressure plate 161.

The back pressure plate 161 includes a fixing plate portion 1611, a first annular wall portion 1612, and a second annular wall portion 1613.

A plate-side back pressure hole (hereinafter referred to as a second back pressure hole) 1611a penetrates the fixing plate portion 1611 in the axial direction. The second back pressure hole 1611a communicates with the compression chamber V through the first back pressure hole 1513. Accordingly, the second back pressure hole 1611a, together with the first back pressure hole 1513, communicates between the compression chamber V and the back pressure chamber 160a.

The first annular wall portion 1612 and the second annular wall portion 1613 surround the inner peripheral surface and the outer peripheral surface of the fixed plate portion 1611 on the upper surface of the fixed plate portion 1611. Accordingly, the outer peripheral surface of the first annular wall portion 1612, the inner peripheral surface of the second annular wall portion 1613, the upper surface of the fixing plate portion 1611, and the lower surface of the floating plate 165 form an annular back pressure chamber 160a. do.

An intermediate discharge port 1612a communicating with the discharge port 1511 of the non-orbiting scroll 150 is formed in the first annular wall portion 1612. A valve guide groove 1612b into which the discharge valve 155 is slidably inserted is formed inside the middle discharge port 1612a. A backflow prevention hole (1612c) is formed in the center of the valve guide groove (1612b). Accordingly, the discharge valve 155 selectively opens and closes between the discharge port 1511 and the intermediate discharge port 1612a to block the discharged refrigerant from flowing back into the compression chambers (V1) (V2).

The floating plate 165 is formed in a ring shape. The floating plate 165 may be made of a material lighter than the back pressure plate 161. Accordingly, the floating plate 165 moves in the axial direction with respect to the back pressure plate 161 according to the pressure of the back pressure chamber 160a and is attached to and detached from the lower side of the high and low pressure separator plate 115. For example, when the floating plate 165 comes into contact with the high-low pressure separator plate 115, it serves to seal the discharged refrigerant so that it is discharged to the high-pressure section 110b without leaking into the low-pressure section 110a.

O, an unexplained symbol in the drawing, is the center of the rotation axis.

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

That is, when power is applied to the stator coil 121a of the stator 121, the rotor 122 rotates together with the rotation shaft 125. Then, the orbiting scroll 140 coupled to the rotation axis 125 makes a orbital movement with respect to the non-orbiting scroll 150, and between the orbiting wrap 142 and the non-orbiting wrap 152, two pairs of compressions are formed. A thread (V) is formed.

The compression chamber (V) gradually decreases in volume as it moves from the outside to the inside according to the turning movement of the turning scroll (140). At this time, the refrigerant is sucked into the low-pressure part (110a) of the casing (110) through the refrigerant suction pipe (117), and a part of this refrigerant is sucked directly into each suction pressure chamber (not marked) forming both compression chambers (V). The remainder moves toward the drive motor 120, cools the drive motor 120, and is then sucked into the suction pressure chamber (not marked).

Next, the refrigerant sucked into the suction pressure chamber (not marked) is compressed while moving toward the intermediate pressure chamber and the discharge pressure chamber (not marked) along the movement path of the compression chamber (V). The refrigerant moving to the discharge pressure chamber (not marked) is discharged to the high pressure section (110b) through the discharge port 1411 and the intermediate discharge port 1612a while pushing the discharge valve 145, and this refrigerant fills the high pressure section (110b) and then discharges the refrigerant. A series of processes are repeated to discharge through the condenser of the refrigeration cycle through the pipe 118.

In addition, another part of the refrigerant compressed while passing through the intermediate pressure chamber (not denoted) also flows into the back pressure chamber 160a before reaching the discharge port 1411, so that the back pressure chamber 160a forms intermediate pressure. Then, the non-orbiting scroll 150 descends toward the orbiting scroll 140 and seals the gap between it and the orbiting scroll 140, thereby suppressing leakage between compression chambers.

In addition, as described above, the lower end of the rotating shaft 125 is supported by the lower bearing 180, which will be described later, and rotates while submerged in the oil stored in the oil storage space 110c of the casing 110. Then, the oil in the oil storage space 110c is pumped by the oil pickup 126, and this oil is absorbed along the oil passage 1253 of the rotating shaft 125 and scatters inside the rotating shaft coupling portion 143. Some of this oil flows down along the inner peripheral surface of the rotating shaft coupling portion 143 and is supplied to the bearing surfaces between neighboring members through the orbital space portion 133 to lubricate them.

Meanwhile, foreign substances may be generated in the compressor during the assembly process, contaminating the oil. For example, the lower bearing into which the lower end of the rotating shaft is inserted must be located on the same axis as the base insertion protrusion of the base that is press-fitted into the cylindrical shell. For this purpose, the inner peripheral surface of the lower bearing is coaxially processed with respect to the base insertion protrusion after assembling the base, and foreign substances such as metal residue generated at this time remain on the upper surface of the base, that is, in the oil storage space. . These foreign substances may be mixed with the oil and flow into the bearing surface along the oil passage of the rotating shaft. Then, the bearing surface may be damaged by foreign substances and compression efficiency may decrease.

Accordingly, in this embodiment, as the lower bearing penetrates and is coupled to the center of the opened base 113, foreign matter generated during processing of the inner peripheral surface of the lower bearing 180 is exposed to the upper surface of the base 113, that is, the casing 110. Remaining in the oil storage space 110c can be prevented in advance. However, in this embodiment, the inner space of the casing 110 can be sealed by covering the central portion of the opened base 113 with the lower cap 114, which is a separate cap member.

Figure 2 is a perspective view showing the periphery of the lower bearing in Figure 1 broken away, Figure 3 is a perspective view showing Figure 2 disassembled from the top, Figure 4 is a perspective view showing Figure 2 disassembled from the bottom, and Figure 5 is Figure 4 is a perspective view showing the lower bearing disassembled, Figure 6 is a cross-sectional view showing the surroundings of the lower bearing in Figure 2 assembled, Figure 7 is a cross-sectional view "IX-IX" of Figure 6, and Figure 8 is the lower cap in Figure 2. This is a cross-sectional view showing the assembly location.

Referring to FIGS. 2 to 5, the base 113 according to this embodiment is formed in a roughly square shape when projected in the axial direction, but the corners extend in the radial direction and may be provided with a buffer member (not shown) such as rubber. there is. Accordingly, the base 113 covers the lower end of the cylindrical shell 111, forms part of the casing 110, and forms a compressor fixing part fixed to the compressor installation surface.

In addition, a bearing mounting hole 113a is formed in the center of the base 113 through which the lower bearing 180, which will be described later, passes. The bearing mounting hole 113a is formed to correspond to the shape of the lower bearing 180. In this embodiment, as the bearing protrusion 182 of the lower bearing 180, which will be described later, is formed in a cylindrical shape, the bearing mounting hole 113a may also be formed in a cylindrical shape.

Additionally, a bearing support protrusion 113b may be formed around the bearing mounting hole 113a to radially support the bearing protrusion 182 of the lower bearing 180, which will be described later. For example, the bearing support protrusion 113b extends in the axial direction, but the bearing support protrusion 113b may extend in a direction toward the lower cap 114, or, conversely, may extend in a direction toward the drive motor 120. there is. This embodiment shows an example in which the bearing support protrusion 113b extends in a direction toward the drive motor 120. Accordingly, even if the base 113 is formed to be thin, the lower bearing 180 can be stably supported.

In addition, a base insertion protrusion 113c is formed on the outer portion of the base 113, that is, on the outside of the bearing mounting hole 113a, to be inserted into and fixed to the cylindrical shell 111. For example, the base insertion protrusion 113c is formed in an annular shape and may protrude toward the bottom of the cylindrical shell 111 by a preset height. Accordingly, the outer peripheral surface of the base insertion protrusion 113c is in close contact with the inner peripheral surface of the cylindrical shell 111, thereby sealing the lower end of the cylindrical shell 111 forming the oil storage space 110c.

In addition, a first fastening hole 113d may be formed between the bearing mounting hole 113a and the base insertion protrusion 113c, that is, around the bearing mounting hole 113a, for fastening the lower bearing 180, which will be described later. there is. The first fastening hole 113d may be formed to correspond to the second fastening hole 1811a of the lower bearing 180, which will be described later, on the same axis. Accordingly, the lower bearing 180 can be fixedly coupled to the base 113 by the fastening member 184 inserted into and fastened to the first fastening hole 113d and the second fastening hole 1811a.

The first fastening holes 113d may be formed in the same number as the second fastening holes 1811a, or may be formed in more numbers than the second fastening holes 1811a. This embodiment shows an example in which the first fastening holes 113d are formed more than the second fastening holes 1811a. For example, a plurality of first fastening holes 113d may be formed around the bearing mounting hole 113a, precisely outside the bearing support protrusion 113b, at predetermined intervals along the circumferential direction. In this case, a portion of the first fastening hole 113d is formed on the same axis as the second fastening hole 1811a, which will be described later, so that the fastening member 184 for fastening the base 113 and the lower bearing 180 penetrates. You can. And the remaining first fastening hole 113d is exposed to the outside of the lower bearing 180, that is, the outside of the fixing protrusion 181, which will be described later, and communicates with the bearing receiving portion 114a of the lower cap 114, which will be described later, and forms a cylindrical shell. A type of oil hole is formed between the inner space of (111) and the bearing receiving portion (114a) of the lower cap (114).

A lower bearing 180 supporting the lower end of the rotating shaft 125 in the radial and axial directions is inserted and coupled to the center of the base 113 according to this embodiment, that is, the bearing mounting hole 113a. The lower bearing 180 may be fixed to the outer surface, i.e., lower surface, of the base 113, or may be fixed to the inner surface, i.e., upper surface, of the base 113. This embodiment shows an example in which the lower bearing 180 is fixed to the outer surface of the base 113.

Referring to Figures 5 and 6, the lower bearing 180 according to this embodiment includes a fixing protrusion 181 and a bearing protrusion 182. The fixing protrusion 181 is a part where the lower bearing 180 is fixed to the base 113, and the bearing protrusion 182 is a part into which the rotation shaft 125 is inserted and supported in the radial direction.

The fixing protrusion 181 extends in the radial direction from the bottom of the bearing protrusion 182, and may be formed in a circular cross-section shape or an angular cross-section shape. This embodiment shows an example in which the fixing protrusion 181 is formed in an angular cross-sectional shape.

Specifically, the fixing protrusion 181 may have a plurality of extension parts 1811 (three in the drawing) extending in the radial direction, so that when projected in the axial direction, the fixing protrusion 181 may be formed into a substantially triangular angular cross-sectional shape. The previously described second fastening holes 1811a may be formed in each of the extension portions 1811. In other words, the second fastening hole 1811a may be formed so that the virtual circle connecting the center of each second fastening hole 1811a has the same diameter as the virtual circle connecting the center of the first fastening hole 113d. . Accordingly, the fixing protrusion 181 of the lower bearing 180 can be fastened to the lower side of the base 113 using the fastening member 184 penetrating the first fastening hole 113d and the second fastening hole 1811a. You can.

In addition, as the fixing protrusion 181 is formed by extending a plurality of extension parts 1811 in the radial direction as described above, the space between the extension parts 1811 may be formed as a straight surface. Accordingly, among the plurality of first fastening holes 113d, the first fastening hole 113d is located on a different axis from the second fastening hole 1811a, that is, the first fastening hole 113d does not overlap in the axial direction with the extension portion 1811. The fastening hole 113d is exposed to the outside of the fixing protrusion 181, and the first fastening hole 113d exposed to the outside of the fixing protrusion 181 is the inner space of the cylindrical shell 111 and the lower cap (to be described later) It communicates with the bearing receiving portion 114a of 114) to form a type of oil hole.

The bearing protrusion 182 is formed in a cylindrical shape and is open at both ends in the axial direction. For example, the outer diameter of the bearing protrusion 182 is formed to be smaller than or equal to the inner diameter of the bearing mounting hole 113a, and the inner diameter of the bearing protrusion 182 is formed to be larger than or equal to the outer diameter of the rotating shaft 125. Accordingly, the bearing protrusion 182 may be inserted into the bearing mounting hole 113a and supported in the radial direction, while the rotation shaft 125 may be inserted into the inner peripheral surface of the bearing protrusion 182 and supported in the radial direction.

The inner peripheral surface of the bearing protrusion 182 may be formed on the same axis as the outer peripheral surface of the base insertion protrusion 113c. In other words, as the rotating shaft 125 is formed on the same axis as the inner peripheral surface of the cylindrical shell 111 and the inner peripheral surface of the stator 121, the inner peripheral surface of the bearing protrusion 182 into which the lower end of the rotating shaft 125 is inserted is also cylindrical shell 111. ) is formed on the same axis as the inner peripheral surface of the base insertion protrusion (113c) and the outer peripheral surface of the base insertion protrusion (113c).

Although not shown in the drawing, the lower bearing 180 may be fixed to the inner surface of the base 113, that is, the upper surface of the base 113. For example, the fixing protrusion 181 of the lower bearing 180 may extend radially from the middle of the outer peripheral surface of the bearing protrusion 182. Accordingly, the lower end of the bearing protrusion 182 may be coupled by penetrating the bearing mounting hole 113a of the base 113, and then the fixing protrusion 181 of the lower bearing 180 may be placed on the upper surface of the base 113 and fastened. there is. In this case, since the fixing protrusion 181 of the lower bearing 180 is supported in the axial direction by the base 113, the lower bearing 180 can be supported more stably.

Referring to Figures 5 and 6, an axial bearing member 185 supporting the lower end of the rotating shaft 125 in the axial direction is inserted and fixed to the inner peripheral surface of the bearing protrusion 182 according to this embodiment. For example, a bearing support surface 1821 on which the annular axial bearing member 185 is supported in a direction toward the rotation axis 125 is formed to be stepped on the lower half of the inner peripheral surface of the bearing protrusion 182. Accordingly, the inner circumferential surface of the bearing protrusion 182 is formed so that the inner diameter of the drive motor 120, which forms the radial bearing surface 182a, is smaller than the inner diameter of the lower cap 114, which forms the bearing mounting surface 182b. Through this, when inserting the axial bearing member 185, the insertion position of the axial bearing member 185 is limited, so that the axial bearing member 185 can be easily and accurately mounted.

In addition, a guide groove 1822 is formed on the inner peripheral surface of the bearing protrusion 182, that is, the inner peripheral surface of the bearing mounting surface 182b, into which the guide protrusion 1851 provided on the outer peripheral surface of the axial bearing member 185 is inserted. For example, the guide protrusion 1851 extends radially from the outer peripheral surface of the axial bearing member 185, and the guide groove 1822 extends along the axial direction from the inner peripheral surface of the bearing mounting surface 182b. Accordingly, the guide protrusion 1851 is inserted into the guide groove 1822 and is slidably coupled along the axial direction.

A plurality of guide protrusions 1851 (two in the drawing) are formed at preset intervals along the circumferential direction of the axial bearing member 185, and the guide groove 1822 is formed in the bearing to correspond to the guide protrusion 1851. On the inner peripheral surface of the mounting surface 182b, a plurality of pieces (two in the drawing) are formed at predetermined intervals along the circumferential direction. Accordingly, when the axial bearing member 185 is inserted, the guide protrusion 1851 is guided in the axial direction along the guide groove 1822, thereby suppressing distortion of the axial bearing member 185 and lowering the lower end of the rotation shaft 125. It can be supported stably.

In addition, a bearing support member 186 for supporting the axial bearing member 185 is inserted on the lower side of the bearing support surface 1821 among the inner peripheral surface of the bearing protrusion 182, that is, the inner peripheral surface of the bearing mounting surface 182b. A groove 1823 is formed. For example, the bearing support member may be formed as a C-ring, and the bearing support groove 1823 may be formed as an annular shape. Accordingly, after inserting the axial bearing member 185 into the bearing mounting surface 812b of the bearing protrusion 182, the axial bearing member 185 can be stably supported using the bearing support member 186.

Although not shown in the drawing, the axial bearing member 185 may be inserted into the radial bearing surface 182a. In other words, the inner diameter of the radial bearing surface 182a forming the upper half of the bearing protrusion 182 may be formed to be larger than the inner diameter of the bearing mounting surface 182b forming the lower half of the bearing protrusion 182. Accordingly, the bearing support surface 1821 supporting the axial bearing member 185 in the axial direction may be formed to be stepped from the inner peripheral surface of the radial bearing surface 182a toward the center. In this case, there is no need to separately provide a bearing support member (not shown) to support the axial bearing member 185, thereby lowering the manufacturing cost.

Referring again to FIGS. 3 and 4, the lower cap 114 according to this embodiment has a bearing receiving portion 114a that accommodates the lower bearing 180 and is coupled to the outer surface, that is, the lower surface, of the base 113. do. For example, the lower cap 114 may be formed in a “cup” cross-sectional shape or an “inverted cap” cross-sectional shape. This embodiment shows an example in which the lower cap 114 is formed in an “inverted cap” cross-sectional shape.

Specifically, the lower cap 114 is formed in the center so that the previously described bearing receiving portion 114a is recessed to a depth that can accommodate the lower bearing 180 extending to the lower side of the base 113, and the bearing receiving portion ( The upper end of 114a) is open toward the lower surface of the base 113. The inner diameter D1 of the lower cap 114 is larger than the inner diameter D2 of the bearing mounting hole 113a. Accordingly, the bearing mounting hole 113a of the base 113 is covered by the lower cap 114, and the internal space of the casing 110 is sealed.

Referring to FIGS. 7 and 8, the inner diameter D1 of the lower cap 114 may be formed larger than the inner diameter D2 of the bearing mounting hole 113a, as described above. In other words, the inner diameter (D1) of the lower cap (114) will be larger than the diameter (D4) of the virtual circle (C1) connecting the center of the first fastening hole (113d) provided around the bearing mounting hole (113a). You can. Accordingly, among the first fastening holes 113d, the first fastening hole 113d exposed outside the fixing protrusion 181 of the lower bearing 180 will overlap the bearing receiving portion 114a of the lower cap 114 in the axial direction. You can. Through this, the bearing receiving portion 114a forms part of the oil storage space 110c.

Additionally, the inner diameter D1 of the lower cap 114 may be formed to be smaller than or equal to the outer diameter (and/or inner diameter) D3 of the base insertion protrusion 113c. In other words, the lower cap 114 may be formed to be located inside the base insertion protrusion 113c of the base 113. Accordingly, an increase in manufacturing cost can be suppressed by optimizing the size of the lower cap 114.

In the scroll compressor according to the present embodiment as described above, a bearing mounting hole (113a) is formed through the base (113), and the bearing mounting hole (113a) is covered with a separate lower cap (114) for post-assembly to remove oil. It is possible to prevent foreign substances from remaining in the storage space 110c.

As described above, after the bearing protrusion 182 is assembled to the base 113, post-processing is performed on its inner peripheral surface, that is, inner peripheral processing to form the radial bearing surface 182a. For example, after fixing the base insertion protrusion 113c of the base 113 by press-fitting it into the cylindrical shell 111, the lower bearing 180 is fastened to the base 113, and the inner peripheral surface of the bearing protrusion 182 is post-processed. A radial bearing surface 182a is formed on the inner peripheral surface of the bearing protrusion 182 to support the lower end of the rotating shaft 125 in the radial direction. In this case, the inner peripheral surface of the bearing protrusion 182 forming the radial bearing surface 182a is formed on the same axis as the inner peripheral surface of the cylindrical shell 111, that is, the outer peripheral surface of the base insertion protrusion 113c.

At this time, during the process of machining the inner peripheral surface of the bearing protrusion 182, foreign substances such as metal residue are generated, and if these foreign substances are mixed with oil and flow into the bearing surface, the bearing surface may be worn and compressor performance may be reduced.

However, in this embodiment, not only is the lower end of the bearing protrusion 182 open, but the lower end of the bearing protrusion 182 penetrates the base 113 and is located outside the base 113. Thereafter, the lower cap 114 accommodating the lower bearing 180 is subjected to coaxial processing (or inner peripheral processing) on the inner peripheral surface of the bearing protrusion 182, and then the bearing mounting hole 113a of the base 113 is covered. It is welded to the lower surface of the base 113. Accordingly, foreign substances such as metal debris generated during processing of the bearing protrusion 182 can be discharged to the outside of the casing 110 before the lower end of the casing 110 is sealed. Through this, it is possible to prevent foreign substances from remaining in the internal space of the casing 110, that is, the oil storage space 110c, and mixing with the oil.

Meanwhile, other examples of the lower cap are as follows.

That is, in the above-described embodiment, the inner diameter of the lower cap is formed to be smaller than or equal to the inner diameter of the base insertion protrusion, but in some cases, the inner diameter of the lower cap may be formed to be larger than or equal to the inner diameter of the base insertion protrusion.

Figure 9 is a broken perspective view of another embodiment of the lower cap in Figure 1, and Figure 10 is a cross-sectional view showing the assembly position of the lower cap in Figure 9.

Referring to FIGS. 9 and 10, the basic structure of the scroll compressor including the base 113, lower bearing 180, and lower cap 114 according to this embodiment is similar to those of the above-described embodiment, so detailed details thereof are provided. The description is replaced with a description of the above-described embodiment.

However, in this embodiment, the inner diameter of the lower cap 114 that is welded to the outer surface, that is, the lower surface, of the base 113 and covers the bearing mounting hole 113a of the base 113 may be formed larger than that of the above-described embodiment. there is. Accordingly, the volume of the bearing receiving portion 114a can be expanded to form the oil storage space 110c as large as possible.

For example, the lower cap 114 is recessed so that the side facing the base 113 is open to form a bearing receiving portion 114a in the center, and the inner diameter D1 of the lower cap (or bearing receiving portion) 114 is may be formed to be larger than or equal to the outer diameter (and/or inner diameter) D3 of the base insertion protrusion 113c that protrudes annularly toward the cylindrical shell 111. This embodiment shows an example in which the inner diameter D1 of the lower cap (or bearing receiving portion) 114 is formed larger than the outer diameter (and/or inner diameter) D3 of the base insertion protrusion 113c.

In this case as well, the depth of the bearing receiving portion 114a may be the same as the depth of the bearing receiving portion 114a in the above-described embodiment, for example, a depth capable of accommodating the lower bearing 180.

As described above, the inner diameter D1 of the lower cap (or bearing receiving portion) 114 is formed to be larger than or equal to the outer diameter (and/or inner diameter) D3 of the base insertion protrusion 113c, and thus the base receiving portion 114a ) increases, and as a result, the volume of the oil storage space 110c is expanded, so that the oil storage capacity can be increased even if the inner diameter and length of the casing 110 are the same. Through this, oil shortage in the refrigeration cycle device including the compressor can be prevented in advance, thereby improving the efficiency of the compressor and/or the efficiency of the refrigeration cycle device.

Meanwhile, in the above-described embodiments, the structure in which the back pressure chamber assembly 160 consisting of the back pressure plate 161 and the floating plate 165 is provided on the rear of the non-orbiting scroll has been described. However, in some cases, the back pressure chamber assembly 160 is provided on the back of the non-orbiting scroll. The same can be applied to a scroll compressor in which (160) is excluded and the non-orbiting scroll (150) is fastened to and fixed to the casing (110) and/or the main frame (130). In this embodiment as well, the basic configuration of the base 113, the lower bearing 180, and the lower cap 114 and the resulting effects may be almost the same as those of the above-described embodiments.

110: Casing 110a: Low pressure part (suction space)
110b: High pressure part (discharge space) 110c: Oil storage space
111: cylindrical shell 112: upper cap
113: Base 113a: Bearing mounting hole
113b: Bearing support protrusion 113c: Base insertion protrusion
113d: first fastening hole 114: lower cap
114a: Bearing receiving portion 115: High and low pressure separator plate
116: Refrigerant suction pipe 117: Refrigerant discharge pipe
120: Drive motor 121: Stator
1211: stator core 1212: stator coil
122: rotor 1221: rotor core
1222: Permanent magnet 125: Rotating axis
1251: Eccentric part 1252: Oil passage
1253: Oil oil path 130: Main frame
131: main flange part 132: main bearing part
132a: Axial hole 133: Swivel space part
134: scroll support 135: Oldham ring support
136: frame fixing part 140: orbiting scroll
141: Swivel hard plate 142: Swivel wrap
143: Rotating shaft coupling part 150: Non-orbiting scroll
151: Non-swivel plate portion 1511: Discharge port
1512: Bypass hole 1513: First back pressure hole
152: Non-swivel lap 153: Non-swivel side wall portion
1531: Inlet 154: Guide protrusion
145: Discharge valve 160: Back pressure chamber assembly
160a: Back pressure chamber 161: Back pressure plate
1611: fixing plate part 1611a: second pressure hole
1612: First annular wall portion 1612a: Middle discharge port
1612b: Valve guide groove 1612c: Backflow prevention hole
1613: Second annular wall 165: Floating plate
170: Oldham ring 180: Lower bearing
181: fixing protrusion 1811: extension part
1811a: second fastening hole 182: bearing protrusion
182a: Radial bearing surface 182b: Bearing mounting surface
1821: Bearing support surface 1822: Guide groove
1823: Bearing support groove 184: Fastening member
185: Axial bearing member 1851: Guide protrusion
186: Bearing support member C1: Virtual circle
D1: Inner diameter of lower cap D2: Inner diameter of bearing mounting hole
D3: Outer diameter of base insertion protrusion D4: Diameter of virtual circle
O: Center of rotation axis V, V1, V2: Compression chamber

Claims (14)

drive motor;
A rotation shaft that transmits the rotational force of the drive motor;
A turning scroll coupled to the rotating shaft and performing a turning movement;
A non-orbiting scroll engaging the orbiting scroll to form a compression chamber;
a cylindrical shell into which the drive motor is inserted and fixed, and which is open at both ends;
A base provided with a base insertion protrusion to be inserted into the lower end of the cylindrical shell to cover the lower end of the cylindrical shell, and through which a bearing mounting hole passes in the axial direction;
a lower bearing that penetrates the bearing mounting hole of the base and supports the rotating shaft; and
A scroll compressor including a lower cap coupled to the base and having a bearing receiving portion to accommodate the lower bearing. According to paragraph 1,
The bearing mounting hole is,
A scroll compressor formed on the same axis as the base insertion protrusion. According to paragraph 2,
A bearing support protrusion is formed around the bearing mounting hole to support the lower bearing in the radial direction,
A scroll compressor wherein the bearing support protrusion is formed in an annular shape. According to paragraph 1,
The lower bearing is,
A fixing protrusion fixed to the base; and
A scroll compressor comprising a bearing protrusion extending axially from the fixing protrusion so as to penetrate the bearing mounting hole, and the rotation shaft being rotatably inserted and supported in the radial direction. According to paragraph 4,
The fixed protrusion,
A scroll compressor extending radially from one end of the bearing protrusion and being fixed to the outer surface of the base from the outside of the cylindrical shell. According to clause 5,
A plurality of first fastening holes are formed between the bearing mounting hole and the base insertion protrusion at predetermined intervals along the circumferential direction, and a second fastening hole is provided on the fixing protrusion to correspond in the axial direction to a portion of the first fastening hole. A fastening hole is formed,
Other portions of the plurality of first fastening holes are,
A scroll compressor communicating with the bearing receiving part of the lower cap outside the fixing protrusion. According to clause 6,
The fixed protrusion,
A scroll compressor in which a plurality of extension parts extend in the radial direction and have an angular cross-sectional shape when projected in the axial direction, and the second fastening holes are formed in each of the extension parts. According to paragraph 4,
A scroll compressor in which an axial bearing member is provided on the inner peripheral surface of the bearing protrusion to support the rotating shaft in the axial direction. According to clause 8,
A scroll compressor in which the inner peripheral surface of the bearing protrusion is provided in an annular shape and the bearing support surface on which the axial bearing member is supported in the axial direction toward the rotation axis is formed to be stepped. According to clause 9,
The bearing support surface has an inner diameter on a side facing the drive motor that is smaller than an inner diameter on a side facing the lower cap,
A scroll compressor in which a bearing support member is provided on one axial side of the bearing support surface to support the axial bearing member in a direction opposite to the rotation axis. According to clause 9,
The axial bearing member has a bearing body formed in an annular shape, and a guide protrusion extending radially from the outer peripheral surface of the bearing body is formed,
A scroll compressor in which a guide groove is formed on the inner peripheral surface of the bearing protrusion into which the guide protrusion is slidably inserted in the axial direction. According to any one of claims 1 to 11,
The lower cap is,
A scroll compressor in which the inner diameter of the bearing receiving portion is formed to be larger than or equal to the outer diameter of the lower bearing and the lower bearing is fixed to the outer surface of the base. According to clause 12,
A scroll compressor in which the inner diameter of the bearing receiving portion is formed to be smaller than or equal to the outer diameter of the base insertion protrusion. According to clause 12,
A scroll compressor in which the inner diameter of the bearing receiving portion is formed to be larger than or equal to the outer diameter of the base insertion protrusion.

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